JP2015135152A - Frictional engagement device lubrication structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a frictional engagement device lubrication structure capable of optimizing the flow rate and flow velocity of lubricating oil discharged toward a frictional material while securing a supply quantity of the lubricating oil necessary to lubricate the frictional material.SOLUTION: A spline (36) of a brake hub (34) includes a pair of sidewalls (37, 38) disposed on a front side and a back side of a cylindrical portion (35) in a rotational direction (R), respectively, and protruding radially outward; and a bottom wall (39) extending in the rotational direction (R) and coupling outside-diameter-side end portions (37a, 38a) of the paired sidewalls (37, 38) with each other, a lubricating hole (40) formed of a through-hole is provided in the back-side sidewall (38) at a position away from an inner surface (39a) of the bottom wall (39) by a predetermined dimension (ΔD) to an inside diameter side, and at least part of lubricating oil supplied to an inner circumferential surface (35a) of the cylindrical portion (35) is introduced toward an outer circumferential surface (35b) of the cylindrical portion (35) via the lubricating hole (40) so as to be discharged toward a frictional material (33).

Description

  The present invention relates to a lubrication structure for a friction engagement device.

  Conventionally, a drum fixed to a rotating shaft or a case, a plurality of outer plates (friction materials) spline-coupled to the inner peripheral surface of the drum in the axial direction of the rotating shaft, and a cylindrical shape located in the drum A wet-type multi-plate clutch or brake comprising a hub that has a shaft and is rotatably supported, and a plurality of inner plates (friction materials) that are splined to the outer peripheral surface of the hub so as to be slidable in the axial direction of the rotary shaft (Friction engagement device) is known (see, for example, Patent Document 1).

  The clutch or brake as described above causes the lubricating oil supplied to the hub to flow from the inner peripheral surface side to the outer peripheral surface side of the cylindrical portion through a lubricating hole formed in the cylindrical portion. A lubrication structure is provided to supply the friction material.

  In the friction engagement device having such a lubrication structure, the supply amount of the lubricating oil to the friction material is adjusted according to the diameter size and the number of the lubrication holes of the hub, or complicated as described in Patent Document 1. It was adjusted with a simple structure. The structure described in Patent Document 1 is a structure that intentionally increases the supply amount of the lubricating oil as the supply unit rotates.

  However, in the lubrication structure having the lubrication holes as described above, if the rotation speed of the hub or friction material exceeds a certain region, the flow rate of the supplied lubricating oil may become too high or the flow rate may become too high. is there. As a result, there is a possibility that the friction material may be damaged (broken) due to an event such as the friction sheet affixed to the surface of the friction material rolling up from the end and peeling off. For this reason, it is necessary to optimize the flow rate and flow velocity of the lubricating oil supplied to the friction material while securing the supply amount of the lubricating oil necessary for lubricating the friction material.

JP 2010-174917 A

  The present invention has been made in view of the above-described points, and an object of the present invention is to provide lubrication that discharges toward a friction material while ensuring a supply amount of lubricating oil necessary for lubrication of the friction material with a simple configuration. An object of the present invention is to provide a lubrication structure for a friction engagement device capable of optimizing the flow rate and flow rate of oil.

  In order to solve the above-described problems, a lubricating structure for a friction engagement device according to the present invention includes a rotating member (34) having a cylindrical portion (35) rotatably installed around an axis, and the cylindrical portion (35). A plurality of splines (36) extending in the axial direction and projecting to the outer diameter side of the cylindrical portion (35), and a plurality of friction materials (33) stacked along the axial direction. And the end of the friction material (33) is fitted to the spline (36), so that the friction material (33) can be moved in the axial direction with respect to the cylindrical portion (35) In the friction engagement device (B1) installed in a state in which the movement of the direction is restricted, the spline (36) is arranged on the near side and the far side in the rotation direction (R) of the cylindrical portion (35). And a pair of side walls (37, 38) projecting outward in the radial direction and extending in the rotational direction (R) A bottom wall (39) that connects end portions (37a, 38a) on the outer diameter side of the pair of side walls (37, 38), and the bottom wall (39) of the back side wall (38). A lubricating hole (40) comprising a through hole provided at a position separated from the inner surface (39a) by a predetermined dimension (ΔD) toward the inner diameter side is provided, and is supplied to the inner peripheral surface (35a) side of the cylindrical portion (35). At least a part of the lubricating oil is guided to the outer peripheral surface (35b) side of the cylindrical portion (35) through the lubricating hole (40) and discharged toward the friction material (33). It is characterized by that.

