AU427217B2 - Improved vehicle transmission - Google Patents

Description

This inventi~n i concerned S with an improved vehicle transmission, an Yore particularly with a Power shift transmission having two planetary gearsets, and countershaft gearing driving gears on input and output clutch housings. Clutches carried on said housings are selectively engaged and disengaged with elements of- the planetary gearsets to provide a plurality of speed ratios through said transmission. Draft vehicles use an internal combustion engine primarily as the source of power. The internal combustion engine operates with greatest efficiency within a predetermined speed range and the engine will-also deliver the required torque characteristics within a predetermined speed range. The vehicle transmission is designed to provide smooth transmission of power to carry the draft load. The magnitude of the draft load and the speed at which the load must be drawn vary widely and. in the case of a tractor, the transmission should have a- plurality of speed ratios to accommodate the varying speed and torque requirements for greatest efficiency interna combustion engine on the and versatility of operation. The torque converter is used on many vehicles and will provide an infinite number of.speed ratios for transmitting power. A torque converter, however is expensive and there is a certain amount of power loss due to fluid friction in the torque converter. Its use also may cause a-wide variation in vehicle speed %Then loads .are imposed which is detrimental to accomplishing satisfactory power takeoff work. There are, therefore, inherent advantages in.use of a direct gear drive power

2 4-27217

16,153 70 of speed ratios ransmission providing an adequate number the convenience of ire built into the transmission and is efficient shifting from one :peed ratio to another

and trouble-free. an It is an object of this invention to provide having two improved pover shift vehicle transmission gearing with a planetary gearsets and countershaft and output clutch plurality of clutches mounted on input on the ring gear, housings including friction elements planetary sun gear, or planetary carriers of said power paths and speed gearsets to provide a plurality of

ratios for the transmission. a According to the invention there is provided output shafts vehicle transmission comprising input and a first planetary rotatably mounted in a tr-ansmission casing, the input shaft, gearset having an input sun gear driven by an output sun gear a second planetary gearset having first planetary connected to the planet carrier of the a ring gear of the gearset for driving the output shaft, a ring gear of the first planetary gearset connected to ring gear, the second planetary gearset to form a unitary an input clutch housing ring gear optionally being integral, with the input rotatably mounted for concentric rotation mounted for concentric shaft, and an output clutch housing plurality of clutches rotation with the output shaft, a first on the input clutch housing and arranged, respectively, to the input sun for connecting the input clutch housing the ring gear, a gear, the input planet carrier, and output clutch housing second plurality of clutches on the the output clutch and arranged,respectively, for connecting housing to the output shaf?, J UpI planet carrier of the second planetary gearset, and the output'sun gear, a brake operatively positioned between the input clutch housing and the transmission casing, a drive gear attached to the input clutch housing, a driven gear attached to the output clutch housing, a countershaft gearset having gears connected to said drive and driven gears respectively, and means for selectively actuating two of said clutches or one of said clutches and said brake for providing a plurality of power paths of different gear ratios through the transmission.

Preferably, in such a transmission, when in operation, the input clutch housing is connected by a clutch of the first plurality of clutches to the ring gear, and the output clutch housing is connected by a clutch of the second plurality of clutches to the sun gear of the second planetary gearset, there is thereby provided two power paths through the transmission, the first power path being through the first and second planetary gearsets, and the second power path being through the countershaft gearset, wherein the transmission will provide a reverse speed which is the resultant of the difference -between a positive torque supplied to the sun gear of the second planetary gearset through the countershaft gearset and a negative torque delivered from the ring gear to produce a resultant reverse output of the output shaft.

Preferably, when in operation of the transmission, the input clutch housing is connected by a clutch of the first plurality of clutches to the ring gear, and the output clutch housing is connected by a clutch of the second

4 4.2- 2 17'

6153 /70 planet carrier of tho second plurality of clutches to reaction planetary gearset, there is thereby produced carrier of the torque on the ring gear and the planet and positive second planetary gear set which is additive gearset, so as to to the sun gear of the second planetary a high numerical provide thereby a forward speed having

torque ratio-on the output shaft. transmission, Preferably, when in operation of the by a clutch of the the output clutch housing is connected planet carrier of the second plurality of clutches to the clutch housing is second planetary gearset, and the input said brake, there is restrained from rotation by action of the planet carrier thereby produced a positive torque on positive torque from of the first planetary gearset and a second planetary the ring gear to the sun gear of the torque output gearset, so as to provide thereby a positive

of the output shaft. Preferably, when in operation of the transmission, of the the input clutch housing is connected by a clutch and the input first plurality of clutches to the ring gear, of the clutch housing is restrained from rotation by action brake, there is thereby provided a simple planetary to said reduction through the first planetary gearset _output shaft. Preferably, when in operation of the transmission, of the the input clutch housing is connected by a clutch the first plurality of clutches to the planet carrier of housing is first planetary gearset, and the output clutch .connected by a clutch of the second plurality of clutches to said planet carrier of said second planetary gearset,

