JP2017180646A - Friction engagement device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a friction engagement device which can homogenize the cooling of a plurality of pieces of friction plates.SOLUTION: An overlapping region overlapped on a second cylindrical part 61 when viewed in a radial direction R, and a non-overlapping region not overlapped on the second cylindrical part 61 when viewed in the radial direction are arranged at a first cylindrical part 52, oil is supplied to the non-overlapping region from the inside R1 of the radial direction by a supply part A3, a plurality of oil holes 56 penetrating the first cylindrical part 52 in the radial direction R are formed at the first cylindrical part 52 in the overlapping region, a plurality of the oil holes 56 are arranged in a plurality of points in an axial direction L, and dispersed in a plurality of points in a peripheral direction, a groove 57 in the axial direction which is formed into a groove shape extending along the axial direction L is formed at an internal peripheral face of the first cylindrical part 52, and the groove 57 in the axial direction is formed in a position corresponding to the oil holes 56 in the peripheral direction.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a friction engagement device including a supply unit that supplies oil to a plurality of friction plates.

  As such a friction engagement device, for example, a device described in JP 2004-053023 A (Patent Document 1) is known. Hereinafter, in the description of the background art column, reference numerals and member names in Patent Document 1 are quoted in []. In the friction engagement device of Patent Document 1, a plurality of friction plates [pressure plate: 4 and end plate 6] are supported from the inside by the first cylindrical portion of the first member [clutch hub: 2]. . An oil hole [oil supply passage: 9.1, 9.2, 9.3, 9.4] penetrating in the radial direction is formed in the first cylindrical portion. The first member [clutch hub: 2] includes a first annular portion extending radially inward from the first tubular portion, and the second member [balance piston: 14] is a second circle extending in the radial direction. An annular portion [spring support: 14.1] is provided. And, the oil extending in the radial direction between the first annular portion of the first member [clutch hub: 2] and the second annular portion [spring support: 14.1] of the second member [balance piston: 14]. A space [11] is formed. The oil flowing through the oil space [11] passes through the oil holes [oil supply passages: 9.1, 9.2, 9.3, 9.4] and a plurality of friction plates [pressure plates: 4 and ends] The plurality of friction plates [pressure plate: 4 and end plate 6] are cooled.

JP 2004-053023 A

  In the friction engagement device of Patent Document 1, the second cylindrical portion [cylindrical body wall: 14.3] of the second member [balance piston: 14] is the first of the first member [inner support portion: 32]. An oil passage extending in the axial direction is provided between the first cylindrical portion and the second cylindrical portion (cylindrical wall: 14.3). It is formed over the entire circumference in the circumferential direction. The oil that has flowed through the oil space [11] flows through the oil passage, and then passes through the oil hole [oil supply passage: 9.1, 9.2, 9.3, 9.4], and a plurality of friction plates [inside Friction plate: 31A]. However, the oil flowing in the oil passage is easy to flow in the oil hole [oil supply passage: 9.1] existing on the second axial side that is upstream of the oil flow in the axial direction, and the axial direction first on the downstream side. The oil hole [oil supply passage: 9.4] existing on one side becomes difficult to flow. Therefore, the oil holes [oil supply passages: 9.1, 9.2, 9.3, 9.4] differ in the amount of oil flowing depending on the position in the axial direction, so a plurality of sheets arranged along the axial direction. It was difficult to uniformly cool the friction plates [pressure plate: 4 and end plate 6].

  Therefore, it is desired to realize a friction engagement device capable of achieving uniform cooling for a plurality of friction plates.

  In view of the above, the characteristic configuration of the friction engagement device includes a first member having a cylindrical first cylindrical portion, a plurality of the members arranged along the axial direction of the first cylindrical portion, and the first member. An annular plate-like friction plate supported from the inside in the radial direction by one cylindrical portion, and arranged on the inside in the radial direction of the first cylindrical portion, and arranged along the inner peripheral surface of the first cylindrical portion. A second member having a cylindrical second cylindrical portion, and a supply portion for supplying oil to the plurality of friction plates, the first cylindrical portion being viewed in a radial direction. An overlapping region that overlaps with the second cylindrical portion, and a non-overlapping region that does not overlap with the second cylindrical portion when viewed in the radial direction, and the supply unit is in a radial direction with respect to the non-overlapping region Oil is supplied from the inside, and the first cylindrical portion includes a plurality of oil holes in the overlapping region that penetrate the first cylindrical portion in the radial direction. According to the axial arrangement interval of rubbing, it is arranged at a plurality of locations in the axial direction and is arranged at a plurality of locations in the circumferential direction, and the inner circumferential surface of the first cylindrical portion and the second cylindrical portion An axial groove formed in a groove shape extending along the axial direction is provided on at least one of the outer peripheral surfaces, and the axial groove is formed at a position corresponding to the oil hole in the circumferential direction. is there.

  According to this characteristic configuration, the plurality of oil holes (56) formed in the overlapping region (T1) of the first cylindrical portion are distributed and arranged at a plurality of locations in the circumferential direction (C). The axial grooves (57) formed at positions corresponding to the plurality of oil holes (56) are also distributed and arranged at a plurality of locations in the circumferential direction (C). Then, the oil supplied from the radial inner side (R1) to the non-overlapping region (T2) from the supply unit (A3) is divided into a plurality of axial grooves (57) and flows into the axial grooves (57). ) And flows to the first axial side (L1), is supplied to the oil hole (56) corresponding to the axial groove (57), passes through the oil hole, and the plurality of friction plates (31B) Supplied in between. That is, the axial direction groove (56) of the oil hole (56) is branched by guiding the oil supplied from the supply section to each oil hole by an axial groove formed at a position corresponding to the oil hole in the circumferential direction. ) Regardless of the position, an equal amount of oil can be supplied to each oil hole. Therefore, it is possible to make the cooling of the plurality of friction plates (31B) uniform.

