JP2009243596A - Starting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a starting device capable of regulating leak of working oil from a working oil passage while meeting a request for size reduction. <P>SOLUTION: In the starting device, a first working oil passage a1 is formed at an input shaft 13 of an automatic transmission mechanism, and an oil sump chamber 31a of a turbine hub 31 and a first working oil passage a1 are connected through a second working oil passage a2 formed penetrating to an outer circumference surface of a tip part of the input shaft 13 in the radial direction. The second working oil passage a2 is connected to a cylinder oil chamber 37 through a third working oil passage a3 formed penetrating through the inside of a turbine hub 31 in the radial direction. A fitting member fitted in an inner circumference surface of the turbine hub 31, and an oil seal 50 provided with a lip seal of which the radial direction outer part is fixed on the fitting member and of which the radial direction inner part slide-contacts on the outer circumference surface of the input shaft 13 while being elastically deformed are press-fitted at two positions on both axial sides between which an opening at an outer circumference side of the second working oil passage a2 and an opening at an inner circumference side of the third working oil passage a3 are interposed, in the oil sump chamber 31a of the turbine hub 31. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a starting device in a vehicle having an automatic transmission.

  Generally, in a vehicle having an automatic transmission, the engine torque is smoothly transmitted to the speed change mechanism by using a starting device at the time of starting. This starting device has an oil-tight housing (input side member) connected to the output shaft of the engine, and the input shaft of the speed change mechanism is usually inserted into the housing by spline coupling. And a turbine mechanism (output side member) coupled so as to be integrally rotatable with each other, and a clutch mechanism for mechanically connecting and directly coupling the turbine hub and the housing by operating a clutch. An oil passage for supplying hydraulic oil for switching the clutch mechanism from a non-engaged state to an engaged state as necessary forms an oil passage structure corresponding to the location of the clutch mechanism in the housing. It has been.

  For example, in the starting device described in Patent Document 1, a hydraulic oil passage for supplying hydraulic oil discharged from an oil pump to a clutch mechanism is provided with the following oil passage structure. That is, in the starting device of Patent Document 1, the hydraulic oil passage includes an oil passage extending in the axial direction from the tip of the input shaft of the transmission mechanism and extending in the axial direction, and a tip of the oil passage extending in the axial direction ( An oil passage structure including at least a radially extending oil passage drilled from the front end) toward the hydraulic chamber of the clutch mechanism portion located radially outward from the front cover constituting the front half of the housing. is doing.

  However, when the hydraulic oil passage has such an oil passage structure, the hydraulic pressure of the hydraulic oil discharged from the front end opening (oil hole) of the oil passage extending in the axial direction toward the front side in the axial direction is the front cover. There is a risk that the front cover will be deformed due to stress applied to the front cover. Therefore, as an oil passage structure for avoiding such a concern, for example, the following oil passage structure can be considered.

In other words, when the turbine hub is connected to the input shaft of the speed change mechanism, the oil hole is opened in the outer peripheral surface portion of the input shaft that faces the inner peripheral surface of the through hole of the turbine hub. The oil passage extending in the axial direction is bent radially outward on the tip end side of the input shaft. The turbine hub is formed with at least a radially extending oil passage that penetrates the inside of the turbine hub radially outward from the inner peripheral surface of the through hole, and the axially extending oil passage and the radial direction are formed. If the oil passage structure communicates with the hydraulic chamber of the clutch mechanism section (hereinafter referred to as “improved oil passage structure”) via an oil passage extending to the hydraulic mechanism, a hydraulic oil passage that can avoid the possibility of deformation of the front cover is provided. realizable.
International Publication Number WO2003 / 016736

  By the way, when the above-described improved oil passage structure is adopted as the hydraulic oil passage structure, the hydraulic oil discharged from the oil hole opening in the outer peripheral surface of the input shaft passes through the outer peripheral surface of the input shaft and the turbine hub. It is necessary to regulate leakage in the axial direction between the inner peripheral surface of the hole. Therefore, a seal member is interposed between the outer peripheral surface of the input shaft and the inner peripheral surface of the through hole in the turbine hub. In general, a pair of O-rings are interposed so that an oil hole opened on the outer peripheral surface of the input shaft in the hydraulic oil passage is sandwiched from both sides in the axial direction of the input shaft.

  That is, by forming annular concave grooves at two positions on the outer peripheral surface of the input shaft that sandwich the oil holes opened on the outer peripheral surface of the input shaft from both sides in the axial direction, and inserting O-rings into these concave grooves, respectively. In addition, while restricting the axial movement of each O-ring, the pair of front and rear O-rings restricts hydraulic oil from leaking along the axial direction.

  However, in the above-described improved oil passage structure, it is necessary to form an annular groove for fitting the O-ring on the outer peripheral surface on the tip side of the input shaft, and in order to secure a space for forming this groove, the input shaft However, there is a problem that the size increases in the radial direction and the axial direction. Recently, in order to meet various needs for automatic transmissions, there is a demand for downsizing of the starting device, so it is desirable to solve such problems. Even when a seal ring is used as the seal member, since an annular concave groove for fitting the seal ring is formed on the outer peripheral surface of the input shaft, the same problem as in the case of the O-ring is included. .

  The present invention has been made in view of such circumstances, and an object thereof is to suitably regulate leakage of hydraulic oil supplied through the hydraulic oil passage in the axial direction while responding to a request for downsizing. It is to provide a starting device that can be used.

  In order to achieve the above object, a starting device of the present invention has an input-side member connected to an output shaft of a drive source, a through-hole through which the input shaft of a speed change mechanism can be inserted, and the through-hole has the above-mentioned When the input shaft is inserted from the tip, the output side member connected to the input shaft so as to rotate integrally with the input shaft is directly coupled to the input side member and the output side member so that power can be transmitted by operating the clutch. The input shaft so that an oil hole is opened in an outer peripheral surface portion of the input shaft facing the inner peripheral surface of the through hole in a state where the output side member is coupled to the input shaft of the transmission mechanism. Between the outer peripheral surface of the input shaft and the inner peripheral surface of the through hole so that the oil passage of the oil passage is disposed from both sides in the axial direction of the input shaft. A sealing member interposed between the sealing member and the sealing member. An annular fitting member that is fitted into the through-hole of the force-side member so as to be in pressure contact with the inner peripheral surface of the through-hole, and a radially outer portion is fixed to the fitting member and the radially inner portion The portion includes an annular seal lip formed to be slidable with elastic deformation with respect to the outer peripheral surface of the input shaft.