427217'

16,153. 170 there is thereby produced a positive torque'transferred to the planet carrier of the first planetar gearset and a positive torque on the sun gear of the second planetary gearset so-as to provide thereby a positive torque on the output shaft. Preferably, when in operation of the transmission, said input clutch housing is connected by a clutch of the first plurality of clutches to the planet carrier. of the first planetary gearset, and the output clutch housing is connected by a clutch of the second plurality of clutches to the ring gear, there is thereby produced a positive torque on the planet carrier of the first planetary gearset and a net positive output of the transmission.- Preferably, when in operation of the transmission, the input clutch housing is connected by a clutch of the first plurality of clutches to the sun gear of the first planetary gearset, and the output clutch housing is connected by a clutch of the second plurality of clutches to the sun gear of the second planetary gearset, both planetary gearsets are thereby rendered inoperative and the countershaft gearset transmits power from the input shaft-to the output shaft. Preferably, when in operation of the transmission, the input clutch housing is connected by a clutch of the first plurality of clutches to the sun gear of the first planetary gearset, and the output clutch housing is connected by a clutch of the second plurality of clutches to the planet carrier of the second planetary gearset, there is thereby provided an output torque which is the'

6- 4,27 2 17'

16153 P0 3um of resultant torque of the sun gear of the second planetary gearset and the torque of the planet carrier Df the first planetary gearseto Preferably, when in operation of the transmission,

the input clutch housing is connected by a clutch of the first plurality of clutches to the sun gear of the first planetary gearset, and the output clutch housing is connected by a clutch of the second plurality of clutches to the ring gear, there is thereby provided an output torque in said transmission which is the sum

of the resultant torque of the ring gear torque from the- first planetary gearset transferred to the output clutch housing and the portion of the input torque applied to the nun gear of the first -planetary gearset. Preferably, Yhen in operation of the transmission, the input clutch housing is connected by a clutch of the first plurality of clutches to the sun gear of the first planetary gearset, and said input clutch housing is also connected

by another clutch of the first plurality of clutches to the ring gear, there is thereby provided a drive through the first planetary gearset which is locked to the output

shaft to produce a forward output of said transmission. Preferably, when in operation of the transmission, the output clutch housing is connected by a clutch of the second plurality of clutches to the sun gear of the second planetary gearset and said brake is actuated, there .is-thereby produced a braking torque .of said transmission to lock the transmission output shaft. Preferably said input clutch housing includes three clutches connectable respectively to the sun Gear, ring gear,

4 272 1T and planet carrier of said first planetary gearset, and said output clutch housing includes three clutches connectable respectively to the sun gear, ring gear, and planet carrier of said second planetary gearset, to provide in operation a transmission having nine speeds forward and one reverse. Preferably, when in operation of the transmission, the output clutch housing is connected by a clutch of the second plurality of clutches to the sun gear of the second planetary gearset, and said brake is actuated to lock the input clutch housing to the transmission casing, the input shaft thereby provides a power take-off drive, the clutch connection to the sun gear of the second planetary gearset and the actuation of said brake serving to provide braking of the output shaft while permitting the input shaft to rotate. Preferably the output shaft comprises a quill shaft, and the input shaft extends coaxially through the output quill shaft and includes means for providing a power take-off connection, and wherein, when in operation, the output clutch housing is connected by a clutch of the second plurality of clutches to the sun gear of the second planetary gearset and said brake is actuated, the input and output clutch housings are locked through the countershaft gearset thereby to lock the output shaft while permitting continued rotation of the power input shaft for power take-off. Thus the object of this invention is accomplished by the use of a power shift transmission using two planetary gearsets mounted for rotation on concentric centers and in series arrangement. An input shaft is connected to the

427217'

