WO2017047475A1 - 油圧式動力伝達装置 - Google Patents
油圧式動力伝達装置 Download PDFInfo
- Publication number
- WO2017047475A1 WO2017047475A1 PCT/JP2016/076356 JP2016076356W WO2017047475A1 WO 2017047475 A1 WO2017047475 A1 WO 2017047475A1 JP 2016076356 W JP2016076356 W JP 2016076356W WO 2017047475 A1 WO2017047475 A1 WO 2017047475A1
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- WIPO (PCT)
- Prior art keywords
- hydraulic
- clutch
- power transmission
- transmission device
- hydraulic power
- Prior art date
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 65
- 230000001105 regulatory effect Effects 0.000 claims abstract description 53
- 239000010720 hydraulic oil Substances 0.000 claims description 22
- 230000002093 peripheral effect Effects 0.000 claims description 13
- 230000007423 decrease Effects 0.000 abstract description 3
- 230000001141 propulsive effect Effects 0.000 abstract 2
- 239000003921 oil Substances 0.000 description 85
- 238000005461 lubrication Methods 0.000 description 12
- 230000007246 mechanism Effects 0.000 description 8
- 239000002783 friction material Substances 0.000 description 7
- 239000010687 lubricating oil Substances 0.000 description 4
- 230000006866 deterioration Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000013019 agitation Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
Images
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/644—Hub construction
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/083—Actuators therefor
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
- F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0221—Valves for clutch control systems; Details thereof
Definitions
- the present invention relates to a hydraulic power transmission device including a hydraulic clutch, and more particularly, to a hydraulic power transmission device that transmits a driving force by engaging a clutch when a hydraulic piston presses a friction material.
- the multi-plate clutch mechanism is mainly composed of a bottomed cylindrical clutch guide and a clutch hub disposed concentrically inside the clutch guide.
- a plurality of separator plates (friction materials) are attached to the inner peripheral surface of the clutch guide by spline fitting (coupling).
- a plurality of friction plates (friction materials) are alternately attached to the outer peripheral surface of the clutch hub by spline fitting with the separator plate (see, for example, Patent Document 1).
- the multi-plate clutch mechanism includes a hydraulic piston that applies pressure to the laminated body (friction engagement portion) of the separator plate and the friction plate to press-bond, and a piston chamber that drives the hydraulic piston. Accordingly, when hydraulic oil (oil) is supplied to the piston chamber, the hydraulic piston is driven in the axial direction, and the friction engagement portion is pressed in the axial direction by the hydraulic piston, thereby causing the clutch guide side, the clutch hub side, Torque is transmitted between the two.
- the transmission torque capacity of the multi-plate clutch mechanism varies depending on the degree of engagement of the friction engagement portion. Therefore, a pressing load receiving portion that receives the pressing force of the hydraulic piston is provided at the rear portion of the clutch guide so that the pressing force applied by the hydraulic piston is efficiently transmitted to the friction engagement portion.
- a hydraulic control circuit that supplies oil to the multi-plate clutch mechanism, an oil strainer that accumulates oil, an electric oil pump that sucks oil from the oil strainer and pumps it to the oil passage, and a piston that drives a hydraulic piston that engages the clutch Chamber, a linear solenoid valve provided downstream of the piston chamber for regulating hydraulic oil to a predetermined pressure, an oil passage on the side from the electric oil pump to the piston chamber, and a return from the piston chamber to the linear solenoid valve 2.
- a hydraulic control device including a side oil passage is known (see, for example, Patent Document 2).
- the oil sucked up by the electric oil pump from the oil strainer is supplied to the piston chamber of the hydraulic piston through the oil passage on the going side, and then returned from the piston chamber to the return side. After being adjusted to a predetermined oil pressure, a part is returned to the oil strainer, and the rest is supplied to lubrication of rotating sliding parts such as bearings and clutches.
- the linear solenoid valve is controlled by a computer based on a signal output from the hydraulic sensor, it is stored in a case called a hydraulic control body.
- the lubrication for the rotating sliding parts such as the bearing and the clutch is performed via an oil passage (axial oil passage) formed inside the shaft of the center shaft.
- the shaft is lubricated.
- the hydraulic control body is disposed on the shaft of the center shaft and in the vicinity of the center of the device so that the amount of oil lubrication for the left and right clutches is equal.
- a tapered roller bearing, an angular ball bearing, or the like is used as a bearing for the center shaft spline-coupled with a hypoid gear that transmits a driving force at a substantially right angle.
- these bearings are fixed to a case with a tightening margin added by a ring member (bearing set plate) having an open center.
- the arrangement of the hydraulic control body limits the degree of freedom related to the arrangement of the pressure load receiving portion that receives the pressing force of the hydraulic piston.