  According to the above configuration, since the oil seal is applied as the seal member that seals the oil hole of the hydraulic oil passage, it is unnecessary to provide the annular concave groove for installing the seal member in the input shaft of the transmission mechanism. Become. Therefore, it is not necessary to secure the space for disposing the concave groove in the input shaft, and leakage of the hydraulic oil from the hydraulic oil passage can be regulated while meeting the demand for downsizing the entire apparatus.

  In the starting device of the present invention, the seal member further includes an urging member that urges the radially inner portion of the seal lip so as to be in pressure contact with the outer peripheral surface of the input shaft.

  According to the above configuration, the biasing member can enhance the sealing function of the seal member by applying a load radially inward toward the outer peripheral surface of the input shaft with respect to the radially inner portion of the seal lip. it can.

  Further, in the starting device of the present invention, the output side member and the input shaft are arranged on the outer peripheral surface of the input shaft with respect to the concavo-convex engaging portion formed on the inner peripheral surface of the through hole in the output side member. Is formed on the outer peripheral surface of the input shaft. The concave / convex engaged portion is formed so as to be relatively movable in the axial direction of the input shaft and immovable in the circumferential direction. In this embodiment, the input shaft is formed at a position closer to the base end side of the input shaft than the position at which the seal member is disposed.

  According to the above configuration, when the input shaft is assembled to the output side member, the concave-convex engaging portion formed on the outer peripheral surface of the input shaft is inserted to the position where the seal member press-fitted into the output side member is inserted. Never happen. Therefore, in the process of assembling the input shaft, it is possible to prevent the uneven engagement portion of the input shaft from damaging the seal member due to frictional sliding with respect to the seal member.

In the starting device of the present invention, the peripheral edge of the tip surface of the input shaft of the transmission mechanism is chamfered.
According to the above configuration, when the input shaft is assembled to the output side member, the inner peripheral side of the seal member smoothly slides in the axial direction along the slope formed by chamfering the corner portion of the tip end surface of the input shaft. Moved. Therefore, it is possible to suppress the inner peripheral side of the seal member from being turned up in the insertion direction of the input shaft during the assembly process of the input shaft.

  Further, in the starting device of the present invention, the seal member has a portion where the outer peripheral surface of the input shaft in sliding contact with the outer peripheral surface of the input shaft is in contact with the outer peripheral surface of the input shaft. It is formed so as to have a surface shape that allows the radially inner portion to ride on the surface.

  According to the above configuration, when the input shaft is assembled to the output side member, the radially inner portion of the seal lip is slid smoothly so as to ride on the outer peripheral surface of the input shaft. Therefore, it is possible to prevent the seal lip from being caught on the input shaft during the assembly process of the input shaft.

  Hereinafter, an embodiment of a starting device embodying the present invention will be described with reference to FIGS. In the following description of the present specification, when referring to the “front-rear direction”, the front-rear direction indicated by arrows in FIG.

  As shown in FIGS. 1 and 2, the starting device 11 is a device for transmitting the torque of the output shaft 12 of the engine as a drive source to the input shaft 13 of the transmission mechanism, and is connected to the output shaft 12 of the engine. The front cover 14 and the pump cover 15 fixed by welding to the outer peripheral side end portion of the front cover 14 constitute a housing 16 as an input side member. The housing 16 accommodates a damper device 17 and a starting clutch 18 as a clutch mechanism, and ATF (automatic transmission fluid) as hydraulic oil and lubricating oil is filled in an oil-tight manner. Yes.

  The front cover 14 has a substantially cylindrical shape with a bottom closed on the front side and an opening on the rear side, and an output of the engine to a connecting portion 14a projecting forward from a substantially central portion of the outer surface (front surface) of the bottom wall. When the shaft 12 is connected, the shaft 12 rotates about the axis L of the input shaft 13 of the transmission mechanism based on the rotational drive of the output shaft 12 of the engine. The pump cover 15 has a substantially annular shape capable of closing the opening on the rear side of the front cover 14, and a cylinder connected to a drive shaft of an oil pump (not shown) as a hydraulic source at the center thereof. A fixed support cover 19 is fixed so as to constitute a part of the pump cover 15. That is, the rotation of the output shaft 12 of the engine is transmitted to the oil pump through the front cover 14 and the pump cover 15 (and the support cover 19).

  The damper device 17 includes an annular damper plate 20 connected to the engine side, an annular damper disk 21 connected to the transmission mechanism side, and torque transmission means for transmitting the rotational force of the damper plate 20 to the damper disk 21. 22. The damper plate 20 is fixed to a rear surface on the outer peripheral side of the front cover 14 (an inner surface facing the pump cover 15), and rotates integrally with the front cover 14. The damper disk 21 is engaged with a cylindrical support member 23 whose inner peripheral edge is fixed to the rear surface of the front cover 14, thereby restricting movement in the axial direction about the axis L of the input shaft 13 of the speed change mechanism. In this state, it is supported rotatably. Further, when the relative angle with respect to the front cover 14 exceeds a predetermined angle during the rotation of the damper disk 21, the predetermined portion in the circumferential direction is locked to a part of the outer peripheral surface of the support member 23, More rotation is restricted.

  The torque transmission means 22 includes a plurality of damper springs 24 and an intermediate member 25 interposed between the damper springs 24 so that the damper springs 24 are elastically connected in series. Each damper spring 24 has one end abutting against the damper plate 20 or the damper disk 21 and the other end abutting against the intermediate member 25. Therefore, the rotational drive from the output shaft 12 of the engine transmitted to the damper plate 20 via the front cover 14 is a torque that exhibits a damper function by the damper spring 24 and the intermediate member 25 being elastically connected in series. It is transmitted to the damper disk 21 via the transmission means 22. Since the damper disk 21 is rotationally restricted by locking with the support member 23 so that the relative angle with the front cover 14 does not exceed a predetermined value, the spring length of the damper spring 24 reaches the limit value. It does not shrink.