Schematic diagram showing the schematic configuration of a vehicle drive device Sectional view of a part of a vehicle drive device Partial enlarged view of FIG. Development view of the second annular part viewed from the inside in the radial direction VV sectional view of FIG. The development which looked at the 2nd annular part of another embodiment from the diameter direction inside

1. Embodiment An embodiment of a friction engagement device according to the present invention will be described with reference to the drawings. The friction engagement device CL according to the present embodiment is provided in the vehicle drive device 1. The vehicle drive device 1 is a vehicle drive device (hybrid vehicle drive device) for driving a vehicle (hybrid vehicle) including both the internal combustion engine E and the rotating electrical machine MG as a drive force source for the wheels W of the vehicle. is there. Specifically, the vehicle drive device 1 is configured as a drive device for a 1-motor parallel type hybrid vehicle.

  In the following description, unless otherwise specified, the “axial direction L”, “radial direction R”, and “circumferential direction C” are the rotational axis X of the friction engagement device CL (hereinafter referred to as the axial center X). (Abbreviated). The axis X of the friction engagement device CL is a rotating member provided in the friction engagement device CL (a first friction plate 31A, a second friction plate 31B, a first support member 32, a second support member 33, etc., which will be described later). Is the axis of rotation. “Axial direction first side L1” represents a direction toward the one side in the axial direction L (right side in FIG. 2). “Axial second side L2” is the other side of axial direction L, and represents the direction opposite to axial first side L1 (left side in FIG. 2). The “radial inner side R1” represents a direction toward the inner side of the radial direction R, and the “radial outer side R2” represents a direction toward the outer side of the radial direction R. In addition, the direction about each member represents the direction in the state in which the said member was assembled | attached to the vehicle drive device 1. FIG. Further, terms relating to the direction, position, etc. of each member are used as a concept including a state having a difference due to an allowable error in manufacturing.

1-1. Overall Configuration of Vehicle Drive Device As shown in FIG. 1, a vehicle drive device 1 includes an input shaft 10 that is drivingly connected to an internal combustion engine E, a friction engagement device CL, a rotating electrical machine MG, and a transmission input shaft 11. And a transmission device TM and an output shaft O that is drivingly connected to the wheels W. The friction engagement device CL, the rotating electrical machine MG, and the transmission device TM are provided in the power transmission path connecting the input shaft 10 and the output shaft O in the order described from the input shaft 10 side. The vehicle drive device 1 further includes an oil pump OP and a pump drive mechanism 60. These are housed in the case 2 (see FIG. 2).

  The friction engagement device CL is provided in a power transmission path between the input shaft 10 and the rotating electrical machine MG. The friction engagement device CL selectively connects the internal combustion engine E and the input shaft 10 to the rotating electrical machine MG. That is, the friction engagement device CL connects or releases the input shaft 10 and the rotating electrical machine MG. In the present embodiment, the friction engagement device CL is configured to be hydraulically driven. The friction engagement device CL functions as an internal combustion engine disconnecting device that disconnects the internal combustion engine E from the wheel W in a state where the engagement is released.

  As shown in FIG. 2, the input shaft 10 is supported to be rotatable with respect to the case 2. In this embodiment, a boss portion 25A extending to the second axial side L2 is formed at the end of the support wall 25 in the radial direction R1 in the case 2, and the outer peripheral surface of the input shaft 10 and the boss portion 25A are An input bearing 26 is arranged between the inner peripheral surface. Thereby, the input shaft 10 is rotatably supported by the support wall 25 via the input bearing 26. Further, a seal member 27 is disposed between the outer peripheral surface of the input shaft 10 and the inner peripheral surface of the support wall 25 so as to contact both of them. The seal member 27 is disposed at a distance from the input bearing 26 on the first axial side L1.

  The rotating electrical machine MG can perform a function as a motor (electric motor) that generates power upon receiving power supply and a function as a generator (generator) that generates power upon receiving power supply. . The rotating electrical machine MG is electrically connected to a power storage device (battery, capacitor, etc.). The rotating electrical machine MG is powered by receiving power from the power storage device, or supplies the power storage device with power generated by the torque of the internal combustion engine E or the inertial force of the vehicle. The rotary electric machine MG is drivingly connected so as to rotate integrally with the transmission input shaft 11.

  The rotating electrical machine MG includes a stator St (see FIG. 1) fixed to the case 2, and a rotor Ro that is installed on the radially inner side R1 of the stator St and rotatably supported by the case 2 as shown in FIG. And a rotor support member 20 that supports the rotor Ro. The rotor support member 20 includes a rotor support portion 21 and a radially extending portion 22. The rotor support portion 21 is formed in a cylindrical shape extending in the axial direction L, and holds the rotor Ro from the radially inner side R1. The rotor support portion 21 is coupled to rotate integrally with the first support member 32 of the friction engagement device CL. In the present embodiment, the rotor support portion 21 and the first support member 32 are connected by the spline engagement portion A in a state where relative rotation in the circumferential direction C is restricted. The radially extending portion 22 is formed in an annular plate shape extending from the end region on the first axial side L1 of the rotor support portion 21 to the radially inner side R1. A bearing 28 is disposed between the inner peripheral surface of the radially extending portion 22 and the outer peripheral surface of the boss portion 25 </ b> A, and the rotor support member 20 is rotatably supported by the support wall 25.

