JP4980981B2 - Stator support device in torque converter - Google Patents

Description

  The present invention relates to a stator support device in a torque converter mainly used as a power device for automobiles, and in particular, a torque converter designed to shorten the axial direction of the stator support portion and improve the lubrication function of the stator support portion. The present invention relates to an improvement of a stator support device.

2. Description of the Related Art Conventionally, in a stator support device for a torque converter, a thin retainer 21 is used instead of a conventional stator carrier so that the axial distance of the stator support device is shortened to make the torque converter compact. (See Patent Document 1 below).
Utility Model Registration No. 2607205

  By the way, since the stator support device of the torque converter receives an excessive load from the radial direction and the axial direction, in order to maintain the desired function for a long time in the stator, the rigidity necessary for properly supporting the load is obtained. It is required to ensure a lubrication function that prevents the relative position of each component member from being displaced and that the lubrication is sufficiently performed. Since the axial space of the retainer can be shortened, the retainer that replaces the conventional stator carrier becomes thinner, making it difficult to secure sufficient rigidity and difficult to set up a lubrication passage for sufficient lubrication. There is.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a stator support device in a novel torque converter that solves the above-described problems.

In order to achieve the above-mentioned object, the invention according to claim 1 includes a pump impeller coupled to the drive side, a turbine impeller coupled to the driven side, and a one-way clutch interposed between the two impellers. The one-way clutch includes an outer race fixed to the stator hub, an inner race coupled to the stator shaft, and a sprag disposed between the two races. In the torque converter,
A thrust bearing that supports a thrust load acting on the one-way clutch is disposed on both axial sides of the one-way clutch, and a thrust bearing support member that supports the thrust bearing between the one-way clutch and the thrust bearing. Is provided,
On the adjacent opposing surface of the outer race and / or inner race and the thrust bearing support member, a non-rotating projection and a non-rotating groove that can be engaged with each other, and a first lubricating oil groove and a second lubricating oil groove that communicate with each other. And the anti-rotation projection and the anti-rotation groove cooperate to form the anti-rotation means of the thrust bearing support member, and the first lubricating groove and the second lubricating oil groove cooperate. Lubricating oil passage means for lubricating the stator support portion is formed.

  In order to achieve the object, the invention according to claim 2 provides the invention according to claim 1, wherein the rotation preventing means and the lubricating oil passage means are both provided at the same position in the circumferential direction of the adjacent facing surface. It is characterized by being.

  According to the invention described in the claims, it is possible to secure the necessary lubricating oil passage and position the thrust bearing support member while greatly reducing the axial interval of the stator support device of the torque converter. .

  Further, according to the present invention, it is possible to reduce the number of setting points of the detent means and the lubricating oil passage means.

  Embodiments of the present invention will be described below based on the embodiments of the present invention shown in the accompanying drawings.

  First, a first embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 is a cross-sectional view of a main part of a torque converter provided with a stator support device of the present invention, FIG. 2 is an enlarged view of a virtual line encircled portion taken along line 2 in FIG. 1, and FIG. 4 is a sectional view taken along line 4-4 of FIG. 2, and FIG. 5 is an exploded perspective view of the outer race and the thrust bearing support member.

  In FIG. 1, an automotive torque converter T as a fluid transmission device, indicated as a whole by the symbol T, is disposed between a pump impeller 2, a turbine impeller 3 disposed opposite thereto, and an inner peripheral portion thereof. A stator impeller 4 is provided, and a circulation circuit 6 is formed between the three impellers 2, 3, 4 for transmitting power by operating oil.

  A side cover 5 covering the outer peripheral surface of the turbine impeller 3 is integrally connected to the pump impeller 2 by welding. A ring gear 7 for starting is welded to the outer peripheral surface of the side cover 5, and a drive plate 8 coupled to the crankshaft 1 of the engine is fixed to the ring gear 7 with bolts 9. A thrust bearing 16 is interposed between the turbine hub 3 h fixed to the inner periphery of the turbine impeller 3 and the side cover 5.

  An output shaft 10 arranged concentrically with the crankshaft 1 is disposed at the center of the torque converter T. The output shaft 10 is splined to the turbine hub 3 h of the turbine impeller 3.