16,15370 sun gear of the first planetary gearset while the

output shaft is connected to the sun gear of the

second planetary gearset and the planetary carrier

of the first planetary gearset. The input drive shaft is adapted for clutching

to the input clutch housing which rotates about a

common axial center with the input drive shaft, and

the output clutch housing is adapted for clutching to

an output drive shaft and rotates about a common axial center with the output drive shaft. A countershaft. is mounted in parallel with the input and output drive shafts and has a gear driven by a gear on the, input

clutch housing and driving a gear on the output clutch

housing. A plurality of clutches are mounted on each

of said housings adapted for selectively and alternatively

engaging a frictionelement of the clutches on.the sun

gear, planetary carriers, and/or ring gear of their mating

planetary gearsets to provide a plurality of power paths

through said transmissions. The transmission operates

through a single planetary gearset, or through two

planetary gearsets in series, or as a combination of

planetary gearsets and countershaft gearing to provide

a plurality of speed ratios and torque output to

accommodate varying speed and torque load demands of

the vehicle.

The power shift vehicle transmission of the invention

is capable of providing nine forward speeds and one reverse

speed through the use of two planetary gearsets and countershaft gearing. The operator selectively engages and disengages clutches in the clutch housings driven

9 427217 bybyCuntrshft hec~uteshat16p te 153 170 o povide power transmission of nine speed ratio.s forward and one reverse. The'powe r shift transmission includes means for selective operation of clutches in the clutch housings for engagement with the elements of the planetary gearsets such as the surn gears, the planetary carriers, or the ring gear producing power paths through the planetary gearsets and countershaft gearing.

This power shift transmission provides a maximum. number of shift transitions employing a minimum number of cli tches. The clutches have low relative clutch plate

speeds in the forward ranges to provide minimum drag

losses and-accomplish smooth shift transition from one

speed ratio to another. The drive shaft, driven shaft,

and countershaft, together with the gearing, ar e supported

by the end walls of the transmission casing which provide

adequate support. The same ring gear is used for both of tha twio planetary gearsets to simplify drive from the

first to the second planetary gearset.

The invention will now be described in detail and is

illustrated, by way of example, in the accompanying drawings---

to427 217' in which: 16153,I70 Figure la shows the input end of the transmission. Figure lb showis the output end of the transmission.

Figure 2 is a schematic illustration of'the transmission.

Figure 3 is a table showing gear ratios of the

transmission and -indicating the clutches engaged to obtain-

each gear ratio forward and reverse.-

The transmission as shown in Figures 1la and t~is

adapted for use In a draft vehicle such as a tractor.

The transmission is positioned between the internal

comblustion engine and the differential on the-tractor with

the shaft 4 driven by the engine. The shaft housing 1

is fastened to the transmission case 2 by means of a

plurality of bolts 3. The housing 1 rotatably supports

the drive shaft'4 which extends through the transmission

case 2 and is splined at 5 to operate as a live constant

speed power takeoff if so desired.

The input drive shaft 4 is rotatably mounted in

the seal assembly 6 which is embraced by the end plate 7

fastened to the housing 1 by means of a plurality of

bolts 8. The housing 1 is also formed with annular.

recess 9 which receives the bearing assembly 11 for

rotatably supporting an input clutch housing 12,. The input

clutch housing 12 is also supported by bearing assembly 13

received within the annular recess 14 in the housing I. _The.. 1. 427 217T inpt riv saf 4is input drive shaft 4 is 16 1531(7b rotata61y mounted in the bearing assembly 15 which is held by the snap rings 16 ih the outer periphery of the input drive shaft 4 and Clutch housing 12 to provide a rotatable relationship between the input clutch housing 12 and the input shaft 4. The input drive gear 17 embraces the input clutch housing 12 and is fastened thereto by means of a plurality of bolts 18 which also fastens the brake hub 19'to the Input clutch housing 12. The brake hub 19 is formed with a spline 21 on its outer periphery adapted for receiving.aplurallty of rotatable brake discs 22. Interposed between the plurality of brake discs 22 are a plurality of stationary brake discs 23 fastened to the housing 1. The brake discs 22 and 23 are annular discs concentriL to the axis of the input drive shaft 4 and adapted for axial movement to frictionally engage each other or run freely in side- 'by-side relation when the brake is not engaged. The brake 10 is operated by an annular piston 24 defining an actuating chamber in the housing 1. When the brake 10 is actuated, the brake hub 19 is braked to a stationary condition relative to the housing I whic defines the annular cylinder for receiving the annular piston 24. The input drive gear 17 drives the gear 26 wiAch is fastened to the countershaft 27 by means of a spline connectlon. The countershaft 27 is rotatably mounted in the bearing assembly: 28 mounted in the housing 1. The bearing assembly 28 is held in position on the housing I by a snap ring 29. The seal plug 31is-- mounted stationary at the front end of the countershaft 27 in the housing 1. The bearing assembly 32 is mounted within the transmissic case 2 and retained by the snap ring 33 on housing 2. Retainer ocknuts-34 on-the-ends-ofthe_ countershart 27- clamp- the gears 26 and 35 and inner races of bearings 28 and'32 so as to prevent a loose relationship relative to the countershaft 27. The 12 427217" untershaft 27 is splined 67 15 3 170 'receive a mating splined pinion ar 35. The pinion gear 35 drives the driven gear 36 which fastened to the output clutch housing 37 by means of a-plur-- ity of bolts 133. A sleeve 38 is fastened to the gear case 2 means of a plurality of bolts 39. The external periphery of e sleeve 38 is embraced by bearing assemblies 41 and 42. The tput clutch housing.37 embraces the bearing assemblies 41-and and is rotatably mounted for rotation upon a common axial nter with the input drive shaft 4 which extends through the ar case 2.