1-2. General Configuration of Friction Engaging Device As shown in FIGS. 2 and 3, the friction engaging device CL is a wet friction engaging device. In the present embodiment, the friction engagement device CL is disposed so as to have a portion that is inside the radial direction R with respect to the rotor Ro of the rotating electrical machine MG and overlaps the rotor Ro when viewed in the radial direction R. . As shown in FIG. 3, the friction engagement device CL includes at least one first friction plate 31A and a plurality of second friction plates arranged so as to sandwich the first friction plate 31A from both sides in the axial direction L. 31B, a first support member 32 that rotates integrally with the first friction plate 31A, a second support member 33 that rotates integrally with the second friction plate 31B, and an oil passage forming member 35 are provided. The first friction plate 31 </ b> A is slidably supported in the axial direction L in a state where relative rotation in the circumferential direction C is restricted with respect to the first support member 32. The second friction plate 31 </ b> B is slidably supported in the axial direction L in a state where relative rotation in the circumferential direction C is restricted with respect to the second support member 33. The first support member 32 is drivingly connected to rotate integrally with the transmission input shaft 11, and the second support member 33 is drive connected to rotate integrally with the input shaft 10. In the present embodiment, a plurality of second friction plates 31B are arranged along the axial direction L. A plurality of second friction plates 31B are arranged along the axial direction L so as to sandwich each of the plurality of first friction plates 31A from both sides in the axial direction L. In the present embodiment, the second support member 33 corresponds to a “first member”, the second friction plate 31B corresponds to an annular plate-like “friction plate”, and the oil passage forming member 35 corresponds to a “first member”. It corresponds to “two members”.

  The friction engagement device CL further includes a piston 34 and a spring 36. The piston 34 presses the first friction plate 31A and the second friction plate 31B from the second axial side L2. The spring 36 urges the piston 34 to the second axial side L2 that is opposite to the hydraulic pressure. In the present embodiment, the piston 34 corresponds to a “pressing member” that presses the plurality of second friction plates 31B from the first axial side L1, and the spring 36 attaches the piston 34 to the first axial side L1. It corresponds to a “biasing member”. On the first axial side L1 with respect to the piston 34, there is provided a working hydraulic chamber H1 for moving the piston 34 to the second axial side L2 by the hydraulic pressure by the supplied oil. Further, a cancel hydraulic chamber H2 is formed on the second axial side L2 with respect to the piston 34 to cancel out the centrifugal hydraulic pressure acting on the working hydraulic chamber H1. The cancel hydraulic chamber H2 is formed between the piston 34 and the oil passage forming member 35 in the axial direction L.

  In the engaged state in which the frictional engagement device CL is engaged, the connection between the rotating electrical machine MG that is drivingly connected to the first support member 32 and the input shaft 10 that is drivingly connected to the second support member 33 is maintained. Is done. At this time, torque is transmitted between the first support member 32 and the second support member 33 by the frictional force generated between the first friction plate 31A and the second friction plate 31B. The engagement state includes a slip engagement state and a direct engagement state. The sliding engagement state is an engagement state in which there is a difference in rotational speed between the first friction plate 31A and the second friction plate 31B, and the direct engagement state is the first friction plate 31A and the second friction plate 31B. In this engagement state, there is no rotational speed difference. Further, in the released state in which the frictional engagement device CL is released, the connection between the rotating electrical machine MG drivingly connected to the first support member 32 and the input shaft 10 drivingly connected to the second support member 33 is released. Is done. At this time, transmission torque may be generated unlike the command by dragging between the first friction plate 31A and the second friction plate 31B. However, basically, in the released state, the first support member 32 and the second friction plate 31B. Torque is not transmitted to and from the support member 33. For example, during the execution of the electric travel mode in which the vehicle travels only by the torque of the rotating electrical machine MG, the friction engagement device CL is basically controlled to the released state. During execution of the hybrid travel mode in which the vehicle travels with the torque of both the internal combustion engine E and the rotating electrical machine MG, the friction engagement device CL is basically controlled to be in the direct engagement state. Further, for example, when the internal combustion engine E in a stopped state is started by the torque of the rotating electrical machine MG, when the vehicle is stopped in a state where the torque of the internal combustion engine E is transmitted to the wheels W on a slope or the like, For example, when the vehicle is started by torque, the friction engagement device CL is controlled to be in a sliding engagement state.

1-3. Specific Configuration of Friction Engaging Device The first friction plates 31A and the second friction plates 31B are alternately arranged along the axial direction L one by one. Each of the first friction plate 31A and the second friction plate 31B is an annular plate-like member (a plate-like and annular member).
As shown in FIG. 3, the first friction plate 31 </ b> A has friction contact surfaces on which friction materials are provided on both sides in the axial direction L. The second friction plate 31B has friction contact surfaces on which the friction material is not provided on both sides in the axial direction L. Here, the friction contact surface of the first friction plate 31A is a region overlapping the second friction plate 31B when viewed in the axial direction L on the surface facing the axial direction L of the first friction plate 31A. The friction contact surface of 31B is a region overlapping the first friction plate 31A when viewed in the axial direction L on the surface facing the axial direction L of the second friction plate 31B. The friction material is made of paper, synthetic resin, or the like as a base material.