  A stator shaft 12 that supports the stay hub 4h of the stator impeller 4 via the one-way clutch 11 is disposed on the outer periphery of the output shaft 10, and a bearing bush that allows relative rotation between the output shaft 10 and the stator shaft 12 is disposed. 13 is interposed. The outer end portion of the stator shaft 12 is supported by the transmission case 14 so as not to rotate.

  Thrust needle bearings 17 and 17 'serving as thrust bearings are interposed between the stator hub 4h of the stator impeller 4 and the pump hub 2h and the turbine hub 3h of the pump impeller 2 and the turbine impeller 3 opposed to the stator hub 4h. Is done.

  Further, on the outer periphery of the stator shaft 12, an auxiliary machine drive shaft 20 coupled to the pump impeller 2 is disposed in relative rotation, and an oil pump 21 that supplies hydraulic oil to the torque converter T is provided by the auxiliary machine drive shaft 20. Driven.

  Next, the support structure of the stator 4 according to the first embodiment of the present invention will be described with reference to FIGS.

  The one-way clutch 11 disposed on the outer periphery of the stator shaft 12 fixed to the transmission case 14 includes an outer race 26, an inner race 27, and a plurality of sprags 28 interposed therebetween. The outer race 26 is press-fitted and fixed to the stator hub 4h, the inner race 27 is spline-fitted to the stator shaft 12, and the plurality of sprags 28 are held at predetermined positions by a cage 29. On both sides of the outer race 26 and the inner race 27, there are respectively disposed thrust bearing support members 30 which will be described later, and these thrust bearing support members 30 support the thrust bearings 17, 17 'and the outer race 26. And the inner race 27 are kept constant, and further, the plurality of sprags 29 are restricted from moving in the axial direction. Further, a thrust bearing race 31 of the thrust bearings 17, 17 ′ is disposed adjacent to the outer end surface of the thrust bearing support member 30, and the outer periphery of the thrust bearing race 31 is locked to the stator hub 4 h by a circlip 32. The surface of the thrust bearing race 31 is subjected to surface processing or surface treatment so that the needles of the thrust bearings 17 and 17 'roll smoothly. The thrust load acting on the one-way clutch 11 is supported by thrust bearings 17 and 17 '.

  On both opposing end surfaces of the outer race 26 and the thrust bearing support member 30, there are provided anti-rotation means and lubricating oil passage means for suppressing their relative rotation.

As shown in FIGS. 4 and 5, on the left and right outer end surfaces of the annular outer race 26, there are four anti-rotation grooves 70 and four first lubricating oil grooves 71 at equal intervals in alternate circumferential directions. Each of the anti-rotation grooves 70 and each of the first lubricating oil grooves 71 is open to the outer peripheral surface 26 o and the inner peripheral surface 26 _i of the outer race 26 and has a U-shaped cross section. In addition, the circumferential width of the rotation preventing groove 70 is slightly wider than the width of the first lubricating oil groove 71 in the circumferential direction.

On the other hand, as shown in FIGS. 2, 3, and 5, the thrust bearing support member 30 is fitted to the outer circumferential surface 30 o fitted to the inner circumferential surface 26 _i of the outer race 26 and the outer circumferential surface 27 o of the inner race 27. is formed in an annular shape and an inner peripheral surface 30 _i, the outside half of the outer peripheral surface 30o, four detent to exist a step may fit into four detent groove 70 of the outer race 26 The protrusions 80 are integrally projected radially outwardly in the radial direction. Further, a flange-like projecting portion 30p projects integrally in the axial direction at the radial intermediate portion of the thrust bearing support member 30, and the first lubricating oil groove 71 of the outer race 26 is formed on the projecting portion 30p. Are formed at equal intervals in the circumferential direction, and these second lubricating oil grooves 81 are opened on the outer surface of the thrust bearing support member 30. Thus, it is formed in a U-shaped cross section. The overhanging portion 30o is provided with four lubricating oil holes 82 at intervals in the circumferential direction. These lubricating oil holes 82 are provided inside the one-way clutch 11 and outside the thrust bearing support member 30. Communicate.

As shown in FIG. 2, the thrust bearing support members 30 are fitted on both sides of the one-way clutch 11 so as to position them radially between the inner peripheral surface 26 _i of the outer race 26 and the outer peripheral surface 27 o of the inner race 27. The four anti-rotation protrusions 80 are engaged so as to be accommodated in the anti-rotation groove 70 on the outer end surface of the outer race 26. The opposing surfaces of the outer race 26 and the thrust bearing support member 30 are almost adjacent to each other and no gap is formed in the axial direction thereof, and the thrust bearing support member 30 is prevented from rotating.