The inner periphery of the sleeve 38 is formed with nular recesses 43 and 44 to receive the bearing assembly d the needle bearing assembly 46. The ball bearing assembly and the needle bearing assembly 46 embrace the quill output aft 47. The input drive shaft 4 extends coaxially through the ill shaft 47 and the needle bearing 48 is positioned intermediate e outer end of the input drive shaft 4 and.the quill shaft 47. e inner end of the quill shaft 47 defines a recess 49 which re- ives the needle bearing assembly 51 to- maintain concentric ro- tion .of the input drive shaft 4 with the quill shaft 47. The ill shaft 47 is splined on its end to provide a suitable drive

ans to the output drive of the vehicle.

The output clutch housing 37 is constructed with a Lurality of hydraulic actuators inzluding annular cylinders and Istons and pressure plates for engaging a stack of clutch discs. aferring to Fig. Ib, the output clutch housing 37 defines an inular cylinder 51 which receives a piston 52. The cylinder 51 ad the piston 52 define a pressu-zing chamber 53. The piston 52

ampresses the disc stack 54 against a reaction portion 55 of cylin- sr 62 when the clutch is actuated. A -plurality of clutch discs are splined on the inner periphery thereof and are'received on ne mating spline external periphery 57 of the clutch hub 58. The 1 427217 clutch hub 58 also defines a spline connection 59 on its inne periphery for engaging the spline 61 on the external peripher3 of the quill shaft 47. Accordingly, the drive connection thrc the countershaft 27 is connected to the output shaft 47 when t clutch 70 is engaged. The output clutch housing 37 carries th clutch 60 which is defined by the annular cylinder 62 which re ceives the annular piston 63 defining a pressurizing chamber 6 The planetary carrier 66 of the planetary gearset 75 forms a splined external periphery 67 which is embraced by a plurality of clutch discs 68 which have mating splined internal peripheriE Intermediate the clutch disc 68 Is-a plurality of discs 69 whic are received on the spline 71 of the cylinder 62.- The reaction portion 73 is positioned on the opposite side of the discs from the cylinder 62. The output clutch housing 37 also includes an annular cylinder 7. which receives the annular piston 175 which in turn defines a pressurizing chamber 76. The ring gear 77 for the planetai- gearset 65 and 75 is integral and forms a splined external periphery 78 whfch receives aplurality of-clutch discs 79. Interposed between the clutch discs 79 is a. plurality of clutch discs 81. A reaction plate 82 is received within the inner periphery of the cylinder 74 and lacked in place by snap. ring 176. Reaction plate 82 provides a means for supportingly compressing the discs stack of the clutch 50 when the clutch is engaged..

