Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 1 of 41 PageID #:
`13307
`
`EXHIBIT W
`
`

`

`(*) Notice:
`
`(54) TRANSMISSION
`(75) Inventors: Norihiro Ishii, Hyogo (JP); Koji Iwaki,
`Hyogo (JP)
`(73) Assignee: Kanzaki Kokyukoki Mgf. Co., Ltd.,
`Amagasaki-shi, Hyogo (JP)
`Subject to any disclaimer the term of this
`patent is extended or adjusted under 35
`U.S.C. 154(b) by 939 days.
`(21) Appl. No.: 12/914,474
`22) Filed:
`Oct. 28, 2010
`(22) File
`9
`(65)
`Prior Publication Data
`US 2011/0099993 A1
`May 5, 2011
`Foreign Application Priority Data
`
`(30)
`
`FOREIGN PATENT DOCUMENTS
`S588853
`1, 1983
`H10-167687. A
`6, 1998
`(Continued)
`OTHER PUBLICATIONS
`Extended European Search Report for EP Application No. 10188869.
`1-2421, European Patent Office, mailed Feb. 14, 2011, 5 pages.
`(Continued)
`Primary Examiner—Ned Landrum
`Assistant Examiner — Logan Kraft
`(74) Attorney, Agent, or Firm — Sterne, Kessler, Goldstein
`& Fox PL.L.C.
`ABSTRACT
`(57)
`A transmission comprises a casing, an output element, a
`Oct. 30, 2009 (JP) ................................. 2009-251135
`hydrostatic stepless transmission unit (HST) and a forward/
`Nov. 9, 2009 (JP) ................................. 2009-256570
`backward traveling direction selecting unit (reverser). The
`Aug. 5, 2010 (JP) ................................. 2010-1768O1
`output element is supported by the casing. The HST is dis
`posed in the casing so as to be driven by a drive source
`(51) Int. Cl.
`disposed outside of the casing. The HST includes a pump
`FI6D 39/00
`(2006.01)
`shaft and a motor shaft member. The pump shaft is drivingly
`FI6H 47/04
`(2006.01)
`connected to the drive source. The motor shaft member is
`FI6H 47/02
`(2006.01)
`fitted around the pump shaft coaxially to the pump shaft so as
`FI6H 37/08
`(2006.01)
`to be rotatable relative to the pump shaft, thereby constituting
`(52) U.S. Cl.
`a hydraulic pump and a hydraulic motor centered on the pump
`CPC ................ F16H 4704 (2013.01); F16H 4702 E.stubs,(NESENSE
`(2013.01); F16H 2037/0886 (2013.01)
`of an axially distal end of the pump shaft so that axial ends of
`USPC ............................................... 60/488: 60/487
`the pump shaft are the axially most distal ends of the HST in
`(58) Field of Classification Search
`the axial direction of the pump shaft. The reverser is disposed
`USPC ........ 60/439, 487,488: 475/83, 198, 225, 23;
`in the casing so as to transmit power outputted from the HST
`to the output element. The reverser includes a forward-trav
`74/730.1
`See application file for complete search history.
`eling drive train, a backward-traveling drive train, and a
`clutch for selecting either the forward-traveling drive train or
`the backward traveling drive train to transmit the power out
`putted from the motor shaft member to the output element.
`The reverser and the output element are entirely disposed
`between the axial ends of the pump shaft in the axial direction
`of the pump shaft.
`11 Claims, 20 Drawing Sheets
`
`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 2 of 41 PageID #:
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`USOO8806864B2
`
`(12) United States Patent
`Ishii et al.
`
`(10) Patent No.:
`(45) Date of Patent:
`
`US 8,806,864 B2
`Aug. 19, 2014
`
`JP
`JP
`
`(56)
`
`References Cited
`U.S. PATENT DOCUMENTS
`4.373.359 A
`2, 1983 Ehrli
`tal
`- -
`rlinger et al.
`4,939,900 A * 7/1990 Furumoto et al. ..............