  As shown in FIGS. 1 and 2, the input shaft 13 of the speed change mechanism has a spline 30 as an uneven engagement portion on the outer peripheral surface 13 a on the base end (rear end) side by a predetermined distance from the front end (front end). It is formed along the front-rear direction. In addition, a tapered surface 13b whose diameter decreases toward the distal end side by chamfering is formed on the periphery of the distal end surface of the input shaft 13. The input shaft 13 of the speed change mechanism is inserted through a turbine hub 31 serving as an output side member in the axial length from the tip to the position where the spline 30 is formed.

  That is, the turbine hub 31 is formed in a columnar shape, and a through hole 32 through which the input shaft 13 can be inserted is formed through the shaft center. The through hole 32 is formed as a small diameter portion 32a having a diameter substantially the same as the diameter of the input shaft 13 from the middle in the axial direction, and has a diameter larger than that of the small diameter portion 32a from the middle in the axial direction. The large diameter portion 32b is formed. On the inner peripheral surface of the small diameter portion 32 a of the through hole 32, the turbine hub 31 and the input shaft 13 can be moved relative to each other in the axial direction with respect to the spline 30 formed on the outer peripheral surface 13 a of the input shaft 13 and in the circumferential direction. A spline 33 is formed as a concavo-convex engaging portion that engages so as not to be relatively movable.

  When the front end portion of the input shaft 13 is inserted from the rear side into the through hole 32 of the turbine hub 31, the spline 33 formed on the inner peripheral surface of the small diameter portion 32 a of the through hole 32 is the input shaft 13. The input shaft 13 and the turbine hub 31 are connected to each other so as to be integrally rotatable by engaging with the spline 30 formed on the side in a concavo-convex manner. A pair of front and rear oil seals 50 are press-fitted into the large-diameter portion 32b of the through hole 32 in the turbine hub 31 in a state where the tip end portion of the input shaft 13 is inserted in this manner so as to function as a seal member. ing. A specific configuration related to the oil seal 50 will be described in detail later.

  The turbine hub 31 is connected to the input shaft 13 of the speed change mechanism in a state where annular thrust bearings 34a and 34b capable of withstanding the load in the thrust direction accompanying the rotation are disposed on both sides in the axial direction. That is, the first thrust bearing 34a is interposed between the rear surface (inner surface) of the front cover 14 and the axial front end surface of the turbine hub 31, and the rear end surface of the turbine hub 31 and the pump cover 15 (support cover). 19), a second thrust bearing 34b is interposed between the front surface (inner surface). The thrust bearings 34 a and 34 b are disposed in annular regions that are radially outward from the through holes 32 at the front and rear end surfaces of the turbine hub 31. Washers 35a and 35b are interposed between the thrust bearings 34a and 34b and the turbine hub 31 for the purpose of improving the stability of the contact state between them.

  Further, as shown in FIG. 1, a starting clutch 18 capable of directly connecting the output shaft 12 of the engine and the input shaft 13 of the speed change mechanism by operating the clutch is disposed on the back surface (rear surface) side of the damper device 17. Yes. The starting clutch 18 includes a cylindrical clutch hub 26 that extends to the rear side in a state of being fastened by a pin 48 on the inner peripheral side of the damper disk 21, and plural clutch hubs 26 (in this embodiment, on the outer peripheral side). Four) inner frictional engagement plates 27 are spline-fitted so as to be movable in the front-rear direction. Further, the bottom inner peripheral edge of the bottomed substantially cylindrical clutch drum 36 whose front side is open is fixed to the outer peripheral part of the rear end of the turbine hub 31, and the inner peripheral side of the outer peripheral side cylinder part 36 a of the clutch drum 36. A plurality of (four in this embodiment) outer friction engagement plates 28 are spline-fitted so as to be movable in the front-rear direction so as to be alternately positioned with the inner friction engagement plate 27 one by one in the front-rear direction.

  An annular piston 29 is supported on the peripheral surface of the turbine hub 31 so as to be movable in the axial direction with respect to the turbine hub 31 by fitting the inner periphery of the piston 29 so as to be slidable. . The piston 29 is formed such that the cross-sectional shape along the axial direction forms a crank shape, and the outer peripheral surface of the intermediate cylinder portion 29 a bent in the crank shape is the inner peripheral cylinder portion 36 b of the clutch drum 36. Is slidably fitted on the outer peripheral surface of the. O-rings c <b> 1 and c <b> 2 are provided between the intermediate cylinder portion 29 a of the piston 29 and the inner peripheral cylinder portion 36 b of the clutch drum 36 and between the inner peripheral edge of the piston 29 and the peripheral surface of the turbine hub 31, respectively. The hydraulic chamber 37 is formed on the back surface (rear surface) side of the piston 29 by the sealing function of the O-rings c1 and c2.

  In addition, an annular cancel plate 38 is supported in a state in which movement is restricted by a snap ring 39 at a position on the outer peripheral portion of the front end of the turbine hub 31 in front of the piston 29 in the axial direction. A return spring 49 is disposed between the cancel plate 38 and the piston 29. The biasing force of the return spring 49 causes the piston 29 to always approach the clutch drum 36 (each friction engagement plate 27). , 28).

  In other words, the engagement state of the starting clutch 18 is such that the piston 29 moves forward against the urging force of the return spring 49 as the ATF in the hydraulic chamber 37 increases, so that the outer friction engagement plate 28 is moved to the inner side. This is realized by pressing against the friction engagement plate 27. On the other hand, the disengagement state of the start clutch 18 is that the piston 29 moves rearward in accordance with the urging force of the return spring 49 as the ATF in the hydraulic chamber 37 drops, thereby causing the outer friction engagement plate 28 to move to the inner friction engagement. This is realized by separating from the plywood 27.

