Description
April 4, 1950 - A. T. Nabstedt ETAL 2502799GEAR REYERSING Filed March 15, 1947 6 sheets leaves August 1, 33 July 1950 AT Nabstedt Brak'ymderaa E'IV'AL Ap Q 2502799Investment Mechanism 6 Sheets - 2 Sheet Filed March 15, 1947 113 [ll / DXT I f M In my n : 1 mik \ 1 / magnet April 4, 1950 AT -T ETAL NABSTED REVERSE GEAR 6 Sheets - Sheet 4 filed 15 Ap 4 March 1947 , 1950 . A. T. Nabstedt ET AL 2502799' GEAR INVESTMENT Filed March 15, 1947 I Sheet tabs Nabstedt s April 1950 AT ET AL 2502799INVESTMENT GEAR Filed March 15, 1947 6 SheefS sheets 6 patented April 4, 1950 reversin T GEAR Arthur T. Nabstedt , Hamden , and John 0 . Berndtson , Short Beach , Conn., assignors to snow - Nabstedt Gear Corporation , New Haven , Connecticut , a Connecticut company Application March 15, 1947 , Serial No. 734 974
2 Claims .
This invention relates to reverse gear , and particularly those for use in connection with marine engines , although the invention is not limited in this respect.One object is to provide a reverse gear compared to previous devices of this kind takes up less linear space in the boat and is lighter in weight in comparison with the transmitted power .I further object to provide a device of this type in which the structure is of the utmost simplicity and maximum accesses . the most likely to require access.Another object is to provide a reverse gear having improved performance means the type of fluid pressure , the fluid pressure means to be either gaseous or liquid .Another object is to provide a controlled fluid device of this kind which requires a minimum number of joints that operate in connection with a rotating member or members Preventin order to exhaust control fluid , such as air or oil .A further purpose of the invention to provide an improved arrangement and simple means for Fluidcontrol brake clutch and a reverse gear , and to improve the organization of the parts of the reverse gear .In the accompanying drawings :Figs. 1 and 2 are views that collectively show a reverse gear embodying the invention , vertical longitudinal section , being the parties to the forward drive position ;. Figure 3 shows , on a larger scale, and in sectionsome of the parts shown in FIG . 1, the clutch , however , being in the disengaged position ;. Figure 4 is a detail plan view of the brake means in relation to the gear assembly , showing the brake band in the braking position ;. Figure 4 is a fragmentary end view of the band - . Mechanism of the clamping lever shown in Fig . 4;. Figure 5 is a line section of Fig -55 . 1;. Figure 6 is a detail longitudinal section of the sealing means used in connection with the drive shaft ;. '7 figure is a schematic view showing the arrangement of the internal gears and pinions of the gear assembly Figs. 8, 9 and 10 are somewhat schematic sectional views showing the operation of the fluid valve is illustrated in Fig . 2;Figs. 11 and 12 together show a vertical longitudinal section of a modified form of reverse changes , the clutch is in the engaged position ;. 13 is a sectional view on an enlarged scale showing parts shown in FIG . 11, the friction clutch , however , being in the disengaged position ;. 14 is a section along the line I l - J4 of Fig . 11; and. 15 is a schematic view of the gears and pinions of the gear assembly .The gearshown invest in the figures. 1 and 2 comprises a housing , the left end of which is intended to be mounted adjacent the flywheel end of a marine engine , and within the housing is a reverse gear having the end portion adjacent to marine engine of a friction clutch having an outer member rotates continuously from the engine shaft , said friction clutch being concentric with a drive shaft which extends centrally and longitudinally of the housing , the housing having at its end portion the right rear of a stub shaft driven from the drive shaft through a reduction gear and carry off the carcass of a coupling for a propeller or other decision- 01f . Within the housing and in close proximity to the friction clutch is a gear set having an external drum or band member and associated brake , the gear assembly being concentric with the drive shaft. The friction clutch is actuated in one direction by a fluid pressure device , which in this case is located radially inward of the friction clutch and the brake band has associated with it a clamping device adapted to be actuated by a fluid pressure device . In the case illustrated the friction clutch is performed normally in the coupling position to provide forward drive , by a number of springs used in the clutch structure , and the