Flanetary gearset 65 also is connected to a plurality of clutches on the input clutch housing 12. A clutch hub 83 is connected by means of a splined connection 85 to the input drive shaft 4. The clutch hub 83 has a splined external periphery 86 which receives a plurality of discs 87. Interposed between the discs 87 are a plurality of discs 88 connected to the input clutcl housing 12. The input clutch housing 12 defines annular hydrauli( 14 -4272 17

1.6 3 17o 90 defining the cylinder 89 which receives in annular pi3ton pressurizing chamber 91. When the clutch is actuated the of the clutch piston moves to compress the disc stack by the annular hydraulic against the reaction plate 92 formed cylinder 93. the annular The annular hydraulic cylinder 93 receives chamber 95. The planetary piston.94 which defines a pressurizing 65 forms a spline 95 to re- carrier 84 of the planetary gearset spline discs 97 engage ceive mating spline discs 97. The mating cylinder 93 of the input the discs 99 which are connected to a 100 forms a reaction clutch housing 12. The'hydraulic cylinder plate 101 for clutch an annular piston The hydraulic cylinder 100 receives 103. The ring gear 77 102 which forms a pressurizing chamber 105. A. plurality of discs. is embraced by a plurality of discs discs 105. The reaction 106 are positioned intermediate the inner periphery of the cylinder plate 107 is received within the 108. 100 and locked in position by a snap ring 6 a sun gear 110 which .The planetary gearset- 5 includes received on the mating issplined on its inner periphery and the external periphery of splined portion of the spline 111 on 110 meshes with a plurality the input drive shaft 4. The sun gear on a pin 113 in the carrier 84. of planetary gears 112 each mounted the ring gear 77 which is in- The planetary gears 112 mesh with planetary gearset 75. The plan- tegral with the ring gear for the supporting annulus 115 which- etary carrier 84 includes a carrier a mating spline portion of the is splined at 116 and embraces provides quill output shaft 47. The carrier supporting annulus 115 gearset 65 to the quill a drive from the carrier of the planetary drive shaft.. shaft 47 which is the transmission output a sun gear 117 The planetary gearset 75 also includes mating portion on the quill splined at 118 and embracing a splined oq 17' 15 s .4272 41

_L output shaft 47. The sun gear 117 meshes with a plurality of planetary gears 119 each mounted on a pin 120. The pins 120 z supported in the carrier 66 which carries the clutch discs 68. Planetary gears 119 mesh with the ring gear 77 which has gear teeth 121 on Its inner periphery. The ring gear 77 1 supported by an annular support 122 locked in the position sho in Fig. la by snap rings 123 and 124. Annular support 122 is supported on the bushing 125 carriled on the support annulus 11! The annular support 122 is free to rotate relative to the quil: output shaft 47 and the input shaft 4.

Referring to Fig. 2 the power shift transmission is shown schematically. The brake 10 Is connected to the housing for braking the input housing 12. The input housing 12 carries the gear 17 which meshes with gear 26 on the countershaft 27. The countershaft 27 also carries the pinion gear 35 which meshe with the driven gear 35 on the output clutch housing 37. The input drive shaft 4 is spllned to the sun gear 110. The planet, carrier.84 is splined te_the quill shaft 47 providing- the output drive from the transmission. -The ring gear 77 engages the plane tary gears 112 of gearset 65 and the planetary,gears 119 of gear set 75. The sun gear 117 of the planetary gearset 75 is also spllned to the quill shaft 47. The schematic illustration of Fig. 2 illustrates the operation of the transmission in a more simplified form and Fig. 3 illustrates the gear range and trans- mission speed ratios when the brake and clutches as Indicated arc actuated. The functional operation will be more completely described in the subsequent paragraphs.

The transmission as shoum includes hydraulic actuators for actuating the brake and clutches as shown in Fig. 2. A source of pressurized fluid Is provided by the pump 131 receiving the hydraulic fluid from thereservoir 132.. The pu.p 131 supplie pressurized fluid to the clutch and brake actuation -control 133, 16 427217

Fluid released from the a and clutches is returned to the reservoir 132 through the clutch and brake actua-

tion control 133. The lever 134 on the clutch and brake actuation control 133 is adapted to actuate the brake 10 and the clutches 40, 50, 60 and 70. Hydraulic conduits singularly connect the actuation control 133 with the actuator 130 of the brake 10 and the actuator 89, 93, 100, 74, 62 and 51 for the clutches. The actuation control is adapted to actuate any of these actuators singularly or in any combination to provide the gear ranges as shown in Fig. 3 when the clutches Indicated are actuated.

