JP2007032636A - Drum clutch for automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To secure strength of a centrifugal cancel plate without causing deterioration of fuel consumption in regard to a drum clutch with an outermost diameter position of a centrifugal cancel chamber provided in an outer side than an outermost diameter position of a cylinder chamber of a clutch piston. <P>SOLUTION: The drum clutch for an automatic transmission is provided with the clutch piston 130 slidably held in an inner side of a drum 120 and forming a cylinder chamber R1 with a bottom 121, and the centrifugal cancel plate 140 comprised by forming a recessed part on the piston, and forming the centrifugal cancel chamber R2 with an outermost diameter in an outer side than the outermost diameter position of the cylinder chamber R1, in an inner side of the recessed part. A plurality of concentrically arranged springs 151 with one ends seated in a back face of a first pressure receiving face, and an annular spring retainer 15 with its back face joined to the cancel plate are provided between the piston and the cancel plate. Through holes 1, 2 arranged in a caulking hole 3 formed by punching of the retainer, and communicating the centrifugal cancel chamber R2 with an exterior of the centrifugal cancel chamber are formed in the cancel plate. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a drum clutch of an automatic transmission.

In the conventional drum clutch, a clutch piston is arranged inside the clutch drum to form a cylinder chamber, while a concave portion is formed on the back surface of the clutch piston and a centrifugal cancel plate is arranged inside the concave portion. There is a chamber in which a centrifugal cancel chamber having an outermost diameter position outside the outermost diameter position of the chamber is formed (see, for example, Patent Document 1).
JP-A-2-96072

  According to such a configuration, in order to reduce the ratio of the cylinder chamber in the radial direction of the drum clutch, the cylinder chamber is laid out so as to be axially overlapped radially inward of the pressing portion of the clutch piston, thereby reducing the axial dimension. It is going to become. In the drum clutch disclosed in the above-mentioned document 1 (hereinafter referred to as “conventional clutch A”), the outer surface of the clutch hub, which is directly coupled / disconnected via a friction element, faces the inner surface of the cylindrical portion of the clutch drum. As a result, since the centrifugal cancel plate is provided on the inner diameter side of the clutch hub, there is no restriction on the outer diameter and the diameter can be made relatively large.

  In addition, the conventional clutch A is provided with a notch groove on the inner diameter side of the centrifugal cancel plate, and drains hydraulic oil in the centrifugal cancel chamber from the notch groove, thereby reducing the effective diameter of the centrifugal cancel chamber without reducing it. This makes it possible to discharge centrifugal cancellation oil.

  However, in the conventional clutch A, a large centrifugal force acts on the centrifugal cancel plate and the stress is notched into the groove when the rotary member is a high-rotation member or is used frequently in a high-rotation region. Therefore, there is a problem that it is difficult to secure the strength against the centrifugal cancel plate.

  On the other hand, based on the conventional clutch A, instead of notching the inner diameter side of the centrifugal cancel plate, it can be considered to simply provide a discharge hole. A recess for holding the oil and an overhang for preventing the spring from falling are formed, and it is very difficult to avoid these and form a discharge hole that does not hinder the oil discharge function. .

In addition, as another conventional clutch, there is an clutch in which an oil passage is formed in a rotating shaft fixed to the inner diameter side of the centrifugal cancel plate, and a groove is provided on the back surface of the centrifugal cancel plate so as to communicate with the oil passage (for example, , See Patent Document 2.)
JP 2001-41261 A

  According to the drum clutch disclosed in the above-mentioned document 2 (hereinafter referred to as “conventional clutch B”), the rotating member is a high-rotating member, or even when used frequently in a high-rotation region. The strength against the cancel plate can be ensured.

  However, in the conventional clutch B, since the outermost diameter position of the centrifugal cancellation chamber is outside the outermost diameter position of the cylinder chamber, the centrifugal hydraulic pressure acting on the centrifugal cancellation chamber is more than the centrifugal hydraulic pressure acting on the cylinder chamber. Always excessive. For this reason, it is effective because the excessive centrifugal hydraulic pressure does not increase so much under the usage situation where the rotating member of the conventional clutch B has a low rotation or is frequently used in the low rotation region. If it is used for a clutch that is rotating or used frequently in a high rotation range, the excessive centrifugal hydraulic pressure becomes very excessive, so it is necessary to apply a large hydraulic pressure as the hydraulic fluid for the clutch. As a result, friction increases and fuel consumption deteriorates.

