WO2013021691A1 - 作業車両 - Google Patents
作業車両 Download PDFInfo
- Publication number
- WO2013021691A1 WO2013021691A1 PCT/JP2012/060442 JP2012060442W WO2013021691A1 WO 2013021691 A1 WO2013021691 A1 WO 2013021691A1 JP 2012060442 W JP2012060442 W JP 2012060442W WO 2013021691 A1 WO2013021691 A1 WO 2013021691A1
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- WIPO (PCT)
- Prior art keywords
- input shaft
- shaft
- input
- oil
- drive shaft
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0215—Details of oil circulation
Definitions
- the present invention relates to a work vehicle.
- a torque converter for transmitting power from a power source such as an engine to an input shaft of a transmission.
- the torque converter generally includes a torque converter body that transmits power through fluid and a lockup clutch device.
- the lockup clutch device mainly includes a piston operated by hydraulic pressure and a clutch unit which is turned on (power transmission) and turned off (power transmission is interrupted) by the operation of the piston. Then, when the speed of the vehicle reaches a predetermined speed or more, the clutch portion of the lockup clutch device is turned on, and the power from the engine is directly transmitted to the transmission input shaft via the lockup clutch device without passing through the torque converter main body. It is transmitted.
- a hydraulic pump is required to supply hydraulic fluid to the torque converter body or to the piston of the lockup clutch device.
- This hydraulic pump is often arranged, for example, in a transmission case eccentrically from an axis extending the input axis.
- Patent Document 1 a configuration is proposed in which the hydraulic pump and its drive shaft are disposed coaxially with the rotation shaft of the torque converter.
- the lockup clutch device is operated by a method of operating a piston using hydraulic fluid flowing into or out of the torque converter main body, and hydraulic fluid supplied by a hydraulic circuit of a system separate from the hydraulic fluid of the torque converter main body.
- a method of operating the piston In the latter type, it is necessary to supply the hydraulic oil from the hydraulic pump to the oil chamber on the back of the piston.
- the oil chamber on the back of the piston is provided on the front side of the torque converter main body.
- a gun drill is used when forming a hole in the inside of a pump drive shaft, it is difficult to form a small diameter hole generally with a gun drill. Therefore, if a hole is formed by a gun drill inside the pump drive shaft, the thickness of the pump drive shaft becomes thinner. When heat treatment is performed on such a pump drive shaft, axial distortion of the pump drive shaft is increased.
- a work vehicle includes an engine, a transmission connected to the engine, and a hydraulic pump.
- the transmission includes an input member to which power from the engine is input, a transmission main body having a cylindrical input shaft, a torque converter main body, a lockup clutch device, a pump drive shaft, and an oil passage.
- the torque converter body is coupled to the input member, and transmits the power from the input member to the input shaft through the fluid.
- the lockup clutch device includes a hydraulically actuated piston, an oil chamber formed on the back of the piston, and a clutch unit for transmitting power from the input member to the input shaft by actuation of the piston.
- the pump drive shaft penetrates the inside of the input shaft and is arranged coaxially with the input shaft to transmit the driving force to the hydraulic pump.
- the oil passage is formed between the inner peripheral surface of the input shaft and the outer peripheral surface of the pump drive shaft, and communicates with the oil chamber of the lockup clutch device.
- the hydraulic pump is driven by the pump drive shaft, and the hydraulic fluid discharged from the hydraulic pump is conducted to the oil chamber of the lockup clutch device through the oil passage which is the gap between the pump drive shaft and the input shaft. It is eaten.
- the work vehicle according to a second aspect of the present invention is the work vehicle according to the first aspect, wherein the tip of the pump drive shaft extends from the tip end surface of the input shaft toward the engine.
- the input member has a connection hole, a fitting hole, an oil reservoir, and a communication hole.
- the connection hole is disposed at the center of the input member, and the tip of the pump drive shaft is connected.
- the fitting hole is disposed coaxially with the connecting hole, is formed larger in diameter than the connecting hole, and fits with the outer peripheral surface of the tip of the input shaft.
- the oil reservoir is formed by the inner peripheral surface of the fitting hole, the tip end surface of the input shaft, and the outer peripheral surface of the pump drive shaft, and communicates with the oil passage.
