Gear train assemblies

Gear train assemblies

DESCRIPTION
August 20, 1968 GE MOORE ASSEMBLIES gear train 5 sheets sheets 1 Filed April 28, 1967 Figure A.
August 20, 1968 G. E. MOORE GEAR TRAIN ASSEMBLY 5 Leaves -2 Sheet Filed April 28, 1967 20 , 1968 s . E. MOORE 3397589
Gearing ASSEMBLIES Filed April 28, 1967 5 Leaves leaves 5 ​​g I- 20 , GE MOORE 1968 3397589
Gearing ASSEMBLIES Filed April 28, 1967 5 Leaves leaves April 20, 1958 GE MOORE 3397589
Gearing ASSEMBLIES Filed April 28, 1967 5 Leaves leaves 5 ​​Inn { N726 fleas HM zit / c jfaa / e United States patent abstract description of a set of driving gears , driven gears and pulley, idler gear may move radially of the other gears , and the gears are cylindrical spacers to locate in mesh relatively accurate and is arranged so that during driving of the gears. a resultant driving force acting on the idler gear in a direction between the other gears to encourage and maintain the correct idle gear meshed with the other arts.
BACKGROUND OF THE INVENTION
(1) Field of the Invention This invention relates to gear train sets . I ( 2) Description of the Prior Art In some sets of known gear train which requires a gear wheel drive and a gear wheel driven to rotate in the same direction , a gear wheel is used to transmit intermediate driving unit to the driven sprocket. In such assemblies when driving and driven gear ratios are modified by replacement of one of the gear wheels with one of a pitch circle diameter different idler wheel then requires careful and accurate repositioning to properly position mesh with the driving and driven sprockets. As is known, the idler wheel is correctly engaged with each of the other wheels when your contacts gear pitch circle of the gear pitch circle each other in a point commontangential . It is found to be very difficult in practice to place the idler wheel in mesh with the driving and driven gear wheels and if the gears are located in positions that are incorrectly mesh , this situation can lead to more gear tooth wear faster and also the additional loading and increased gear bearings .

To avoid the above disadvantages , a set of gear train may be replaced by a sprocket assembly and which comprises a chain driven sprocket wheel and the driving sprocket that are rotated in the same direction by an endless chain located in driving engagement with the teeth of both gears , the chain is tensioned by a tensioning device in the chain. A set of gears and the chain is , however , more cumbersome than a set of gear train. A further disadvantage encountered when required to replace one of the sprockets is untension chain is necessary and then removed before the gear wheel is removable and after the replacement gear has been fitted , it is necessary to replace the chain and then re-tension .
SUMMARY OF THE INVENTION 