  Thrust bearings 17, 17 ′ are assembled on both sides of the one-way clutch 11, and the outer race 26 and the thrust bearing race 31 are adjacent to each other, and the first and second lubricating oil grooves 71, communicating in the radial direction therebetween, 81, a lubricating oil passage means that communicates the inside and the outside of the outer race 26 in the radial direction can be formed, and the circulation of the lubricating oil around the one-way clutch 11 can be facilitated, and the stator support portion including the one-way clutch 11 can be formed. Lubrication efficiency can be increased. Further, the lubricating oil is positively supplied into the one-way clutch 11 through the lubricating oil hole 82 provided in the thrust bearing support member 30, and the one-way clutch 11 can be efficiently lubricated.

  Thus, according to the first embodiment, the dimension in the axial direction of the stator support portion is not increased even by the formation of the detent means and the lubricating oil passage means.

  Again, referring back to FIG. 1, the inner peripheral portion of the turbine impeller 3 and the outer peripheral portion of the turbine hub 3 h are integrally connected by a plurality of rivets 51 with an annular holding plate 53 interposed therebetween. An annular holding means H that holds the inner peripheral edge of the damper holding plate 50 directly and slidably is provided on the outer peripheral edge of the turbine hub 3h. A concave portion 52 having an L-shaped cross section extending in the radial direction is formed at the outer peripheral end of the turbine hub 3 h, and the annular holding plate 53 faces the open side surface of the concave portion 52. The holding means H of the damper holding plate 50 having an annular holding groove having a U-shaped cross section in cooperation with the plate 53 is configured. In the holding groove of the holding means H, an inner peripheral portion of a disk-shaped damper holding plate 50 that is aligned with the central axis LL of the crankshaft 1 and the output shaft 10 is slidably fitted and held. Thus, the damper holding plate 50 is rotatable relative to the crankshaft 1 and the output shaft 10. An appropriate clearance that does not increase sliding resistance is formed between the holding means H and the damper holding plate 50, and the centering of the damper holding plate 50 is automatically performed properly. Further, the holding groove H can prevent the damper holding plate 50 from falling down.

  The turbine impeller 3 and the side cover 5 have a clutch chamber 22 defined therebetween, and a lockup clutch that directly connects the turbine impeller 3 and the side cover 5 is accommodated in the clutch chamber 22. The clutch piston 25 constituting the main part of the lockup clutch is supported by the boss portion 5b of the side cover 5 and is movable in the axial direction. The clutch chamber 22 is connected to each independent turbine impeller 3 side. Are divided into an inner chamber 22a and an outer chamber 22b on the side cover 5 side. Regardless of engagement or disengagement of the lock-up clutch, the external working oil is constantly regulated by a pressure regulating means (not shown) and passes from the oil passage 40 through the inner chamber 22a, the circulation circuit 6, and the one-way clutch 11. It flows to the outside. Further, hydraulic oil from a hydraulic pump (not shown) is supplied to the outer chamber 22b through a control valve.

  A multi-plate clutch mechanism CL is provided between the side cover 5 and the damper holding plate 50. The clutch mechanism CL includes a cover side clutch member 54 connected to the side cover side and a damper side clutch member 55 connected to the damper holding plate 50. The cover-side clutch member 54 includes a cylindrical clutch guide 54a fixed to the side cover 5 and a plurality of cover-side clutch plates 54b provided on the clutch guide 54a. The damper-side clutch member 55 is a damper holding member. It consists of a cylindrical clutch hub 55a riveted to the plate 50 and a plurality of damper side disk plates 55b provided on the clutch hub 55a. The clutch piston 25 is movable on the boss 5b of the side cover 5 in the direction of the central axis LL.

  The clutch piston 25 is operated by the balance between the hydraulic pressure in the inner chamber 22a on the turbine impeller 3 side and the hydraulic pressure in the outer chamber 22b on the cover 5 side, and the engagement between the cover side clutch member 54 and the damper side clutch member 55 The disengagement can be performed.