- the pressing load receiving portion is arranged offset with respect to the pressing position of the hydraulic piston, thereby reducing the thrust efficiency of the hydraulic piston at the time of clutch engagement, and there is a possibility that the transmission torque capacity of the clutch will be insufficient with respect to the required amount. is there.
- the bearing set plate that adds a tightening margin to the taper roller bearing or the like is fastened with bolts and fixed to the case.
- the degree of freedom related to the arrangement of the pressing load receiving portion is limited by the arrangement of the bolts, and as a result, the pressing load receiving portion is arranged offset with respect to the pushing position of the hydraulic piston as in the arrangement of the hydraulic control body. As a result, the transmission torque capacity at the time of clutch engagement may be insufficient with respect to the required amount.
- the present invention has been made in view of the above-described problems of the prior art, and an object of the present invention is to provide a hydraulic power transmission device that can suppress a pressure loss in an oil passage downstream from a piston chamber of a hydraulic clutch. There is.
- Another object of the present invention is to provide a hydraulic power transmission device capable of preventing a decrease in transmission torque capacity at the time of clutch engagement by eliminating an offset between a pressing position of a hydraulic piston and a receiving position of the pressing force. It is to provide.
- a hydraulic power transmission device includes an input shaft (4) to which a driving force from a driving source is transmitted, and a hydraulic pressure for connecting and disconnecting the driving force transmitted to the input shaft (4).
- a hydraulic power transmission device including a clutch (5) and an output shaft (6) connected to an input shaft (4) via a hydraulic clutch (5), wherein the hydraulic clutch (5) A friction engagement element (51, 52) for connecting and disconnecting the piston, and a piston chamber (59) for driving a piston member (57) for applying a pressing force to the friction engagement element (51, 52).
- the pressure regulating valve (8) for regulating the hydraulic oil flowing out from the piston chamber (59) of the hydraulic clutch (5) is provided adjacent to the piston chamber (59). 59) to the pressure regulating valve (8), the length of the oil passage can be kept short, thereby reducing the pressure loss in the oil passage.
- the pressure regulating valve (8) is provided adjacent to the piston chamber (59) of the hydraulic clutch (5), the hydraulic control body required in the conventional hydraulic power transmission device becomes unnecessary, An oil passage from the piston chamber (59) to the hydraulic control body becomes unnecessary. As a result, the entire apparatus can be downsized and the manufacturing cost can be reduced.
- the friction engagement elements (51, 52) of the hydraulic clutch (5) are provided on either the input shaft (4) side or the output shaft (6) side clutch hub ( 52), a clutch guide (51) provided on either the input shaft (4) side or the output shaft (6) side, a first friction material (53) engaged with the clutch hub (52), and a clutch And a friction engagement portion in which second friction materials (54) engaged with the guide (51) are alternately stacked, and the clutch hub (52) has a bearing (13) for supporting the clutch hub (52). ) And a second through hole (52b) communicating from the radially inner peripheral surface of the clutch hub (52) to the outer peripheral surface.
- the first through hole (52a) has an opening projecting in the axial direction on the outer diameter side of the opening portion of the first through hole (52a) or on the outer diameter side of the opening portion of the second through hole (52b).
- the protrusion part (52c) which covers the outer-diameter side of a part may be formed.
- the protruding portion (52c) is provided on the outer diameter side of the opening portion of the first through hole (52a) or the second through hole (52b), centrifugal force is applied to the introduced hydraulic oil. Even if the above-mentioned operation occurs, the projecting portion (52c) serves as a guide portion for the hydraulic oil, guides (introduces) the hydraulic oil into the first through hole (52a) or the second through hole (52b), and the bearing ( 13) and the frictional engagement portion can be lubricated.
- a case (58) that accommodates at least a part of the hydraulic power transmission device and an inner peripheral surface of the case (58) are formed and discharged from the pressure regulating valve (8).
- a discharge port (60a) through which hydraulic oil flows out, and another protrusion (60b) protruding axially on the outer diameter side of the discharge port (60a) and covering the outer diameter side of the discharge port (60a) May be provided.
- discharge portion (60b) that discharges in the axial direction and covers the outer diameter side of the discharge port (60a) is provided on the outer diameter side of the discharge port (60a) on the inner peripheral surface of the case (58). Therefore, even when centrifugal force acts on the introduced hydraulic oil, the discharge port (60a) serves as a guide portion for the hydraulic oil, and guides (introduces) the hydraulic oil to the hydraulic clutch (5, 6). It is possible to lubricate sliding rotating parts such as bearings.