band brake relative to the gear assembly is usually in a released position . A dispensing valve connected to the pressure device mentioned above and a fluid with a suitable source of pressurized fluid may have one of its members easily moved by hand to a position where the friction clutch is moved by the means pressure to the disengaged position for the placement of the investment team at a standstill ;and when desired, the mobile element of the control valve can be shifted to cause the clamping of the brake band such that the shaft can be rotated in the reverse direction .In the drawings, the housing is shown in A, the central drive shaft B, the driven shaft displacement has the power take- 01f , in C, the reduction gear between the two axes in D , the clutch E friction in the gear set to F , and the braking device associated with the gear iband fixed G. the fluid pressure device , which relatively large or obtuse . from the axis B, as described below , in this case acts to release the friction clutch ,is generally indicated at H, the same having a fluid supply conduit within the B axis , as described below, and which is controlled by manipulating external valve controllin I i connections to the pressure source fluid . thefluid pressure device to tighten the brake band is generally indicated , J , and this has operated valve connections I, as described below .The drive shaft B is a suitable bearing in the rear end portion of the housing A,and at the front the axle is supported by the engine speed up the'reversing is associated. The housing has a front wall 2! flywheel'ofthe positioned adjacent the engine , a portion of which is indicated in the flywheel February 2 , andthe flywheel is suitably connected , as by fasteners 23 , to a rotating disk or strip 24 . This disc or band has a portion located forwardly of the wall 2 | , and a portion disposed within a wall aperture 25in 2 | , and a further part 21 in a hubinto theshape extending the shaft forwardend - B . The hub portion - as 21 is hollow and provided with a transverse wall or'partition - 28; . providing a recess cupshaped accommodate an antifriction bearing 29 , the'outer race of which engages the portion 21 and the inner race of which engages the forward end of the shaft B.The disc or drive band 24 is arranged to rotate the outer member of the friction clutch E, outer member - which is arranged inside the front end portion of the housing and is a member interiorly round chamber enclosing the inner member theclutch and enclosing the fluid - pressure device H, and having a front wall attached to the disc 24 , and a back wall or web rotatably supported with respect to axis B , and a member operatively connected to the gear assembly F , as described below . thethe front wall of the outer clutch member indicated at 30 , and this wall is provided on the front end with a flange 3 | conveniently connected peripheral portion of the wall or web 33 . These walls provide a whole , hollow member having opposing inclined friction surfaces 35, 36 which cooperates with separate parts 31, 38 of the inner clutch member , the parts 31 and 38 having opposed conical surfaces 39 and 49 provided inclinedouter material suitable coating and adapted to engage the surfaces of the inner cone of the outer clutch member . The inner clutch parts are driven by helical springs - 4 | positioned between them and received in matching outlets 42, said springs tend to separate the inner clutch parts - and to hold them in firm engagement with the friction surfaces outer clutch member . The clutch. parts 31, 38 are ring-shaped parts is referably internally chambered for cooling purposes ; These portions have their surfaces arranged to provide friction between the angle of which is related theman These parts are mounted so as to be freely slidable , in an axial direction with - respect to each other and the shaft in its axial movements '38 . from Figure 3, the front end of the shaft section 44 limits, the arrangement being that when desired sucn release the clutch the fluid pressure device H can be put into action to is provided with a flange 41, and the rear end section " 43 with a'flange 48, the flanges being interconnected'bythe bolts 45, and said flanges provided at conjunctionarecess 49 receive a flange 50 formed on the ring member 46 . the flange 50 is carried held in this recess by means such as screws 5 | .. flange 50 projecting radially inwardly from the rear end of the ring member 45 the radially outer surface of the ring member 46 is provided with a plurality of splines5'2 ' hooked with the corresponding