According to the present invention, a set of gear train comprises a driving and driven gear units , and a gear unit idler wheel operable to connect driving and driven units , the unit forwarding being movable radially with respect to at least one of the other units, and each unit comprises a sprocket and at least one coaxial cylindrical separator , the separator or each idler unit located in engagement with the spacers of the other units where the gear teeth of the forwarding unit are correct 3397589 patented August 20, 1968 " ice mesh with those of the other units, and the teeth properly mesh units , the provision units is such that when the drive unit is rotated in a direction to drive the driven unit , a resultant force of the driving forces applied to the teeth of the forwarding unit acts along a path between the centers of rotation of the other units so as to keep the teeth of the forwarding unit constantly correct mesh with the teeth of the other units .
It is clear to the applicants that the relative arrangement of the units is an important consideration in the invention. In practice, it is found that if all units have external gear teeth then the units must be relatively arranged so that when the teeth are in the correct mesh forwarding unit with the teeth of the other units, the angle produced between a line connecting the rotational centers forwarding unit and the drive unit and another line connecting the centers of rotation of the forwarding unit and driven unit is at least twice the pressure angle of the set. Furthermore, one of the driving and driven units can be an annular unit with internal gear teeth . In this case, the angle produced between a line joining the centers of rotation of the forwarding unit and driving do not cancel or driven unit and an extension of another line connecting the centers of rotation of the unit and the unit forwarding cancel is at least twice the pressure angle . Pressure angle term is used in its normal sense in the art accepted gear manufacturing .
Furthermore, the term correct mesh as mentioned above and throughout the specification indicates normal engagement of the teeth of the forwarding unit with each of the other units where the pitch circles of contact units in a single common tangent point .
According to another aspect of the invention, a gear assembly comprises a driving gear and driven gear units , the distance between the centers of rotation of the driving and driven units being variable , and a drive idler wheel operable to connect driving and driven units , the forwarding unit being movable radially with respect to at least one of the other units, and each unit comprises a sprocket and at least one coaxial cylindrical spacer , the or each separator unit forwarding ' lying in engagement with the spacers of the other units when the gear teeth of the forwarding unit are in correct mesh with those of the other units, and the teeth properly mesh units , the relative disposition of the units is such that when the drive unit is rotated in a direction to drive the driven unit , a resultant force of the driving forces applied to the teeth of the forwarding unit acts along a path between the centers of rotation of the other units so as to hold the teeth of the forwarding unit constantly in mesh with the correct teeth of the other units .
According to yet a further aspect of the invention, a gear train assembly comprising units of driving driven sprocket and idler wheels and first and second gears arranged either side of a line connecting the centers of rotation driving and driven units , each relay unit being movable radially with respect to at least one of the driving and driven units , each unit comprising a sprocket element and at least one coaxial cylindrical spacer the or each spacer of each idler UNI -T lying in engagement with the spacersof driving and driven units when the gear teeth of the forwarding unit are in proper mesh with the driving and driven units , and the teeth of the first mesh unit or secondidler correct teeth driving and driven units , the relative arrangement of the units is such that when the drive unit is rotated , respectively , in one direction or in the opposite direction driving the driven unit , a resultant force of the drive forces applied to the gear teeth of the first or second forwarding unit , as the case may be, acts along a path between the centers of the'rotational driven and 3. driving units in order to keep the teeth of the forwarding unit constantly correct mesh with the teeth of the other units, means being provided to prevent or restrict the movement of the teeth of each unit mesh forwarding correct the drive unit when the resultant force is not applied along said path .
In an assembly according to the invention, at least one unit may comprise two spacerslocated one on each side of the gear wheel elements , Alternatively or in addition , at least one unit, the gear wheel element can comprise two coaxially separate gear which is disposed between at least one spacer .
It is preferable that in each unit, the or each spacer has a diameter substantially equal to the pitch circle diameter of the unit.
DMWINGS brief description of embodiments of the invention will now ' be described by way of example with reference to the accompanying drawings in which:
Figure 1 is a front elevational view of a drive arrangement for a rolling mill , the drive arrangement which includes two sets of gear train according to the invention;
Figure 1A is a cross sectional view along line IA -IA in Figure 1 which shows schematically the gear train assemblies ;
FIGURE 2 is on a larger scale than Figure 1 and is a cross sectional view along the line IIII in Figure 1 , one of the assemblies illustrated schematically ;
Figure 3 is a view similar to Figure 2 of the gear train assembly which indicates the manner in which the assembly operates in practice;
Figure 4 is a cross sectional view of the line IVIV of the gear assembly of Figure 3 ;
FIGURES S , 6 and 7 are views similar to Figure 2 of the modification of the first embodiment;
Figures 8 and 9 are views similar to Figure 2 of a second embodiment showing different relative positions of drives from a reversible gear train ;
Figure 10 is a view similar to Figure 2 of a third embodiment showing different relative positions of units of a gear train assembly reversible ;
Figure 11 is an axial end view schematic of a set of gear train forming a fourth embodiment ;
Figure 12 is a view similar to Figure 11 of a fifth embodiment ;
Figures 13 and 14 are cross sectional views respectively along lines XIVXIV XIIIXIII and in Figure 12 ;
Figure 15 is an axial end view schematic of a set of gear train composed of a sixth embodiment ;
Figure 16 is a cross sectional view along the line XVIXVI in Figure 14 .
Description of the Preferred Embodiments In the following embodiments and modifications thereof , mutually identical parts bear like reference numerals .
\ In a first embodiment, shown in Figures 1 to 4 in a rolling mill comprising two drive shafts the rollers 1 operable connected to two rolling rolls (not shown) of conventional design to provide a nip to reduce the thickness of the metal strip fed therethrough . Is desirable to be able to automatically adjust the positions of the centers of the work rolls during operation of the mill to keep the rolled strip thickness between specific limits . To enable this setting a drive arrangement 2 is used as will now be described .
The " layout unit 2 comprises two sets of gear train 3 according to the invention. Each set 3 as shown in Figures 2 , 3 and 4 comprises a drive gear wheel drive and four wheel drive driven gear 5 . Unit 4 fixed gear coaxially fixed a drive shaft 6 extending from a main drive box 7, the main unit box to ensure that the two axes are driven in opposite directions with speeds equal angular . unit 5 of each set is coaxially fixed to a drive shaft 1. As shown particularly in Figure 4 , the driving unit 4 comprises a gear wheel which is a single gear wheel 8 formed integrally 9 with coaxial cylindrical spacers located on either side of the sprocket. driven unit 5 is similarly formed with a gear wheel 10 having integral spacers 11 (Figs. 1 and 2). a tensioning unit 12 comprises a wheel 13 with integral gear 14 coaxial spacers located on either side.
Spacers each having a diameter equal to the pitch circle diameter of the respective gear wheel and the teeth of the gear wheel 13 are in proper engagement with the teeth of the sprockets 8 - and 10 when the peripheral surfaces of spacers 14 lie in engagement with the peripheralsurfaces separators 9 and 11.
Three units of each set are arranged relatively so that when the gears are in proper mesh two lines extending one between the centers of rotation of the units 4 and 12 and one between the centers of rotation of units 5 and 12 produce between them an angle which is at least twice the pressure angle of the gear wheels . Preventing or restricting movement means , ie elastic means in the form of two tension springs 15 are used one on each side of each unit to maintain forwarding idler wheel correct continuous meshing engagement with the other gear wheels . Every spring extends from a'sleeve 16 can swivel unit short forwarding to a fixed support 17. For reasons to be explained , however , the spring is unnecessary to retain the idler wheel in this position during rotation of the gear wheel , while the forwarding unit is mounted on a shaft fixed relative to the other units and movable radially of the other gears .
In use of the mill , the drive shafts 6 are driven by the box unit 7 for rotating the driving units 4 . 3 in each set , the forwarding unit is operated to drive the driven unit under meshing engagement of the gears 8 and 13 and the gear wheels 13 and 10 . Each unit 4 is rotated in one direction , so that each portion of the unit moves into the space between the units 4 and 5 , as it moves away from the forwarding unit . For the upper assembly 3 the rotational arrows in Figures 2 and 3 indicate the directional movement of the units. During the rotation of each unit 4 in this direction, a force in the direction of arrow A ( Figure 3) is applied to the teeth of the sprocket teeth 13 of the gear wheel 8 . Also, as the gear wheel 13 drives the gear wheel 10, a force is applied to the teeth of the sprocket 13 by the gear wheel 10 in the direction of arrow B. Due to the relative arrangement of the units mentioned above, the resultant force C of these two forces acting on the idler unit 12 along a path between the centers of rotation of the units 4 and 5, as shown in figure 3, in order to maintain forwarding unit with spacers 14 in continuous engagement with the spacers 9 and 11 through which the teeth of gear wheel 13 are held in constant mesh with the teeth and correct the other wheels gear during rotation of the units in the directions indicated .
With this mounting arrangement , provided that the relative arrangement of the units, ie its angular relationship with respect to the pressure angle is maintained above a explained, each of the units " 5 can move into and out of its drive gear during four wheel rotation as this movement only results in a consequent and corresponding forwarding unit , while their teeth are maintained in proper mesh with the other units . Itwill be appreciated that this space movement units 5 permits the roll nip is adjusted while working metal strip is reduced in thickness to maintain the reduced thickness between the limits specified if required in each set to replace one of the units 4, 5 and unit 12 with a different pitch circle diameter of gear wheel to alter the speeds driven work rolls is a simple matter to remove the forwarding unit 12 to allow this replacement. Moreover, when a unit is added replacement , no need for manual adjustment in the position of forward drive to ensure that the gear wheel 13 meshes properly with the other gear wheels , gear wheel that correct meshing is always guaranteed , then no rotation the drive unit in the direction indicated by the virtue of the resultant force acting on C idler unit .
A further advantage obtained with each gear train assemblydescribed above is that idler wheel is always in mesh tothe correct gear wheels other despite shaft deflections or wear on the shaft bearings because any radial movement of the rotational axes of the other units in use is accommodated by corresponding movement of the automatic forwarding unit . Furthermore, as correct gear meshing always warranted , then no gear wear may occur due to incorrect meshing . Moreover, do not use a fixed mounting shaft and bearing for idler unit .
In the embodiment described above , with the use of springs 15, each gear train assembly can be used successfully in any position of the gear wheel drives with horizontal rotational axes . For example, if the units 4 and 5 are spaced horizontally positioned , instead of vertically spaced , with the unit 12 beneath the units 4 and 5, then the unit 12 is held in place by the springs when the assembly not in use .
However, in a modification of the above embodiment in which each gear train assembly of the units 4 and 5 are horizontally separated , the gear 13 is in mesh with the other gear wheels to the unit 12 located at above the other units. In this case, the springs 15 and dispenses the unit 12 is carried out automatically with the wheel 13 in mesh with the other gear wheels when the assembly is not in use , under the weight of the unit 12.
In a modification of the first embodiment as shown in figure 5, the forwarding unit , the springs 15 and the support 17 are replaced by an annular forwarding unit 18 and a movement restriction means in the form of an element cap or plug 19. Unit 18 is provided with a gear wheel 20 and spacer 21 similar to the unit 12 of the first embodiment. The stop pin is fixed at one end to a box housing the main unit 7 and extends radially and axially into the ring as shown in Figure 5.
When the gear wheel 20 is in correct engagement with the gear wheels 8 and 10, the pin is slightly separated from the inner surface 18a of the unit 18. However, when the resultant force F is not applied to the unit 18 such as occurs when the gears are not being driven or when braking gear when a resultant force in the reverse direction can be imposed on the unit 18 any movement of the grid unit 18 with the other units right is limited by engagement of the pin on the inner surface of the unit. PEG is positioned so as to stop the movement of the mesh unit 18 right before the teeth of the gear wheel 20 are completely decoupled from the gear wheel 8 . Therefore, when the resultant force is applied again to the unit 18 during the next application of the driving car operated units , this force urges the unit 18 in its correct position of the teeth mesh with the other units .
In another modification of the first embodiment shown in Figure 6 , the springs 15 and the support 17 are replaced by a restricting means in the form of a stop element . This stop element is a shoe 22 is held in fixed position in the box casing the'main unit 7 and is slightly separated from the forwarding unit 24 when the drive teeth are engaged properly with the other unit. Difiers unit 24 of the unit 12 in which no short shaft with a sleeve 16 mounted thereon . An area of ​​23 0f opposes shoe unit 24 is concave to fit the unit should leave this engages correctly with the other units in the circumstances described in the last shoe previous paragraph'The insuflicient prevents movement of the unit 24 to allow for complete withdrawal of the gear teeth of the gear wheel 8 so that the unit 24 is returned to the right of teeth mesh when the resultant force C is applied next .