- the communication hole communicates the oil reservoir with the oil chamber of the lockup clutch device.
- the hydraulic oil that has passed through the oil passage between the pump drive shaft and the input shaft is led to the oil reservoir and further led to the oil chamber of the lockup clutch device through the communication hole. Even if a plurality of communication holes are provided, the total cross-sectional area is narrower than the outer peripheral area of the pump drive shaft (the width is taken as the diameter of the communication hole). Then, the hydraulic oil in the outer peripheral portion of the pump drive shaft is collected in the communication hole. Further, since the distance between the outer peripheral surface of the pump drive shaft and the inner peripheral surface of the input shaft is short, the pressure loss of the hydraulic oil becomes large. As a result, the operation of the lockup clutch may be delayed. Therefore, by providing the oil reservoir, the flow of hydraulic fluid from the oil passage between the pump drive shaft and the input shaft to the communication hole becomes smooth, and the pressure loss is reduced.
- the work vehicle according to a third aspect of the present invention is the work vehicle according to the second aspect, further including a turbine hub and a bearing.
- the turbine hub has a cylindrical portion at its center, and its inner periphery is connected to the outer periphery of the input shaft to transmit power from the torque converter main body to the input shaft.
- the inner periphery of the bearing is fitted to the outer periphery of the cylindrical portion.
- the input member further has a support hole. The support hole is coaxial with the fitting hole, disposed in the input member and fitted with the outer periphery of the bearing.
- the input shaft is supported by the input member via a turbine hub and a bearing.
- the pump drive shaft is connected to the input member at the connection hole.
- the input shaft is supported by the input member via a turbine hub and a bearing. Since both the pump drive shaft and the input shaft are supported by the input member, the distance between the inner peripheral surface of the input shaft and the outer peripheral surface of the pump drive shaft can be easily maintained constant.
- the communication hole is formed in the input member, and the hydraulic oil guided to the tip end portion of the input shaft is guided to the oil chamber of the input member. Therefore, the hydraulic circuit can be realized with a simple configuration.
- the hydraulic pump is disposed on the extension of the transmission input shaft, and the hydraulic pump drive shaft is disposed inside the transmission input shaft, the oil chamber of the lockup clutch device having a simple configuration.
- FIG. 2 is an enlarged partial view of FIG. 1;
- FIG. 2 is an enlarged partial view of FIG. 1;
- FIG. 1 shows a cross-sectional view of a portion of a transmission 1 according to an embodiment of the present invention.
- the transmission 1 is, for example, a transmission of a backhoe loader, and includes a main body case 2 and a front case 3 fixed to the engine side (left side in FIG. 1) of the main body case 2.
- a transmission main body 5 including an input shaft 4 is accommodated.
- the transmission main body 5 has members such as a plurality of hydraulic clutches for forward / reverse switching, a plurality of hydraulic clutches for speed stage switching, a gear mechanism, and the like.
- the transmission 1 also has a pump drive shaft 12 (hereinafter referred to as “PTO shaft”) coaxially disposed with the input shaft 4.
- PTO shaft pump drive shaft
- a hydraulic pump 13 mounted on the main body case 2 is provided on an extension of the input shaft 4.
- the hydraulic pump 13 is driven by the PTO shaft 12.
- the input member 8 has a PTO shaft coupling portion 15 on the engine side and an input shaft support portion 16 on the transmission side.
- the PTO shaft coupling portion 15 and the input shaft support portion 16 are fixed to each other by bolts 17 for fixing the flexible plate 7 to the PTO shaft coupling portion 15.
- the PTO axial connection part 15 is a disk shaped member which has the large diameter part 21 and the small diameter part 22.
- a protrusion 21a that protrudes to the engine side is formed, and as shown in FIG. 1, the tip of this protrusion 21a is the inner periphery of the flywheel 6 via the bearing 23. It is supported by the department.
- the inner peripheral portion of the flexible plate 7 is fixed to the side surface on the engine side of the large diameter portion 21, and the outer peripheral portion of the flexible plate 7 is fixed to the outer peripheral portion of the flywheel 6.
- a spline hole 21 b is formed at the central portion of the large diameter portion 21.