`(Continued)
`
`
`
`fib
`
`16
`
`51a
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`- " -
`
`23
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`29
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`still,’
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`457
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`A017b
`
`27
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`37
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`
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`-->
`
`58
`
`

`

`US 8,806,864 B2
`Page 2
`
`(56)
`
`References Cited
`
`U.S. PATENT DOCUMENTS
`
`1449 703 A2
`JP
`2006O76451
`JP
`2008.309325
`JP
`WO WO2008/106929 A1
`
`8, 2004
`3, 2006
`12/2008
`9, 2008
`
`4.951469 A * 8/1990 Hayashi et al. ................. 60/489
`2004/0182076 A1* 9, 2004 Shiozaki et al. ................ 60/487
`2009/00951O2 A1
`4/2009 Koga et al.
`
`FOREIGN PATENT DOCUMENTS
`
`OTHER PUBLICATIONS
`
`Office Action with English Translation issued Dec. 17, 2013, in
`Japanese Patent Application No. 2010-176801, 4 pages.
`
`JP
`
`2003-14079 A
`
`1, 2003
`
`* cited by examiner
`
`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 3 of 41 PageID #:
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`U.S. Patent
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`Aug. 19, 2014
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`Sheet 1 of 20
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`US 8,806,864 B2
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`Fig. 1
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`U.S. Patent
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`Aug. 19, 2014
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`Sheet 2 of 20
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 5 of 41 PageID #:
`13311
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`U.S. Patent
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`Aug. 19, 2014
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`Sheet 3 of 20
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`US 8,806,864 B2
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`Fig. 3
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`13312
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`U.S. Patent
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`Sheet 4 of 20
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`US 8,806,864 B2
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`Fig. 4
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 7 of 41 PageID #:
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`U.S. Patent
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`Sheet 5 of 20
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`US 8,806,864 B2
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`Fig. 5
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 8 of 41 PageID #:
`13314
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`U.S. Patent
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`Sheet 6 of 20
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 9 of 41 PageID #:
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`U.S. Patent
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`Aug. 19, 2014
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`Sheet 7 of 20
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 10 of 41 PageID #:
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`U.S. Patent
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`Aug. 19, 2014
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`Sheet 8 of 20
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 11 of 41 PageID #:
`13317
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`U.S. Patent
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`Sheet 9 of 20
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`US 8,806,864 B2
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`Fig. 9
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 12 of 41 PageID #:
`13318
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`U.S. Patent
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`Sheet 10 of 20
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`US 8,806,864 B2
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`Fig. 10
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 13 of 41 PageID #:
`13319
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`U.S. Patent
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`Aug. 19, 2014
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 14 of 41 PageID #:
`13320
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`U.S. Patent
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`Aug. 19, 2014
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`Sheet 12 of 20
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 15 of 41 PageID #:
`13321
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`U.S. Patent
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`Aug. 19, 2014
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`Sheet 13 of 20
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 16 of 41 PageID #:
`13322
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`U.S. Patent
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`Sheet 14 of 20
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 17 of 41 PageID #:
`13323
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`Sheet 15 of 20
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 18 of 41 PageID #:
`13324
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`U.S. Patent
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`Sheet 16 of 20
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`US 8,806,864 B2
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 19 of 41 PageID #:
`13325
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`U.S. Patent
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`Sheet 17 of 20
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`US 8,806,864 B2
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`S.
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 20 of 41 PageID #:
`13326
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`U.S. Patent
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`Sheet 18 of 20
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`US 8,806,864 B2
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`800Z
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 21 of 41 PageID #:
`13327
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`U.S. Patent
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 22 of 41 PageID #:
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`61 61
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`U.S. Patent
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`Aug. 19, 2014
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`Sheet 20 of 20
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`US 8,806,864 B2
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`Fig. 20
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`C. max
`
`8
`
`Neutral
`
`ReverSe
`
`
`
`RS O
`
`-2a
`Off
`(formard)
`On
`(backward)
`High Speed
`
`Neutral
`LOW Speed
`
`204
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`2O3
`
`VS
`
`{
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`
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`- - - - - -
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`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 23 of 41 PageID #:
`13329
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`Forward 4a -------------------4--------- - - - - - - - - - - - - - - - - - - - - - - - - - - - -
`216 + 2a - - - - - - - - - -------------it- |
`}
`1--
`0 - - - - - - - - - - - - - - - - - -- - - - - - - - - - - - - - - - ------------ - - - - - - - - -
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`Backward a
`.