  In addition, a fluid coupling 40 having no torque amplifying action is disposed at a position corresponding to the outer peripheral side front surface (the inner surface opposite to the front cover 14) of the pump cover 15 in the housing 16, so that it can be used for starting and shifting. The rotational difference between the pump cover 15 and the clutch drum 36 at the time is absorbed. In the fluid coupling 40, one of the paired blade members is fixed to the pump cover 15 and the other blade member is fixed to the clutch drum 36 by a rivet 41.

Next, the configuration of the hydraulic oil passage for supplying ATF as hydraulic oil to the hydraulic chamber 37 will be described in detail.
As shown in FIGS. 1 to 3, a first hydraulic oil passage a <b> 1 that communicates with the oil pump on the base end side is formed in the input shaft 13 of the speed change mechanism along the axial direction. The opening of the hydraulic oil passage a1 is closed by a plug member 42. Then, in the longitudinal direction of the first hydraulic oil passage a1, a position on the tip side of the input shaft 13 where the spline 30 is formed and a position corresponding to the large diameter portion 32b of the through hole 32 of the turbine hub 31 The second hydraulic oil passage a2 is bent so as to open the oil hole 43 to the outer peripheral surface 13a of the input shaft 13 outward in the radial direction. The second hydraulic oil passage a <b> 2 is formed by a pair of front and rear oil seals 50 in the large-diameter portion 32 b of the through hole 32 of the turbine hub 31 through the oil hole 43 opened in the outer peripheral surface 13 a of the input shaft 13. It communicates with the oil sump chamber 31a.

  Further, a third hydraulic oil passage a3 that penetrates the inside of the turbine hub 31 radially outward from the inner peripheral surface of the large-diameter portion 32b of the through hole 32 communicates with the hydraulic chamber 37 in the turbine hub 31. In this way, it is formed so as to be inclined and linear. The first hydraulic fluid passage a1, the second hydraulic fluid passage a2, the oil reservoir chamber 31a, and the third hydraulic fluid passage a3 provide ATF as hydraulic fluid to the hydraulic chamber 37 during clutch operation. A hydraulic oil passage to be supplied is configured. In the present embodiment, the first hydraulic oil passage a1 constitutes an oil passage extending in the axial direction of the hydraulic oil passage, the second hydraulic oil passage a2, the oil reservoir chamber 31a, and the third hydraulic oil. An oil passage extending at least in the radial direction of the hydraulic oil passage is constituted by the passage a3.

Next, the configuration of the lubricating oil passage that circulates and supplies ATF as lubricating oil into the housing 16 will be described in detail.
As shown in FIGS. 1 to 3, a first lubricating oil passage b <b> 1 communicating with the base end side oil pump is provided in the input shaft 13 of the speed change mechanism with a first hydraulic oil passage a <b> 1 of the hydraulic oil passage. It is formed along the axial direction in parallel. The first lubricating oil passage b1 has an opening at the tip (front end) surface of the input shaft 13, and oil formed at the substantially central portion of the inner surface (rear surface) of the bottom wall of the front cover 14 through the tip opening. It communicates with the path forming recess 45.

  Further, in the axial front and rear end surfaces of the turbine hub 31, radial positions perpendicular to the axis L of the input shaft 13 are located at positions corresponding to the thrust bearings 34 a and 34 b in the radial direction, as shown in FIGS. 1 to 3. A plurality (four in this embodiment) of oil grooves 46 and 47 are formed extending in a straight line. The oil grooves 46 and 47 are spaced at equal angular intervals (90-degree intervals) in the circumferential direction around the axis L of the input shaft 13 of the speed change mechanism, and the second and third hydraulic oil passages of the hydraulic fluid passages. a2 and a3 are formed such that the oil passage extending directions are shifted in the circumferential direction. The first lubricating oil passage b1, the oil passage forming recess 45, and the oil grooves 46 on the front end face side allow the lubricating oil from the oil pump side to be lubricated in the housing 16 (for example, the starting clutch 18). A supply oil passage for supplying the oil is configured.

  Further, a second lubricating oil passage b2 communicating with the base end side oil pump is provided between the outer peripheral surface 13a of the input shaft 13 of the speed change mechanism and the inner peripheral surface of the support cover 19 in the pump cover 15 on the rear end surface side. These oil grooves 47 are formed so as to communicate with the radially inner side. The second lubricating oil passage b2 and the respective oil grooves 47 on the rear end face side allow the lubricating oil supplied to the location where lubrication is required (for example, the start clutch 18) in the housing 16 through the supply oil passage. A return oil passage for returning to the oil pump side is configured.

  In this embodiment, the first lubricating oil passage b1, the oil passage forming recess 45, and the supply oil passage including the oil grooves 46 on the front end face side, the second lubricating oil passage b2 and the rear end face side. A lubricating oil passage that circulates and supplies ATF as lubricating oil into the housing 16 is constituted by the return oil passage formed by the oil grooves 47. In the present embodiment, the first lubricating oil passage b1 and the second lubricating oil passage b2 constitute an oil passage extending in the axial direction of the lubricating oil passage, and the oil passage forming recess 45 and each oil groove 46, 47 constitutes an oil passage extending at least in the radial direction of the lubricating oil passage.

  In particular, as shown in FIGS. 1 and 2, each oil groove 46 on the front end surface side of each oil groove 46, 47 constituting at least a part of the oil path extending in the radial direction is at least in the radial direction in the hydraulic oil path. The installation space in the axial direction of the input shaft 13 overlaps with the oil passage on the radially inner side of the second hydraulic oil passage a2 and the third hydraulic oil passage a3 that constitute a part of the oil passage extending to It is formed to do. That is, at the same position in the axial direction of the input shaft 13 or in the vicinity thereof, each oil groove 46, the second hydraulic oil path a2, and the oil path on the radially inner side of the third hydraulic oil path a3 are: Each oil passage extending direction is formed so as to be along the radial direction in a state of being partially overlapped in the axial direction of the input shaft 13.