- a collar insertion hole 22a having an inner diameter larger than the spline hole 21b and a fitting hole 22b having an inner diameter larger than the collar insertion hole 22a are formed.
- the input shaft support portion 16 is an annular member, and the small diameter portion 22 of the PTO shaft connection portion 15 is inserted into the hole 16a of the inner peripheral portion.
- the input shaft support portion 16 has a cylindrical portion 25 extending to the transmission side at the outer peripheral portion.
- An annular recess 16 b is formed on the inner peripheral side of the cylindrical portion 25 and on the side surface of the input shaft support 16 on the torque converter main body 9 side.
- the annular recess 16 b functions as an oil chamber (described later) of the lockup clutch device 10.
- a flange portion 26 extending to the outer peripheral side is provided at the tip of the cylindrical portion 25.
- the torque converter main body 9 mainly includes a pump 28, a turbine 29, and a stator 30, and a one-way clutch 32 disposed between the stator 30 and the fixed shaft 31. .
- An outer peripheral portion of the pump 28 is connected to the flange portion 26 of the input shaft support portion 16. Further, the inner peripheral portion of the pump 28 is rotatably supported by the fixed shaft 31 via the bearing 34.
- the fixed shaft 31 is fixed to the front case 3 by a bolt 35.
- the turbine 29 is disposed opposite to the pump 28.
- a turbine hub 38 is fixed to the inner circumferential portion of the turbine 29.
- a substantially cylindrical cylindrical portion is formed at the central portion of the turbine hub 38, and a spline hole 38a is formed at the inner peripheral portion of the cylindrical portion.
- the outer peripheral surface of the cylindrical portion of the turbine hub 38 is partially reduced in diameter, and the inner periphery of the bearing 39 is fitted.
- the outer periphery of the bearing 39 is fitted to the inner peripheral surface of a support hole 16 d provided in the input shaft support portion 16.
- the turbine hub 38 is rotatably supported by the input shaft support 16 via the bearing 39.
- the lockup clutch device 10 includes an oil chamber 16b, a piston 41, first and second clutch plates 42 and 43 constituting a clutch portion, and a damper mechanism 44.
- the lockup clutch device 10 includes an oil chamber 16b, a piston 41, first and second clutch plates 42 and 43 constituting a clutch portion, and a damper mechanism 44.
- FIG. 2 is an enlarged view of a part of one side in the radial direction of FIG. 1
- FIG. 3 is an enlarged view of a part of the other side in the radial direction of FIG.
- the oil chamber 16 b is an annular recess formed in the input shaft support 16 as described above.
- the piston 41 is disposed in the oil chamber 16b. Further, as shown in FIG. 3, holes 41a and 16c are formed in the piston 41 and the input shaft support portion 16 at positions facing each other, and one rod 46 is inserted into these holes 41a and 16c. There is. As a result, the piston 41 is movable in the axial direction with respect to the input shaft support portion 16 and can not relatively rotate.
- the first clutch plate 42 is an annular member, and friction materials are provided on both sides. Internal teeth are formed on the inner peripheral portion of the first clutch plate 42, and these internal teeth mesh with external teeth formed on an input plate (described later) that constitutes the damper mechanism 44. Therefore, the first clutch plate 42 is connected to the damper mechanism 44 so as to be axially movable and relatively non-rotatable.
- the second clutch plate 43 is an annular member, and has external teeth formed on the outer peripheral portion. On the other hand, internal teeth are formed on the inner peripheral surface of the cylindrical portion 25 of the input shaft support portion 16, and the external teeth of the second clutch plate 43 mesh with the internal teeth. Therefore, the second clutch plate 43 is connected to the input shaft support 16 so as to be axially movable and relatively non-rotatable.
- a back plate 48 is provided on the transmission side of the second clutch plate 43 to restrict axial movement of the second clutch plate 43.
- the damper mechanism 44 is a mechanism that transmits the power from the first clutch plate 42 to the turbine hub 38.
- the damper mechanism 44 includes an input plate 51, a pair of output plates 52 disposed on both sides of the input plate 51, and a plurality of torsion springs 53 supported by the plates.