  According to the lubricating structure of the friction engagement device according to the present invention, the lubricating hole provided in the spline of the rotating member (cylindrical portion) is provided in the side wall on the back side of the spline so that the lubricating hole is directed to the friction material. Thus, the flow rate of the lubricating oil discharged can be suppressed to a low level, and the friction material can be effectively prevented from being damaged by the impact of the lubricating oil. That is, in the conventional lubrication structure, since the lubrication hole is provided in the bottom wall of the spline, the flow rate and flow rate of the lubricating oil discharged from the lubrication hole in the bottom wall toward the friction material by the centrifugal force accompanying the rotation of the hub is reduced. If it becomes too high, the friction material may be damaged. On the other hand, the lubrication hole of the present invention is provided on the side wall of the spline, so that the flow rate and flow rate of the lubricating oil discharged from the lubrication hole toward the friction material can be reduced compared to the conventional structure. . Therefore, it is possible to optimize the flow rate and flow velocity of the lubricating oil supplied to the friction material while securing the supply amount of the lubricating oil necessary for lubricating the friction material.

  Further, the lubricating hole of the present invention is provided at a position away from the inner surface of the bottom wall of the spline by a predetermined dimension toward the inner diameter side, so that only a part of the lubricating oil flowing along the spline is rubbed from the lubricating hole. It can be discharged toward the material. Thereby, since it is possible to prevent an excessive amount of lubricating oil from being discharged, it is possible to effectively prevent the friction material from being damaged by the pressure (momentum) of the discharged lubricating oil.

  Furthermore, according to the present invention, it is only necessary to change the arrangement and orientation of the lubrication holes as compared with the conventional lubrication structure, so that a mechanism such as a valve for adjusting the flow rate of the lubricating oil is provided, and the processing is troublesome. It is not necessary to form a small-diameter lubricating hole. Therefore, the manufacturing process of the friction engagement device can be simplified and the manufacturing cost can be reduced.

  Further, in the above lubricating structure, the pair of side walls (37, 38) of the spline (36) may have a direction in which the surface direction is inclined with respect to the radial direction (Z) of the cylindrical portion (35). .

  According to this configuration, by providing the lubrication hole of the spline on the side wall inclined with respect to the radial direction of the cylindrical portion, it is possible to suppress the momentum of the lubricating oil discharged from the lubrication hole toward the friction material.

  Moreover, in said lubrication structure, it is good for the lubrication hole (40) to extend in directions other than the radial direction (Z) of a cylindrical part (35).

Since the lubrication hole provided in the bottom wall of the conventional spline is a through hole extending in the radial direction of the cylindrical portion, the lubrication hole is discharged from the lubrication hole of the bottom wall toward the friction material by centrifugal force accompanying the rotation of the rotating member. In addition to the high flow rate and flow rate of the lubricating oil, the lubricating oil is discharged directly (directly) toward the friction material. On the other hand, according to the above configuration according to the present invention, the lubrication hole provided in the side wall extends in a direction other than the radial direction of the cylindrical portion, and is discharged from the lubrication hole toward the friction material. The flow velocity and flow rate of the lubricating oil can be kept low, and the lubricating oil can be more effectively prevented from being discharged directly toward the friction material.
In addition, the code | symbol in said parenthesis shows the code | symbol of the component in embodiment mentioned later as an example of this invention.

  According to the lubricating structure of the friction engagement device according to the present invention, the flow rate of the lubricating oil discharged toward the friction material and the supply amount of the lubricating oil necessary for lubricating the friction material can be secured with a simple configuration. The flow velocity can be optimized.

It is a sectional side view which shows a part of automatic transmission provided with the friction engagement apparatus concerning one Embodiment of this invention. FIG. 2 is an enlarged view of a portion X in FIG. 1 for explaining a detailed configuration of a first brake. It is a figure which shows the YY arrow cross section of FIG. 2, and is the elements on larger scale which looked at the spline of the brake hub from the axial direction.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. FIG. 1 is a side sectional view showing a part of an automatic transmission including a friction engagement device according to an embodiment of the present invention. The automatic transmission 1 shown in the figure includes an input shaft 12 connected to an engine crankshaft (both not shown) via a torque converter, and a planetary gear mechanism PGSa provided on the outer periphery of the input shaft 12. . The input shaft 12 is supported by a stator shaft 19 of the torque converter via a ball bearing 28. In addition, a clutch C1, a first brake B1, and a second brake B2 are provided in order to switch the coupling relationship between the elements of the planetary gear mechanism PGSa and establish a gear position. The clutch C1 and the first brake B1 are configured by a wet multi-plate type, and the second brake B2 is configured by a mechanical type (for example, a one-way clutch).