- the hydraulic power transmission device includes an input shaft (4) to which a driving force from a driving source is transmitted, and a hydraulic clutch (5) that connects and disconnects the driving force transmitted to the input shaft (4). And an output shaft (6) connected to the input shaft (4) via the hydraulic clutch (5).
- the hydraulic clutch (5) is a friction engagement element (51, 52) for connecting and disconnecting the driving force.
- the pressure oil is communicated with the piston chamber (59) to regulate the hydraulic oil flowing out from the piston chamber (59).
- a pressure valve (8), and the pressure regulating valve (8) is connected to the piston chamber (59). While being disposed in contact, the pressing portion of the piston member (57) (81) and the pressing load receiving (82) is characterized in that it is at approximately the same relates radially.
- the pressure regulating valve (8) for regulating the hydraulic oil flowing out from the piston chamber (59) of the hydraulic clutch (5) is provided adjacent to the piston chamber (59) of the hydraulic clutch (5).
- the degree of freedom related to the arrangement of the pressing load receiving portion (82) that receives the pressing force (thrust) of the piston member (57) is improved, and the pressing load receiving portion (82) and the pressing portion of the piston member (57) ( 81) can be arranged at substantially the same position in the radial direction.
- the pressing portion (81) and the pressing load receiving portion (82) of the piston member (57) are disposed at substantially the same position in the radial direction, the pressing position and the pressing force of the piston member (57) at the time of clutch engagement.
- the thrust efficiency of the piston member (57) is improved, and the reduction of the transmission torque capacity in the hydraulic clutch (5) is preferably prevented.
- the hydraulic power transmission device includes a case (9) that houses at least a part of the hydraulic power transmission device, and the pressing load receiving portion (82) is a friction engagement element (51) in the case (9). , 52) may be a protrusion-like portion protruding in the axial direction toward the friction engagement element. According to this configuration, it is possible to configure the pressing load receiving portion that receives the pressing load of the piston member applied to the friction engagement element by using a part of the case that accommodates the hydraulic clutch. The number of points can be reduced to simplify the configuration.
- the hydraulic power transmission device includes a bearing (11, 12) that rotatably supports the input shaft (4), and a case (9) that accommodates at least a part of the hydraulic power transmission device. (11, 12) may be fixed by a structure sandwiched between the stepped portions (9a, 9b) of the case (9) and the stepped portions (4aa, 3a) of the input shaft (4) supported by the bearing. Good.
- the bearings (11, 12) are fixed by a structure sandwiched between the stepped portions (9a, 9b) of the case (9) and the stepped portions (4aa, 3a) of the input shaft (4).
- the bearing set plate and its fixing bolt, which are necessary as means for fixing the bearing, are no longer necessary.
- the degree of freedom related to the arrangement of the pressing load receiving portion (82) that receives the pressing force of the piston member (57) is improved, whereby the pressing load receiving portion (82) is moved to the pressing portion (81 of the piston member (57). ) In substantially the same radial position.
- the piston member (57) and the pressing load receiving portion (82) are provided with the first thrust bearing (83) and the first thrust bearing (83) that rotatably support the friction engagement elements (51, 52).
- Two thrust bearings (84) may be provided, and the first thrust bearing (83) and the second thrust bearing (84) may be arranged at substantially the same position in the radial direction.
- the hydraulic oil discharged from the pressure regulating valve (8) does not pass through the inside of the input shaft (4) or the inside of the output shaft (6), and the frictional engagement of the hydraulic clutch (5). It may be configured to be introduced into the combination element (51, 52).
- the hydraulic oil discharged from the pressure regulating valve (8) does not pass through the input shaft (4) or the output shaft (6), and the friction engagement element (51) of the hydraulic clutch (5).
- the friction engagement element (51) of the hydraulic clutch (5) Since it is configured to be introduced into the inside, it is based on lubrication (shaft core lubrication) by an oil passage (shaft core oil passage) formed inside the input shaft (4) or the output shaft (6). Therefore, the inside of the hydraulic clutch (5) can be suitably lubricated.
- the output shaft (6) is a pair of rotating shafts (6L, 6R) that extend in the width direction of the vehicle and transmit driving force to the left and right drive wheels of the vehicle.
- the clutch (5) is a pair of clutches (5L, 5R) provided between the input shaft (4) and each of the pair of rotating shafts
- the pressure regulating valve (8) is an outer side in the width direction of each of the pair of clutches. It may be a pair of pressure regulating valves (8L, 8R) arranged adjacent to each other.
- the output shaft (6) is a pair of rotating shafts (6L, 6R)
- the hydraulic clutch (5) is a pair of clutches (5L, 5R)
- the pressure regulating valve (8) is a pair of pressure regulating valves ( 8L, 8R)
- the hydraulic power transmission device of the present invention can be applied to a vehicle differential. This makes it possible to distribute desired torque to the left and right drive wheels when the clutch (5L, 5R) is engaged.