  A plurality of damper springs 60 made of coil springs are provided on the outer periphery of the damper holding plate 50. These damper springs 60 are held at both ends by the damper holding plate 50 and have a central axis L−. They are arranged side by side in the circumferential direction centered on L. On the other hand, the outer shell of the turbine impeller 3 is provided with a projecting member 61 projecting and extending toward the turbine holding plate 50, and the damper D is constituted by the damper spring 60 and the projecting member 61. When relative rotation occurs between the turbine holding plate 50 and the turbine impeller 3, the projecting member 61 compresses each damper pilling 60 to actuate the damper D, whereby the engine power is drastically increased. The transmission to the car 3 can be prevented.

  When the engine is operated, the output torque of the crankshaft 1 of the engine is transmitted to the drive plate 8, the side cover 5, and the pump impeller 2 to rotate it. By the way, in the low speed operation region including engine idling, the internal pressure of the torque converter T, that is, the hydraulic pressure of the inner chamber 22a is higher than the hydraulic pressure of the outer chamber 22b in the clutch chamber 22, and the pressure difference causes the clutch piston. Since 25 is pressed toward the side cover 5, the clutch mechanism CL of the lockup clutch is disengaged, and the pump impeller 2 and the turbine impeller 3 allow relative rotation. Therefore, when the pump impeller 2 is rotationally driven from the crankshaft 1, the working oil that has filled the circulation circuit 6 circulates in the circulation circuit 6 as indicated by an arrow, so that the rotational torque of the pump impeller 2 is reduced to the working oil. To the turbine impeller 3 to drive the output shaft 10.

  At this time, if a torque amplifying action is generated between the pump impeller 2 and the turbine impeller 3, the reaction force accompanying this is borne by the stator impeller 4, and the stator impeller 4 is locked by the locking action of the one-way clutch 11. Fixed.

  When the torque amplification action is finished, the stator impeller 4 rotates in the same direction together with the pump impeller 2 and the turbine impeller 3 while rotating the one-way clutch 11 by reversing the torque direction received by the stator impeller 4.

  When the torque converter T is in such a coupling state, hydraulic oil is supplied from the outside into the outer chamber 22b through the oil passages 39 and 38, so that the outer chamber 22b has a higher pressure than the inner chamber 22a. The clutch piston 25 is pressed in a direction away from the side cover 5 due to the pressure difference, and the clutch mechanism CL of the lockup clutch is in the connected state. Then, the rotational torque transmitted from the crankshaft 1 to the pump impeller 2 is mechanically transmitted from the side cover 5 to the turbine impeller 3 via the clutch piston 25, the clutch mechanism CL, the damper holding plate 50, the damper spring 60, and the protruding member 61. Therefore, the pump impeller 2 and the turbine impeller 3 are directly connected, and the output torque of the crankshaft 1 can be efficiently transmitted to the output shaft 10. At this time, when a sudden torque fluctuation occurs between the pump impeller 2 and the turbine impeller 3, the damper spring 60 is compressed and the damper D is activated, and the pump impeller 2 and the turbine impeller 3 are relatively rotated. By doing so, torque shock is absorbed.

  Thus, according to the first embodiment, as described above, no other member is interposed between the outer race 26 of the one-way clutch 11 and the thrust bearing support member 30 disposed adjacent to both end faces thereof. Since the rotation preventing means and the lubricating oil passage means are provided, the lubricating performance of the stator supporting portion including the one-way clutch 11 can be improved without increasing the axial dimension of the stator supporting portion, and the thrust bearing supporting member 30 It is possible to secure the rotation prevention, prevent the deviation, and ensure the expected function of the stator support portion over a long period of time.

  Next, a second embodiment of the stator support device of the present invention will be described with reference to FIGS.

  6 is a sectional view of the stator support portion corresponding to FIG. 2 of the first embodiment, FIG. 7 is a side view taken along line 7-7 of FIG. 6, and FIG. 8 is taken along line 8-8 of FIG. FIG. 9 is an exploded partial perspective view of the outer race and the thrust bearing.

  In the second embodiment, the structure of the outer race 26 and the thrust bearing support member 30 is different from that of the first embodiment, and the rotation preventing means is provided at the same position in the circumferential direction of the outer race 26 and the thrust bearing support member 30. And lubricating oil passage means.

As shown in FIGS. 8 and 9, the left and right end faces of the outer race 26 are deeper than the first embodiment, serving as four first lubricating oil grooves 271 at equal intervals in the circumferential direction. ) Anti-rotation grooves 270 are provided radially, and these anti-rotation grooves 270 have a U-shaped cross section as in the first embodiment, and are formed on the outer peripheral surface 26o and the inner peripheral surface 26 _i of the outer race 26. It is open.