  The single pinion planetary gear mechanism PGSa includes a sun gear Sa, a carrier Ca, a ring gear Ra, and a plurality of pinions Pa. The pinion Pa rotatably supported by the carrier Ca meshes with the sun gear Sa and the ring gear Ra at the same time. . The sun gear Sa can be coupled to the transmission case 13 via the first brake B1. The ring gear Ra is connected to a carrier of another planetary gear mechanism (not shown) via a connecting member 27.

  The connecting member 20 extending radially outward from the carrier Ca can be coupled to the transmission case 13 via the second brake B2. The carrier Ca can be coupled to the input shaft 12 via the clutch C1. That is, the clutch C1 is disposed between the clutch hub 22 connected to the radially inner end of the carrier Ca via the connecting member 21, the clutch drum 23 fixed to the input shaft 12, and the clutch hub 22 and the clutch drum 23. A plurality of friction materials 24 and a clutch piston 25 slidably disposed inside the clutch drum 23, and the friction piston 24 is driven by the hydraulic pressure supplied to the oil chamber 26. Are engaged with each other, the carrier Ca is coupled to the input shaft 12.

  Each gear of the planetary gear mechanism PGSa is composed of a helical gear so as to reduce fluctuations in transmission torque. However, since a thrust force in the axial direction acts on the helical gear due to the meshing reaction force, a thrust bearing is arranged between the relatively rotating members. Is done.

  As the above thrust bearing, a first thrust bearing T1 disposed between the stator shaft 19 and the clutch drum 23, a second thrust bearing T2 disposed between the clutch drum 23 and the clutch hub 22, and a clutch hub. 22, the third thrust bearing T3 disposed between the sun gear Sa of the planetary gear mechanism PGSa, the fourth thrust bearing T4 disposed between the sun gear Sa of the planetary gear mechanism PGSa and the carrier Ca, and the planetary gear mechanism. A fifth thrust bearing T5 is provided between the connecting member 27 connected to the ring gear Ra of the PGSa and a sun gear (not shown) of another adjacent planetary gear mechanism.

  The first brake B1 includes a brake hub (rotating member) 34 integral with the sun gear Sa, a brake drum 31 integral with the transmission case 13, and a plurality of friction materials disposed between the brake hub 34 and the brake drum 31. 33 (the friction plate 33a and the friction disk 33b) and the brake piston 16 disposed so as to be slidable in the axial direction with respect to the transmission case 13, and the brake piston 16 is hydraulically supplied to the oil chamber 17. , And the friction materials are engaged with each other, so that the sun gear Sa is coupled to the transmission case 13.

  FIG. 2 is an enlarged view of a portion X in FIG. 1 and is a diagram for explaining a detailed configuration of the first brake B1. As shown in the figure, the first brake (friction engagement element) B 1 is a substantially cylindrical brake drum 31 formed integrally with the transmission case 13 and a circular ring that engages with the inner periphery of the brake drum 31. A plurality of friction plates (friction materials) 33a, a brake hub 34 having a substantially cylindrical cylindrical portion 35 concentrically arranged with respect to the brake drum 31, and an outer periphery of the cylindrical portion 35. A plurality of friction disks (friction materials) 33b made of circular annular flat plates are provided, and the friction plates 33a and the friction disks 33b (hereinafter, these may be collectively referred to as the friction material 33) in the axial direction. They are arranged in an alternating manner.

  A plurality of splines (grooves) 32 extending in the axial direction are formed on the inner peripheral surface of the brake drum 31 at predetermined intervals in the circumferential direction, and the same number of protrusions as the splines 32 are formed on the outer periphery of the friction plate 33a. A tooth part (fitting part) is formed. Then, the tooth portion of the friction plate 33a is fitted to the spline 32 of the brake drum 31 so as to be slidable in the axial direction but not relatively rotatable.