The first support member 32 is formed in a cylindrical shape that extends from the end of the radially outer side R2 of the first annular portion 41 toward the first axial side L1. The outer side support part 42 and the 1st cylindrical part 43 formed in the cylindrical shape extended toward the axial direction 1st side L1 from the edge part of radial direction inner side R1 of the 1st annular part 41 are provided.
A first engagement portion 44 is provided on the inner peripheral surface of the outer support portion 42. An end of the first friction plate 31A on the radially outer side R2 is engaged with the first engagement portion 44 (in this example, spline engagement), whereby the first support member 32 and the first friction plate are engaged. 31A is configured to rotate integrally.

Further, the outer peripheral surface of the outer support portion 42 and the inner peripheral surface of the rotor support portion 21 are engaged by the spline engaging portion A (in this example, spline engagement), whereby the first support member 32 and the rotor are engaged. The support member 20 is configured to rotate integrally.
The outer support portion 42 is provided with a discharge oil passage 45 for discharging the oil supplied from the radial inner side R1 to the first friction plate 31A and the second friction plate 31B.
The inner peripheral surface of the first cylindrical portion 43 and the outer peripheral surface of the transmission input shaft 11 are engaged (in this example, spline engagement), whereby the first support member 32 is integrated with the transmission input shaft 11. It is configured to rotate.

  The second support member 33 is formed in a cylindrical shape that extends from the end of the radially outer side R2 of the second annular portion 51 toward the first side L1 in the axial direction. And a second cylindrical portion 53 formed in a cylindrical shape extending from the end of the radial inner side R1 of the second annular portion 51 toward the first axial side L1. As described above, the second support member 33 includes the cylindrical inner support portion 52 and the second annular portion 51 extending from the inner support portion 52 to the radially inner side R1. In the present embodiment, the inner support portion 52 corresponds to a “first cylindrical portion”, and the second annular portion 51 corresponds to a “first radially extending portion”.

  A second engagement portion 54 is provided on the outer peripheral surface of the inner support portion 52. An end of the radially inner side R1 of the second friction plate 31B is engaged with the second engagement portion 54 (in this example, spline engagement), whereby the second support member 33 and the second friction plate are engaged. 31B is configured to rotate integrally. The inner peripheral surface of the second cylindrical portion 53 and the outer peripheral surface of the input shaft 10 are engaged (in this example, spline engagement), whereby the second support member 33 rotates integrally with the input shaft 10. It is configured as follows. The second cylindrical portion 53 is provided with a supply oil passage 55 for supplying the first friction plate 31A and the second friction plate 31B from the radially inner side R1.

  The oil passage forming member 35 is formed in a cylindrical shape, and an annular shape extending from the end portion on the first axial side L1 of the third cylindrical portion 61 toward the radially outer side R2. The outer third annular portion 62 and the inner third annular portion 63 formed in an annular shape extending from the end of the second axial side L2 of the third cylindrical portion 61 toward the radially outer side R2. I have.

  The oil passage forming member 35 has a portion that overlaps with the second annular portion 51 when viewed in the axial direction L, and a portion that overlaps with the inner support portion 52 when viewed in the radial direction R. The oil passage forming member 35 has a portion overlapping the piston 34 when viewed in the axial direction L. In the present embodiment, the inner third annular portion 63 overlaps the second annular portion 51 and the piston 34 when viewed in the axial direction L, and the inner third annular portion 63 is the second annular portion 51 in the axial direction L. And the piston 34. The third cylindrical portion 61 overlaps with the inner support portion 52 when viewed in the radial direction R. Thus, the oil passage forming member 35 extends in the radial direction R from the third cylindrical portion 61 between the cylindrical third cylindrical portion 61 and the axial direction L between the second annular portion 51 and the piston 34. An inner third annular portion 63. In the present embodiment, the third cylindrical portion 61 corresponds to a “second cylindrical portion”, and the inner third annular portion 63 corresponds to a “second radially extending portion”.

  The inner third annular part 63 is arranged on the first axial side L1 side with respect to the second annular part 51 with a gap in the axial direction L between the second annular part 51 and the inner third part. A third oil passage A3 is formed between the annular portion 63 and the second annular portion 51. The third oil passage A <b> 3 is formed over the entire circumference in the circumferential direction C between the inner third annular portion 63 and the second annular portion 51. In the present embodiment, the third oil passage A3 corresponds to a “supply section” that supplies oil to a plurality of friction plates.

  An end of the inner third annular portion 63 on the radially inner side R1 is engaged with the outer peripheral surface of the second cylindrical portion 53 (in this example, spline engagement). Accordingly, the oil passage forming member 35 is configured to rotate integrally with the second support member 33. As described above, the second support member 33 and the oil passage forming member 35 are coupled so as to rotate at the same speed.

  The third tubular portion 61 is disposed on the radially inner side R <b> 1 of the inner support portion 52, and is disposed along the inner peripheral surface of the inner support portion 52. In the present embodiment, the third cylindrical portion 61 is installed such that a slight gap is formed between the outer peripheral surface of the third cylindrical portion 61 and the inner peripheral surface of the inner support portion 52. In addition, you may install the 3rd cylindrical part 61 so that the outer peripheral surface of the 3rd cylindrical part 61 and the inner peripheral surface of the inner side support part 52 may contact.

  The oil passage forming member 35 is provided with a second side support portion 64 that supports a spring 36 that biases the piston 34 toward the first axial direction L1. In the present embodiment, the second side support portion 64 is provided on the surface of the inner third annular portion 63 facing the axial first side L1, and the first side support portion is disposed on the surface of the piston 34 facing the axial second side L2. 38 is provided. The spring 36 is disposed in a compressed state between the second side support portion 64 of the inner third annular portion 63 and the first side support portion 38 of the piston 34 in the axial direction L. It is biased toward the first direction L1. In the present embodiment, the second side support portion 64 corresponds to a “support portion” that supports the spring 36.