slots 53 and 54 formed'upon radially inner faces of the clutch members theinner .The device H is fluid pressure " and arranged'in constructed so that , when introducing the pressure medium in a pressure chamber arranged between two pressure members axially movable pistons or thedevice , therear MOV - ' element clutch 38 will be able to move in a forward direction , and the element 31 theforwardly'located moved in a rearward direction in order to release the " clutch . " With this view in theconstruction and arrangement of the fluid pressure device is preferably as follows : it leaves enough anti- frictionbearing betweenthe 29 and the flange at the rear end of the shaft section forwards movement to accommodate pressure members 55 oppositely and 56 disposed around the shaft forward section having seals devicesor contacting said packing section in its periphery. Section44 principal axis - is provided with an axial feed line 51 . in communication with a supply conduit 58 in the short axial portion 43 , and forward closed nearthe Passages'59 end'of Etlateral step . lead'to the exterior'of the struc ' --- ing axis and space fluid pressure . an.annular '60 between members 55 and 0.56. The pressure member 55 has an inner sleeve portion directed forwards 6 | provided with suitable package material 62 . held in contact with the shaft surface with'the .The pro wall member55 has'a'transverse part - packing provided inside 63 'instead of a plate or plates 64and 65 screws . The B3 packaging: free'e'dge has committed to a cylindrical surface 6'6 previews. a cylindrical wall portion 61 member56 pressure . Pressure member 56 is provided at its radially inner portion with a sleeve portion 168 - extends therefrom forward and provided with packing material 68 * , and the member 56 - having a transverse wall parallel to the transverse wall ofzmember55 , thefirstmentioned . transverse wall . wallportion being integral with the cylinder 35 ' . The pressure element 55 ishalsoprovided with a cylindrical outer wall portion , the same being'indicated at 59 , and it extends in a forwarddirec tion of: so'asto pressure'm'ember be inside and inzcontact - part withthe cylindrical wall of the other pressure member , the arrangement being'such - the : pressure members telescope, with a pressure chamber provided between them,packing and preventing any escape of fluid between ' the memberswhere outwardportions the'radially make contact with each ansoavea 5' . another , and each member of the pressure of being free. slide axially relative to the other pressure member .Members 55 and 56 are provided at their front ends with flanges I and II, respectively, arranged in transverse planes , the flange II is disposed forwardly of the clutch section 31 and is adapted to contact with said section in the radially thelatter inward . The cylindrical wall portion of member 56 is disposed - immediately raises into the toothed member 46, described above, said tooth member having a smooth cylindrical inner surface to help guide the pressure element 56 . While flange II is adapted to move the clutch 3'1 section in one direction, a change of the clutch section 38 in the opposite direction is carried out by a ring member adapted to contact I2 with section 38 in the radially inner portion thereof, I2 ring member is engaged at its rear face by I3 nuts screwed onto the rear ends of the bars - I4, which bars can be moved freely in holes I5 I2 provided in the ring member. The rods 14 are in a number of circumferential locations relative to the pressing member 55, and pass through holes in the flange 16 is , and the nuts 11 are screwed onto the rods forward flange I0 . I4 rods also pass through the holes in the flange and through I8 II I9 suitable holes provided in the toothed member 46 .Gear assembly F , mentioned above , is placed around the axis B to a location immediately to the rear of the band member 33, described above. In this case, the gear assembly is driving and driven internal gear , being similar to one of the gear assemblies shown in Nabstedt patent No. 2,286,223 of 16 June 1942. This set of changes has a driving gear 80 and a driven gear 8 | , the structure includes a pinion box having a drum 82 is surrounded by outer brake band G ' and having end walls which are mounted between the long pinions and short and meshingwith willing to engage the respective internal gears as described in the aforementioned patent . Internal drive gear 80 is directly connected to the network 33 in a suitable manner , as by bolts 83 , being connected in an intermediate region between the edges