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`252
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`253
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`

`

`US 8,806,864 B2
`
`1.
`TRANSMISSION
`
`BACKGROUND OF THE INVENTION
`
`2
`This HST is now compared with a typical HST in which
`hydraulic pump and motor have respective cylinder blocks
`and a motor shaft serving as an HST output member is fixed
`to the cylinder block of the hydraulic motor. As for the typical
`HST, the hydraulic motor is rotated in one direction by tilting
`a movable Swash plate serving as a pump Swash plate in one
`direction from its neutral position, and the hydraulic motor is
`rotated in the opposite direction by tilting the movable swash
`plate in the opposite direction from the neutral position. On
`the contrary, as for the above-mentioned HST having the
`common cylinder block for the hydraulic pump and motor,
`the rotary speed of the motor shaft member becomes Zero
`when the pump Swash plate reaches a maximum tilt angle in
`one direction from the neutral position, and the rotary speed
`of the motor shaft member becomes its maximum when the
`pump Swash plate reaches a maximum tilt angle in the oppo
`site direction from the neutral position, so that the rotational
`direction of the motor shaft member is constant while the
`pump Swash plate moves between the maximum tilt angle in
`one direction from the neutral position and the maximum tilt
`angle in the opposite direction from the neutral position. In
`other words, as for the HST whose hydraulic pump and motor
`have respective cylinder blocks, the tilt of the pump swash
`plate from the neutral position to the maximum tilt angle in
`one direction provides the variable speed range of output
`rotation of the HST in one direction, and the tilt of the pump
`Swash plate from the neutral position to the maximum tilt
`angle in the opposite direction provides the variable speed
`range of output rotation of the HST in the opposite direction.
`On the contrary, as for the HST whose hydraulic pump and
`motor have a common cylinder block, the whole tilt range of
`the pump swash plate between the maximum tilt angle in one
`direction from the neutral position and the maximum tilt
`angle in the opposite direction from the neutral position pro
`vides the whole variable speed range of output rotation of the
`HST in only one direction. Therefore, the HST having a
`common cylinder block is adapted to be combined with a
`forward/backward traveling direction selecting device, i.e.,
`reverser, which includes a forward traveling gear train, a
`backward traveling gear train and a reverser clutch for select
`ing either the forward or backward traveling gear train, so as
`to ensure a wide variable speed range of a vehicle in each of
`forward and backward traveling directions of the vehicle.
`
`10
`
`15
`
`25
`
`30
`
`35
`
`40
`
`1. Field of the Invention
`The present invention relates to a vehicle-driving power
`transmission provided with a hydrostatic stepless transmis
`sion (hereinafter, “HST). Especially, the present invention
`relates to an integral transmission, which is defined as inte
`grally including an HST and a forward/backward traveling
`direction selecting unit (reverser) in this application.
`2. Background Art
`As disclosed by JP H10-167687A, there is a conventional
`forklift equipped with an HST serving as a transmission for
`transmitting power of an engine serving as a prime mover to
`drive wheels. In this forklift, a hydraulic pump is directly
`attached to the engine, a hydraulic motor is directly attached
`to a transaxle incorporating a differential mechanism, and the
`hydraulic pump and motor are fluidly connected to each other
`via hydraulic fluid pipes so as to constitute the HST. This HST
`is not easily assembled because the hydraulic pump and the
`hydraulic motor are attached to different places separately
`from each other.
`In this regard, there is a conventional HST whose hydraulic
`pump and motor are assembled integrally as disclosed by JP
`2003-14079 A. In this HST, a cylinder block is fixed on a
`pump shaft, pump plungers and motor plungers are fitted into
`respective pump and motor cylinder holes bored in the cylin
`der block so as to be reciprocally movable in parallel to the
`pump shaft, a pair of fluid passages are formed in the cylinder
`block so as to be interposed between the pump cylinder holes
`fitting the pump plungers therein and the motorcylinderholes
`fitting the motor plungers therein, a movable Swash plate
`serving as a pump Swash plate is pressed against heads of the
`pump plungers projecting outward from one end Surface of
`the cylinder block, and a motor Swash plate is formed on a
`motor shaft member relatively rotatably fitted on the pump
`shaft and is pressed against heads of the motor plungers
`projecting outward from the other end surface of the cylinder
`block, so that the hydraulic pump and motor are made to be
`coaxial to each other.