- the input plate 51 is connected to the first clutch plate 42, and the pair of output plates 52 are fixed to the turbine hub 38 by rivets.
- the input shaft 4 is disposed coaxially with the rotation shaft of the engine, and rotatably supported by the front case 3 via a bearing 55. Further, the input shaft 4 is formed in a cylindrical shape, and a through hole 4 a is formed at the center of the input shaft 4.
- the input shaft 4 is provided with a hydraulic clutch 56 such as a forward / reverse switching clutch (only a part of which is shown in FIG. 1), and a plurality of gears.
- a spline shaft 4 b is formed on the outer periphery of the tip end portion of the input shaft 4. The spline shaft 4 b is engaged with a spline hole 38 a formed on the inner peripheral surface of the turbine hub 38.
- the tip end of the spline shaft 4b of the input shaft 4 is inserted into the fitting hole 22b of the PTO shaft connecting portion 15 and rotatably supported.
- a seal member is mounted on the outer peripheral surface of the input shaft 4, and the outer peripheral surface of the input shaft 4 and the inner peripheral surface of the fitting hole 22b are sealed.
- the input shaft 4 is supported by the input shaft support 16 via the turbine hub 38 and the bearing 39.
- the PTO shaft 12 is disposed through the through hole 4 a of the input shaft 4.
- a gap is formed between the outer peripheral surface of the PTO shaft 12 and the inner peripheral surface of the input shaft 4.
- the tip end of the PTO shaft 12 protrudes from the tip end surface of the input shaft 4 further toward the engine side, and a spline shaft 12 a is formed at this tip portion.
- the spline shaft 12 a is engaged with the spline hole 21 b of the PTO shaft coupling portion 15. Further, a part of the spline shaft 12 a of the PTO shaft 12 on the transmission side is inserted into the collar insertion hole 22 a of the PTO shaft coupling portion 15.
- a collar 58 is inserted between the outer peripheral surface of the PTO shaft 12 and the inner peripheral surface of the collar insertion hole 22a.
- the outer peripheral surface of the collar 58 is in close contact with the inner peripheral surface of the collar insertion hole 22 a, and the inner peripheral surface of the collar 58 is in close contact with the outer peripheral surface of the PTO shaft 12.
- a seal member is provided on the outer peripheral surface of the PTO shaft 12, and a space between the outer peripheral surface of the PTO shaft 12 and the inner peripheral surface of the collar is sealed.
- the space formed by the tip end surface of the input shaft 12, the end surface of the collar 58, the outer peripheral surface of the PTO shaft 12, and the inner peripheral surface of the fitting hole 22b functions as the oil reservoir 60.
- the hydraulic pump 13 is connected to the end opposite to the tip end of the PTO shaft 12.
- the hydraulic pump 13 is driven by the rotation of the PTO shaft 12, and discharges hydraulic fluid to the gap between the outer peripheral surface of the PTO shaft 12 and the inner peripheral surface of the input shaft 4.
- the hydraulic oil discharged from the hydraulic pump 13 is supplied to the oil chamber 16b of the lockup clutch device 10 via a hydraulic circuit.
- the hydraulic circuit as shown in FIG. 2, includes a first oil passage 61, the above-described oil reservoir 60, a second oil passage 62, a third oil passage 63, and a fourth oil passage 64. ing.
- the first oil passage 61 is formed by a gap between the outer peripheral surface of the PTO shaft 12 and the inner peripheral surface of the input shaft 4 as described above.
- the end of the first oil passage 61 on the engine side communicates with the oil reservoir 60.
- the second oil passage 62 is formed by a first through hole formed in the small diameter portion 22 of the PTO shaft coupling portion 15. Specifically, an annular groove 22c is formed in the small diameter portion 22 of the PTO shaft coupling portion 15, and one first through hole 62 is formed to communicate with the oil reservoir 60 from the annular groove 22c. It is done. A plurality of first through holes may be formed.
- the third oil passage 63 is formed by a second through hole penetrating from the outer peripheral surface of the input shaft support portion 16 toward the inner peripheral portion.
- the inner peripheral side of the second through hole 63 communicates with the annular groove 22 c of the PTO shaft coupling portion 15.