or boundaries of the inner and outer side , and the shouldered portion web be directly engaged with the internal gear . The driven internal gear 8 | is rigidly connected by a flanged hub member 84 with the axis B, the said hub being keyed to the shaft , as shown at 85 , and the antifriction bearing rearmost gear set 86 is supported on a portion of the hub. The front anti-friction bearing 81 0f the gear assembly is coupled to a cylindrical portion of axis B, and immediately before the anti- friction bearing 81 one similar anti- friction bearing 88 is provided on this part of the shaft in a manner to support the inner edge of the web 33 .G brake mechanism 89 comprises an elastic band wrapped with suitable friction material and embraces the drum 82 of the pinion cage that is in close association with their ends to a tightening mechanism consists of a lever mechanism driven by the J device fluid pressure , the fluid pressure device being operatively connected with the control valve I. In this particular embodiment , the device J fluid pressure is mounted within the housing on top of the latter, and is adapted to apply the brake, when it is desired the application of the brakes, by imparting a thrust to . mechanism of the brake lever to tighten andwhich the pressure device is located rearward of the brake band , and the lever mechanism suitably constructed for the purpose intended . The fluid pressure device comprises a fluid pressure cylinder 90 , disposed longitudinally ' ally with respect to the housing and contains a piston 9 | provided with suitable packing material 92 . One side of the cylinder is exposed on the outside of the casing, and this side is provided with an inlet passage 93 that leads into the cylinder , said inlet passage is connected to the valve I by means such as a flexible tube 94 . The piston 9 | is prevented from tilting in the cylinder by the arrangement of a pin 95 disposed rearwardly of the piston rod which slides in a socketed portion 96 provided on the rear wall of the cylinder. The piston is also provided with a cylindrical portion 91 that protrudes forward , the front face of which is adapted to make contact with the lever mechanism mentioned above for the purpose of applying the brake. Lever arrangement for tightening the belt is generally of the type described in Patent No. 2,370,484 Nabstedt of 27 February 1945, thebrake band itself is supported resiliently in the release position . In this example , -However, the gripping action is ensured by a thrust on the primary clamping lever , and , moreover , the arrangement is such that the pressure device can not force the lever mechanism beyond a neutral position , and can not , therefore , block the brake. In the present example , one end of the band is provided with an upright lug 98 and the other with a stud 99 which has loaded a clearance hole I00 receive the threaded pin which is provided on the outer side of the tab with nut IOI . The clamping lever primary band shown in I02 , and this lever has one end pivoted on the I 03 at a kerf provided at the inner end of the plug I00 . At its opposite end to I02 to I04 lever is pivoted to a duplex secondary lever I05 .I04 is pivot at one end of a lever I05 , and at the opposite end of the lever has a swivel connection on the pole tion 99, as shown in Nabstedt Pat . -ent No. 2,370,484 . On the top of post 99 is a pivot block I-06 having an opening therein in which slides a rod I01 is connected to an I08 projection provided at the upper end of the member pivotally connected with lever pin I00 I02 clearance . Among projection I 08 and I-06 block a coil spring I01 I09 embraces the stem.. Figure 4 shows the piston device J projected forward to the maximum , and it will be noted that in this position the piston has moved the lever to an extent sufficient I02 togive full brake application , but the pin has not yet I04 reached a neutral position . As shown , this position can not be reached by the fact that I05 lever has a curved edge portion forward. I II 0 abuts the post 99 in order to prevent further aging oscillation flat face of the extension of the piston,with the friction clutch and brake.impressive weaand the . Hello portion is located: laterally from the 1. pivot. I 0.4.Inorderto holdthebrake 89 band . in. position . while the device - is thefluid thrust exerted pressure on the lever mechanism , the adjacent . end of the strap is secured . against ; dislocation forexample , producing post 99 extends upwardly into . an opening : a fixture : plate. 