- symbol in the parenthesis in the means to solve this subject shows the drawing reference number of the corresponding component in embodiment mentioned later for reference.
- the length of the oil passage from the piston chamber to the pressure regulating valve can be shortened, so that the pressure loss in the oil passage from the piston chamber to the pressure regulating valve is reduced. It becomes possible to suppress. Further, the hydraulic control body and the oil passage from the piston chamber of the hydraulic clutch to the hydraulic control body, which are necessary in the conventional hydraulic power transmission device, are not required. As a result, the entire apparatus can be downsized and the manufacturing cost can be reduced. Further, when the hydraulic power transmission device of the present invention is applied to a vehicle differential, it is possible to suitably prevent the influence of the clutch drag phenomenon on the vehicle behavior and the deterioration of the fuel consumption rate.
- the pressure regulating valve for regulating the hydraulic oil discharged from the piston chamber of the hydraulic clutch is provided adjacent to the piston chamber of the hydraulic clutch.
- the hydraulic control body which was necessary for core lubrication, is no longer necessary.
- the bearing is fixed by a structure that sandwiches the front and rear in the axial direction, a bearing set plate and its fixing bolt, which are necessary as conventional means for fixing the bearing, become unnecessary.
- the hydraulic control body, the bearing set plate, and the bolts for fixing the hydraulic control body are not required, the degree of freedom related to the arrangement of the pressing load receiving portion that receives the pressing force of the piston member is improved, and the pressing load receiving portion is connected to the piston. It becomes possible to arrange
- desired torque can be distributed to the left and right drive wheels, respectively, when the clutch is engaged.
- FIG. 1 is an explanatory cross-sectional view of a main part showing a hydraulic power transmission device 100 according to an embodiment of the present invention.
- FIG. 2 is an enlarged explanatory view of a part A in FIG.
- FIG. 3 is a perspective explanatory view showing a hydraulic circuit of the hydraulic power transmission device 100.
- the hydraulic power transmission device 100 is configured as a differential mechanism (differential mechanism) for distributing the rotation of the drive shaft 1 to left and right wheels (not shown).
- the drive shaft 1 is coupled to a propeller shaft (not shown) to transmit a driving force from a drive source (engine) (not shown).
- the hydraulic power transmission device 100 is arranged so as to rotate integrally with the drive bevel gear 3, the drive bevel gear 2 that rotates integrally with the drive shaft 1, the driven bevel gear 3 that meshes with the drive bevel gear 2, and the drive bevel gear 3.
- Left and right output shafts 6L, 6R, electric oil pump 7 for supplying hydraulic oil (oil) to the piston chambers 59 (FIG.
- the center shaft 4 is supported by a differential case 9 of a differential mechanism via tapered bearings 11 and 12.
- the center shaft 4 is roughly configured to include a central large diameter portion 4a, left and right middle diameter portions 4b of the large diameter portion 4a, and left and right small diameter portions 4c adjacent to the middle diameter portion 4b.
- the driven bevel gear 3 is fixed to the large diameter portion 4a, and the entire center shaft 4 rotates integrally.
- a plurality of spline teeth are formed in the circumferential direction in each of the small diameter portions 4c at the left and right ends of the center shaft 4 so as to rotate integrally with the respective clutch guides 51 (FIG. 2) of the corresponding left and right clutch devices 5L and 5R. Splined.
- the left and right clutch devices 5L and 5R are composed of wet multi-plate clutches (hydraulic clutches). Since the left and right clutch devices 5L and 5R have the same configuration, only the right clutch device 5R will be described here with reference to FIG. For the same reason, in the following description, the subscripts L and R meaning “left” or “right” are omitted unless it is particularly necessary to distinguish them.
- a plurality of separator plates (first friction materials) 53 are splined to the inner peripheral surface of the clutch guide 51, which is an input side rotating member, at predetermined intervals in the axial direction, and output side
- a plurality of friction plates (second friction materials) 54 are splined to the outer peripheral surface of the clutch hub 52, which is a rotating member, at predetermined intervals in the axial direction, and each separator plate 53 and each friction plate 54 has a shaft.
- the separator plates 53 and the friction plates 54 are stacked so as to be alternately arranged in the direction.
- a spline portion 55 is formed near the base of the clutch guide 51, and the spline portion 55 is splined to the small diameter portion 4 c at the right end of the center shaft 4.
- a spline portion 56 is formed near the root of the clutch hub 52. Accordingly, the spline portion 56 is splined to the right output shaft 6R, and the clutch hub 52 is rotatably fixed to the case 58 via the ball bearing 14, and rotates integrally with the right output shaft 6R.