- the outer peripheral end of the second through hole 63 is sealed by mounting a screw member 65.
- the fourth oil passage 64 is formed by a communication hole connecting the oil chamber 16 b formed in the input shaft support 16 and the third oil passage 63.
- the lockup clutch device 10 is off. That is, no hydraulic oil is supplied to the oil chamber 16 b of the lockup clutch device 10. In this case, the power input from the engine to the input member 8 is transmitted to the input shaft 4 via the torque converter main body 9.
- the hydraulic oil from the hydraulic pump 13 is supplied to the lockup clutch device 10. Specifically, the hydraulic oil discharged from the hydraulic pump 13 passes through the first oil passage 61 and is guided to the oil reservoir 60. Thereafter, it is supplied from the oil reservoir 60 through the second oil passage 62, the third oil passage 63, and the fourth oil passage 64 to the oil chamber 16b. The piston 41 is moved to the transmission side by the hydraulic oil supplied to the oil chamber 16b. Therefore, the first clutch plate 42 is in pressure contact with the piston 41 and the second clutch plate 43.
- the hydraulic oil discharged from the hydraulic pump 13 is led to the lockup clutch device 10 through an oil passage 61 which is a gap between the PTO shaft 12 and the input shaft 4. For this reason, it is not necessary to form a hole as an oil passage inside the PTO shaft 12. Therefore, the hydraulic oil from the hydraulic pump 13 can be guided to the lockup clutch device 10 with a simple configuration and with less hydraulic oil leakage. Further, since the PTO shaft 12 can be formed solid, distortion in the heat treatment process can be suppressed.
- the oil reservoir 60 Since the oil reservoir 60 is provided, the flow of hydraulic oil from the oil passage 61 between the PTO shaft 12 and the input shaft 4 to the second oil passage 62 becomes smooth, and the pressure loss of the hydraulic oil is reduced. For this reason, the delay in the operation of the lockup clutch can be avoided.
- the through holes 62 and 63 and the communication hole 64 formed in the PTO shaft connection portion 15 and the input shaft support portion 16 are formed in a direction perpendicular to the rotation axis or along the rotation axis. For this reason, it is not necessary to form a hole in an oblique direction, and processing becomes easy.
- the configuration of the hole as an oil passage formed in the PTO shaft connection portion and the input shaft support portion is not limited to the above embodiment, and various configurations can be adopted.