1-4. Oil hole 56 and axial groove 57
As shown in FIGS. 3 and 4, the inner support portion 52 overlaps with the third cylindrical portion 61 when viewed in the radial direction R, and overlaps with the third cylindrical portion 61 when viewed in the radial direction R. And a non-overlapping region T2 that is not to be used. In the present embodiment, the boundary portion 35 </ b> A between the third cylindrical portion 61 and the inner third annular portion 63 in the oil passage forming member 35 is also the third cylindrical portion 61.

  The inner support portion 52 includes a plurality of oil holes 56 penetrating the inner support portion 52 in the radial direction R in the overlapping region T1. In the illustrated example, the oil hole 56 is not provided in the non-overlapping region T2. Here, “equipped with the oil hole 56 in the overlapping region T1” means that at least a part of the oil hole 56 is located in the overlapping region T1. In the present embodiment, when the center of the oil hole 56 in the axial direction L is located in the overlap region T1, the oil hole 56 is provided in the overlap region T1. On the other hand, “the oil hole 56 is not provided in the non-overlapping region T2” means that the oil hole 56 is not located in the non-overlapping region T2 as a whole.

  The plurality of oil holes 56 are arranged at a plurality of locations in the axial direction L according to the arrangement interval in the axial direction L of the plurality of second friction plates 31B, and are distributed and arranged at a plurality of locations in the circumferential direction C. Yes. In the present embodiment, the plurality of oil holes 56 are arranged at positions in the axial direction L corresponding to the gaps between the pair of adjacent second friction plates 31B. In addition, an oil hole group G is formed by a plurality of oil holes 56 included in each of the circumferential sections S divided at regular intervals in the circumferential direction C, and each of the oil hole groups G includes a plurality of second friction plates. Oil holes 56 are provided at positions in the axial direction L corresponding to the gaps between the second friction plates 31B formed by 31B. In the present embodiment, five gaps are formed by the six second friction plates 31B.

  The inner support portion 52 is divided into eight circumferential sections S in the circumferential direction C. When the five gaps are defined as the first gap, the second gap, the third gap, the fourth gap, and the fifth gap from the gap on the second axial side L2, one circumferential section S The oil hole 56 (first oil hole 56A) corresponding to the first gap, the oil hole 56 (second oil hole 56B) corresponding to the second gap, and the oil hole corresponding to the third gap 56 (third oil hole 56C), an oil hole 56 (fourth oil hole 56D) corresponding to the fourth gap, and an oil hole 56 (fifth oil hole 56E) corresponding to the fifth gap , Is formed. That is, each of the oil hole groups G includes a first oil hole 56A, a second oil hole 56B, a third oil hole 56C, a fourth oil hole 56D, and a fifth oil hole 56E. Yes. In the example shown in FIG. 4, the first oil hole 56A, the second oil hole 56B, the third oil hole 56C, the fourth oil hole 56D, and the fifth oil hole 56E are arranged in this order along the circumferential direction C. Has been.

  Each oil hole 56 is formed in a circular shape when viewed in the radial direction R, and is formed such that the center in the axial direction L of the oil hole 56 is positioned at the center in the axial direction L in the corresponding gap. Further, in the present embodiment, the diameter of the oil hole 56 is formed larger than the width in the axial direction L in the corresponding gap, and the thickness in the axial direction L of the second friction plate 31B is set to the width in the axial direction L in the corresponding gap. It is formed smaller than the added length.

A fourth oil passage A4 extending in the axial direction L is formed between the inner peripheral surface of the inner support portion 52 in the second support member 33 and the outer peripheral surface of the third cylindrical portion 61 in the oil passage forming member 35. ing. One fourth oil passage A4 is formed for each of the plurality of oil holes 56, and is formed in the circumferential direction C so as to be formed at a position overlapping the corresponding oil hole 56 when viewed in the radial direction R. A plurality are formed in a distributed manner.
In the present embodiment, the inner circumferential surface of the inner support portion 52 is provided with an axial groove 57 formed in a groove shape that extends in the axial direction L and that is recessed in the radially outer side R2. The fourth oil passage A4 is formed by covering the radially inner side R1 of the axial groove 57 with the third cylindrical portion 61. The axial groove 57 is formed at a position corresponding to the oil hole 56 in the circumferential direction C. An oil hole 56 is formed on the bottom surface of the axial groove 57.

  The axial groove 57 is formed so as to extend along the axial direction L over the entire region in the axial direction L where the plurality of oil holes 56 are arranged. In the present embodiment, the region in the axial direction L where the plurality of oil holes 56 are arranged is the axial direction in the oil hole 56 (here, the first oil hole 56A) on the second axial side L2 in the axial direction L. This is a region from the second side L2 end to the axial first side L1 end in the oil hole 56 (here, the fifth oil hole 56E) on the most axial first side L1. In this example, each of the plurality of axial grooves 57 extends along the axial direction L over a region in the axial direction L wider than the region in the axial direction L in which the plurality of oil holes 56 are disposed. It is formed to extend. It is preferable that each of the plurality of axial grooves 57 is formed at least over the entire overlap region T1.