  On the other hand, as shown in FIGS. 7 and 9, anti-rotation protrusions 280 are provided in the radial direction so as to correspond to the four anti-rotation grooves 270 at equal intervals in the circumferential direction of the thrust bearing support member 30. The thickness of the anti-rotation protrusion 280 is approximately ½ of the depth of the anti-rotation groove 270. The base of the anti-rotation protrusion 280 has a second U-shaped cross section that opens to the outer surface. A lubricating oil groove 281 is formed, and a lubricating oil hole 282 that communicates the inside and outside of the one-way clutch 11 is formed in the back wall of the second lubricating oil groove 281.

  As shown in FIG. 6, the anti-rotation protrusion 280 of the thrust bearing support member 30 is engaged in the anti-rotation groove 270 that also serves as the first lubricating oil groove 271 on both end faces of the outer race 26. Since the thickness of the anti-rotation protrusion 280 is approximately ½ of the depth of the anti-rotation groove 270, the anti-rotation groove 270 cooperates with the anti-rotation protrusion 280 to form a first U-shaped cross section. A lubricating oil groove 271 is formed, and the first lubricating oil groove 270 communicates with the second lubricating oil groove 282 formed in the thrust bearing support member 30 in the radial direction so that the outer race 26 and the thrust bearing race 31 are separated from each other. Between them, without providing an axial gap therebetween, the first and second lubricating oil grooves 271 and 281 can form lubricating oil passage means communicating in the radial direction of the outer race 26, The lubricating efficiency of the stator support portion can be increased, and the lubricating oil is positively supplied into the one-way clutch 11 through the lubricating oil hole 282 provided in the thrust bearing support member 30.

  Thus, in the second embodiment, the rotation preventing means and the lubricating oil passage means of the thrust bearing support member 30 can be formed together at the same position in the circumferential direction, which is more than that of the first embodiment. The number of setting points for the rotation preventing means and the lubricating oil passage means is small. .

  Next, a third embodiment of the stator support device of the present invention will be described with reference to FIGS.

  10 is a cross-sectional view of the stator support portion corresponding to FIG. 2 of the first embodiment, FIG. 11 is a side view taken along line 11-11 of FIG. 10, and FIG. 12 is an exploded view of the outer race and the thrust bearing support member. It is a fragmentary perspective view.

  In the third embodiment, the structure of the four anti-rotation protrusions 380 formed on the outer periphery of the thrust bearing support member 30 in the second embodiment is slightly modified. The surface is formed into a channel-shaped saddle shape, and a first lubricating oil groove 371 is formed inward in the radial direction. On the other hand, the depth of the anti-rotation groove 370 is formed to be approximately the same as the axial width of the anti-rotation protrusion 380, and the anti-rotation protrusion 380 is engaged in the anti-rotation groove 370, so that the first lubricating oil Lubricating oil passage means is formed by the groove 371 and the second lubricating oil groove 381 formed in the thrust bearing support member 30.

  Thus, the third embodiment also has the same effect as the second embodiment, and the anti-rotation protrusion 380 can be strengthened compared to the second embodiment.

  Next, a fourth embodiment of the stator support device of the present invention will be described with reference to FIGS.

  13 is a cross-sectional view of the stator support portion corresponding to FIG. 2 of the first embodiment, FIG. 14 is a side view taken along the line 14-14 in FIG. 13, and FIG. 15 is taken along the line 15-15 in FIG. It is sectional drawing.

  In the first to third embodiments, the rotation preventing means for the thrust bearing support member 30 and the lubricating oil passage means for the stator support device are set on both end faces of the outer race 26 of the one-way clutch 11 in the axial direction. In the embodiment, the rotation stop means of the thrust bearing support member 30 and the lubricating oil passage means of the stator support device are set on both outer end surfaces in the axial direction of the inner race 27 of the one-way clutch 11.

  The inner race 27 is formed longer in the radial direction than those of the first to third embodiments, and the left and right outer end surfaces of the inner race 27 are connected to the pump hub 2h and the turbine hub 3h via the thrust bearings 17 and 17 '. Is supported by The thrust bearing race 31 of the thrust bearing 17, 17 ′ is clipped to the inner race 27 by a circlip 432.