- the hydraulic pump is disposed on the extension of the transmission input shaft, and the hydraulic pump drive shaft is disposed inside the transmission input shaft. It can introduce hydraulic oil. Further, in the working vehicle of the present invention, since it is not necessary to form a hole as an oil passage inside the pump drive shaft, it is possible to suppress the deformation of the pump drive shaft at the time of heat treatment or the like.
Abstract
Description
図1に、本発明の一実施形態によるトランスミッション1の一部の断面構成を示している。このトランスミッション1は、例えば、バックホーローダのトランスミッションであり、本体ケース2と、本体ケース2のエンジン側(図1において左側)に固定されたフロントケース3と、を有している。本体ケース2には、入力軸4を含むトランスミッション本体5が収納されている。トランスミッション本体5は、前後進切換用の複数の油圧クラッチ、速度段切換用の複数の油圧クラッチ、歯車機構等の部材を有している。また、フロントケース3には、エンジン側のフライホイール6に連結されたフレキシブルプレート7と、フレキシブルプレート7に固定された入力部材8と、入力部材8に固定されたトルクコンバータ本体9と、ロックアップクラッチ装置10と、が配置されている。また、このトランスミッション1は、入力軸4と同軸に配置されたポンプ駆動軸12(以下、「PTO軸」と記す)と、を有している。
入力部材8は、エンジン側のPTO軸連結部15と、トランスミッション側の入力軸支持部16と、を有している。PTO軸連結部15と入力軸支持部16とは、フレキシブルプレート7をPTO軸連結部15に固定するボルト17によって互いに固定されている。
図1に示すように、トルクコンバータ本体9は、主に、ポンプ28、タービン29、及びステータ30と、ステータ30と固定軸31との間に配置されたワンウェイクラッチ32と、を有している。
図2及び図3に示すように、ロックアップクラッチ装置10は、油室16bと、ピストン41と、クラッチ部を構成する第1クラッチプレート42及び第2クラッチプレート43と、ダンパ機構44と、を有している。なお、図2は図1の径方向一方側の一部を拡大して示した図であり、図3は図1の径方向他方側の一部を拡大して示した図である。
図1~図3に示すように、入力軸4は、エンジンの回転軸と同軸に配置され、軸受55を介してフロントケース3に回転自在に支持されている。また、入力軸4は筒状に形成され、入力軸4の中心部には貫通孔4aが形成されている。この入力軸4には、前後進切換用クラッチ(図1では一部のみを示している)等の油圧クラッチ56や、複数のギアが設けられている。入力軸4の先端部外周には、スプライン軸4bが形成されている。このスプライン軸4bは、タービンハブ38の内周面に形成されたスプライン孔38aに係合している。入力軸4のスプライン軸4bのさらに先端部は、PTO軸連結部15の嵌合孔22bに挿入されて回転自在に支持されている。入力軸4の外周面にはシール部材が装着されており、入力軸4の外周面と嵌合孔22bの内周面とはシールされている。
PTO軸12は入力軸4の貫通孔4aを貫通して配置されている。PTO軸12の外周面と入力軸4の内周面との間には隙間が形成されている。PTO軸12の先端は、入力軸4の先端面からさらにエンジン側に突出して延びており、この先端部にはスプライン軸12aが形成されている。スプライン軸12aはPTO軸連結部15のスプライン孔21bに係合している。また、PTO軸12のスプライン軸12aのトランスミッション側の一部は、PTO軸連結部15のカラー挿入用孔22aに挿入されている。そして、PTO軸12の外周面とカラー挿入用孔22aの内周面との間にはカラー58が挿入されている。カラー58の外周面はカラー挿入用孔22aの内周面に密着しており、カラー58の内周面はPTO軸12の外周面に密着している。また、PTO軸12の外周面にはシール部材が設けられており、PTO軸12の外周面とカラー内周面との間はシールされている。
油圧ポンプ13はPTO軸12の先端とは逆側の端部に連結されている。油圧ポンプ13は、PTO軸12の回転によって駆動され、作動油をPTO軸12の外周面と入力軸4の内周面との間の隙間に吐出する。
油圧ポンプ13から吐出された作動油は、油圧回路を介してロックアップクラッチ装置10の油室16bに供給される。油圧回路は、図2に示すように、第1油路61と、前述の油溜め部60と、第2油路62と、第3油路63と、第4油路64と、から構成されている。
車両の低速領域では、ロックアップクラッチ装置10はオフされている。すなわち、ロックアップクラッチ装置10の油室16bに作動油は供給されていない。この場合は、エンジンから入力部材8に入力された動力は、トルクコンバータ本体9を介して入力軸4に伝達される。
油圧ポンプ13から吐出された作動油は、PTO軸12と入力軸4との間の隙間である油路61を通ってロックアップクラッチ装置10に導かれる。このため、PTO軸12の内部に油路としての孔を形成する必要がない。したがって、簡単な構成で、かつ作動油の漏れを少なくして、油圧ポンプ13からの作動油をロックアップクラッチ装置10に導くことができる。また、PTO軸12を中実で形成できるために、熱処理工程における歪みを抑えることができる。
本発明は以上のような実施形態に限定されるものではなく、本発明の範囲を逸脱することなく種々の変形又は修正が可能である。
4 入力軸
5 トランスミッション本体
8 入力部材
9 トルクコンバータ本体
10 ロックアップクラッチ装置
12 PTO軸(ポンプ駆動軸)
13 油圧ポンプ
15 PTO軸連結部
16 入力軸支持部
16b 油室
16d 支持孔
21b スプライン孔(連結用孔)
22b 嵌合孔
38 タービンハブ
39 ベアリング