In yet another modification of the first embodiment shown in Figure 7, each gear train assembly , a drive unit 25 is operable connected to a guide unit 26 by the forwarding unit 24. Units 25 and 26 are cylindrical spacers 27 and 28 to engage the standoffs 14 of the unit 24 when the gear wheels of the units are in proper mesh .
In this construct, a movement of the tightening unit preventing or restricting means comprises an endless member in the shape of a tape 29 which extends into frictional contact around an engagement surface of each drive belt 25 and 26, this surface is the peripheral surface of a cylindrical coaxial extension member 30 and 31 respectively of the units 25 and 26.
When no force is applied resulting C , frictional engagement with the belt surfaces of the extensions 30 and 31 prevents slipping rotation of the units 25 and 26 relative to each other. Accordingly, the forwarding unit is performed with proper meshing teeth with the other units by virtue of the fact that the teeth of the gear wheels 32 and 33 of the units 25 and 26 lock wheel gear 13 in position and prevent disengagement of the teeth.
In the following embodiments four fifty-eight included , it is understood that the driving , driven and tensioning units are relatively disposed in the manner specified in the first embodiment .
In a second embodiment, a rolling mill is constructed in the manner described in the first embodiment with a drive arrangement to allow automatic adjustment of the roll gap between work centers. In this embodiment , however , requires that the work rolls are reversible in their direction of rotation to allow the metal strip after being reduced in thickness in a first pass through the mill to be further reduced in the thickness in a second pass in the reverse direction . To enable this, each gear train assembly 34 ( one of which is shown in Figures 8 and 9) is different from the construction of the joint 3 of the first embodiment.
Each gear train assembly 34 comprises , as in the first embodiment, a drive unit 4 and the driven unit 5, each with their respective gear wheels 8 and 10 and spacers 9 and 11 as described in the first embodiment. However, each assembly 34 also comprises two tensioning units 12 arranged one on each side of a line connecting the centers of rotation of the driving and driven units .
Means are provided in each assembly to prevent or restrict the movement of each unit forward to move teeth properly mesh with the drive unit . These means comprise a toggle lever 35 which is pivotally mounted at the junction of its arms 36 and 37 about the axis 6. The lever is connected to the friction drive unit for sufficient frictional engagement with the lever shaft to tend to urge the lever in the same direction of shaft rotation. The relative positions of the tensioning units 12 is such that when one unit is in correct mesh with both the driving and driven units , the other forwarding unit is completely out of engagement with the driven unit (see Figures 8 and 9). This prevents tooth wear between the guide unit and idler unit not put in a proper position of the mesh at any time.
In use of the mill , when the guide unit 4 is driven in the direction of clockwise rotation as shown in Figure 8 , the forwarding unit mounted on the arm 37 is in the correct gear teeth with driving and driven units to transfer the unit to the driven unit. When the drive unit is driven in the clockwise direction (Figure 9) to reverse the direction of rotation of the rolling rolls , the resultant force C in the teeth of the forwarding unit 37 on the arm is reversed thereby pushing this mesh forwarding unit to the driven unit of the toggle rotation around axis 6. Furthermovement the bell crank lever in the same direction takes place due to their frictional engagement with the shaft to move the tensioner arm unit 36 in correct mesh with the driving and driven units . The forwarding unit is then held in this position for continued actuation in the same direction by the resultant force F along the path shown in Figure 9 .
The gear train assembly of the second embodiment has the advantages detailed above for the structure described in the first embodiment , but in addition , it also allows the reversal of the driving car operated units . In a third embodiment, a set of gear train 38 (Figure 10) incorporates a simple roller unit 12 while allowing the gap between the driving and driven units 4 to be varied and also while allowing reversal drive unit 4 reverse the direction of rotation of the unit 5 .
In this embodiment , the means for preventing or restricting the movement of the forwarding unit to move their teeth properly mesh with the drive unit comprises an arm 39 which is pivotally mounted about an axis which coincides with the center rotation of the drive unit on the drive shaft 6 . The arm is connected by friction to the drive unit by its frictional engagement with the shaft 6 so that the arm is urged to move pivotally in the same direction as the direction of shaft rotation. In use, while the driving unit 4 is rotated in the clockwise direction shown by the arrow indicated in Figure 10 complete, the forwarding unit is in correct mesh ( full outline position shown) the units 4 and 5. If the drive unit is then driven in the reverse direction , ie in the direction of the dashed arrow in Figure 10 , the arm 39 , by virtue of their frictional contact with the shaft 6, is pivotally moved around the drive unit in the counterclockwise direction to move the forwarding unit outside its correct position shown in full mesh side of the driving and driven units to a correct position mesh with these two units in the other side of the units, as shown by the dotted line . If the drive unit is activated and then again in the direction of clockwise , the arm 39 is moved by the friction also in the direction of clockwise to return the unit to its proper position forwarding mesh shown in full outline .
In a fourth embodiment shown in Figure 11 , a set of drive gear train 40 to drive a reversible mechanism comprises a drive unit 41 fixed to a drive shaft 42 and being similar in construction to the unit 4 first embodiment in that comprises a gear wheel 43 flanked on both sides by means of spacers 44 integral coaxial . A driven unit 45 secured to a driven shaft 46 and has a gear wheel 47 coaxial with integral spacers 48 is operable connected to the unit 41 by tensioning units 49 and 50 disposed one on each side of a line passing through the axes of rotation of the units 41 and 45 . Units 49 and 50 are gear wheels 51 of equal pitch circle diameter , each sprocket is flanked on both sides by means of spacers 52 integral coaxial . In each gear wheel drives in the set, the diameter of each spacer is equal to the pitch circle diameter of the sprocket. The two units 49 and 50 are urged toward each other by tension springs 53 on each side locatedone units and fixed at its ends to pins 54 coaxial units . The springs are elastic means forming unit movement preventing or restricting tensioning means . Units 49 and 50 are otherwise freely movable in a radial direction with respect to the units 41 and 45 .
In the use of the set, when the drive unit 41 is rotated in a direction clockwise to drive the driven unit 45 , the unit is provided to the unit 45 unit 49 which is supported with gear teeth . Correct meshing engagement with the gear wheels 43 and 47 by a resultant force , as described in the first embodiment. Driving forces acting on the unit 50 have a resultant force urging the distance unit 50 and to move teeth meshing with the sprockets '43 and 47 . However, the unit 50 is held with its gear teeth in mesh with the sprockets 43 and 47 by springs 53 .
When driving unit 41 in the counterclockwise direction to drive unit 45 in the same direction , the forwarding unit imparts the drive unit 45 and is held in the correct teeth meshing engagement with the sprockets 43 and 47 by a resultant force urging unit 50 to the units 41 and 45 . In this instance, the left -turn unit 41 , the unit 49 is pushed away from the units 41 and 45 but is held in position by the springs 53 .
Be appreciated that, in use, the gear train assembly of the fourth embodiment has all . the advantages to those described in the second embodiment except that the distances between the centers of driving and driven units can not be varied while the engine is carried out as opposed to idle gears mesh lock positional relationship of the centers of the driving and driven v units .
In a fifth embodiment in which the size of the gear wheels required to provide a desired gear ratio for driving a mechanism can not be accommodated in one plane due to the distance between driving and insufiicient shaft centers driven , the following construction is used as shown in figures 12, 13 and 14.
In the fifth embodiment, a set of gear train comprises a drive unit 55 comprises a gear wheel which consists of two gear wheels 56 ( Figures 13 and 14 ) which are coaxially fixed to a drive shaft 57 and are separated by a sleeve 58 . The sprockets are of equal diameter and each pitch circle wheel is provided with a spacer 59 which is formed coaxially with the wheel on its side remote from the other wheel , the diameter of the spacers , equal to the pitch circle diameter of the wheels toothed.
A guiding unit 60 , as shown particularly in Figure 14 , comprises a driven gear wheel 61 comprises a fixed to a driven shaft 62, the sprocket 61 is located in part between the sprockets 56 . The unit is provided with two spacers 63 that are secured coaxially to the shaft 62 and are separated from the gear wheel 61 by sleeves 64 so that each gear 56 and its spacer 59 is located between a spacer part 63 and the sprocket 61 . The spacers 63 have a diameter equal to the pitch circle diameter of the sprocket 61 .
A forwarding unit 65, which is freely movable radially of the other units has a gear 66 (see in particular Figure 13), which has an axial length sufiicient to close the gap between the mesh and with the sprockets 56 . The gear 66 also engages with the sprocket 61 . Unit 65 is also provided with two spacers 67 which are formed coaxially with the sprocket 66 and the flank of the gear wheel . These separators have a diameter equal to the pitch circle diameter of the sprocket 66 and are of sufficient axial length to engage the peripheral surfaces of the spacers 59 and 63 . Each of the units is symmetrical about a mid-circumferential plane of the unit so that there is no out of balance forces are imparted to the forwarding unit to vacate the unit out of its correct position during use.
In use of the gear train assembly during rotation of the driving and driven units in a direction clockwise in Figure 12 the forwarding unit is pushed toward the other units by a resultant force , as described in the first embodiment , so that spacers 67 are held in peripheral engagement with the spacers 59 and 63 so that the gear 66 is maintained in proper meshing engagement with the sprockets 56 and 61 .
In a modification of the fifth embodiment , the gear wheels 56 are provided with a single spacer (not shown ) instead of spacers 59 . This unique spacer lies between the gear wheels 56 to space apart and therefore replaces the sleeve 58 . The drive gear wheel 55 modified course requires modification corresponding to each of the other units 60 and 65 to ensure proper engagement of the gears and the participation of the spacers.
In a sixth embodiment , as shown in Figures 1H and 16, a gear train assembly 68 suited for a crane unit comprises a driven unit 69 in the form of an annulus with an element of a single sprocket wheel 70 having internal gear teeth . Integrally formed spacers 71 are provided on each side of the sprocket. A drive unit 72 is located axially radially'and ' ; - but eccentrically in the driven unit , and operable "connected" to the driven unit 73 an idler sprocket units 72 and 73 are respectively provided . wheels'74 gear and 75 and spacers 76 and 77 disposed on each side coaxiallyone gear wheels . In each unit the diameter of the spacers corresponds to the pitch diameter gear wheel Ofthe . The drive unit is drivable by a drive shaft 78 (FIGURE 16). The units are relatively arranged so that when the gears are in proper mesh produces an angle between a line connecting the centers of rotation of the forwarding unit and drive unit 72 and another extension line connecting the centers rotation of the forwarding unit and driven unit 69 is at least twice the pressure angle . me
In use of the assembly, the drive wheel is rotated in the direction clockwise as shown in Figure 15 to rotate counterclockwise driven unit . Due to the relative arrangement of the units, a resultant force F of the driving forces acting on the forwarding unit 73 in the direction indicated in Figure 15 has the forwarding unit in the correct mesh with the other units , while the unit is being imparted to the driven unit in the direction indicated .
The gear train assembly of the sixth embodiment which is not reversible in use, but otherwise has the advantages of the assemblies described in the above embodiments . In this embodiment , a particular advantage is that the drive unit is mounted eccentrically and can move radially with respect to the driven unit as long as the force F acts on the still forwarding unit to keep it in position. The need is , therefore , avoided by the precise location of the drive unit with respect to the particular engine unit , as required in conventional drive assemblies incorporating a gear concentric internally toothed ring gear .
In a modification of the sixth embodiment (not shown) is also used a second forwarding unit , the two tensioning units are mounted on the arms of a bell crank lever pivoted on the shaft 78 in a manner similar to the mounting axis 6 in the second embodiment. The assembly is then reversible operation.
In a further modification of the sixth embodiment (not shown) , the driven unit 69 is replaced by a unit which is an annular gear for driving the unit 72 which now becomes the driven gear . Diifers annular driving gear unit 72 only provided with external teeth , as well as internal teeth , the external teeth is operable connected to a worm wheel drive.
Gear train assemblies according to the invention and as described in the embodiments may be used in other mechanical devices or machines , while obtaining the advantages mentioned above. For example, the gear train sets in accordance with the invention can be used in machine tool lathe or gear or gear boxes which provide many gear ratios so that the drive shafts are particularly long , in which case the deviation of the axes is usually an important factor causing gear wear and noise due correct meshing gears . For the reasons explained in the first embodiment using the gear train assemblies according to the invention, gear wheel which meshes properly achieved regardless of shaft deflections and wear of bearings.
One important use of the gear train assemblies according to the invention is for driving the spindles of the drill heads or nut runners multiple machine , each spindle is driven by an adjacent mandrel by a set of train gear . Such a system allows changing the wheelbase of the mandrels and for changing gear ratios without the use of universal joint shafts . Additional sets of gear train may , for example, be used in positive units in small mechanisms in which it is particularly desirable that there is no need for a fixed shaft and bearing assembly for the idler gear due to space limitations . The gear wheel drives the mechanism of this type can be made, for example, rubber or plastic instead of metal.
Claim: v