To shift the transmission to reverse, the clutch 70 and the clutch 40 are actuated, the input torque passes from the sun' gear 110 to the carrier 84 and to ring gear 77. The ring gear torque is then in a negative direction and is connected to the countershaft gear train by the clutch 40. This negative torque Is multiplied by the countershaft gears and transferred to the carrier output by means of clutch 70. The difference between the positive torque glyen to the carrier 115 by thesun gear 110-and the negative

torque given to the carrier 115 by the ring gear multiplied by the countershaft gears is a net resultant negative,torque to the output quill shaft 47 The transmission when shifted into first gear range for- ward as indicated'on the table In Fig. 3, will provide an Input torque which passes to the sun gear 110. Positive torque is trans- ferred to the carrier 84 and negative reaction torque Is transferred to the portion of the ring gear 77 meshing with the front planetary gears 112. This negative torque passes through the portion of the ring gear 77 meshing with the rear planetary 119 and contributes negative torque to the carrier 66. Torque on the carrier 66 is regenerated through the clutch 60 and the countershaft gearset and clutch 40 back to the ring gear 77. This results In a much higher

negative torque on the portion of the ring gear meshing with the rear plan- r l *17 4272 17;

.16,153170 etary gears 119 than the initial reaction from the front planetary gearset 65. The reaction to the total negative torque on the portion of the ring gear 77 meshing with the rear planetary gears 119 is positive on the sun gear.117, so this positive reaction is additive to the torque on the carrier 84 resulting in a high humerical torque ratio multi- plication on the output quill shaft 47. When the transmission is shifted into the second gear range the input torque passes to.the sun gear 110. The carrier 66 is held by the clutch 60 through the countershaft gearset and brake 10 which is grounded.. Torque on the sun gear 110 is transferred as a positive torque to the carrier 84 and negative torque to the ring gear 77. The negative torque on the ring gear is convefted to a positive on the sun gear 117 which adds to the torque on carrier 84 to give a total positive torque on the output quill shaft 47. With the transmission in the third gear range, the input torque passes to the sun.gear 110. The ring gear is held by the clutch 40 which is, in turn, grounded by the brake With the ring gear braked, a simple planetary reduction to the output quill shaft 47 is produced. With the transmission operating in fourth gear range, the input torque passes to the sun gear 110. The positive torqu is transferred to the carrier 84 and negative reaction torque is transferred to the ring gear 77. The ring gear 77 transfers pos tive torque to the sun gear 117 and negative torque to the carri 66. The negative torque on the carrier 66 is .passed by means of the clutch 60 to the countershaft gearset where it is reduced an passed to the clutch 30. The negative torque on the clutch passes to the carrier 84. The difference between the negative torque on the carrier 84 from the clutch 30 and the positive torque from the'sun gear 110 results in a net positive tor ue "8 4 22 1 7

-16.5 on the carrier 84 which adds to thepositive torque on the sun gear 117 of the second planetary gearset to give-a total positive torque on the output quill shaft 47. SWith the transmission shifted into fifth gear range, the input torque passes to the sun gear 110 of the first planetary gearset 65. Positive torque is transferred to the carrier 841and- negative torque is transferred to-the ring gear 77. The negative torque on the ring gear 77 is directly passed by means-of a clutch to the countershaft gearset where the torque is reduced and passed to the clutch 30. The negative torque on the clutch passes to the carrier 84. The difference between the negative torque on the carrier 84 from the clutch 30 and the positive--- torque from the sun gear 110 of the first planetary gearset results in a net positive torque on the output quill shaft 47. With the transmission shifted into the sixth gear range, the input torque passes to the countershaft gear train by the clutch 20. The input torque is multiplied by the countershaft gears and transferred to the output shaft by the clutch 70 which is connected to the sun gear 117 and the output quill shaft 47. The planetary gearsets have no function for this particular gear range and the power flows through the countershaft gear train. With the transmission shifted into seventh gear range, the input torque divides and passes partly to sun gear 110 of the planetary gearset 65 and partly to clutch 20. The portion of the input

torque given to the clutch 20 is multiplied by the countershaft type gears and transferred to the carrier 66 by the clutch A portion of the resultant torque on the carrier 66 becomes re- action for the torque on the carrier 84, and the other portion of the torque on'the carrier 66 is added to the sun gear 117 of the second planetary gearset. The output torque is the sum of the

resultant torque on the sun gear 117 of the second planetary gearset and the resultant torque of the carrier 84. 19 4 272 17'

S1 6 1 53/70 With the transmission shifted into the cighth gear the input torque divides and passes partly to suh gear 110 of

the first planetary gearset 65 and partly to clutch 20. The

portion of the torque given to the clutch 20 is multiplied by

the countershaft type gears and transferred to the ring gear 'by the clutch 50. The output torque is the sum of the resultant ring gear torque and the portion of the input torque going -to the sun gear 110 of the first planetary gearset. When h- the transmission shifts into the ninth gear, .the

input torque passes to the sun gear 110 of the-first planetary gearset and the clutch 20. The clutch 20 drives the clutch 40 which is connected to the ring gear of the first planetary gear- set 65. The planetary gearset 65 is thereby locked together by the clutches 40 and 20 giving a direct drive to the output quill shaft 47.