`Further, the cylinder block is provided therein with spool
`valves connected to the pump cylinder holes and with spool
`valves connected to the motor cylinder holes. The spool
`valves change their slide positions in correspondence to tilt
`ing movement of the pump Swash plate, thereby changing a
`flow of hydraulic fluid between higher and lower pressurized
`fluid passages serving as the pair of fluid passages. The rotary
`speed of the motor shaft member having the motor swash
`plate pressed against the motor plungers changes according to
`change of the flow of hydraulic fluid. More specifically, when
`the tilt angle of the pump Swash plate is Zero, i.e., when the
`pump Swash plate is disposed at its neutral position, the rotary
`speed of the motor shaft member is equal to the rotary speed
`of the cylinder block (and the pump shaft). The rotary speed
`of the motor shaft member relative to the cylinder block
`increases as the pump Swash plate is tilted from the neutral
`position in one direction, and the rotary speed of the motor
`shaft member relative to the cylinder block decreases as the
`pump Swash plate is tilted from the neutral position in the
`other direction.
`The HST is radially compact with respect to the pump shaft
`due to the coaxial arrangement of the hydraulic pump and
`motor. Further, the HST is axially minimized due to the
`cylinder block which is common to both the hydraulic pump
`and motor.
`
`Case 1:17-cv-00770-JDW-MPT Document 120-10 Filed 11/17/22 Page 24 of 41 PageID #:
`13330
`
`45
`
`BRIEF SUMMARY OF THE INVENTION
`
`In consideration of the above situation, a hydrostatic step
`less transmission unit (hereinafter, “HST) and a forward/
`backward traveling direction selecting device Switching unit
`(hereinafter, “reverser') are desired to be integrally combined
`So as to constitute an integral vehicle-driving power transmis
`Sion. In this regard, a small-size vehicle Such as a forklift has
`a narrow space between an axle and a prime mover, Such as an
`engine, and a small width between right and left drive wheels.
`Therefore, the transmission is desired to be so compact as to
`be disposed in the limited space and width.
`A transmission according to the present invention com
`prises a casing, an output element, an HST and a reverser. The
`output element is supported by the casing. The HST is dis
`posed in the casing so as to be driven by a drive source
`disposed outside of the casing. The HST includes a pump
`shaft and a motor shaft member. The pump shaft is drivingly
`connected to the drive source. The motor shaft member is
`fitted around the pump shaft coaxially to the pump shaft so as
`to be rotatable relative to the pump shaft, thereby constituting
`a hydraulic pump and a hydraulic motor centered on the pump
`shaft and the motor shaft member. The reverser is disposed in
`
`50
`
`55
`
`60
`
`65
`
`

`

`4
`Therefore, in a vehicle, a space for the arrangement of the
`transmission member can be reduced in the axial direction of
`the pump shaft.
`Further preferably, the transmission further comprises an
`input element Supported by the casing so as to be drivingly
`connected to the drive source and to drive the pump shaft. An
`outer end of the input element is disposed on an outer end of
`the casing opposite to the outer Surface of the second portion
`of the casing in the axial direction of the pump shaft. There
`fore, the transmission member connected to the outer end of
`the output element and the drive source connected to the outer
`end portion of the input element can be arranged without
`interference with each other. Incidentally, an input shaft inter
`locking with the pump shaft via gears in the casing typically
`serves as the input element. Besides, in case that a tip of the
`pump shaft projects outward from the casing, a spline cou
`pling or a universal joint may be provided on the tip of the
`pump shaft so as to serve as the input element. The same thing
`is adapted to hereinafter-mentioned input elements.
`Further preferably, a charge pump is disposed on the outer
`Surface of the second portion of the casing so as to be juxta
`posed with the outer end of the output element. Therefore, the
`charge pump which must be externally attached to the casing
`of the transmission is disposed in the dead space defined by
`the step, thereby requiring no other space for arranging the
`charge pump, and thereby further compacting a layout of a
`vehicle power transmission system.