  The third hydraulic oil passage a3 constituting at least a part of the hydraulic passage extending in the radial direction in the hydraulic oil passage has an oil passage on the radially outer side, and an oil passage on the radially inner side (and A straight line whose oil passage extending direction is inclined toward the base end side so as to be separated from each oil groove 46 constituting a part of the lubricating oil passage in the axial direction of the input shaft 13 rather than the second hydraulic oil passage a2). It has an oil passage structure.

Next, the configuration of the oil seal 50 interposed between the inner peripheral surface of the through hole 32 (large diameter portion 32b) of the turbine hub 31 and the outer peripheral surface 13a of the input shaft 13 of the speed change mechanism will be described in detail.
As shown in FIG. 4, the oil seal 50 includes an annular fitting member 51 fitted into the large diameter portion 32 b of the through hole 32 in the turbine hub 31, and a radially outer side that is the outer peripheral side of the fitting member 51. And an annular sealing lip 52 to which the portion is fixed. Further, the oil seal 50 includes an annular spring member 53 as an urging member that urges a radially inner portion on the inner peripheral side of the seal lip 52 so as to be pressed against the outer peripheral surface 13 a of the input shaft 13. I have.

  The fitting member 51 is made of a rigid material such as a metal whose cross-sectional shape along the axial direction is L-shaped. The fitting member 51 has an outer diameter slightly larger than the inner diameter of the large-diameter portion 32 b of the through hole 32, and the fitting member 51 is inserted into the large-diameter portion 32 b of the through-hole 32. The outer surface is in pressure contact with the inner peripheral surface of the large diameter portion 32b. In addition, a portion of the radially inner portion of the seal lip 52 where the outer peripheral surface of the input shaft 13 comes into sliding contact is formed to have a curved surface shape, and the spring member 53 is fitted on the outer peripheral surface of the portion where the curved surface is formed. Are combined. The curved surface of the seal lip 52 is urged radially inward by the spring member 53 and slidably contacts the outer peripheral surface 13 a of the input shaft 13 of the speed change mechanism. Based on the above, the radially inner portion of the seal lip 52 is ridden on the outer peripheral surface. As an elastic material applied to the seal lip 52, it is desirable to select an appropriate material in consideration of the type of oil to be sealed, wear resistance, water resistance, and the like.

Next, the operation of the starting device 11 will be described with reference to FIGS.
First, an assembly process for connecting the input shaft 13 of the speed change mechanism and the turbine hub 31 so as to be integrally rotatable in the manufacturing process of the starting device 11 will be described. 5 to 8, other members (piston 29 and the like) accommodated in the housing 16 together with the turbine hub 31 are omitted from the illustration including the housing 16 in order to simplify the drawing contents.

  In this assembling process, the input shaft 13 of the speed change mechanism is inserted through the through hole 32 of the turbine hub 31 from the front end side, and the large diameter portion of the through hole 32 in the turbine hub 31 is inserted in the previous stage. As shown in FIG. 5, a pair of oil seals 50 is mounted in advance in the 32b. That is, one oil seal 50 is fitted and arranged at each of the two positions of the innermost portion 32b and the opening portion in the large diameter portion 32b.

  When the oil seal 50 is fitted into the large-diameter portion 32b, the outer surface of the annular fitting member 51 is in pressure contact with the inner peripheral surface of the large-diameter portion 32b. Therefore, each oil seal 50 is positioned and mounted at each mounting position (the innermost portion and the opening) in a state where movement in the axial direction is restricted. In other words, the oil seal 50 has the large diameter of the through hole 32 as the outer surface of the fitting member 51 is elastically deformed by the seal lip 52 without forming an annular groove on the outer peripheral surface 13 a of the input shaft 13. Since it is in a state of being pressed against the inner peripheral surface of the portion 32b and the outer peripheral surface 13a of the input shaft 13, it is positioned and mounted in a state where movement in the axial direction is restricted.

  Next, when the input shaft 13 is inserted from the distal end side into the small diameter portion 32a of the through hole 32 in the turbine hub 31 in the state where the oil seal 50 is mounted, as shown in FIG. The shaft 13 comes into contact with the seal lip 52 of the oil seal 50 attached to the innermost portion of the large diameter portion 32b when the tip of the shaft 13 passes through the small diameter portion 32a of the through hole 32. At this time, an inclined tapered surface 13b is formed by chamfering at the periphery of the tip surface of the input shaft 13. On the other hand, a radially inner portion of the seal lip 52 that hangs radially inward is bent outward in the radial direction.

  Therefore, the seal lip 52 of the innermost oil seal 50 tilts while the curved surface of the radially inner portion smoothly slides along the tapered surface 13 b at the tip of the input shaft 13. That is, the tip of the input shaft 13 and the radially inner portion of the seal lip 52 are not caught. When the input shaft 13 is further inserted forward in the insertion direction, the seal lip 52 of the oil seal 50 at the innermost portion is pressed against the outer peripheral surface 13a of the input shaft 13 by the urging force of the spring member 53. It comes into sliding contact with elastic deformation.

  When the input shaft 13 is further pushed forward in the insertion direction, the spline 30 formed on the outer peripheral surface of the input shaft 13 and the inner peripheral surface of the small diameter portion 32a of the through hole 32 are formed as shown in FIG. The spline 33 is engaged with the unevenness. When the input shaft 13 is pushed further forward in the insertion direction while maintaining the concave / convex fitting state of both the splines 30, 33, the input shaft 13 is attached to the opening of the large diameter portion 32 b of the through hole 32. The oil seal 50 is in contact with the seal lip 52 of the oil seal 50. Then, as in the case of the seal lip 52 of the deepest oil seal 50, the curved surface of the radially inner portion of the seal lip 52 of the oil seal 50 in the opening is formed on the tapered surface 13b at the tip of the input shaft 13. Tilt while sliding smoothly along. Finally, as shown in FIG. 8, the seal lip 52 is pressed against the outer peripheral surface 13 a of the input shaft 13 by the urging force of the spring member 53 so as to further increase the pressure contact force, with elastic deformation. It comes in sliding contact.