  A plurality of splines (grooves) 36 extending in the axial direction are formed in the cylindrical portion 35 of the brake hub 34 at predetermined intervals in the circumferential direction, and the same number as the splines 36 is provided on the inner periphery of the friction disk 33b. The protruding tooth portion (fitting portion) is formed. The tooth portion of the friction disk 33b is fitted to the spline 36 of the brake hub 34 so as to be slidable in the axial direction and not to be relatively rotatable.

  FIG. 3 is a diagram showing a cross-section taken along the line YY in FIG. As shown in FIGS. 2 and 3, the splines 36 of the brake hub 34 are arranged on the front side and the back side in the rotation direction R of the cylindrical portion 35 and directed toward the outside (outer diameter side) in the radial direction Z. A pair of protruding side walls (tooth surfaces) 37 and 38 and the end portions 37a and 38a (see FIG. 3) on the outer diameter side of the pair of side walls 37 and 38 are connected to each other, extending in the rotation direction R of the cylindrical portion 35. A bottom wall (tooth base) 39. The pair of side walls 37 and 38 are directions in which their surface directions are inclined with respect to the radial direction Z of the brake hub 34.

  A lubrication hole 40 including a through hole is provided in the side wall 38 on the back side in the rotation direction R of the spline 36. The lubricating hole 40 is provided at a position away from the inner surface 39 a of the bottom wall 39 on the side wall 38 by a predetermined dimension ΔD toward the inner diameter side. That is, the difference between the position (radial position) D1 of the inner surface 39a of the bottom wall 39 and the position (D2) of the outer peripheral edge of the inflow side opening 40a in the lubrication hole 40 is ΔD (= D2−D1). . The lubrication hole 40 extends in a direction in which the direction of the central axis is inclined with respect to the radial direction Z of the cylindrical portion 35. That is, the direction of the central axis of the lubrication hole 40 extends in a direction other than the radial direction Z of the cylindrical portion 35.

  In the first brake B1 configured as described above, the lubricating oil supplied to the inner peripheral surface 35a side of the cylindrical portion 35 of the brake hub 34 from the lubricating oil supply path (not shown) of the input shaft 12 is formed on the spline 36. It is led from the inner peripheral surface 35 a side of the cylindrical portion 35 to the outer peripheral surface 35 b side through the hole 40. The lubricating material 33 can be lubricated by being discharged toward the friction material 33 (the plate 33a and the friction disk 33b).

  At this time, as shown in FIG. 3, a portion of the lubricating oil in the spline 36 is provided by providing the lubricating hole 40 at a position away from the bottom wall 39 of the side wall 38 by a predetermined dimension (ΔD). Only the lubricating hole 40 is introduced. Then, as shown by an arrow L in FIG. 2, excessive lubricating oil (excess lubricating oil not introduced into the lubricating hole 40) flows in the axial direction along the inner surface 39a of the bottom wall 39 of the spline 36, It is discharged to the outside of the first brake B1 from the end portion (the end in the axial direction) of the shaped portion 35.

  As described above, according to the lubrication structure of the first brake (friction engagement device) B1 of the present embodiment, the lubrication hole 40 of the spline 36 provided in the cylindrical portion 35 of the brake hub 34 is formed at the back of the spline 36. By providing the side wall 38 on the side, the flow rate of the lubricating oil discharged from the lubricating hole 40 toward the friction material 33 can be kept low, and it is effective that the friction material 33 is damaged by the impact of the lubricating oil. Can be prevented.

  That is, in the conventional lubrication structure, since the lubrication hole is provided in the bottom wall of the spline, the flow rate of the lubricating oil discharged from the lubrication hole in the bottom wall toward the friction material by the centrifugal force accompanying the rotation of the brake hub and If the flow rate becomes too high, the friction material may be damaged. In contrast, the lubrication hole 40 of the brake hub 34 provided in the first brake B1 of the present embodiment is provided in the side wall 38 of the spline 36, so that the lubrication hole 40 leads to the friction material 33 as compared with the conventional structure. The flow rate and flow rate of the lubricating oil discharged toward the outside can be kept low (less). Therefore, it is possible to optimize the flow rate and flow velocity of the lubricating oil discharged toward the friction material 33 while ensuring the supply amount of the lubricating oil necessary for lubricating the friction material 33.