'L- A gear train assembly comprising a gear wheel drive a driven sprocket and an idler wheel to drivablyconnecting driving and driven sprockets wherein the improvement comprises at least one coaxial cylindrical spacer each gear wheel , the idler gear wheel and spacer are movableradially associated with respect to at least one of the other gear wheels and their respective spacer, the spacer lying idle gear wheel in engagement with the spacers of the other gear wheels when the idler gear wheel is in proper engagement with the other gear wheels , gear wheels and being arranged relative to each other during driving of the gear wheels for applying a driving force resulting loca gear wheel along a path between the centers of rotation of the other gear wheels to maintain constant gear wheel nuts in proper mesh with the other gear wheels .
Two . An assembly according to claim 1 wherein the driving and driven gear'wheels are movable relative to each other to adjust the distances between their centers of rotation.
Three . An assembly according to claim 2 including means operatively connected to at least one gear wheel , to prevent or restrict the movement of the idler gear wheel properly mesh with the gear drive when it is applied saidresultant force .
April . An assembly according to claim 3 wherein the movement preventing or restricting means comprises a resilient means operatively connected to the idler wheel to hold it in a position where it is in continuous meshing engagement with wheel correct drive gear .
May . An assembly according to claim 3 wherein the idler gear wheel is a ring gear having teeth on an outer surface of the outer ring, and movement preventing or restricting means comprises a stop element which extends through the ring in a position to engage the idler wheel to sufiicient prevent movement of the idler wheel away from the drive gear wheel completely to disengage the two gear wheels .
June . An assembly according to claim 3 wherein the movement preventing or restricting means comprises a stop element is opposed to the idler wheel in a position to engage the intermediate gear wheel for preventing movement of sufiicient idler wheel away from the drive gear wheel completely to disengage the two gears .
July . An assembly according to claim 3 wherein the movement preventing or restricting means comprises an endless member and each of the driving and driven sprockets is provided with a coaxial cylindrical extension having an outer peripheral surface around the endless member which extends and is in frictional engagement to prevent relative rotational sliding of the driving and driven sprockets .
August . An assembly according to claim 3 wherein the movement preventing or restricting means comprises an arm pivotally mounted about an axis coincident with the axis of rotation of the drive gear wheel , the idler wheel is rotatably mounted on the arm at a fixed distance from the pivot axis , said arm being connected to the friction drive gear wheel and pivotally movable by the drive gear wheel during reversal in rotation to move idler gear wheel from a position on one side of the driving and driven sprockets , around the drive wheel and a position on the opposite side of said gear wheels and allow the assembly to conduct alternately in both directions.
9. An assembly according to claim 1 , which includes first and second gear wheels arranged on either side of a line connecting the centers of rotation of the driving and driven sprockets , the gear wheels being arranged relative to each other during rotation the drive gear wheel in one direction and alternately in the opposite direction to apply a driving force resulting , respectively ,
alternatively the first and second gear wheels along a path between the centers of rotation of the driving and driven sprockets to maintain the first and second idler gears constantly meshed with the driving and right driven sprockets , means associated with toothed wheels being provided to prevent or restrict movement of each idler gear correct mesh with the gear drive when said resultant force is not applied along said path .
10 . An assembly according to claim 9 wherein the preventing or restricting movement means comprise a crank pivotally mounted about an axis coincident with the axis of rotation of the gear wheel drive and idler sprockets are rotatably mounted one on each arm of the lever , the distance between the two idler wheels to ensure that when one of the idler gear wheel is in correct mesh with driving and driven sprockets , the other idler wheel is completely out of engagement with the driven gear and the friction lever is connected to the drive wheel pivotally moving the shift lever on the rotation of the drive gear wheel to move a wheel idler gear mesh with driven unit and to move the other idler gear wheel in mesh with the gear driven .
11. An assembly according to claim 9 wherein the movement preventing or restricting means is an elastic means extending from one wheel to the other intermediate gear .
12. An assembly according to claim 1 wherein the gear wheels have a pressure angle , each gear has an outer peripheral surface for -med with gear teeth , and
Gear wheels are relatively arranged to produce a " angle between a line connecting the centers of rotation of the intermediate gear wheel and the gear wheel drive and a line connecting the centers of rotation of the intermediate gear wheel and the driven gear wheel , said angle being produced at least twice the pressure angle .
13. An assembly according to claim 1 wherein the gear wheels have a pressure angle , one of the driving and driven sprockets is a ring having an inner peripheral surface formed with gear teeth , and the gears are relatively arranged to produce a line connecting centers of rotation angle betweenone wheel and driving idlergear not override or driven wheel , and an extension of another line connecting the centers of rotation of the intermediate gear wheel and the ring , said angle produced at least twice the pressure angle .
14. An assembly according to claim 1 wherein each spacer has a diameter equal to the pitch circle diameter of the respective gear wheel .