  In this case, the spline 30 formed on the outer peripheral surface 13a of the input shaft 13 is unevenly fitted to the spline 33 of the small diameter portion 32a as the input shaft 13 is inserted into the through hole 32. Thus, it does not enter to the front side in the insertion direction (that is, inside the large diameter portion 32b of the through hole 32). Therefore, the spline 30 on the input shaft 13 side does not come into contact with the seal lip 52 of the oil seal 50 attached to the innermost part of the large diameter portion 32 b of the through hole 32, and the seal is formed by contact with the spline 30. The lip 52 is not damaged.

  In the state shown in FIG. 8, both the splines 30 and 33 are concavo-convexly fitted, whereby the input shaft 13 and the turbine hub 31 cannot be moved relative to each other in the circumferential direction and are connected so as to be integrally rotatable. The oil hole 43 of the second hydraulic oil passage a2 opened in the outer peripheral surface 13a on the distal end side of the input shaft 13 is located at a substantially central portion in the axial direction of the large diameter portion 32b of the through hole 32 in the turbine hub 31. . The pair of front and rear oil seals 50 fitted between the outer peripheral surface 13 a of the input shaft 13 and the inner peripheral surface of the large-diameter portion 32 b of the through hole 32 are oil holes opened on the outer peripheral surface 13 a of the input shaft 13. The oil reservoir chamber 31 a is formed between the two oil seals 50 in such a manner that 43 is sandwiched from both sides in the axial direction. Thus, the assembling process for connecting the input shaft 13 of the speed change mechanism and the turbine hub 31 so as to be integrally rotatable is completed.

  When the starting device 11 is used after the assembly process is completed, when the output shaft 12 on the engine side and the input shaft 13 of the transmission mechanism are directly connected, the first hydraulic oil passage a1 and the second hydraulic oil passage a2 from the oil pump side are used. The ATF is supplied as hydraulic fluid into the hydraulic chamber 37 via the hydraulic fluid passage a2, the oil reservoir chamber 31a, and the third hydraulic fluid passage a3. As a result, as the hydraulic pressure in the hydraulic chamber 37 increases, the piston 29 moves in a direction in which the outer friction engagement plate 28 is pressed against the inner friction engagement plate 27, and the starting clutch 18 is changed from the disengaged state to the engaged state.

  In this case, even if the ATF discharged from the oil hole 43 of the second hydraulic oil passage a2 into the oil reservoir chamber 31a leaks in the axial direction along the outer peripheral surface 13a of the input shaft 13, such ATF Leakage is regulated by the sealing function of a pair of oil seals 50 mounted in an arrangement mode in which the oil hole 43 is sandwiched from both front and rear sides in the axial direction. The ATF whose leakage in the axial direction is restricted is promptly supplied to the hydraulic chamber 37 via the third hydraulic oil passage a3 that is linearly inclined toward the hydraulic chamber 37.

  When ATF is circulated and supplied as the lubricating oil into the housing 16 in which the starting clutch 18 repeats the engaged state and the non-engaged state, the first lubricating oil passage b1, the oil passage forming recess 45, and the like are provided from the oil pump side. ATF is supplied to the location where the starting clutch 18 is disposed via the oil grooves 46 on the front end face side, and the housing 16 via the oil grooves 47 on the rear end face side and the second lubricating oil passage b2. ATF is returned from the inside to the oil pump side. In particular, when ATF is supplied into the housing 16, the installation space overlaps with the second hydraulic oil passage a2 (and the oil passage portion on the radially inner side of the third hydraulic oil passage a3) in the axial direction. ATF is supplied as the lubricating oil to the starting clutch 18 side while lubricating the thrust bearing 34a through the respective oil grooves 46 on the front end face side.

According to the present embodiment, the following effects can be obtained.
(1) In the above embodiment, the oil seal 50 is used as a seal member for restricting the ATF from leaking in the axial direction from the oil hole 43 opened in the outer peripheral surface 13 a of the input shaft 13. The oil seal 50 is configured such that the outer surface of the fitting member 51 is in pressure contact with the inner peripheral surface of the large diameter portion 32 b in the through hole 32 of the turbine hub 31 and the seal lip 52 is radially contacted with the outer peripheral surface 13 a of the input shaft 13. The inner part is attached so as not to move in the axial direction by being in pressure contact with elastic deformation. Therefore, it is not necessary to provide an annular concave groove on the outer peripheral surface 13a of the input shaft 13 of the transmission mechanism for mounting the seal member so as not to move in the axial direction. Therefore, an oil hole that opens in the outer peripheral surface 13a of the input shaft 13 of the speed change mechanism while responding to a request for downsizing of the starter device 11 as much as it is not necessary to secure such a space for arranging the concave grooves in the input shaft 13. The leakage in the axial direction of the oil supplied through the oil passage having the oil passage structure including 43 can be preferably controlled.

  (2) Since the oil seal 50 is biased toward the outer peripheral surface 13a of the input shaft 13 by the spring member 53 at the radially inner portion of the seal lip 52, the oil seal 50 only has the elastic force of the seal lip 52 itself. The spring member 53 is pressed against the outer peripheral surface 13 a of the input shaft 13 with a strong pressing force to which the urging force of the spring member 53 is applied. Therefore, the sealing function of the oil seal 50 can be further strengthened by the spring member 53.

  (3) In the above embodiment, the spline 30 on the input shaft 13 side is formed at a position closer to the base end side of the input shaft 13 than the position of the oil seal 50 on the outer peripheral surface 13 a of the input shaft 13. Therefore, when the input shaft 13 is assembled to the turbine hub 31, the spline 30 on the input shaft 13 side is inserted into the large diameter portion 32 b of the through hole 32 in the turbine hub 31 and the seal lip 52 of the oil seal 50 is arranged. Never touch. Therefore, it is possible to prevent the spline 30 of the input shaft 13 from damaging the seal lip 52 of the oil seal 50 during the assembly process of the input shaft 13.