- the clutch guide 51 and the clutch hub 52 are supported by each other via the ball bearing 13 and can rotate relative to each other.
- the laminated body (friction engagement portion) of the separator plate 53 and the friction plate 54 is driven in the axial direction (leftward in FIG. 2) by the piston 57 when the clutch is engaged.
- the piston 57 is driven, the separator plate 53 and the friction plate 54 are frictionally engaged, and the clutch is fastened.
- the piston 57 is hydraulically driven by the piston chamber 59 and is controlled so as to obtain a required clutch engagement amount in the friction engagement portion.
- a pressing portion 81 On the side of the piston 57 facing the friction engagement portion, a pressing portion 81 that protrudes in the axial direction (left direction in the drawing) and presses the friction engagement portion is formed.
- a first thrust bearing 83 that rotatably supports the friction engagement portion in the thrust direction is attached to the distal end portion of the pressing portion 81.
- a pressing load receiving portion 82 that protrudes in the axial direction (right direction in the drawing) and receives the pressing load of the piston 57 applied to the friction engagement portion is formed at a position facing the rear side of the clutch guide 51 in the case 9.
- a second thrust bearing 84 that rotatably supports the clutch guide 51 in the thrust direction is attached to the distal end portion of the pressing load receiving portion 82.
- the first thrust bearing 83 and the second thrust bearing 84 are respectively disposed at the same height position or substantially the same height position in the radial direction. Thereby, the pushing position of the piston 57 and the receiving position of the pushing force are not offset, the thrust efficiency of the piston 57 at the time of clutch engagement is improved, and the necessary transmission torque capacity in the clutch device 5 can be secured. Become.
- the taper bearing 12 that rotatably supports the center shaft 4 is fixed by sandwiching the stepped portion 9a of the case 9 and the stepped portion 4aa of the large-diameter portion 4a of the center shaft 4 in the axial direction (longitudinal direction). Yes. As shown in FIG. 1, the taper bearing 11 that similarly supports the center shaft 4 is fixed by sandwiching the stepped portion 9 b of the case 9 and the stepped portion 3 a formed in the driven bevel gear 3 in the axial direction. ing.
- the tapered bearings 11 and 12 are formed by the stepped portions 9a and 9b of the case 9 and the stepped portion 4aa of the center shaft 4 or the stepped portion 3a of the driven bevel gear 3 which is a support object supported by the bearings 11 and 12. Fixed by the sandwiched structure. Therefore, in the hydraulic power transmission apparatus 100, the bearing set plate and its fixing bolt, which have been conventionally used as a means for fixing the bearing, are unnecessary. As a result, the degree of freedom related to the arrangement of the pressing load receiving portion 82 is improved, whereby the first thrust bearing 83 and the second thrust bearing 84 are respectively arranged at the same height or substantially the same height in the radial direction. This makes it possible to realize a so-called clutch series pushing structure that receives the pushing force of the piston 57 at the same height or substantially the same height in the radial direction.
- the center shaft 4 corresponds to an “input shaft” for the left and right clutch devices 5L and 5R
- the left and right output shafts 6L and 6R correspond to an “output shaft” for the left and right clutch devices 5L and 5R.
- the electric oil pump 7 includes a motor portion 71 that generates rotational power, and the hydraulic power (oil) is sucked from the oil strainer 66 (FIG. 3) by the rotational power, and the left and right clutch devices 5L. , 5R, and the pump part 72 has a double pump structure in which two left and right internal gear pumps 74L, 74R are connected in series on a pump shaft 73.
- the left internal gear pump 74L pumps oil to the piston chamber 59L of the left clutch device 5L
- the right internal gear pump 74R pumps oil to the piston chamber 59R of the right clutch device 5R. Yes.
- the left and right pressure regulating valves 8L and 8R are linear solenoid valves (electromagnetic pressure regulating valves). As shown in FIG. 3, the left and right pressure regulating valves 8L, 8R in the present embodiment are disposed substantially symmetrically beside the piston chambers 59L, 59R of the left and right clutch devices 5L, 5R, respectively. Accordingly, the oil passages from the left and right piston chambers 59L, 59R to the left and right pressure regulating valves 8L, 8R are respectively configured with the shortest distance.
- the oil passages from the left and right internal gear pumps 74L and 74R to the left and right pressure regulating valves 8L and 8R supply oil to the case internal oil passage 64 that supplies oil to the left piston chamber 59L and the right piston chamber 59R. Only the oil passage 65 in the case is sufficient.
- left and right pressure regulating valves 8L and 8R have the same configuration, the subscripts L and R meaning left or right are omitted in the following description unless it is particularly necessary to distinguish them.