99% .carriedby the housing. Some . cases the result samev . could be accomplished by protecting the pressure device rigidly to the brake band .Theipassage o: duct 51 " on . Axis 13 leads . The'shaft the rear end , and adjacent to the rear end . Shaft sealing device is generally indicated in H2 , it is connected to . The I by a valve hose H3 . H2 the sealing device is located within a removable cover H4 therear applied to the wall of the housing. the sealing device may comprise a cylindrical housing which is H5 . supported stationarily and receives internally a tubular member which extends rigidly from the shaft B and in communication with the passage 51 . as shown , tubular member " H5 held rigidly in position relative to the shaft by means of a threaded bushing H.1 - screwed into a socket in the shaft end. H6 tubular member has an extension or H8 head whose periphery in engagement with the rotating inner surface of the housing H5 . the left end (Fig. e) of casingis equipped with a closing plug 19 provided with suitablev I I20 packaging and anti - bearing friction .l2l , I22 are conducted . instead. between head H8 'and hub H1 . Between the head and H8,the right. end ; the housing; (fig. 6) A spring is interposed I23 . Benoted is that the arrangement is such that when the shaft rotates , thewhile at the same time maintaining the communication between the stationary pipe or tube thepassage H3 and the shaft.Control valve may have any preference.. thesequential suitablefor form . Operation of devices associated fluid pressure can be assumed respectively . the fluid is pressurized . liquid, such as oil, and both drawings schematically illustrate a control valve adapted to handle a fluid under pressure . This valve has a round housing that encloses a body 124 of the rotary valve 25 adapted to be converted. I26 by a suitable handle . The casing is connected in an image point of its circumference to a pipe '27 inletv 3 which leads to a source of liquid under pressure, and other points of its periphery is connected to housing thev hoses 94 and H3 , supra and an exhaust pipe or tube I28 - by rotating the valve body . positionsshown three different figures . 8, 9 and 10, the necessary engagement with the outer element of the friction clutch , and the clutch outer member is driven by the motor and transmits rotation to the axis B through the connection sections slotted clutch hub structure'at ' the front end of the shaft. The outer clutch member 8 carrieswith her . Through his connection "with the internal gear 80 of partsof turn the gear set including drum gear assembly that rotates freely inside the brake band . Under these conditions , with rotating parts gear'set as above, the gear train has a actionsimilar tothat of a flywheel . pressure device H , under these conditions , it has the position shown in Fig . 1 ' when parties thisposition one rotatable shaft B , which is non -rota - and connected Tivel members axiallymovable pressure . H device via the connections described above , including the tie rods or tie bolts'passing through these members and through the radially outward from the hub as a structure on which are mounted axially movable clutch elements . device J pressure under these conditions is shown in position - Fi'g . one valve I, being in the posithan of Fig . 8 the fluid supply connections from the valve to the clutch and brake device is in communication with the exhaust pipe and through the inlet pipe 21 which is connected to the pressure source fluid is closed by the valve body .To put the reverse gear in the neutral position , it is necessary to support the device for pressure without admitting pressure to the device H of J. This valveto achievedby converting the position shown in Fig . 9 wherein the inlet of the pressure source is connected to the'device H, J device , on the other hand, is connected to the exhaust . When pressure is admitted to the device H, the interior conical clutch elements are brought towards one another by'the forward movement : from the rear cone section and the rearward movement of the front cone section or forward . . Figure 3 shows the positions in which the cone members are moved by the removal . As illustrated , the release movement of the cone sections is limited by its coming into contact with each other on their adjacent surfaces , as shown in Fig . 3 - , but in some cases the movement may be limited by other means. The opposite movement of the cone sections of the disengaged position inthe engaged position is caused by the movement of the pressure members and 56 when pressure is introduced influenza -
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