`Preferably, the transmission further comprises an input
`element Supported by the casing so as to be drivingly con
`nected to the drive source and to drive the pump shaft. The
`input element, the pump shaft having the motor shaft member
`therearound, a rotary shaft constituting the reverser, and the
`output element are aligned on a spiral line centered on the
`input element when viewed in the axial direction of the pump
`shaft. Therefore, these elements and members are concen
`trated around the input element so as to compact the entire
`transmission while ensuring their good efficiency in power
`transmission. Further, these elements and members can be
`arranged around the input element to keep a good balance of
`the transmission.
`Preferably, the transmission further comprises a pair of
`axles and a differential unit. The axles are extended in the
`axial direction of the pump shaft and are Supported by the
`casing. The differential unit is disposed in the casing so as to
`transmit power outputted from the forward/backward travel
`ing direction selecting unit to the axles. The differential unit
`includes a pair of differential yoke shafts, serving as the
`output element, extended in the axial direction of the pump
`shaft so as to be drivingly connected to the respective axles.
`The differential unit is entirely disposed between the axial
`ends of the pump shaft in the axial direction of the pump shaft.
`Therefore, the transmission can be provided as a transaxle
`Supporting the pair of axles. The axial compactness of the
`differential unit minimizes the width of a vehicle between
`right and left wheels.
`Further preferably, a pair of planetary gear units are dis
`posed in the casing so as to be interposed between the respec
`tive differential yoke shafts of the differential unit and the
`respective axles. At least a part of each of the planetary gear
`units is disposed between the axial ends of the pump shaft in
`the axial direction of the pump shaft. Therefore, the planetary
`gear units can ensure a large speed-reduction ratio while they
`are disposed in the limited space between the axles, thereby
`requiring no additional gears for speed-reduction on the
`power train including the reverser and the differential unit.
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`the casing so as to transmit power outputted from the HST to
`the output element. The reverser includes a forward-traveling
`drive train, a backward-traveling drive train, and a clutch for
`selecting either the forward-traveling drive train or the back
`ward traveling drive train to transmit the power outputted
`from the motor shaft member to the output element.
`In the above-mentioned transmission, an axially distal end
`of the motor shaft member is disposed on the axially proximal
`side of an axially distal end of the pump shaft so that axial
`ends of the pump shaft are the most distal ends of the HST in
`the axial direction of the pump shaft. The reverser and the
`output element are entirely disposed between the axial ends
`of the pump shaft in the axial direction of the pump shaft.
`The HST comprises a cylinder block, a pump plunger, a
`movable Swash plate, a motor plunger, and a valve. The cyl
`inder block is fixed on the pump shaft, and is formed therein
`with a pump cylinder hole parallel to the pump shaft, a motor
`cylinder hole parallel to the pump shaft, and a pair of fluid
`passages interposed between the pump cylinder hole and the
`motor cylinder hole. The pump plunger is fitted into the pump
`cylinder. The movable Swash plate is pressed against the
`pump plunger. The motor plunger is fitted into the motor
`cylinder hole. A swash plate is provided on the motor shaft
`member and is pressed against the motor plunger. The valve is
`disposed in the cylinder block. The valve changes a flow of
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`fluid in the pair of fluid passages according to tilting move
`ment of the movable Swash plate so as to change the rotary
`speed of the motor shaft member.
`This HST is minimized in the radial direction thereof cen
`tered on the axis of the pump shaft because the movable swash
`plate, the cylinder block and the motor shaft member, consti
`tuting the hydraulic pump and motor, are all disposed around
`the pump shaft so as be centered on the axis of the pump shaft.
`Further, this HST is also minimized in the axial direction of
`the pump shaft because the common cylinder block having
`the pump and motor plungers therein constitute both the
`hydraulic pump and motor, whereby the motor shaft whose
`axial ends define the most distal ends of the HST can be
`shortened so as to minimize the entire transmission in the
`axial direction of the pump shaft.