  As shown in FIG. 15, on the left and right outer end surfaces of the inner race 27, there are formed four non-rotating grooves 470 that also serve as the first lubricating oil grooves 471 in the circumferential direction at equal intervals, These anti-rotation grooves 470 have a U-shaped cross section and are open to the outer surface of the inner race 27. Further, as shown in FIG. 14, the inner periphery of the annular thrust bearing support member 30 that is interposed in the radial direction between the outer race 26 and the inner race 27 has a detent that also serves as the four first detent grooves 471. Four anti-rotation protrusions 480 corresponding to the grooves 470 protrude radially inward at equal intervals in the circumferential direction, and the thickness of the anti-rotation protrusions 480 is determined by the anti-rotation groove 471. It is formed to have a dimension that is approximately ½ of the depth.

  As shown in FIG. 13, the four anti-rotation protrusions 480 of the thrust bearing support member 30 are engaged with the anti-rotation grooves 470, respectively, thereby preventing the thrust bearing support member 30 from rotating and preventing them from rotating. In the groove 470, a first lubricating oil groove 471 is formed in cooperation with the anti-rotation protrusion 480, and the first lubricating oil groove 471 is a second lubricating oil groove formed in the thrust bearing support member 30. 481, and first and second lubricating oil grooves 471 and 481 form lubricating oil passage means, and the lubricating oil passage means provides good lubrication to the stator support portion including the one-way clutch 11.

  As shown in FIGS. 13 and 14, the thrust bearing support member 30 is provided with four lubricating oil holes 482 at intervals in the circumferential direction at the intermediate portions of the adjacent anti-rotation protrusions 480. The lubricating oil hole 482 communicates the inside and outside of the one-way clutch 11 and supplies lubricating oil to the inside of the one-way clutch 11 through these lubricating holes 482.

  Next, a fifth embodiment of the stator support device of the present invention will be described with reference to FIGS.

  16 is a cross-sectional view of the stator support portion corresponding to FIG. 2 of the first embodiment, FIG. 17A is a side view taken along line 17A-17A in FIG. 16, and FIG. 17 is a cross-sectional view taken along line 17B-17B, FIG. 18 is a cross-sectional view taken along line 18-18 in FIG. 16, and FIG. 19 is a cross-sectional view taken along line 19-19 in FIG.

  In the fifth embodiment, the one-way clutch 11 is provided with a detent means and a lubricant passage means for the thrust bearing support member 30 across the outer race 26 and the inner race 27.

As shown in FIGS. 16 and 18, four first lubricating oil grooves 571 are formed in the radial direction on the left and right end faces of the outer race 26 at equal intervals in the circumferential direction and these lubricating oil grooves 571. An annular groove 572 that communicates with each other is formed. The first lubricating oil groove 571 has a U-shaped cross section and is open to the outer peripheral surface 26 o and the inner peripheral surface 26 _i of the outer race 26.

  Also, as shown in FIGS. 16 and 19, four detent grooves 570 are formed in the radial direction on the left and right end faces of the inner race 27 at equal intervals in the circumferential direction. It has a U-shaped cross section and is opened on the outer surface of the inner race 27. The first lubricating oil groove 571 and the rotation preventing groove 570 are formed in the same phase in the circumferential direction.

  As shown in FIGS. 16 and 17, the thrust bearing support member 30 interposed between the outer race 26 and the inner race 27 is locked to the inner race 27 via a circlip 532, and the thrust bearing support member 30, each of the four second lubricating oil grooves 581 and the positioning protrusion 580 is provided radially at the same position in the circumferential direction at equal intervals in the circumferential direction. The groove 581 has a U-shaped cross section at the outer peripheral portion of the thrust bearing support member 30 and is open to the outer side. The four anti-rotation protrusions 580 have a diameter larger than the inner peripheral surface of the thrust bearing support member 30. Projected inward in the direction.

  As shown in FIG. 16, the thrust bearing support member 30 is positioned in the circumferential direction by the four anti-rotation projections 580 engaging with the four anti-rotation grooves 570 of the inner race. The lubricating oil grooves 581 communicate with the four first lubricating oil grooves 571 of the outer race via the annular grooves 572, respectively, and provide lubricating oil passage means between the left and right side surfaces of the one-way clutch 11 and the bearing race 31. Form.