- FIG. 4 is a cross-sectional explanatory view of a main part showing the pressure regulating valve 8 according to the present invention.
- 4A is a cross-sectional view taken along the line AA in FIG. 2
- FIG. 4B is a cross-sectional view taken along the line BB in FIG. 4A.
- the pressure regulating valve 8 is configured by connecting a linear solenoid 85 in series to a pressure regulating valve 81 including a valve body 82, a body 83, and a spring 84.
- the linear solenoid 85 includes a coil 86 that generates magnetic lines of force, a hollow cylindrical magnetic body 87 that transmits the magnetic lines of force generated by the coils 86, a plunger 88 that is driven in the axial direction by the action of the lines of magnetic force, and a current that flows through the coil 86.
- the plunger 88 is joined to the end of the valve body 82, and the magnetic body 87 is joined to the body 83.
- the body 83 is formed with an inlet port P / IN, an outlet port P / OUT, and a return port P / FB, respectively. Between the valve body 82 and the body 83, a first annular oil passage 82a and a second annular oil passage 82a are formed. An oil passage 82b, a third annular oil passage 82c, and a fourth annular oil passage 82d are formed.
- the first annular oil passage 82a connects the inlet port P / IN and the outlet port P / OUT, whereas the second annular oil passage 82b, the third annular oil passage 82c, and the fourth annular oil passage 82d are provided in the piston chamber 59.
- This is an annular oil passage through which oil discharged from the oil acts on the valve body 82 as feedback pressure.
- a gap S is partially formed between the piston case 58 and the body 83, and oil discharged from the piston chamber 59 passes through the gap S and returns to the return port P.
- / FB is configured to act on the valve body 82 as feedback pressure.
- the oil flowing from the piston chamber 59 of the clutch device 5 through the filter F into the inlet port P / IN is the feedback pressure (hydraulic pressure) of the oil discharged from the piston chamber 59, the thrust of the plunger 88 of the linear solenoid 85,
- the spring 84 is adjusted to a hydraulic pressure in which three forces, ie, an elastic force acting on the valve body, are balanced, and discharged from the outlet port P / OUT of the pressure regulating valve 8 to the downstream.
- the pressure regulating valve 8 is disposed adjacent to the piston chamber 59, that is, directly beside the piston chamber 59. In this way, by arranging the pressure regulating valve 8 directly beside the piston chamber 59, the oil passage from the piston chamber 59 to the inlet port P / OUT of the pressure regulating valve 8 can be connected at the shortest distance from the piston chamber 59. It is possible to minimize the pressure loss in the oil passage leading to the pressure regulating valve 8. Further, as will be described later, the oil discharged from the outlet port P / OUT of the pressure regulating valve 8 can be introduced into the clutch device 5 without going through the shaft oil passage formed in the shaft. .
- the pressure regulating valve 8 is externally mounted (externally attached) to the differential case 9. Since the pressure regulating valve 8 is externally attached (externally attached) to the differential case 9 as described above, it is not necessary to incorporate the pressure regulating valve 8 as a hydraulic control body inside the differential case 9, and as a result, it is necessary in the conventional hydraulic power transmission device. Thus, the control body and the oil passage from the piston chamber to the control body can be eliminated, and the entire apparatus can be reduced in size and cost.
- a lubricating oil passage 60 is formed in the case 58 to guide the oil discharged from the outlet port P / OUT of the pressure regulating valve 8 directly to the inside of the clutch device 5.
- the lubrication for the rotating and sliding parts such as the ball bearing and the separator plate and the friction plate provided in the clutch device is performed in an oil passage (axial oil passage) formed in the shaft. Oil is supplied and the oil is diffused by the centrifugal force generated by the rotation of the shaft, and the diffused oil is supplied to a rotating sliding portion such as a ball bearing through a through hole (not shown) formed in the outer peripheral surface of the shaft. It was.
- the conventional hydraulic power transmission device employs shaft center lubrication.
- the oil discharged from the outlet port P / OUT of the pressure regulating valve 8 does not pass through the oil passage (axial core oil passage) formed inside the shaft.
- the oil is introduced directly into the clutch device 5 via 60, and the introduced oil is agitated by the rotation of the clutch hub 52, thereby lubricating the rotating sliding portions such as the ball bearings 13 and 14 and the like. That is, the hydraulic power transmission device 100 employs agitation lubrication. Therefore, the oil introduced into the clutch device 5 through the lubricating oil passage 60 is distributed to the ball bearings 13 and 14 efficiently and evenly at a portion facing the ball bearing 13 of the clutch hub 52.
- Through-holes 52a are provided.
- a second through hole 52b penetrating the inner peripheral surface and the outer peripheral surface in the radial direction of the clutch hub 52 is provided so that the oil spreads efficiently and evenly on the separator plate 53 and the friction plate 54.