The transmission is also provided with an output shaft brake which functions in the following manner. For braking, the

torque to be braked passes from the output quill shaft 47 to the

clutch 70. This torque is then reduced by the countershaft gear-

set and transferred to the brake 10 which is grounded. This

braking function stops onlythe output shaft and countershaft-.

leaving the input shaft free to remain being turned by the engine

and to continue driving. a power takeoff load if so desired.

The preferred embodiments of this inv6ntion have been

illustrated and described wherein the transmission operates to

provide a reverse gear, a brake, and nine speeds forward for

selective operation of the actuators actuating the brake and

clutches.

427217'

16153 fo The claims defining the* invention are as follows: 1. A vehicle transmission comprising input and output

3hafts rotatably mounted in a transmission casing, a

first planetary gearset having an input sun gear driven

by the input shaft, a second planetary gearset having an

output sun gear connected to the planet carrier of the

first planetary gearset for driving the output shaft,-

a ring gear of the first planetary gearset connected to

a ring gear of the second planetary gearset to form

a unitary ring gear, the ring gear optionally being

integral, an input clutch housing rotatably mounted for

concentric rotation with the input shaft, and an output

clutch housing mounted for concentric rotation with the

output shaft, a first plurality of clutches on the input

clutch housing and arranged, respectively, for connecting

the input clutch housing to the input sun gear, the input

planet carrier, and the ring gear, a second plurality of

clutches on the output clutch housing and arranged,

respectively, for connecting the output clutch housing

to the output shaft, an output planet carrier of the second'

planetary gearset, and the/ gear, a brake

operatively positioned between the input clutch housing

and the transmission casing, a drive gear attached to the-

input clutch housing, a driven gear attached to the output

clutch housing, a countershaft gearset having gears

connected to said drive and driven gears respectively, and means for selectively actuating two of said clutches

or one of said clutches and said brake for providing a

plurality of power paths of different gear ratios through

the transmission. 2 4272 17

Claims (1)

16.153 170 2. A vehicle transmission according to claim I, wherein, w7hen in operation, the input clutch housing is connected by a clutch of the first plurality of clutches to the

ring gear, and the output clutch housing is connected by- a clutch of the second plurality of clutches to the sun

gear of the second planetary gearset, there is thereby

provided two power paths through the transmission, the

first power path being through the first and second planetary gearsets, and the second power path being through the

countersha-ft gearset, wherein the transmission will provide

a reverse speed which is the resultant of the difference

between a positive torque supplied to the sun gear of the

second planetary gearset through the countershaft gearset

and a negative torque delivered from the ring gear to produce

a resultant reverse output of the output shaft. 3. A vehicle transmission according to claim wherein,

when in operation, the input clutch housing is connected by

a clutch of the first plurality of clutches to the ring gear,

and the output clutch housing is connected by a clutch of

the second plurality of clutches to the planet carrier of

the second planetary gearset, there is thereby produced

reaction torque on the ring gear and the planet carrier of the second planetary gearset which is additive and positive

to the sun gear of the second planetary gearset, so as to provide thereby a forward speed having a high numerical torque

ratio on the output shaft.

4. A vehicle transmission according to claim 1, wherein,

.whenin operation, the output clutch housing is connected

by a clutch of the second plurality of clutches to the

planet carrier of the second planetary gearset, and the

22 427217'

16153 70 input clutch housing isrestrained from rotation by action of said brake, there is thereby produced a positive torque on the planet carrier of the first planetary gearset and a positive torque from the ring gear to the sun gear of -the second planetary gearset, so as to provide thereby a positive torque output of the output shaft. A vehicle transmission according to claim 1, wherein, when in operation, the input clutch housing is connected by a clutch of the first plurality of clutches to' the ring gear, and the input clutch housing is restrained from rotation by action of the brake, there is thereby provided a simple planetary reduction through the first planetary gearset to said output shaft, 6. A vehicle transmission according to claim 1, wherein, when in operation.- the input clutch housing is connected by a clutch of the first plurality of clutches to the planet carrier of the first planetary gearset, and the output clutch housing is connected by a clutch of the second plurality of clutches to said planet carrier of said second planetary gearset, there is thereby produced a positive torque transferred to the planet carrier of thea first planetary gearset and a positive torque on the sun gear of the second planetary gearset so as to provide thereby a positive torque on the output shaft. 7. A vehicle transmission according to claim 1, wherein, when in operation, said input clutch housing is connected by. a clutch of the first plurality of clutches to the planet carrier of the first planetary gearset, and the output clutch housing is connected by a clutch of the second plurality of clutches to the ring gear, there is thercby