  Between the inner peripheral surface of the inner support portion 52 and the outer peripheral surface of the third cylindrical portion 61, there is a fourth oil passage A4 that is a natural number times the number of gaps formed by the plurality of second friction plates 31B. Is formed. In this embodiment, corresponding to the five oil holes 56 being arranged in each of the eight circumferential sections S, eight times the five gaps formed by the second friction plate 31B, that is, 40 pieces. A fourth oil passage A4 is formed. As shown in FIG. 3, the axial groove 57 is formed to have an inclined bottom surface that faces the radially outer side R2 toward the first axial side L1. Thereby, the oil led to the fourth oil passage A4 flows toward the first axial side L1 by the centrifugal force generated by the rotation of the second support member 33. As shown in FIG. 4, the axial groove 57 is formed in a shape in which the width in the circumferential direction C increases toward the first axial side L <b> 1. That is, the radial cross-sectional area of the fourth oil passage A4 is formed so as to extend toward the first axial side L1. Thereby, the flow of the oil which goes to the axial direction 1st side L1 along the axial direction groove | channel 57 is comprised.

1-5. Oil Supply Structure for Friction Engagement Device CL The transmission input shaft 11 is formed with a plurality of in-shaft oil passages extending in the axial direction L in parallel with each other in the circumferential direction C. In such an in-shaft oil passage, a first oil passage A1 communicating with the working hydraulic chamber H1 through a first oil hole 13 formed in the input shaft 10 and a second oil hole formed in the input shaft 10 are provided. A second oil passage A2 communicating with the supply oil passage 55 through 15 is also included. A third oil passage A3 extending in the radial direction R is formed between the second annular portion 51 of the second support member 33 and the inner third annular portion 63 of the oil passage forming member 35. A fourth oil passage A <b> 4 is formed between the inner support portion 52 and the third cylindrical portion 61 of the oil passage forming member 35. The oil supplied from the first oil passage A1 is supplied to the working hydraulic chamber H1 through the first oil hole 13.

  The oil supplied from the second oil passage A2 flows through the second oil hole 15 and the supply oil passage 55 and then flows through the third oil passage A3 from the radially inner side R1 toward the radially outer side R2. As a result, oil is supplied from the radially inner side R1 to the non-overlapping region T2. The oil supplied to the non-overlapping region T2 flows into the plurality of axial grooves 57. The oil flowing in the axial direction L along the axial groove 57 passes through the oil holes 56 corresponding to the axial groove 57, and the second friction plates 31B formed by the plurality of second friction plates 31B. Supplied to the gap. Thereby, oil can be supplied to the friction surfaces of the first friction plate 31A and the second friction plate 31B of the friction engagement device CL, and heat generated by friction between the friction plates can be appropriately cooled.

2. Other Embodiments Next, other embodiments of the friction engagement device will be described.

(1) In the above embodiment, one axial groove 57 is formed for one oil hole 56, but one axial groove 57 may be formed for a plurality of oil holes 56. For example, as shown in FIG. 6, one axial groove 57 may be formed for two oil holes 56 arranged in the circumferential direction C.
Further, the arrangement order of the plurality of oil holes 56 in the circumferential direction C in one oil hole group G is not limited to the arrangement of the above embodiment. The arrangement order of the circumferential direction C of the plurality of oil holes 56 having different positions in the axial direction L may be appropriately changed. For example, as shown in FIG. 6, five oil holes 56 of one oil hole group G are arranged along the circumferential direction C with a first oil hole 56A, a fifth oil hole 56E, a second oil hole 56B, The fourth oil hole 56D and the third oil hole 56C may be arranged in this order.

(2) In the above embodiment, the oil hole 56 is positioned so that the center in the axial direction L of the oil hole 56 is positioned at the center of the gap between the second friction plates 31B formed by the plurality of second friction plates 31B. Although the case where it forms is demonstrated as an example, arrangement | positioning of the axial direction L of the oil hole 56 with respect to a friction board is not limited to this. For example, the oil hole 56 may be formed at a position where the center of the oil hole 56 in the axial direction L overlaps with the friction plate when viewed in the radial direction R. Incidentally, in this case, the diameter of the oil hole 56 may be formed such that the gap between the friction plates adjacent to both sides in the axial direction L and a part of the oil hole 56 overlap each other when viewed in the radial direction R. Good.

(3) In the above embodiment, the axial groove 57 is formed on the inner peripheral surface of the first cylindrical portion 52, but the axial groove 57 may be formed on the outer peripheral surface of the second cylindrical portion 61. In this case, the inner peripheral surface of the first cylindrical portion 52 can be a flat cylindrical surface. Further, the axial grooves 57 may be formed on both the inner peripheral surface of the first cylindrical portion 52 and the outer peripheral surface of the second cylindrical portion 61.

(4) In the above embodiment, the second member is constituted by the oil passage forming member 35 installed to form the cancel hydraulic chamber H2, but the second member is formed by a member other than the oil passage forming member 35. May be. For example, a member that forms the third oil passage A3 and the fourth oil passage A4 may be provided separately from the oil passage forming member 35, and this member may be used as the second member.

(5) In the above-described embodiment, the axial groove 57 is formed so as to extend in the axial direction L over the entire region in the axial direction L where the plurality of oil holes 56 are arranged. Was taken as an example. However, the present invention is not limited to this, and the axial groove 57 may be formed to a length corresponding to each of the plurality of oil holes 56 arranged at different positions in the axial direction L. In this case, the lengths of the plurality of axial grooves 57 differ depending on the positions of the corresponding oil holes 56 in the axial direction L.

(6) In the above-described embodiment, the second support member 33 as the first member and the oil passage forming member 35 as the second member have been described as an example, and are connected so as to rotate at the same speed. It is not limited to this. That is, the structure which a 1st member and a 2nd member rotate relatively may be sufficient.