- FIG. 5 is an explanatory perspective view showing the clutch hub 52 according to the present invention.
- the oil introduced into the clutch device 5 through the lubricating oil passage 60 is efficiently and evenly distributed to the ball bearing 13 and the rotational sliding portions such as the separator plate 53 and the friction plate 54.
- One and two through holes 52a and second through holes 52b are provided at equal intervals. The number is an example, and is not limited to this.
- an eaves-shaped portion (projecting portion) 52c extending in the axial direction is provided on the radially outer side of the first through hole 52a. Therefore, the oil diffused radially outward by the centrifugal force generated by the rotation of the clutch hub 52 is introduced into the first through hole 52a by the eaves-shaped portion 52c, and the ball bearing 13 is efficiently lubricated.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
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- Fluid Mechanics (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
Description
なお、本課題を解決する手段における括弧内の符号は、後述する実施形態における対応する構成要素の図面参照番号を参考のために示すものである。
また、従来の油圧式動力伝達装置において必要であった油圧制御ボディ並びに油圧クラッチのピストン室から油圧制御ボディに到る油路が不要となる。これにより装置全体を小型化すると共に製造コストを下げることが可能となる。
また、本発明の油圧式動力伝達装置を車両の差動装置に適用する場合は、クラッチ引き摺り現象による車両挙動への影響ならびに燃料消費率の悪化を好適に防止することが可能となる。
この油圧式動力伝達装置100は、駆動シャフト1の回転を左右の車輪(図示せず)に配分するための差動機構(ディファレンシャル機構)として構成されている。駆動シャフト1は、図示しないプロペラシャフトに結合し、図示しない駆動源(エンジン)からの駆動力が伝達される。油圧式動力伝達装置100は、駆動シャフト1と一体回転する駆動ベベルギヤ2と、該駆動ベベルギヤ2に噛み合う従動ベベルギヤ3と、駆動シャフト1に直交して配置され、従動ベベルギヤ3と一体回転するように結合されたセンターシャフト4と、該センターシャフト4の左右に配置された左右のクラッチ装置5L,5Rと、左右のクラッチ装置5L,5Rによって伝達される各駆動力を左右の車輪(図示せず)にそれぞれ伝達する左右の出力シャフト6L,6Rと、左右のクラッチ装置5L,5Rの各ピストン室59(図2)に作動油(オイル)を供給する電動オイルポンプ7と、左右のクラッチ装置5L,5Rの各ピストン室59(図2)から排出される各オイルの圧力を調圧する左右の調圧弁8L,8Rと、ディファレンシャル機構を覆う(収容する)デフケース(ケース)9とを備える。以下、各構成について更に説明する。
Claims (10)
- 駆動源からの駆動力が伝達される入力軸と、
前記入力軸に伝達された駆動力を断接する油圧クラッチと、
前記油圧クラッチを介して前記入力軸に接続される出力軸と、を備える油圧式動力伝達装置であって、
前記油圧クラッチは、駆動力を断接するための摩擦係合要素と、該摩擦係合要素に押圧力を付与するピストン部材を駆動するためのピストン室と、を含み、
前記ピストン室に連通して該ピストン室から流出する作動油を調圧する調圧弁を備え、
前記調圧弁は、前記ピストン室に隣接して配置されていることを特徴とする油圧式動力伝達装置。 - 前記油圧クラッチの前記摩擦係合要素は、前記入力軸側と前記出力軸側のいずれか一方に設けたクラッチハブと、前記入力軸側と前記出力軸側のいずれか他方に設けたクラッチガイドと、前記クラッチハブに係合する第1摩擦材と、前記クラッチガイドに係合する第2摩擦材とが交互に積層された摩擦係合部とを備え、
前記クラッチハブには、該クラッチハブを支持するベアリングに連通する第1の貫通穴と、該クラッチハブの径方向の内周面から外周面に連通する第2の貫通穴とが設けられていることを特徴とする請求項1に記載の油圧式動力伝達装置。 - 前記第1の貫通穴の開口部の外径側又は前記第2の貫通穴の開口部の外径側には、軸方向に突出して前記開口部の外径側を覆う突出部が形成されていることを特徴とする請求項2に記載の油圧式動力伝達装置。
- 少なくとも前記油圧式動力伝達装置の一部を収容するケースと、
前記ケースの内周面に形成されて、前記調圧弁から排出される作動油が流出する吐出口と、を備え、
前記吐出口の外径側には、軸方向に突出して前記吐出口の外径側を覆う他の突出部が設けられていることを特徴とする請求項1乃至3の何れか1項に記載の油圧式動力伝達装置。 - 前記油圧クラッチは、前記摩擦係合要素にかかる前記ピストン部材の押圧荷重を受け止める押圧荷重受部を更に備え、
前記ピストン部材の押圧部と前記押圧荷重受部とは、径方向に関し略同じ位置に配置されることを特徴とする請求項1に油圧式動力伝達装置。 - 少なくとも前記油圧式動力伝達装置の一部を収容するケースを備え、