3L. 4 2*72 17

16 153 70 produced a positive torqfIe on-t ic planet carrier of the

first planetary gearset and a net positive output of

the transmission.

8. A vehicle transmission: according to claim 1, wherein,

when in operation, the input clutch housing is connected

by a clutch of the first plurality of clutches to the sun

gear of the first planetary gearset, and the output clutch

housing is connected by a clutch of the second plurality

of clutches to the sun gear of the second planetary gearset,

both planetary gearsets are thereby rendered inoperative

and the countershaft gearset transmits power from the

input shaft to the output shaft.

9. A vehicle transmission according to claim 1, wherein,

when in oncration, the input clutch housing is connected

by a clutch of the first plurality of clutches to the sun

gear of the first planetary gearset, and the output clutch

housing is connected by a clutch of the second plurality

of clutches to the planet carrier of the second planetary

gearset, there is thereby provided an output torque which

is the sum of resultant torque of the sun gear of the

second planetary gearset and the torque of the planet

carrier of the first planetary gearset..

A vehicle transmission according to claim 1, wherein,

-when in operation, the input clutch housing is connected

by a clutch of the first plurality of clutches to the sun

gear of the first planetary gearset, and the output clutch

housing is-connected by a clutch of the second plurality

of clutches to the ring gear, there is thereby provided

an-output torque in said transmission which is the sum of

the resultant torque of the ring gear torque from the first

24 4.27217'

16153 M to the output clutch housing planetary gearset transfeired torque applied to the sun and the portion of the input

gear of the first planetary gears et. to claim I, wherein, J1 A vehicle transmission according clutch housing is connected when in operation, the input of clutches to the sun by a clutch of the first plurality gearset, and said input clutch gear of the first planetary another clutch of the first housing is also connected by is thereby to the ring gear, there plurality of clutches first planetary gearset which provided a drive through the to produce a forward output is locked to the output shaft

of said transmission. to claim 1, whereiln, 12. A vehicle transmission according clutch housing is connected when in operation, the output plurality of clutches to the by a clutch of the second gearset and said brake is sun gear of the second planetary produced a braking torque of actuated, there is thereby transmission output shaft. said transmission to lock the claims I according to any one of 13. A vehicle transmission clutch housing includes three to 12, wherein said input to the sun gear, ring gear, clutches connectable respectively planetary gearset, and said and planet carrier of said first three clutches connectable output clutch housing includes ring gear, and planet carrier respectively to the sun gear, to provide in operation of said second planetary gearset, speeds forward and one reverse. a transmission having nine according to claim i, wherein, 14.. A vehicle transmission clutch housing is connected when in operation, the output the sun plurality of clutches to by a clutch of the second gearset, and said brake is gear of the second planetary 4 27217

16.153 actuated to lock the input clutch housing to the transmission

casing, the input shaft thereby provides a power take-off

drive, the clutch connection to the sun gear of the second

planetary gearset and the actuation of said brake serving

'to provide braking of the output shaft while permitting

tho input shaft to rotate.

A vehicle transmission according to any one of claims I to 14, wherein the output shaft comprises a quill shaft,

and the input shaft extends coaxially through the output

quill shaft and includes means for providing a power take-off

connection, and wherein, when in operation, the output clutch housing is connected by a clutch of the second plurality of clutches to the sun gear of the second planetary gearset and said brake is actuated, the input and output clutch housings are locked through the countershaft gearset thereby to lock the output shaft while permitting continued rotation

of the power input shaft for power take-off.

16. A vehicle transmission as set forth in claim I constructed and arranged substantially as herein described

with reference to, and as shown in, the accompanying drawings. 17. A vehicle when equipped with a transmission as set

forth in any one of claims I to 16.

DATED this 8 day of June 1970 ALLIS-CHLI..ERS iAWUFACTURIiG COMPANY

26 -26

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