(7) In the above embodiment, the oil path forming member 35 as the second member has been described as an example of the configuration including the second side support portion 64 that supports the spring 36 as the biasing member. However, the present invention is not limited to this, and a configuration in which a support member that supports the spring 36 as an urging member may be provided separately from the oil passage forming member 35 as the second member.

(8) It should be noted that the configurations disclosed in the above-described embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction arises. Regarding other configurations, the embodiments disclosed herein are merely examples in all respects. Accordingly, various modifications can be made as appropriate without departing from the spirit of the present disclosure.

3. Outline of the Embodiment The outline of the friction engagement device described above will be described below.

  A plurality of friction engagement devices are arranged along the first member (33) having a cylindrical first cylindrical portion (52) and the axial direction (L) of the first cylindrical portion (52). And an annular plate-like friction plate (31B) supported from the radially inner side (R1) by the first tubular portion (52), and a radially inner side (R1) of the first tubular portion (52). A second member (35) having a cylindrical second cylindrical part (61) arranged along the inner peripheral surface of the first cylindrical part (52), and the plurality of frictions A supply portion (37) for supplying oil to the plate (31B), and the first tubular portion (52) includes the second tubular portion (61) as viewed in the radial direction (R). An overlapping region (T1) that overlaps and a non-overlapping region (T2) that does not overlap with the second cylindrical portion (61) when viewed in the radial direction (R), and the supply unit (37) Non-overlapping territory Oil is supplied from the radially inner side (R1) to (T2), and the first cylindrical portion (52) is an oil hole that penetrates the first cylindrical portion (52) in the radial direction (R). (56) is provided in the overlap region (T1), and the plurality of oil holes (56) are arranged in the axial direction according to the arrangement interval in the axial direction (L) of the plurality of friction plates (31B). (L) are arranged at a plurality of locations, and are arranged at a plurality of locations in the circumferential direction (C), and the inner circumferential surface of the first cylindrical portion (52) and the outer circumferential surface of the second cylindrical portion (61). Is provided with an axial groove (57) formed in a groove shape extending along the axial direction (L), and the axial groove (57) is the oil hole (C) in the circumferential direction (C). 56).

  According to this characteristic configuration, the plurality of oil holes (56) formed in the overlapping region (T1) of the first cylindrical portion (52) are distributed and arranged at a plurality of locations in the circumferential direction (C). The axial grooves (57) formed at positions corresponding to the plurality of oil holes (56) are also distributed and arranged at a plurality of locations in the circumferential direction (C). The oil supplied from the radially inner side (R1) to the non-overlapping region (T2) from the supply unit (37) flows into the plurality of axial grooves (57) and then flows into the axial grooves (57). ) And flows to the first axial side (L1), is supplied to the oil hole (56) corresponding to the axial groove (57), passes through the oil hole (56), and a plurality of friction plates ( 31B). That is, the oil supplied from the supply unit (37) is branched by the axial groove (57) formed at a position corresponding to the oil hole (56) in the circumferential direction (C) to each oil hole (56). By guiding, an equal amount of oil can be supplied to each oil hole (56) regardless of the position of the oil hole (56) in the axial direction (L). Therefore, it is possible to make the cooling of the plurality of friction plates (31B) uniform.

  Here, it is preferable that the first member (33) and the second member (35) are connected so as to rotate at the same speed.

  According to this configuration, even when the axial groove (57) is formed on the inner peripheral surface of the first cylindrical portion (52), the axial groove (57) is formed on the outer peripheral surface of the second cylindrical portion (61). Even when formed, the positional relationship in the circumferential direction (C) between the oil hole (56) and the axial groove (57) can be maintained. Moreover, the internal peripheral surface of a 1st cylindrical part (52) and the outer peripheral surface of a 2nd cylindrical part (61) can be made to contact, and a clearance gap can also be provided among these. That is, according to this structure, the freedom degree of design of an axial direction groove | channel (57) and its surrounding structure can be raised.

  The pressing member (34) further includes a pressing member (34) that presses the plurality of friction plates (31B) from an axial first side (L1) that is one side of the axial direction (L). On the other hand, a working hydraulic pressure chamber (H1) is formed on the first axial side (L1), and the first member (33) extends from the first cylindrical portion (52) to the radially inner side (R1). The second member (35) further includes a first radially extending portion (51), and the second member (35) extends in the axial direction (L) between the first radially extending portion (51) and the pressing member (34). A second radially extending portion (63) extending in the radial direction (R) from the second tubular portion (61) is further provided, and the axial first side (with respect to the pressing member (34)) L1) is the opposite side of the pressing member (34) and the second member (35) between the axial direction (L) and the operation Pressure chamber (H1) cancel oil chamber for canceling the centrifugal hydraulic pressure applied to the (H2) it is preferable that is formed.

  According to this configuration, the axial groove (57) is utilized by utilizing the second member (35) which is a member forming the cancel hydraulic chamber (H2) for canceling the centrifugal hydraulic pressure generated in the working hydraulic chamber (H1). Or the radial inner side (R1) of the axial groove (57) can be covered. Therefore, since it is not necessary to separately provide members for these, the configuration of the friction engagement device (1) can be simplified.

  The second member (35) preferably includes a support portion (64) that supports a biasing member (36) that biases the pressing member (34) toward the first axial direction (L1). is there.

  According to this configuration, the urging member (36) can be supported by the second member (35). Therefore, since it is not necessary to separately provide a member for supporting the biasing means (36), the configuration of the friction engagement device (1) can be simplified.

  Further, it is preferable that one axial groove (57) is formed for each of the plurality of oil holes (56).