41 ピストン
42 第1クラッチプレート
43 第2クラッチプレート
60 油溜め部
61 第1油路
62 第2油路
63 第3油路
64 第4油路
Claims (3)
- エンジンと、
前記エンジンに連結されるトランスミッションと、
油圧ポンプと、
を有する作業車両であって、
前記トランスミッションは、
前記エンジンからの動力が入力される入力部材と、
筒状の入力軸を有するトランスミッション本体と、
前記入力部材に連結され、前記入力部材からの動力を前記入力軸に流体を介して伝達するトルクコンバータ本体と、
油圧によって作動するピストンと、前記ピストンの背面に形成された油室と、前記ピストンの作動によって前記入力部材からの動力を前記入力軸に伝達するクラッチ部と、を有するロックアップクラッチ装置と、
前記入力軸の内部を貫通して前記入力軸と同軸に配置され、前記油圧ポンプへ駆動力を伝達するポンプ駆動軸と、
前記入力軸の内周面と前記ポンプ駆動軸の外周面との間に形成され、前記ロックアップクラッチ装置の油室へ通じる油路と、
を備えた作業車両。 - 前記ポンプ駆動軸は、先端部が前記入力軸の先端面からエンジン側に突出して延びており、
前記入力部材は、
中心部に配置され、前記ポンプ駆動軸の先端部が連結される連結用孔と、
前記連結用孔と同軸に配置され、前記連結用孔より大径に形成され前記入力軸の先端部の外周面と嵌合する嵌合孔と、
前記嵌合孔の内周面と、前記入力軸先端面と、前記ポンプ駆動軸の外周面と、によって形成され、前記油路に連通する油溜め部と、
前記油溜め部と前記ロックアップクラッチ装置の油室とを連通する連通孔と、
を有する、請求項1に記載の作業車両。 - 中心部に円筒部を有し、その内周部が前記入力軸の外周部と連結され、前記トルクコンバータ本体からの動力を前記入力軸へ伝達するタービンハブと、
前記円筒部の外周に、内周が嵌合するベアリングと、
をさらに備え、
前記入力部材は、
前記嵌合孔と同軸であり、前記入力部材に配置され、前記ベアリングの外周と嵌合する支持孔をさらに有し、
前記入力軸は、前記タービンハブ及び前記ベアリングを介して前記入力部材に支持されている、
請求項2に記載の作業車両。
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GB1220114.1A GB2495232B (en) | 2011-08-11 | 2012-04-18 | Work vehicle |
CN2012800017764A CN103052831B (zh) | 2011-08-11 | 2012-04-18 | 作业车辆 |
US13/700,399 US8727088B2 (en) | 2011-08-11 | 2012-04-18 | Work vehicle |
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JP2011175533A JP5106663B1 (ja) | 2011-08-11 | 2011-08-11 | 作業車両 |
JP2011-175533 | 2011-08-11 |
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US (1) | US8727088B2 (ja) |
JP (1) | JP5106663B1 (ja) |
CN (1) | CN103052831B (ja) |
WO (1) | WO2013021691A1 (ja) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2015160673A1 (en) * | 2014-04-17 | 2015-10-22 | Schaeffler Technologies AG & Co. KG | Hub assembly for a torque converter and related method |
KR101900264B1 (ko) * | 2014-05-29 | 2018-09-20 | 대동공업주식회사 | 농용 작업차의 미션조합 |
US11459540B2 (en) | 2015-07-28 | 2022-10-04 | Flodesign Sonics, Inc. | Expanded bed affinity selection |
US11474085B2 (en) | 2015-07-28 | 2022-10-18 | Flodesign Sonics, Inc. | Expanded bed affinity selection |
CN107061662A (zh) * | 2016-01-13 | 2017-08-18 | 熵零技术逻辑工程院集团股份有限公司 | 一种能量调整系统 |
US9759302B2 (en) | 2016-01-25 | 2017-09-12 | Ford Global Technologies, Llc | Bypass clutch for a torque converter |
JP2021152388A (ja) * | 2020-03-24 | 2021-09-30 | 株式会社小松製作所 | 動力伝達装置及び動力伝達方法 |
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Also Published As
Publication number | Publication date |
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CN103052831A (zh) | 2013-04-17 |
CN103052831B (zh) | 2013-11-27 |
JP5106663B1 (ja) | 2012-12-26 |
US8727088B2 (en) | 2014-05-20 |
JP2013036591A (ja) | 2013-02-21 |
US20130146412A1 (en) | 2013-06-13 |
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