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Inlet and bearing support for axial flow compressors

Inlet and bearing support for axial flow compressors

DESCRIPTION
April 9, 1953 w . T. DENNISON 3084849
ENTRY AND BEARING AXIAL FLOW COMPRESSOR Filed May 18, 1960 2 Sheets leaves 1 FIG . 92
/ / Vl E/V7 0R WILLIAM T. Nison DEN line 4 . must M : W
LAWYERS April 9, 1963 w . T. DENNISON 3084849
ENTRY AND BEARING AXIAL FLOW COMPRESSOR 2 Sheets - 2 Sheet Filed May 18, 1960 the figure. 2
. Figure 1 May 5
i ice STATE INPUT BEARING AXIAL COMPRESSOR SUPPQRT FLQW William T. Dennison , West Hartford , Onn . , Assignor to United Aircraft Corporation , East Hartford , Connecticut , a Delaware corporation , filed May 18, 1960 29,981 Being No. '7 claims. ( @ L . 230-4122 ) This invention relates to axial compressor fiow - s , and deals more particularly with an improved construction and integrated to the air inlet and the support for the front bearing in such a machine.
The main object of this invention to provide an improved construction for supporting the front bearing an axial flow compressor in relation to the compressor casing or the mounting structure and the inner ends of the inlet guide vanes , said construction being compact in size, simple arrangement, which requires relatively few parts and enables easy access to the front of the compressor.
Another object of this invention to provide an improved support and lubrication means for the front bearing of the compressor.
A further object of this invention to provide a support structure for the front bearing of a compressor rotor through which the bearing is positioned relative to the oil sump or the lubricant scavenging chamber flows directly from the sump to the bearing result that none of the support members must be perforated or otherwise provided with apertures or passageways for the return of lubricant to the sump.
A further object of this invention to provide means for supporting the front bearing of the compressor from the inner ends of the inlet guide vanes so that the bearing is cantilevered from a single support member with the result radial that a measurable amount of flexibility is present in the bearing, such flexibility that serves to reduce the natural vibration frequency of the compressor rotor so that the rotor can be safely operated at normal speeds which are above the speed corresponding to that natural frequency.
Other objects and advantages of the invention will be apparent from the drawings and the description below.
The drawings show a preferred embodiment of the invention and this embodiment will be described , but it is understood that various changes may be made in the construction described and that the drawings and description should not be interpreted as defining or limiting the scope of the invention, the claims forming a part of this specification be invoked for this purpose.
Drawings :
. Figure 1 is a fragmentary sectional view taken in a plane passing generally through the longitudinal axis of a compressor axial fiow and showing a blade inlet and the front of the bearing support structure embodying this invention , having view taken through the inlet guide vane which contains the lubricant supply duct and parts behind the plane of the view being omitted for clarity,
. Figure 2 is a partial front view of the pallet scaled input and hinge construction is shown in Fig . 1 with the front cover is removed to more clearly show the bearing support structure ,
. Figure 3 is a fragmentary sectional view taken on line 33 'in FIG . 1 and drawn to a reduced scale of the figure. 1
. Figure 4 is a fragmentary sectional view taken through the inlet guide vane containing the lubricant duct sweeping parts behind the plane of the view being omitted for clarity , and
. Figure 5 is a partial sectional view taken along line 5-5 of Fig . April .
In the drawings where the purpose of illustration is shown a preferred embodiment of this invention, and referring first to FIGS . 1 and 2, reference numeral 10 generally indicates the air intake of the axial flow compressor . Gate 10 is of annular form and is defined by concentric , radially spaced inner and outer annular covers 12 and 14 , respectively. The outer cover 14 is adapted to be supported by the mounting structure suitable motor , not shown, by means of a flange extending radially outwards 16 formed in its upstream end and is provided with a plurality of apertures circumferentially spaced 18, 18 which serve for receiving mounting bolts or other fasteners.
Inner annular housing 12 is supported from the outer casing 14 via a plurality of inlet guide vanes 24 , 20) , as shown in Fig . 2, extend radially between the two shrouds and are arranged in an annular series of circumferentially spaced within the air inlet 10 . The inlet guide vanes 20, 20 have a cross section generally in the form of curved support surface and serve to direct the inlet air in proper operational relationship with the first stage rotor blades of the compressor. The blades of the first stage compressor rotor not shown in the figure. 1 but should be understood to lie directly to the right of the guide vane is shown therein . The guide vane is shown in Fig . 1 contains the lubricant supply conduit , as described in more detail below , but in other respects is similar to most other guide vanes 20, 20 . To distinguish the guide vane of Fig . 1, however , those not containing a lubricant supply conduit or additional elements , is designated by the reference 20a . Similarly, the guide vane shown in Fig . 4 containing the lubricant scavenging duct is designated by reference numeral 2 % to distinguish it from the other guide vanes 20, 20 . Again, both the guide vanes 20a and 20b are generally similar to the other guide vanes 20, 20 except for the addition of the lubricant supply conduits and sweeping thereof. Each guide vane is of hollow construction , as
best shown in FIGS . 3 and 5, and is closed at its inner end by an inner cover 22 and at its outer end by an outer covering 24. Opposite end portions of the fins fit into corresponding openings in the inner and outer casings 12 and 14 and are welded to the shroud , as indicated in Fig . 1.
From the figure. 1 also be seen that the outer cover 14 comprises an outer annular ring 26 and an inner annular ring 28 that collectively define an annular chamber 30 adjacent the closed outer end portions of the blades 20, 20 . Similarly, the cover 12 consists of inner annular ring 32 and an inner annular outer annular ring 34 which collectively define an annular chamber 36 adjacent the inner end portions of the blades 20, 20 . The 3t cameras and 36 serve as part of a system for the anti- airflow icing through the vanes 20, 20 and each paddle is provided with openings 38, 38 which communicate with the chambers 30 and 36 to provide air flow radially through the vanes . The anti - icing , however , is not part of this invention, the same structure in relation to the blades 20, 20 is made only by way of example, and other mounting means for the inner and outer ends the blades can be used with or without provision against icing without departing from the scope of this invention . The vanes 20, 20 need not be hollow , but when made ​​in hollow shape is generally desirable that they each include a reinforcement 40 inside the fin extending radially along the length of the blade in engagement with the two opposite interior walls of the vane , as shown in FIGS . 3 and 5.
The compressor housing is generally indicated at 4-2 in Fig . 1 and is preferably integral with the outer annular housing 14, as shown. Housing 42 also preferably extends downstream a distance equal to about half the length of the rotor of the compressor and is at its downstream end connected to another housing portion that extends downstream to the rest of the length of the compressor to not require separate or additional compressor casing . The member 44 partially shown in Fig . 1 is the outer annular seal of the first stage compressor blades and connected to the outer annular casing 14 by a plurality of staggered pins , one of which is shown at 46.
Referring again to FIG . 1, it is seen that the cover 12 has an inner annular flange 48 integrally connected to its portion downstream edge and extending radially inward thereof. The flange 48 serves to support a cylindrical or sleeve that is connected to the support flange 48 by a plurality of bolts 52, 52 which pass through an annular flange that extends outward in the bracket 54 and through inner margin of support flange 48 . Pins 52 , 52 have nuts 56, 56 threadedly received in their upstream ends and a ring seal 58 is used between the flange 54 and the flange 48 , as shown in Fig . 1.
The bracket 50 , as shown in Fig . 1 extends axially upstream of the support flange 48 and beyond the downstream edges of the guide vanes 20 , 2t ) and serves to receive the front bearing 60 of the compressor rotor . The compressor rotor is not shown in detail in FIG . 1, but it is understood that the bearing portion 60 is in front of the rotor and integral with the bell end which is partially illustrated and is indicated at 62. The bearing portion 60 is rotatably supported relative to the carrier 50 via a roller bearing unit 64 that is positioned between the inner hole of the clamp 54) and the outer surface of the bearing portion 60 . The location of the bearing unit is such that it falls between the edges upstream and downstream of the guide vanes that is, the bearing unit is disposed in a radial plane , a plane normal to the rotation axis , which passes through the bodies of the guide vanes . The outer race 66 of the roller bearing'unit 64 is received by a corresponding hole portion 68 of the bracket 50 and held in place with respect to the holder by means of the retaining nut 70 which is threadedly connected to a portion 72 the bracket 50 which extends upstream from the bearing 64 , the outer race 66 includes a flange 74 which is held in engagementwith a shoulder holder hole by the retaining nut 70 .
Downstream of the bearing unit 64 is a seal 76 which closes the space between the bearing and the bracket 50 to prevent the escape of lubricant therebetween. 76 seal plate comprises two annular seals 78, 73 which are held in axially spaced relation by a spacer 80 , and two annular graphite seals 82, 32 each of which engages with the holder hole 50 and a radial face in a corresponding one of the plates together July 8, 78 . Right latch plate July 8 engages a rib formed on the 3-4 of bearing 60 , while the other plate gasket engages the downstream end of the outer race 86 of the bearing 6 ring outer race 86 , the two plate seals 78 , 7S ' and spacer 80 are in turn held in place in the bearing part 60 by means of a retaining nut 88 which is threadably received by the end portion upstream of the bearing part 60 . Loosening movement of the retaining nut 88 is prevented by a tablock 90 . The bearing part is hollow and the upstream end portion thereof is closed by a circular cap 92v is held in place by a shoulder 94 and a retaining ring 96 .
From the foregoing and by reference to FIG . 1 , note that the support flange 48 serves as the only support for the radial support 5i ) and the bearing 64, and it was also observed that the bearing 64 - is upstream of the flange 43 in order to be supported Similarly on a cantilever . In this regard it is noted that the oil supply duct , later described , form no substantial part of the structural support for the support. The cantilever support arrangement for the bearing 64 provides for a certain amount of flexibility in the bearing and thus provides a compressor rotor natural frequency lower than would be the case if the bearing supports sturdier has generally been the case with prior constructions . Rotor speed corresponding to the lowest natural frequency of the vibration produced by this mounting arrangement has been found to be sufficiently below the normal operating speed of the rotor so that the rotor in normal operation will function safe and well above its natural frequency . Moreover, since the bearing 64 is axially aligned with the guide vanes , the radial loads imposed on the support act along radial lines passing through the guide vanes so that torque loads on the shrouds , vanes and other engine parts are minimized .
Besides the advantages achieved by the bearing support structure with respect to the lowest natural frequency , the structure shown at present has more advantages in relation to the provision of means for lubricating the bearing 64 . Since the bearing 64 is subjected to the relatively severe operating conditions , it is desirable to be lubricated by a pressurized spray system . Referring to FIG . 1 , this system includes an oil supply conduit 98 extending through the guide vane 29th . At its outer end of conduit 98 extends beyond the outer cover 24 of the flap 20a has associated therewith a suitable connector 160 for receiving a complementary connector 102 which connects the conduit 98 to another conduit 104 which leads a source of pressurized lubricant . The inner end of conduit 98 extends inwardly beyond the inner cover 22 of the truck 20a and is supported by a sleeve surrounding 106 attached to the cover 22 , the sleeve 106 containing a stamp 1118 which is coupled to the surface outside the conduit 98 . The conduit 98 extends inwardly beyond the inner end of the sleeve 106 and has at its end portion a nozzle 110 having an orifice 112. Port 112 is directed in a generally downstream direction to spray lubricant from the conduit 5 8 on the annular space between the support 50 and the bearing journal 64 portion'60 . Between the inner end of conduit 98 and the nozzle orifice 112 is a filter screen or lubricant 114. The nozzle 119 is , as shown in Fig . 2 secured by threaded fasteners 115, 115 to a tab 116 formed on the upstream end of the bracket 50 and extending radially outwardly therefrom .
Around the clamp 50 is an annular manifold chamber 118 or sweep lubricant . The inner surface of the inner annular housing 12 including the inner flap covers 22 , 22, defines the outer periphery of the scavenging chamber 118, while the support flange 48 defines the right wall of the chamber. The left wall of the chamber is defined by a circular front cover 120 which is secured to a flange 122 extends radially inwardly at the upstream edge of the inner annular housing 12. The support 50 projects freely in the center of the chamber 118 with the result that the upstream side of the bearing 64 is in direct communication along its circumference with the chamber 118 and the inner surface of the inner annular housing 12 which serves as the periphery of the chamber . Therefore, the spent oil or lubricating media can flow directly from the bearing 64 to the outer portions and bottom of the chamber 118 without passing through any member or structural members . This means that none of the structural support members for the bearing has to be perforated or otherwise provided with passages to allow the flow of lubricant to the compression chamber. This, of course , is important in reducing the stress concentration factors unknown to the structure of the compressor.
Lubricant drains into the bottom of the sump or scan camera 118 is removed therefrom by means of a scanning conduct 124 extending radially through the vane 20b, the pallet 2% being located at the lowermost position or six o'clock in the air inlet , as shown in Fig . Two . As shown in the figures. 4 and 5, the waste collection pipe 124 has a flattened cross-section at its inner end and has a mouth 126 positioned adjacent the inner surface of the cover 12 , the cover being in - vane 22 , considered part of the inner surface of the cover 12 , so that the lubricant which is installed on the bottom of the chamber 118 will be withdrawn therefrom through the mouth 126. At its lower end scanning conduit 124 extends through the outer cover 24 and has associated therewith a coupling member 128 which receives a complementary coupling member 130 for connecting the waste collection conduit to another conduit 132 that returns the lubricant to the lubricant .
In addition to providing for proper lubrication of the bearing 64 which is also observed that the lubrication system as described above is integrated with the bearing support structure that both the support structure and the lubrication system forms a compact arrangement of the parts take up little space and require fewer components .
The invention claimed is:

1. The combination of an axial flow compressor , radially spaced inner and outer annular cover concentrically disposed to define an annular air inlet to said compressor , a plurality of guide vanes extending radially arranged in an annular array circumferentially spaced apart from said cover interior and exterior and having their inner ends fixedly secured to said inner cover and outer ends fixedly secured to said outer cover , an annular supporting portion connected to an edge only of said inner cover and extending radially inwardly thereof, a cylindrical support bracket connected to the radially inner portion of said support bracket and extending axially therefrom toward the other edge portion of said inner cover , a rotor which has a bearing part forwardly positioned within said support , and an antifriction bearing between said support and said part of the rotor journal for rotatably supporting portion of said magazine with respect to said support , said bearing being axially spaced from said mounting flange and located in a radial plane passing through said guide vanes so that said bearing is supported flexibly cantilevered from said flange for supporting said cylindrical support .
Two . The combination of an axial flow compressor , radially spaced inner and outer annular cover concentrically disposed to define an annular air inlet to said compressor , a plurality of guide vanes extending radially arranged in an annular array circumferentially spaced apart from said cover inner and outer ends and having inside fixedly secured to said inner cover and outer ends fixedly secured to said outer cover , a flange connected to the annular support only said inner cover along the edge portion of downstream of the latter and extending radially inwardly thereof, a support bracket connected to the cylindrical inner edge of the bearing flange and extending axially at a distance upstream thereof and beyond the edges water downstream of said inlet guide vanes, a rotor having a forward bearing portion positioned within said cylindrical support , and an antifriction bearing between said support and said rotor journal portion for rotatably supporting said journal portion with respect to said support , somedistance said bearing is located upstream of said mounting flange in a radial plane passing through said guide vanes so that said bearing is flexibly supported in cantilever fashion from said flange for supporting said cylindrical holder.
Three . The combination of an axial flow compressor , radially spaced inner and outer annular cover concentrically disposed to define an annular air inlet to said compressor , a plurality of guide vanes extending radially arranged in an annular array circumferentially spaced being - 7 and said inner support housing , a rotor having a forward bearing portion of said carrier positioned within a bearing support betweensaid magazine and said rotor portion for rotatably supporting said magazine portion of said support with respect to a lubricant supply conduit means extending radially through one of said guide vanes and inwardly beyond said inner housing and having a nozzle at its inner end arranged to spray lubricant said conduit means on said support , and a conduit for collecting waste lubricant which extends radially through the other of said guide vanes and having an inner surface adjacent said opening therein for receiving lubricant coating which is collected in said chamber adjacent to said surface of the latter.
April . The combination of an axial flow compressor , radially spaced inner and outer annular cover concentrically disposed to define an annular air inlet to said compressor , a plurality of guide vanes extending radially arranged in an annular array circumferentially spaced apart from said cover inner and outer ends and having inside fixedly secured to said inner cover and outer ends fixedly secured to said outer cover , a flange connected to the annular support only said inner cover along the edge portion of downstream of the latter and extending radially inwardly thereof, a support bracket connected to the cylindrical inner edge of the bearing flange and extending axially at a distance upstream thereof in superposed relationship with said cover axially inward so that an open annular space is defined between said support and said inner cover , a rotor having a forward bearing portion of said carrier positioned within a bearing between said support and said rotor portion magazine for rotatably supporting said journal portion with respect to said support , said bearing is axially spaced upstream from said mounting flange in order to be supported in cantilever fashion and said annular support itself be of such length as to extend axially upstream most beyond said bearing lubricant nozzle portion connected to the upstream end of said support and arranged for spraying lubricant in a generally downstream direction in said bearing , and means of lubricant supply conduit for delivering lubricant pressure to said nozzle and duct means extending through one of said guide vanes and inwardly beyond said inner cover for connection to said nozzle .
May . The combination of an axial flow compressor , means defining an annular inlet means to said compressor and includes an annular cover inside, a support member connected to said annular inner housing only along the edge portion downstream of the latter and extending radially inwardly thereof, a cylindrical support member connected to said support and extending axially upstream thereof at radially and axially spaced relationship to said inner cover overlying a compressor rotor having bearing part positioned within said support , and a bearing between said support and said part of the magazine for rotatably supporting said journal portion with respect to said support , said inner cover and said annular support member defining respectively the outer peripheral wall and the radial wall downstream of a compaction lubricant annular chamber in which said support projects chamber of said annular supporting member with the result that the upstream side of said bearing is in direct communication with the outer periphery of said lubricant compaction chamber along the entire circumference thereof so that the lubricant of the bearing 7 can flow directly to said waste collection chamber without passing through any structural member or members. j 6 . The combination as defined in claim 5, further characterized by a lubricant removal conduit extending through one of said guide vanes and having an opening adjacent the inner surface of said inner shell for the drainage of lubricant from said chamber . 7
July . The combination of an axial flow compressor , radially spaced inner and outer annular cover concentrically disposed to define an annular air inlet to said compressor , a plurality of guide vanes extending radially arranged in an annular array circumferentially spaced apart from said cover inner and outer ends and having inside to'said fixedly secured inner cover and outer ends fixedly secured to said outer cover , a support flange annular portion connected to the downstream edge of said inner cover and extending radially inwardly thereof, a support bracket connected to the cylindrical inner edge of the bearing flange and extending axially at a distance upstream thereof at radially and axially spaced relationship with said inner cover overlying a rotor having a forward bearing portion of said carrier positioned within a bearing between said support and said rotor portion magazine for rotatably supporting portion of said magazine with respect to said support , said clamp and said annular support portion forward bearing having their upstream ends spaced at a distance downstream of the upstream edge portion of said inner cover , means for supplying lubricant to said bearing , a cover connected to the upstream edge portion of said inner cover to cover closes the upstream end of said deck and defines an annular wall of a collection chamber lubricantleaving said bearing , the other walls of said chamber is defined by the inner surface of said inner cover , said annular support flange and said bracket annular support .

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Accessory drive

Accessory drive

DESCRIPTION
HW GUNBERG April 12 1960 Filed accessory drive 1'7 August 1956 2 Material leaves l [ OR IN TOR PAH / P ) M. GUNBERG A TTO / PNEY April 12, 1960 HW GUNBERG ACCESSORIES DRIVE 2 Sheets - 2 Sheet Filed August 17, 1956 ATTORNEY running.
Patent rates UNIT ACCESSORIES Harry W. Gunberg , West Hartford , Conn., assignor to United Aircraft Corporation , East Hartford , ( 30:111 . , A Delaware corporation Appiica'tion August 17, 1956 , Serial No. 605685
1t ) Claims . ( Cl 23il - J - 122) The present invention relates to a gas plant turbinepower where there is high pressure compressor rotors independently and low pressure .
A feature of the invention is an arrangement for driving an accessory gear of the rotors without restricting the thermal expansion of any of the rotors Another feature is an arrangement for driving the accessory gear one rotor without applying any load said rotor axial thrust .
When the rotors are concentric such that an axis extending through the rotor and rotates with respect to the othershaft , it is desirable to support the shafts in concentric relation to each other by an intershaft bearing because if the "two shafts rotate in the same direction, this hearing then operate at a relatively low speed compared to a bearing support shaft with respect to the surrounding stationary structure . one feature of the invention - is the incorporation of the accessory drive end shaft which is supported by an intershaft bearing. Another feature is the incorporation of the labels by which enclose the bearing and accessory drive within achamber lubricant which is substantially tight.
Other objects and advantages will be apparent from the specification and claims and from the accompanying drawings invention.
. Figure 1 is a sectional view through the casing supporting the shafts and rotors is located between the low and high pressure .
- Figure 2 is a sectional view - afragmentary a larger scale of part of the device of FIG . l .
The invention is shown in relation to a division of the type shown compressorof - for example , in the Savin Patentno . 2,747,367 . '2 Outer casing supports the fixed blades 4 which alternate with rows ofblades 6 on the low pressure compressor rotor S , located upstream of the intermediate housing LTL. Inwardlyfrom this casing extends the casing 2 and supports the bearing 12 whereby the low pressure rotor concenillustrate is an embodiment of the electrically inside the housing . The bearings not only support the load compressor rotor radial low pressure " Butare also designed as thrust bearings by which to keep the compressor rotor 8 axially in position within ' the box. To this end, the inner races of -14 bearings are clamped between the flanges 16 and 18 in the rotor shaft 20 forthe .
Downstream of the deck shell 2carries one ' or more rows of stator vanes 22 alternating with rows of the stroke - interior and the support elements 36 so that the " free rotor can be 2-5 to expand axially at this point. be understood that the rotor 26 is supported by the axis of the high pressure rotor 28.
other downstream rolling bearing 30 which functions to maintain the rotor 26 against axial movement at that point with respect to the surrounding support structure .
The housing 10 includes a series of vanes 38 extending radially inwardly projecting from the housing 2 and suitably secured thereto . The inner ends of the blades 38 are interconnected by a ring 40 having a flange which projects inwardly extending obliquely 42 . This flange 44 has openings therein for receiving the bearing 46 to the accessory shaft 48 which extends radially .
Also'includes housing 10 which'are disks 50 and 52 are attached as by bolts 54 at its outer edge to the ring 40 and bearing elements inside ends oppositely extending frusto- conical 56 and 58. Discs 50 and 52 are attached as by bolts 60 at their inner ends to a ring 62 to which is attached the bearing 46 . The screws also support , through the projecting flange 63, a support bearing ring 64 to the thrust and radial bearings 12. The support ring 64 is also bolted to the upstream end of element 56 . This structure therefore supports the bearings 12 against axial movement and radial movement relative to the housing 10.
The bracket 46 has bearings 66 for the attachment shaft 48 which carries at its inner end a transmission gear accessory 68 . This gear is meshed with a gear 76 which is driven to achieve this, the gear 70 is splined to a sleeve 72 , fig. 2, which surrounds the shaft 28 and is driven from the shaft 28 by splines 74 . The gear 70 is held firmly in the socket 72 as by a clamping ring 76 . ' The sleeve 72, however, is axially slidable relative to the shaft 28 and slots 74 are constructed to allow this movement axially slidable .
A radial and thrust bearing 78 mounted on the inner shaft 20 and having its inner race 30 secured against axial movement on it , has its outer race 82 held at the inner surface of sleeve 72 as by a ring clamp 84 . The thrust bearing 78 is closely adjacent to the bearing 12 and accordingly the sleeve 72 is fixed against any axial movement and therefore is held in predetermined relation with the sprocket shaft 68 so that this gear and the gear 70 are engaged at all times. However, since the shaft 28 can move axially relative to the sleeve 72, it is obvious that thermal expansion of the shaft 28 in an axial direction is perand provided to prevent escape of lubricant thereof. This chamber is defined by the ring 62, the tapered element 56, a seal 88 and a ring 90 on the shaft 20 . Downstream of the ring 62 , the chamber is defined by the element 58, and a seal 92 which engages g'ear th'e 70 .
Slidaole seal 88 is axially in a cylindrical surface provided by a support ring 92 and is pushed axially against the ring 90 by a wave spring 94 . The support ring 92 and wave spring 94 are attached as by bolts 96 to the inner end of element 56 . These screws are also coupled to the upstream end of the support sleeve bearing 64 . Ring 90 may be attached to the same shaft 2d between flanges 16 and 18 that retain the inner ring 14 of the bearings 12 in place. Understood'that will flange 18 is not integral with the shaft 2% but is in the form of a clamping ring which can be threaded or otherwise removably attached to the shaft so that the inner races of the bearings can be mounted thereon .
The seal 92 is similar to the self- seal is axially slidable on a cylindrical surface provided by a ring 98 and pushed axially by a wave spring 100 which engages the downstream end of the sealing member and urged against the gear 1t 70 . Both seals 88 and 92 are of the type referred to as reversed seals in the lubricant reaches the seals from a point radially outwardly from the operating surface of the board which engages with the openings of 1% sleeve 72 so that the lubricant reaches the space 106 between the sleeve 72 and the inner shaft 20 , and this space provides lubricant bearings 78 and 30. The inner surface 108 of the high pressure shaft 28 is preferably diverging in a direction towards the audience 30 such that any lubricant which flows from the space past the bearing 106 is discharged by centrifugal force through the apertures 11% axis 28.
Although the surface 1 and 8 which is convergent , it is understood that the outer race 34 for the bearing 30 is not necessarily cylindrical to permit axial sliding movement which is provided for at this point.
Lubricant escape through the holes 110 in the shaft 28 flows along the sleeve 72 to lubricate the grooves 74, and outwardly through oblique bores 114 in the sleeve to be released against the teeth on the gears 68 and 70 .
Besides the accessory drive gear 70 , other units 7 may, for example , gear 116 fixed to the shaft 2%) adjacent to bearing 12 . Since this shaft is held against axial movement in this hearing, the gear can drive directly a gear , not shown, on a radial axis similar to gear 68 , the gear meshing with the gear 116 is angularly displaced from the gear 68 , as be evident.
It is understood that the invention is not limited to the specific embodiment illustrated and described herein, but may be used in other ways without departing from its spirit as defmed by the following claims .
Claim:

1. In a power plant gas turbine rotor having a low pressure compressor and rotary compressor rotor separate high pressure concentric shafts on which are mounted the compressor rotors an accessory drive shaft having a gear tapered at one end, a drive gear driven conical outside said concentric shafts mesh with said first gear , and a thrust bearing on the inside of said axes and connected to said drive gear for taking the axial thrust of said drive gear .
Two . in a power plant gas turbine having a rotor of the low pressure compressor and a rotatable rotor separated high pressure compressor , thus normally concentric shafts can rotate in the same direction and in which the rotors are mounted compressor, accessoly drive shaft between said rotors and having a bevel gear on one end a bevel drive gear and driven around the outside of said concentric shafts and meshed with said first gear , a thrust bearing inside said shafts to take the axial thrust of said driving gear and a bearing between said shaft adjacent said thrust bearing.
Three . In a power plant gas turbine having a rotor of the low pressure compressor and a rotatable rotor separated high pressure compressor , thus normally concentric shafts can rotate in the same direction and in which are mounted the compressor rotors , one housing in which said shafts are supported, an accessory drive shaft between said rotors and having a bevel gear on one end a conical gear drive gear according to the exterior of said concentric shafts and meshed with said first gear , a bearing of between said interior pressure . shaft and said drive gear for taking the drive of said drive gear and a bearing in said housing for supporting ' assaaas carry the inner shaft , said bearing being both a radial and a thrust bearing .
April . In a power plant gas turbine having a rotor of the low pressure compressor and a rotatable rotor separated high pressure compressor , thus normally concentric shafts can rotate in the same direction and in which are mounted the compressor rotors , one housing in which said shafts are supported, an accessory drive shaft between said rotors and having a bevel gear on one end a conical gear drive gear according to the exterior of said concentric shafts and meshed with said first gear , a bearing of thrust between said inner shaft and said drive gear for taking the drive of said drive gear and a bearing in said housing for supporting the inner shaft , said bearing being both a radial and thrust hearing , and a radial bearing between said inner and outer shafts .
May . In a power plant gas turbine having a rotor of low pressure compressor rotor and high pressure compressor separately rotating concentric shafts on which are mounted the compressor rotors , a housing between said rotors and having a thrust bearing within said support shaft against axial movement , a sleeve splined to the outer shaft , a thrust bearing between the inner shaft and said sleeve to maintain said sleeve against axial movement ,
a transmission gear accessories in said sleeve , and a gear driven by said cooperation drive gear and rotatable in said housing .
June . In a power plant gas turbine having a rotor of low pressure compressor rotor and high pressure compressor separately rotating concentric shafts on which the rotors are mounted oompressor a housing between said rotors and having a thrust bearing within said support shaft against axial movement , a sleeve spline to the outer shaft , a thrust bearing between the inner shaft and said sleeve to maintain said sleeve against axial movement , a transmission gear in said accessory gear sleeve and cooperation in said housing and a bearing between said shafts adjacent to said sleeve, and which allows relative axial movement between said shafts .
July . A power plant gas turbine having a rotor of the low pressure compressor and rotating separately ro'tor high pressure concentric shafts to which said rotors are secured , a housing between the rotors , carried by a bearing . said housing for supporting the interior of said shafts against axial movement , a thrust bearing on said inner shaft , a sleeve supported by said thrust bearing against axial movement and which surrounds said axle , said outer shaft grooves and the sleeve whereby the sleeve can be driven by said outer shaft , said grooves providing axial movement between said sleeve and said outer shaft .
August . A power gas turbine having a compressor rotor and separate low'pressure high pressure rotating rotors safe , concentric shafts which are secured said rotors , rotor housing between said one bearing supported by said housing for supporting the inside of said axes , a thrust bearing on said inner shaft , a sleeve carried by said thrust bearings against axial movement and which surrounds said axle , said outer shaft grooves and the sleeve by which the sleeve can be driven by said outer shaft , said grooves providing axial movement between said sleeve and said outer shaft , 2. gear in said sleeve and an accessory drive shaft in said housing having a gear meshing .
9. A power plant gas turbine having a rotor of low pressure compressor rotor and high pressure rotary separate , concentric shafts which are secured said rotors , a housing between said rotors , a bearing carried by said housing for supporting inside said axle thrust bearing on said inner shaft , a sleeve supported by said thrust bearing against axial movement and which surrounds said axle , said outer shaft grooves and the sleeve by which the sleeve may be driven by said outer shaft , said grooves providing axial movement between said sleeve and said outer shaft , said housing providing a chamber surrounding said bearing and sleeve , and sealing means located in said housing adjacent said first mentioned bearing.
10 . A power plant gas turbine having a rotor of low pressure compressor rotor and high pressure rotary separate , concentric shafts which are secured said rotors , a housing between said rotors , a bearing carried by said housing for supporting inside said axle thrust bearing on said inner shaft , a sleeve supported by said thrust bearing against axial movement and which surrounds the sleeve may be driven by said outer shaft ,
such grooves providing axial movement between said sleeve and said outer shaft , said housing providing a chamber which surrounds said bearings and sleeve , and sealing means located in said housing adjacent said first and said bearing sleeve adjacent to the end away from said first bearing.

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Gas turbine engine and the starting thereof

Gas turbine engine and the starting thereof.