  (4) In the above-described embodiment, the peripheral edge of the tip surface of the input shaft 13 is a tapered surface 13b that is chamfered and has a smaller diameter toward the tip side. Therefore, when the input shaft 13 is assembled to the turbine hub 31, the curved surface of the oil seal 50 on the radially inner side of the seal lip 52 is tilted while smoothly sliding along the tapered surface 13 b at the tip of the input shaft 13. To come. Therefore, in the process of assembling the input shaft 13, the radially inner portion of the seal lip 52 of the oil seal 50 is not caught on the tip of the input shaft 13, and the assembling work of the input shaft 13 to the turbine hub 31 is smooth. You can get none.

  (5) In the above embodiment, the radially inner portion of the seal lip 52 of the oil seal 50 is bent outward in the radial direction. Therefore, when the input shaft 13 is assembled to the turbine hub 31, the curved surface formed at the radially inner portion of the seal lip 52 slides smoothly from the tip of the input shaft 13 to the outer peripheral surface 13 a. Therefore, in the process of assembling the input shaft 13, the input shaft 13 is not caught by the seal lip 52, and the assembling work of the input shaft 13 to the turbine hub 31 can be performed smoothly.

  (6) In the above-described embodiment, each oil groove 46 serving as a part of an oil path extending at least in the radial direction in the lubricating oil path, and a second operation serving as a part of the oil path extending at least in the radial direction in the hydraulic oil path. The oil passage a2 (and the oil passage on the radially inner side of the third hydraulic oil passage a3) is formed so as to overlap each installation space in the axial direction. Therefore, in the starting device 11, the axial length of the entire device can be shortened by this overlap. Therefore, even when a plurality of oil passages such as a hydraulic oil passage and a lubricating oil passage are provided side by side with an oil passage structure including at least an oil passage extending in the radial direction, the starting device 11 is restrained from increasing in the axial direction. Can meet the demands for downsizing.

  (7) In the above embodiment, each oil groove 46 in the lubricating oil path and the second hydraulic oil path a2 in the hydraulic oil path (and the oil path on the radially inner side of the third hydraulic oil path a3) are Each of the radially outer side portions extends so as to be separated from each other in the circumferential direction centering on the axis L of the input shaft 13. Therefore, it is possible to easily realize an oil passage configuration in which the installation spaces of the oil passages extending at least in the radial direction in the respective oil passages partially overlap in the axial direction.

  (8) In the above embodiment, each oil groove 46 in the lubricating oil passage is arranged on the radially outer side of the oil passage on the radially inner side of the third hydraulic oil passage a3 in the hydraulic oil passage, whereby the respective oil passages are arranged. It is possible to easily realize an oil passage configuration in which the installation spaces overlap in the axial direction.

  (9) In the above embodiment, since the thrust bearings 34a and 34b are disposed between the axial end surface of the turbine hub 31 and the inner surface of the housing 16, the thickness of the thrust bearings 34a and 34b is equal to the axial thickness. There is a concern that the axial length of the entire starter 11 will become longer. However, in the above embodiment, each of the oil grooves 46 that lubricate the thrust bearing 34a on the front end face side in the lubricating oil path is the second hydraulic oil path a2 (that is a part of the oil path that extends at least in the radial direction of the hydraulic oil path. Since the oil passage is partially overlapped in the axial direction with the oil passage portion on the radially inner side of the third hydraulic oil passage a3, the shaft length is shortened in response to such concerns. This can be dealt with suitably.

  (10) In the above embodiment, the second hydraulic oil passage a2 constituting the oil passage extending in the radial direction from the first hydraulic oil passage a1 constituting the oil passage extending in the axial direction in the hydraulic oil passage is radially outward. The position where it is bent toward the direction and the hydraulic chamber 37 of the starting clutch 18 are arranged apart from each other in the axial direction. However, the third hydraulic oil passage a3 communicating with the second hydraulic oil passage a2 through the oil reservoir chamber 31a penetrates the inside of the turbine hub 31 linearly toward the hydraulic chamber 37 in an oblique manner. Therefore, ATF can be quickly supplied to the hydraulic chamber 37.

  (11) In the above embodiment, the third hydraulic oil passage a3 that is at least a part of the hydraulic passage extending in the radial direction in the hydraulic oil passage is connected to the turbine hub 31 that is connected to the input shaft 13 so as to be integrally rotatable. Is formed. Therefore, the opening on the inner diameter side of the third hydraulic oil passage a3 in the turbine hub 31 is always disposed so as to face the oil hole 43 formed in the outer peripheral surface portion of the input shaft 13 along the radial direction. Therefore, the hydraulic pressure supplied through the first hydraulic oil passage a1 can be supplied to the start clutch 18 with high responsiveness through the third hydraulic oil passage a3.

In addition, you may change the said embodiment as follows.
In the above embodiment, the radially inner portion of the seal lip 52 of the oil seal 50 does not necessarily have to be bent outward in the radial direction, and may be formed in a straight line. In this case, it is desirable that the radially inner portion of the seal lip 52 be inclined with respect to the axial direction.

-In above-mentioned embodiment, the input shaft 13 does not need to chamfer the periphery of the front end surface.
In the above embodiment, the oil seal 50 may have a configuration in which the spring member 53 that urges the radially inner portion of the seal lip 52 so as to press the outer peripheral surface 13a of the input shaft 13 is omitted. Also in this case, the radially inner portion of the seal lip 52 can be pressed against the outer peripheral surface 13a of the input shaft 13 with elastic deformation by the elastic force of the seal lip 52 itself.

  In the above embodiment, the oil seal 50 is arranged in such a manner that the oil holes 43 opened to the outer peripheral surface 13a of the input shaft 13 are sandwiched from both sides in the axial direction in the large diameter portion 32b of the through hole 32 in the turbine hub 31. Then, not only a pair of front and rear, but also a configuration in which three or more oil seals 50 are arranged may be used.

  In the above embodiment, the second hydraulic oil passage a2 and the third hydraulic oil passage a3 that constitute the oil passage extending in the radial direction in the hydraulic oil passage may be formed to be bent or curved. .

  In the above embodiment, the thrust bearings 34a and 34b disposed on both sides in the axial direction of the turbine hub 31 may be omitted. In this case, the shaft length of the starting device 11 can be shortened by a distance corresponding to the installation space of the thrust bearings 34a and 34b.