  According to this configuration, oil once flowing into one axial groove (57) flows out only through one oil hole (56) corresponding to the axial groove (57), and therefore the oil hole (56). The oil can be supplied reliably. Therefore, an equal amount of oil can be supplied to each oil hole regardless of the position of the oil hole (56) in the axial direction (L).

  An oil hole group (G) is formed by the plurality of oil holes (56) included in each of the circumferential sections (S) divided at regular intervals in the circumferential direction (C), and the oil hole group ( Each of G) is an oil hole (56) disposed at a position in the axial direction (L) corresponding to each gap between the friction plates (31B) formed by the plurality of friction plates (31B). It is preferable to have

  According to this configuration, the oil holes (56) corresponding to the gaps between the friction plates (31B) formed by the plurality of friction plates (31B) are arranged in each of the circumferential sections (S). It will be. That is, according to this configuration, the oil holes (56) having the same or close position in the axial direction (L) are not arranged in a partial region in the circumferential direction (C), and a plurality of oil holes ( 56) are distributed almost uniformly in the axial direction (L) and the circumferential direction (C). Accordingly, for example, a partial region in the circumferential direction (C) of the first cylindrical portion (52), such as a configuration in which the circumferential direction (C) of the first cylindrical portion (52) is immersed below the oil surface. Even when the oil is supplied in a biased manner, the oil can be uniformly supplied to all the gaps between the friction plates (31B) formed by the plurality of friction plates (31B).

  The axial groove (57) is formed so as to extend along the axial direction (L) over the entire region in the axial direction (L) where the plurality of oil holes (56) are disposed. It is preferable that

  According to this configuration, regardless of the position of the oil hole (56) in the axial direction (L), the axial groove (57) and the oil hole (56) corresponding to the axial groove (57) are arranged in the radial direction ( R) can be duplicated. Therefore, regardless of the position of the corresponding oil hole (56) in the axial direction (L), the axial groove (57) can be formed in the same shape, and the process of forming a plurality of axial grooves (57) can be simplified. .

  The technology according to the present disclosure can be used in a friction engagement device including a supply unit that supplies oil to a plurality of friction plates.

31B: Second friction plate (friction plate)
33: Second support member (first member)
34: Piston (pressing member)
35: Oil passage forming member (second member)
36: Spring (biasing member)
37: Third oil passage (supply section)
51: Second annular portion (first radially extending portion)
52: Inner support part (first cylindrical part)
56: Oil hole 57: Axial groove 61: Third cylindrical part (second cylindrical part)
63: Inner third annular portion (second radially extending portion)
64: Second side support part (support part)
C: circumferential direction CL: friction engagement device H1: working hydraulic chamber H2: cancel hydraulic chamber L: axial direction L1: axial first side R: radial direction R1: radial inner side S: circumferential section T1: overlapping region T2 : Non-overlapping area

Claims (7)

A first member provided with a cylindrical first cylindrical portion;
A plurality of annular plates arranged along the axial direction of the first cylindrical portion and supported by the first cylindrical portion from the inside in the radial direction; and
A second member provided with a cylindrical second cylindrical portion that is arranged on the radially inner side of the first cylindrical portion and is arranged along the inner peripheral surface of the first cylindrical portion;
A supply section for supplying oil to the plurality of friction plates,
The first cylindrical portion has an overlapping region that overlaps with the second cylindrical portion when viewed in the radial direction, and a non-overlapping region that does not overlap with the second cylindrical portion when viewed in the radial direction,
The supply unit supplies oil from the radially inner side to the non-overlapping region,
The first tubular portion includes a plurality of oil holes in the overlapping region that penetrate the first tubular portion in the radial direction,
The plurality of oil holes are arranged at a plurality of locations in the axial direction according to the arrangement interval in the axial direction of the plurality of friction plates, and are arranged at a plurality of locations in the circumferential direction,
At least one of the inner peripheral surface of the first cylindrical portion and the outer peripheral surface of the second cylindrical portion is provided with an axial groove formed in a groove shape extending along the axial direction,
The axial groove is a friction engagement device formed at a position corresponding to the oil hole in the circumferential direction.   The friction engagement device according to claim 1, wherein the first member and the second member are coupled so as to rotate at the same speed. A pressing member that presses the plurality of friction plates from an axial first side that is one side of the axial direction;
A working hydraulic chamber is formed on the first axial side with respect to the pressing member,
The first member further includes a first radially extending portion extending radially inward from the first tubular portion,
The second member further includes a second radial extension portion extending in the radial direction from the second cylindrical portion between the axial directions of the first radial extension portion and the pressing member,
Cancellation for canceling centrifugal hydraulic pressure acting on the working hydraulic chamber between the pressing member and the second member on the side opposite to the first axial direction and between the pressing member and the second member The friction engagement device according to claim 1 or 2, wherein a hydraulic chamber is formed.   The friction engagement device according to claim 3, wherein the second member includes a support portion that supports a biasing member that biases the pressing member toward the first axial side.   The frictional engagement device according to any one of claims 1 to 4, wherein one axial groove is formed for each of the plurality of oil holes. An oil hole group is formed by the plurality of oil holes included in each of the circumferential sections divided at regular intervals in the circumferential direction,
6. The friction according to claim 5, wherein each of the oil hole groups includes oil holes arranged at positions in the axial direction corresponding to gaps between the friction plates formed by the plurality of friction plates. Engagement device.   The said axial direction groove | channel is formed so that it may extend along the said axial direction over the whole area | region of the said axial direction by which these oil holes are arrange | positioned. Friction engagement device.

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