  Further, the lubricating hole 40 of the brake hub 34 provided in the first brake B1 of the present embodiment is provided at a position away from the inner surface 39a of the bottom wall 39 of the spline 36 by a predetermined dimension ΔD toward the inner diameter side, thereby the bottom wall 39. Only a part of the lubricating oil flowing in the axial direction along the inner surface 39a of the oil can be discharged from the lubricating hole 40 toward the friction material 33. Thereby, since it is possible to effectively prevent the excessive amount of lubricating oil from being discharged, it is possible to effectively prevent the friction material 33 from being damaged by the pressure (momentum) of the discharged lubricating oil.

  Furthermore, according to the lubrication structure of the present embodiment, it is only necessary to change the arrangement and orientation of the lubrication holes 40 as compared with the conventional structure, so that a mechanism such as a valve for adjusting the flow rate of the lubricating oil can be provided, There is no need to form a small-diameter lubricating hole that is troublesome for processing. Therefore, the manufacturing process of the automatic transmission 1 can be simplified and the manufacturing cost can be reduced.

  Further, in the above-described lubricating structure, the pair of side walls 37 and 38 of the spline 36 is a direction in which their surface directions are inclined with respect to the radial direction Z of the cylindrical portion 35. According to this configuration, the lubricating hole 40 of the spline 36 is provided in the side wall 38 that is inclined with respect to the radial direction of the cylindrical portion 35, thereby increasing the momentum of the lubricating oil discharged from the lubricating hole 40 toward the friction material 33. It can be suppressed more effectively.

  Further, since the lubrication hole provided in the bottom wall of the conventional spline is a through hole extending in the radial direction of the cylindrical portion, the lubrication hole in the bottom wall is directed from the lubrication hole of the bottom wall toward the friction material by the centrifugal force. In addition to the high flow velocity and flow rate of the lubricating oil discharged, the lubricating oil is directly discharged toward the friction material. On the other hand, in the lubricating structure of the present embodiment, the lubricating hole 40 provided in the side wall 38 of the spline 36 extends in a direction other than the radial direction Z of the cylindrical portion 35. Thereby, the flow velocity and flow rate of the lubricating oil discharged from the lubricating hole 40 toward the friction material 33 can be kept low, and the lubricating oil can be more effectively discharged directly toward the friction material 33. Can be prevented.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Deformation is possible. For example, in the above embodiment, as an example of the friction engagement device having the lubrication structure according to the present invention, the brake drum 31 facing the brake hub 34 is provided integrally with the transmission case (fixing member) 13. Although the brake is shown, the friction engagement device according to the present invention may be a clutch having a configuration in which both the brake hub 34 and the brake drum 31 are installed in a rotatable state.

DESCRIPTION OF SYMBOLS 1 Automatic transmission 12 Input shaft 13 Transmission case 16 Brake piston 17 Oil chamber 31 Brake drum 33 Friction material 33a Friction plate 33b Friction disk 34 Brake hub (rotating member)
35c Tubular portion 36 Spline 37, 38 Side wall 39 Bottom wall 39a Inner surface 40 Lubrication hole B1 First brake (friction engagement device)
B2 Second brake C1 Clutch PGSa Planetary gear mechanism

Claims (3)

A rotating member having a cylindrical portion rotatably installed around an axis;
A plurality of splines extending in the axial direction formed in the tubular portion and projecting to the outer diameter side of the tubular portion;
A plurality of friction materials laminated along the axial direction,
The frictional member is configured such that the end of the friction material is fitted to the spline so that the friction material can be moved in the axial direction with respect to the cylindrical portion and the movement in the circumferential direction is restricted. In the combined device,
The spline is disposed on the front side and the back side in the rotation direction of the cylindrical portion and protrudes toward the outside in the radial direction, and extends in the rotation direction on the outer diameter side of the pair of side walls. A bottom wall connecting the ends,
A lubrication hole comprising a through hole provided at a position separated from the inner surface of the bottom wall by a predetermined dimension to the inner diameter side of the back side wall;
A configuration in which at least a part of the lubricating oil supplied to the inner peripheral surface side of the cylindrical portion is guided to the outer peripheral surface side of the cylindrical portion through the lubricating holes and discharged toward the friction material. A lubrication structure for a friction engagement device. 2. The lubricating structure for a friction engagement device according to claim 1, wherein the pair of side walls have a surface direction inclined with respect to a radial direction of the cylindrical portion. The lubricating structure for a friction engagement device according to claim 1, wherein the lubricating hole extends in a direction other than a radial direction of the cylindrical portion.

Images