`Preferably, the casing is adapted to be directly attached to
`an engine serving as the drive source. Therefore, when the
`engine is mounted onto a vehicle body via a vibration isolat
`ing member, the effect of the vibration isolating member is
`also applied to the transmission whose casing is directly
`attached to the engine, thereby reducing costs because then
`there is no need for an additional vibration isolating member
`for vibration-isolatingly supporting the transmission. Fur
`ther, the engine and the transmission can be assembled
`together as a single apparatus, which reduces the process for
`attachment or detachment of the transmission to the engine.
`Preferably, the casing includes a first portion and a second
`portion. The first portion incorporates a drive train interposed
`between the motor shaft member and the reverser. The second
`portion incorporates the reverser and the output element. The
`first portion expands more distally in the axial direction of the
`pump shaft than the second portion so as to form a step
`between an outer surface of the first portion and an outer
`surface of the second portion. An outer end of the output
`element is disposed on the outer Surface of the second portion.
`Therefore, the outer end of the output element can be dis
`posed inward from the outer surface of the first portion of the
`casing, thereby facilitating its protection, and thereby axially
`overlapping the first portion with a transmission member,
`such as a propeller shaft, to be connected to the outer end of
`the output element. In other words, a dead space defined by
`the step is used for arrangement of this transmission member.
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`These, and other objects, features, and advantages will
`appear more fully from the following description with refer
`ence to the accompanying drawings.
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`BRIEF DESCRIPTION OF THE DRAWINGS
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`FIG. 1 is a schematic plan view of a vehicle V1 equipped
`with an integral transmission T1.
`FIG. 2 is a skeleton diagram as a schematic developed plan
`view of transmission T1.
`FIG. 3 is a perspective view of transmission T1.
`FIG. 4 is a side view of transmission T1.
`FIG. 5 is a schematic front view of transmission T1.
`FIG. 6 is a developed sectional view of transmission T1
`taken along VI-VI arrowed line of FIG. 5.
`FIG. 7 is a fragmental sectional view of transmission T1
`showing gears interposed between an input shaft 21 and a
`pump shaft 22.
`FIG. 8 is an HST circuit diagram for transmission T1.
`FIG. 9 is a schematic plan view of a vehicle V2 equipped
`with an integral transmission T2.
`FIG. 10 is a skeleton diagram as a schematic developed
`plan view of transmission T2.
`FIG. 11 is a schematic side view of transmission T2.
`FIG. 12 is a skeleton diagram of a vehicle V3 equipped with
`an integral transmission T3.
`FIG. 13 is a skeleton diagram of a vehicle V4 equipped with
`an integral transmission T4.
`FIG. 14 is a skeleton diagram of a vehicle V5 equipped with
`an integral transmission T5.
`FIG. 15 is a skeleton diagram of a vehicle V5a equipped
`with an integral transmission T5a omitting an HST.
`FIG.16 is a skeleton diagram of a vehicle V6 equipped with
`a transmission T6 separated from an engine to which an HST
`is directly attached.
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`FIG. 17 is a skeleton diagram of a vehicle V6a equipped
`with a transmission T6 directly attached to an engine and with
`an HST externally attached to transmission T6.
`FIG. 18 is a skeleton diagram of a vehicle T7 equipped with
`an integral transmission T7.
`FIG. 19 is a block diagram showing change of variable
`speed range while power is transmitted through transmission
`T7.
`FIG. 20 is a chart showing control processes of units or
`parts in transmission T7 during a process of change of a
`vehicle speed (rotary speed of an output shaft) from a maxi
`mum backward traveling speed to a maximum forward trav
`eling speed.
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`Various transmissions and various vehicles or vehicle-driv
`ing power transmission system equipped with the respective
`transmissions will be described with reference to the accom
`panying drawings. Hereinafter descriptions regarding direc
`tions are based on an assumption that arrows F shown in the
`drawings are directed forward.
`An embodiment shown in FIGS. 1 to 8 will be described. A
`vehicle V1 shown in FIG. 1 is a small-sized work vehicle such
`as a forklift or a utility vehicle. Vehicle V1 has a vehicle body
`100, which is provided at a front portion thereof with right and
`left front wheels 2 serving as drive wheels, and at a rear
`portion thereof with laterally turnable right and left rear
`wheels 3 serving as steerable wheels. An engine 1 serving as
`a prime mover for driving a transmission T1 is mounted onto
`a lateral middle portion of vehicle body 100 in front of rear
`wheels 3 via vibration-isolating members 101 (see FIG. 2),
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`Such as rubbers. A casing 5 of integral transmission T1 is
`directly attached at a rear end thereof to a front surface of
`engine 1.