前記押圧荷重受部は、前記ケースにおける前記摩擦係合要素に対向する部分を該摩擦係合要素に向けて軸方向に突出させた突起状の部分であることを特徴とする請求項5に記載の油圧式動力伝達装置。 - 前記入力軸を回転自在に支持する軸受を備え、
前記軸受は、前記ケースの段差部と前記入力軸の段差部とによって挟み込まれる構造によって固定されることを特徴とする請求項5又は6に記載の油圧式動力伝達装置。 - 前記ピストン部材および前記押圧荷重受部は、前記摩擦係合要素を回転自在に支持する第1のスラスト軸受および第2のスラスト軸受をそれぞれ備え、該第1のスラスト軸受と該第2のスラスト軸受とは径方向に関し略同じ位置に配置される
ことを特徴とする請求項5乃至7のいずれか1項に記載の油圧式動力伝達装置。 - 前記調圧弁から排出される作動油は、前記入力軸の内部又は前記出力軸の内部を通らずに前記油圧クラッチの前記摩擦係合要素へ導入されるように構成されている
ことを特徴とする請求項1乃至8のいずれか1項に記載の油圧式動力伝達装置。 - 前記出力軸は、車両の幅方向に延びて該車両の左右の駆動輪に駆動力を伝達する一対の回転軸であり、
前記油圧クラッチは、前記入力軸と前記一対の回転軸それぞれとの間に設けた一対のクラッチであり、
前記調圧弁は、前記一対のクラッチそれぞれの前記幅方向の外側に隣接して配置した一対の調圧弁である
ことを特徴とする請求項1乃至9のいずれか1項に記載の油圧式動力伝達装置。
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CN201680052578.9A CN108026982B (zh) | 2015-09-14 | 2016-09-07 | 液压式动力传递装置 |
US15/757,438 US10563706B2 (en) | 2015-09-14 | 2016-09-07 | Hydraulic power transmission device |
JP2017539858A JP6400217B2 (ja) | 2015-09-14 | 2016-09-07 | 油圧式動力伝達装置 |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
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CN108953415A (zh) * | 2017-05-19 | 2018-12-07 | 本田技研工业株式会社 | 动力传递装置 |
CN108953416A (zh) * | 2017-05-19 | 2018-12-07 | 本田技研工业株式会社 | 动力传递装置 |
US10801596B2 (en) | 2016-12-14 | 2020-10-13 | Honda Motor Co., Ltd. | Power transmission device |
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JP6427609B2 (ja) * | 2016-12-14 | 2018-11-21 | 本田技研工業株式会社 | 動力伝達装置 |
JP6694865B2 (ja) * | 2017-12-28 | 2020-05-20 | 本田技研工業株式会社 | 動力伝達装置 |
JP6734967B1 (ja) * | 2019-06-07 | 2020-08-05 | 川崎重工業株式会社 | 湿式多板クラッチの給油構造およびアジマススラスタ |
CN111895001B (zh) * | 2020-06-16 | 2021-11-26 | 常熟理工学院 | 具有轮载电控液压助力离合装置的轮毂电机轮及变速方法 |
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- 2016-09-07 JP JP2017539858A patent/JP6400217B2/ja not_active Expired - Fee Related
- 2016-09-07 CN CN201680052578.9A patent/CN108026982B/zh active Active
- 2016-09-07 US US15/757,438 patent/US10563706B2/en active Active
- 2016-09-07 WO PCT/JP2016/076356 patent/WO2017047475A1/ja active Application Filing
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JPS5578821A (en) * | 1978-12-05 | 1980-06-13 | Doornes Transmissie Bv | Clutch controller |
JPS62166140U (ja) * | 1986-04-14 | 1987-10-22 | ||
JPH03102623U (ja) * | 1990-02-06 | 1991-10-25 | ||
JPH0663939U (ja) * | 1993-02-19 | 1994-09-09 | 本田技研工業株式会社 | 摩擦係合装置 |
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US10801596B2 (en) | 2016-12-14 | 2020-10-13 | Honda Motor Co., Ltd. | Power transmission device |
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CN108953416A (zh) * | 2017-05-19 | 2018-12-07 | 本田技研工业株式会社 | 动力传递装置 |
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US20180245642A1 (en) | 2018-08-30 |
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CN108026982B (zh) | 2019-12-20 |
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