  In the above embodiment, the third hydraulic oil passage a3 that constitutes a part of the oil passage that extends in the radial direction in the hydraulic oil passage is the front end face side that constitutes a part of the oil passage that extends in the radial direction in the lubricating oil passage. Each oil groove 46 and the whole oil path may overlap in the axial direction.

  In the above embodiment, an oil passage extending in the radial direction from the middle of the first lubricating oil passage b1 of the lubricating oil passage is formed by bending, and the oil hole of the oil passage is in the through hole 32 and the outer peripheral surface 13a of the input shaft 13 An oil seal may be provided so that the oil hole is opened and the oil hole is sandwiched from both sides in the axial direction.

  In the above embodiment, the second hydraulic oil passage a2 and the third hydraulic oil passage a3 constituting a part of the oil passage extending in the radial direction in the hydraulic oil passage are the oil passages extending in the radial direction in the lubricating oil passage. The oil passage extending direction may not be shifted in the circumferential direction around the axis L of the input shaft 13 with respect to each of the oil grooves 46 constituting a part. Even in this case, if the oil passage portion on the radially inward side of the third hydraulic oil passage a3 is positioned on the radially inward side of the portion on the radially inward side of each oil groove 46, the shaft An oil passage structure overlapping in the direction can be formed.

  In the above embodiment, the starting device 11 is not limited to the one provided with the multi-plate starting clutch 18. For example, the present invention can be applied to a torque converter provided with a lockup clutch whose engagement state is switched based on the hydraulic pressure supplied to the clutch mechanism.

The longitudinal cross-sectional view of the starting apparatus of this embodiment. The principal part expanded sectional view of the starting apparatus of this embodiment. FIG. 3 is a partial cross-sectional view taken along line 3-3 in FIG. 2. The perspective view which shows the oil seal mounting state of this embodiment. The longitudinal cross-sectional view explaining the assembly | attachment process of the input shaft of a speed change mechanism, and a turbine hub. The longitudinal cross-sectional view explaining the assembly | attachment process of the input shaft of a speed change mechanism, and a turbine hub. The longitudinal cross-sectional view explaining the assembly | attachment process of the input shaft of a speed change mechanism, and a turbine hub. The longitudinal cross-sectional view explaining the assembly | attachment process of the input shaft of a speed change mechanism, and a turbine hub.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 11 ... Starting device, 12 ... Output shaft, 13 ... Input shaft, 13a ... Outer peripheral surface of input shaft, 14 ... Housing as input side member, 18 ... Starting clutch as clutch mechanism, 30 ... As uneven engagement part Spline 31... Turbine hub as output side member, 31 a. Oil reservoir chamber, 32... Through hole, 33. Spline as concave and convex engaging portion, 34 a and 34 b... Thrust bearing, 37. 43... Oil hole 45. Oil passage forming recess constituting an oil passage extending at least in the radial direction of the supply oil passage in the lubricating oil passage, 46... Constituting an oil passage extending at least in the radial direction of the supply oil passage in the lubricating oil passage. Oil groove 47... Oil groove constituting an oil path extending at least in the radial direction of the return oil path in the lubricating oil path 50. Oil seal as a seal member 51. Fitting member 52 Seal lip, 53... Spring member as an urging member, a1... First hydraulic oil passage constituting an oil passage extending in the axial direction of the hydraulic oil passage, a2... Oil passage extending at least in the radial direction of the hydraulic oil passage. A second hydraulic oil passage, a3 ... a third hydraulic oil passage constituting an oil passage extending at least in the radial direction of the hydraulic oil passage, b1, ... a first lubrication constituting an oil passage extending in the axial direction of the supply oil passage. Oil passage, b2 ... A second lubricating oil passage constituting an oil passage extending in the axial direction of the return oil passage.

Claims (5)

An input side member connected to the output shaft of the drive source;
An output-side member that has a through-hole through which the input shaft of the speed change mechanism can be inserted, and is connected to the input shaft so as to be integrally rotatable by being inserted into the through-hole from the tip portion;
A clutch mechanism that directly connects the input side member and the output side member so as to transmit power by operating a clutch;
In the state where the output side member is connected to the input shaft of the speed change mechanism, an oil hole is formed in the input shaft so as to open an outer peripheral surface portion of the input shaft facing the inner peripheral surface of the through hole. Oil passage,
A seal member interposed between the outer peripheral surface of the input shaft and the inner peripheral surface of the through-hole so as to have an arrangement mode in which the oil hole of the oil passage is sandwiched from both axial sides of the input shaft; With
The sealing member is
An annular fitting member that is fitted into the through hole of the output side member so as to be in pressure contact with the inner peripheral surface of the through hole;
A radially outer portion is fixed to the fitting member, and a radially inner portion is provided with an annular seal lip formed so as to be slidable with elastic deformation with respect to the outer peripheral surface of the input shaft. A starting device characterized by that. The starting device according to claim 1,
The starter according to claim 1, wherein the seal member further includes a biasing member that biases a radially inner portion of the seal lip so as to press-contact the outer peripheral surface of the input shaft. In the starting device according to claim 1 or 2,
On the outer peripheral surface of the input shaft, the output side member and the input shaft are arranged in the axial direction of the input shaft with respect to the concavo-convex engaging portion formed on the inner peripheral surface of the through hole in the output side member. A concavo-convex engaged portion is formed that is relatively movable and engages in the circumferential direction so as not to be relatively movable.
The concavo-convex engaged portion is formed on the outer peripheral surface of the input shaft at a position closer to the base end side of the input shaft than a position where the seal member is disposed. In the starting apparatus as described in any one of Claims 1-3,
A starting device, wherein a peripheral edge of a tip surface of the input shaft of the transmission mechanism is chamfered. In the starting apparatus as described in any one of Claims 1-4,
In the sealing member, a portion where the outer peripheral surface of the input shaft in a radially inner portion of the seal lip is in sliding contact with the outer peripheral surface of the input shaft is located on the outer peripheral surface on the radially inner portion. It is formed so that it may form the surface shape which can ride up.

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