`A driver's seat 4 is mounted onto vehicle body 100 above
`engine 1 and transmission T1, and a steering wheel 14 serving
`as a steering operation device is Supported by vehicle body
`100 in front of driver's seat 4. A transaxle 10 is supported by
`vehicle body 100 between right and left front wheels 2 in front
`of transmission T1. When a driver rotates steering wheel 14,
`right and left rear wheels 3 are turned rightward or leftwardso
`that vehicle V1 turns right or left.
`As shown in FIG. 2 and others, transmission T1 includes a
`later-discussed hydrostatic stepless transmission unit (here
`inafter, referred to as “HST) 6 and a later-discussed forward/
`backward traveling direction selecting unit (hereinafter,
`referred to as “reverser') 7. Casing 5 of transmission T1
`incorporates HST6 and reverser 7. HST6 is driven by engine
`1, and reverser 7 is driven by HST 6. As shown in FIG. 1,
`transaxle 10 has a casing 11, which incorporates a differential
`unit 12 and a pair of planetary gear units 13. Each of planetary
`gear units 13 is interposed between differential unit 12 and
`each of axles 2a serving as center axial shafts of respective
`front wheels 2 so as to serve as a speed reduction unit.
`As shown in FIG. 2 and others, an output shaft 27 serving
`as an output element of transmission T1 is Supported by
`casing 5 so as to have a horizontal axis extended in the
`fore-and-aft direction of vehicle V1. As shown in FIGS. 2 to
`4, a flange 28 Serving as a connection member is fixed onto a
`front end of output shaft 27 and is exposed forward from
`casing 5. On the other hand, as shown in FIG. 1, an input shaft
`12a of differential unit 12 projects rearward from casing 11 of
`transaxle 10. As shown in FIGS. 1 and 2, a connection shaft
`57a extended from a universal joint 57 is fixed at a rear end
`thereof to flange 28 coaxially to output shaft 27. On the other
`hand, input shaft 12a of differential unit 12 is connected at a
`rear end thereof to universal joint 57 via a universal joint 58
`and a propeller shaft 56. Therefore, an output power of trans
`mission T1 is transmitted to right and left front wheels 2 via
`transaxle 10, i.e., differential unit 12 and right and left plan
`etary gear units 13.
`Transmission T1 will be described. Casing 5 of transmis
`sion T1 includes a main casing member 15, a rear casing
`member 16, a front casing member 17 and a front cover 18,
`which are joined together to constitute casing 5. Main casing
`member 15 has an outer peripheral surface extended in the
`fore-and-aft direction of vehicle V1, and is opened at a front
`end thereof. As shown in FIGS.2, 6, 7 and others, main casing
`member 15 is closed at a rear end thereof so as to form a
`vertical rear wall 15a. Rear casing member 16 is joined at a
`frontend thereof to a rear end surface of rear wall 15a of main
`casing member 15. Front casing member 17 is joined at a rear
`end thereof to the front end of main casing member 15 so as
`to cover the opening at the front end of main casing member
`15. Front casing member 17 has a vertical front wall 17a and
`is formed with an expanded portion 17b which is expanded
`forward from a top portion of front wall 17a. Front cover 18
`is joined at a rear end thereof to a front end of expanded
`portion 17b so as to cover an opening at the front end of
`expanded portion 17b.
`A main chamber C1 is formed in main casing member 15
`and front casing member 17 between rear wall 15a of main
`casing member 15 and front wall 17a offront casing member
`17. An input gear chamber C2 is formed in rear casing mem
`ber 16 between rear wall 15a of main casing member 15 and
`the vertical rear end wall of rear casing member 16. An
`intermediate gear chamber C3 is formed in expanded portion
`17b of front casing member 17 between front wall 17a of
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`front casing member 17 and the vertical frontend wall offront
`cover 18. In this way, casing 5 is formed therein with main
`chamber C1, with input gear chamber C2 rearward from mai