  As shown in FIGS. 16 and 17, the thrust bearing support member 30 includes four lubricating oils spaced in the circumferential direction at the intermediate portions of the adjacent anti-rotation protrusions 580 and the second lubricating oil grooves 581. Holes 582 are formed, and these lubricating oil holes 582 communicate with the inside of the one-way clutch 11 and supply lubricating oil to the inside of the one-way clutch 11 through these lubricating oil holes 582.

  As mentioned above, although 1-5 Example of this invention was described, this invention is not limited to these Examples, A various Example is possible within the scope of the present invention.

Cross-sectional view of a main part of a torque converter provided with a stator support device of the present invention (first embodiment) Enlarged view of the imaginary line encircled portion taken along line 2 in FIG. 1 (first embodiment) Side view along line 3-3 in FIG. 2 (first embodiment) Sectional view along line 4-4 in FIG. 2 (first embodiment) Disassembled perspective view of outer race and thrust bearing support member (first embodiment) Sectional view of a stator support portion corresponding to FIG. 2 of the first embodiment (second embodiment) Side view along line 7-7 in FIG. 6 (second embodiment) Sectional drawing which follows the 8-8 line of FIG. 6 (2nd Example). Disassembled partial perspective view of outer race and thrust bearing (second embodiment) Sectional view of a stator support portion corresponding to FIG. 2 of the first embodiment (third embodiment) Side view along line 11-11 in FIG. 10 (third embodiment) Disassembled partial perspective view of outer race and thrust bearing support member (third embodiment) Sectional view of a stator support portion corresponding to FIG. 2 of the first embodiment (fourth embodiment) Side view along line 14-14 in FIG. 13 (fourth embodiment) Sectional drawing which follows the 15-15 line of FIG. 13 (4th Example). Sectional view of a stator support portion corresponding to FIG. 2 of the first embodiment (fifth embodiment) 17A is a side view taken along line 17A-17A in FIG. 16, and FIG. 17B is a cross-sectional view taken along line 17B-17B in FIG. 16 (fifth embodiment). Sectional drawing which follows the 18-18 line of FIG. 16 (5th Example) Sectional view along line 19-19 in FIG. 16 (fifth embodiment)

Explanation of symbols

2 .... Pump impeller 3 .... turbine impeller 4 .... stator impeller 4h ... stator hub 11 ... one-way clutch 12 ... ... Stator shafts 17, 17 '... Thrust bearing 26 ... Outer race 27 ... Inner race 30 ... Thrust bearing support member 70; 270; 370; 470; 271; 371; 471; 571 ... the first lubricating oil groove 80; 280; 380; 480; 580; 281; 381; 481; 581... Second lubricating oil groove

Claims (2)

The pump impeller (2) connected to the drive side, the turbine impeller (3) connected to the driven side, and the both impellers (2, 3) are interposed between the one-way clutch (11). The one-way clutch (11) is connected to an outer race (26) fixed to the stator hub (4h) and the stator shaft (12). The stator impeller (4) is connected to the stator shaft (12). In a torque converter comprising an inner race (27) and a sprag (28) disposed between both races (26, 27),
Thrust bearings (17, 17 ') for supporting a thrust load acting on the one-way clutch (11) are disposed on both sides in the axial direction of the one-way clutch (11), and further, the one-way clutch (11) and the thrust are A thrust bearing support member (30) for supporting the thrust bearing (17, 17 ') is provided between the bearing (17, 17'),
Non-rotating protrusions (80; 280; 380; 480; 580) that can be engaged with each other are disposed on the opposing surfaces of the outer race (26) and / or the inner race (27) and the thrust bearing support member (30). A detent groove (70; 270; 370; 470; 570) and a first lubricant groove (71; 271; 371; 471; 571) and a second lubricant groove (81; 281; 381; 481) communicating with each other 581), and the anti-rotation protrusion (80; 280; 380; 480; 580) and the anti-rotation groove (70; 270; 370; 470; 570) cooperate to form a thrust bearing support member (30). ) And the first lubricating oil groove (71; 271; 371; 471; 571) and the second lubricating oil groove (81; 281; 381; 48). ; 581), characterized in that is to form the lubricating oil passage means for lubricating the stator support portion cooperate stator support unit in a torque converter.   The stator support device for a torque converter according to claim 1, wherein the rotation preventing means and the lubricating oil passage means are both provided at the same position in the circumferential direction of the adjacent facing surface.

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