Description
December 14, 1954 F. c . MARCHANT RRM . 2GAS TURBINE ENGINE AND STARTING THE SAME Filed August 13, 1948 4 Sheets sheets l 5:00 a.m. mm ML N nw 5 F. c . l . MARCHANT ETAL 2696711GAS TURBINE ENGINE AND THE SAME Filed August 13, 1948 4 Sheets sheets 3 14 December I954 F. c . l . MARCHANT ETAL 2696711GAS TURBINE ENGINE AND STARTING THE SAME Filed August 13, 1948 4 Sheets - Page 4 / / Yl f/V7 '015 E63 1. [ Mew/4md one. 44 . 45mm U.S. Patent GAS TURBINE ENGINE AND SAME STARTING Ivor Francis Charles Manns Marchant and Lewis Gordon , Bristol , England , assignors to the Bristol Aeroplane Company Limited , Bristol , England , a British company application 13 of August 1948 , serial number 44014
2 Claims . ( Cl 60-3914 )
 This invention relates to gas turbine engines and is intended to improve the qualities of starting and operating the engine.According to this invention, a gas turbine engine having a pair of turbines through which the working fluid passes in succession and compressor assembly composed of a unit which is independently driven by a turbine , characterized in that there is provided a starter motor for driving said compressor unit only and all or some of the engine accessories .The present invention finds particular application to gas turbine engines for driving airplanes and according to another feature of the invention , an engine of this type having a low compressor and high pressure in each of which is independently powered by a turbine through which the working fluid passes in succession characterized in that a starter motor for driving only the high pressure compressor and turbine and engine accessories which are driven with the high pressure compressor and the accessories are driven ticket with the low pressure compressor .A practical application of the present invention will now be described , by way of example with reference to the accompanying drawings , which :Figure 1 is a schematic sectional elevation of a gas turbine engine according to the present invention,Figure 2 is a view on an enlarged scale of part of the engine of Figure 1 ,Figure 3 is a cross section showing a part of the motor of Figure l and an enlarged scale, andFigure 4 is an elevational view in section showing a detail construction of the output of the compressor assembly .
Referring to Figure l:

The engine comprises a pair of turbines 5 and 6 which are part of the turbine generally indicated at 7. The engine also comprises a compressor assembly indicated generally at 8, and the combustion apparatus , indicated generally at 9, which connects the compressor assembly 8 with the turbine assembly 7 .The combustion apparatus comprises an annular combustion chamber 10 which contains a plurality of flame tubes 11, the fuel is supplied individually to each of the flame tube in a known manner , the fuel burns in the flame tube and the products of combustion passing along the annular combustor 10 to the turbine assembly 7 . The combustion air is obtained from the assembly of compressor 8 . Combustion products pass successively through the turbines 5 and 6 , respectively.Compressor assembly 8 comprises a low-pressure axial flow compressor 12 and a high pressure axial flow compressor 13. The compressor 12 supplies the compressor 13 which in turn supplies the combustion device 9.The air from the compressor 12 is transmitted to compressor 13 through an annular duct 14 which lies between the compressors. Stator housings of the compressors 12 and 13 are bolted to the duct 14. The compressor 13 is connected to the combustion apparatus by a housing 9 annular air duct 15.Be seen in Figure 1 that the housing 15 is bolted to the stator housing 13 and the compressor outer wall of the annular combustor 10 . The arrangement described thus provides continuous outer layer that surrounds the motor of the compressor outlet to the outlet end comice turbine - the ring housing 16 of the turbine forming part of the shell.The diameter of the shell decreases from the compressor inlet to the annular combustion chamber , and then increased so that the motor shell has a waist portion formed by the air duct housing 15.The high pressure compressor 13 is coupled to the high pressure turbine 5 for a drive shaft 17 and , similarly, the low pressure compressor 12 is connected to the low pressure turbine 6 by a drive shaft 18 , this latter is nested within the hollow shaft 17.The engine is being described is particularly adapted for use in an aircraft and , as is well known , and the plane theengine each requires certain accessories for its operation . For example, the engine requires a starter , lubrication pumps , fuel pumps , and so on while the aircraft requires vacuum pumps , generators, pumps, pressure and so on.An engine constructed in accordance with this invention, the engine starter motor and some other access - ' accessory are carried by the housing 15 and are coupled through suitable gearing with the axle 17. This gear is indicated schematically in Figure l at 19.The detailed construction of the gear 19 of Figure l IINS shown in Figures 2 and 3 to which reference will now e had.The shaft 17 carries a pinion 20 which meshes with a gear wheel 21 mounted on an intermediate shaft 22. The latter is supported by bearings on a frame 23 which is integrally formed with a diaphragm 24 that is bolted , at 25 , to the inner wall of the housing 15. The intermediate shaft 22 carries a bevel gear 26 meshing with a bevel pinion 27 carried by a shaft 28 . The latter is the drive shaft of the starter motor 29 which is bolted to the top of the housing 15 . Thereby the starter motor is connected to the axle 17.A similar gear train 20, 30 , 31, 32 is provided for connecting the shaft 17 with a drive shaft 33 extending down to the bottom of the housing 15 .Bolted to the underside of the housing 15 is a gear box 34 which carries a pair of fuel pumps 35, the pressure pump 36 and a recovery pump 37 . Sweeping and pressure pumps 36, 37 are driven directly by the shaft 33 . Fuel pumps 35 are driven through a gear train 38, 39 , 40, 41 carried within the gearbox 34 .Therefore, it is seen that the starter motor 29 and some accessories 35 , 36 and 37 are coupled to shaft 17 by a gear train (located within the inner wall of the housing 15 ) and the axles radially arranged 28, 33 . Inner and outer walls of the housing 15 are interconnected by a series of hollow radial arms 42 and each of the shafts 28 , 33 passes through one of said arms . The arms 42 are streamlined in the direction of air flow from the compressor to the combustion chamber .With the described arrangement , when it is desired to start the engine starter motor 29 is operated to drive the shaft 17. As a result , the compressor temperature HIGH - pressure turbine 13 and 5 may be rotated while the engine accessories 35 , 36 and 37 are actuated . These accessories include startlng and essential for engine operation. When starting the combustion of high pressure turbine 5 starts driving the compressor 13 and engine accessories . Thus, the starting operation takes gently on the impeller 5 : At the same time, the turbine 6 begins to drive the low pressure compressor 12.Incorporated in the coupling between the starter motor 29 and the shaft 17 is a known construction of free-wheel device to ensure that when the impeller 5 is set in motion the shaft 17 is free to run over the starter motor 29.It is preferred that aircraft accessories not to be taken to start the engine as this requires a larger starter motor horsepower .Accordingly, aircraft accessories are mounted on a gear box supported by a portion of the aircraft convenient and driven by a radial shaft connected to low pressure shaft 18. Such arrangement is shown schematically in Figure 1 in which the aircraft accessories 43, 44, 45 and 46 are carried by a gearbox 47 which is driven by a shaft 48 . The latter is coupled to shaft 18 by a gear train generally indicated at 49 -, - the shaft 48 passes through a hollow radial arm 50 which connects the inner and outer walls of the duct 14.When the turbine i begins. turbinewill operateunderits own power to low pressure is . implemented to boost compressor'll as indicated above . When this happens the whole enginelas power delivery is so wide . J is then available. to conduct . aircraft accessories 43-47 . iii The arms 42, 50 that extendacross walls of the housing and direct the conduit '14 respectively . airaxially through the engine , it is necessary that the circumferential component cira theair ofmovementof out . the compressor 13 and reduce orfeliminated . to .. this "reason of . output . of theicompressor . 13 is provided with two rows of stator. Vanes51 , 52 ( see - Eigurefi ) lying one immediately behind the other . La . statorvanes 51 reduce the circumferential component and direct air . really along an axial path wheretheprocedure in'tofrow 52 repeats. Leaving the air. Thecompressoriassembly 8 engine flows substantially longitudinally .Dos. stator rows . vanes 51, 5.2tare provided to straighten the flow of air from the circumferential component to be eliminatedislarge . Provisionofztwo th blade rows in such aLconditiondoes . The'compressor adiversely Afiect not efficien'cy'as whenansingle straightening blade row is provided . 
The provision of two rows. Stator . vanes has the advantage that the two rows of blades can be relatively adjusted so that to ensure the most efficient flowiof ainthrough palettes. For example, it may be more advantageousto . the downstream rowofvanes space . theupstream circumferential row of vanesso vanes52 found between the vanes 51 centrallyor the contrary. With this arrangement also higher. spacing . such vanes and allowed for . the combined effect is . - That the air flow is turned in the axial direction with less loss than if provided asingle row of blades ;It is understood that the invention is not'restricted a gas turbine engine compressor having low axial flow and'highpressure . -8 Theasse'rnb1y may consist of a axial -flow compressor in the low pressure delivery of a high pressure centrifugal compressor , or alternatively, may consist of a low pressure compressor axial flow gives andcentrifugalcornpressor acombinedaxial .
We claim :

1. A gas turbine engine for the propulsion of an aircraft comprising a multi-stage turbine , a compressor stage multistage each of which is independently powered by a turbine rotor , compressor and turbine that has a common rotation axis and spaced longitudinally thereof, combustion equipment in the space between the compressor and air turbine cornpressor tojreceive and to deliver products of combustion to the turbine, accessories needed for engine operation operation, it is driven by the high pressure compressor , accessories necessary for operation of the aircraft , said accessories being driven by the rotor of the turbine to a low pressure compressor , a starter motor to drive said compressor only high pressure and engine accessories , yun shell that surrounds the engine provided with a waist portion having an outer diameter smaller than the diameter over- all was said , shell , said said starter motor and engine accessories are arranged around waist , he said. portioinof shell that is positioned substantially in diameter on - all out of the shell.Two . Argas turbineengine as claimed in claim 1 characterized by, that said comprises a housing waistportion air duct connecting the high pressure compressor to said combustion device , said housing has concentric inner and outerwalls and radialarms extends through the walls, atleasttwo ofsaid armsbeing ' each recess for receiving a shaft connecting said starter motor and said engineflaccessories the drive shaft between the high pressure - turbineand its compressor.

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