  That is, when the structure of the conventional clutch B is adopted for a clutch whose rotating member is a high rotating member or used frequently in a high rotating region, the outermost diameter position of the cylinder chamber that actually operates the clutch piston is centrifugal. Since it is inside the outermost diameter position of the cancellation chamber, a new problem of causing deterioration in fuel consumption occurs.

  The present invention has been made on the basis of the above fact recognition, and the problem to be solved is a drum clutch having a built-in centrifugal cancel chamber, and in particular, the outermost diameter position of the centrifugal cancel chamber is the clutch piston. With respect to the drum clutch outside the outermost diameter position of the cylinder chamber, the strength of the centrifugal cancel plate is ensured without causing deterioration of fuel consumption.

  The invention according to claim 1 has a bottom portion and a cylindrical portion extending in the axial direction from the bottom portion, and includes a clutch drum connected to the rotating member, and an outer surface disposed to face the inner side surface of the cylindrical portion of the clutch drum. A clutch hub connected to another rotating member, a friction element disposed between the outer surface of the clutch hub and the inner surface of the cylindrical portion of the clutch drum, and slidably disposed on the inner side of the clutch drum. A clutch piston that forms a cylinder chamber with the bottom of the clutch drum, and an axially opposite side of the bottom of the cylinder chamber between the clutch piston and an outermost diameter position of the cylinder chamber Are arranged between the centrifugal cancel plate and the clutch piston, and one end side is the front side. An automatic transmission comprising a plurality of return springs that abut against the clutch piston, the other end is seated on a seat provided on the centrifugal cancel plate, and biases the clutch piston toward the cylinder chamber. In the drum clutch, the seat portion has a through hole that communicates the inside and the outside of the centrifugal cancel chamber at a position corresponding to the axial center of the return spring, and the oil in the centrifugal cancel chamber is communicated from the through hole. Is characterized in that it is discharged to the outside.

    According to a second aspect of the present invention, in the first aspect, the seat portion punches out a portion corresponding to the center of the return spring, integrally caulks the other end of the return spring, and a back surface thereof contacts the centrifugal cancel plate. And the through hole is composed of the caulking hole and a long hole extending in a radial direction so as to overlap with at least one of the caulking holes. .

  According to a first aspect of the present invention, in the drum clutch of the automatic transmission in which the outermost diameter position of the centrifugal cancel chamber is provided outside the outermost diameter position of the cylinder chamber and the axial dimension is shortened, the centrifugal cancel chamber is When the oil is discharged to the outside, a through hole is provided at a position corresponding to the axial center of the plurality of return springs in the seat portion of the centrifugal cancel plate.

  According to such a configuration, since the structure for escaping oil in the centrifugal cancel chamber is not a notch groove but a through hole, stress concentration is smaller than that of the notch groove, so that the strength of the centrifugal cancel plate is easily secured and durable. Will improve. In addition, the invention according to claim 1 is configured to discharge the oil in the centrifugal cancel chamber from the existing caulking hole formed in the spring retainer through the through hole provided in the centrifugal cancel plate. In addition, there is no need to form a hole avoiding a concave portion for holding the snap ring and an overhanging portion for preventing the spring from collapsing, and the hole can be formed relatively easily.

  In addition, according to the invention of claim 1, the centrifugal oil pressure acting on the centrifugal cancellation chamber is high even when the clutch drum and the clutch hub are at a high rotation speed or are used frequently in a high rotation area. Since the hydraulic pressure does not exceed the centrifugal hydraulic pressure acting on the cylinder chamber, it is not necessary to apply a large hydraulic pressure as the hydraulic fluid for the clutch, and the fuel consumption is not deteriorated.

  Therefore, according to the first aspect of the present invention, the degree of freedom in forming the oil passage that allows the centrifugal cancellation chamber to communicate with the outside without securing a large design change or deterioration in fuel consumption is ensured, and the centrifugal cancellation is performed. The strength of the plate can be improved.

  According to the invention described in claim 2, a caulking hole is formed when a plurality of coil springs are caulked together in a spring retainer in which the seat portion is configured separately from the centrifugal cancel plate. In view of the above, it is preferable that the through hole according to the present invention is composed of the caulking hole and a long hole extending in the radial direction so as to overlap at least one of the caulking holes. In this case, when the spring retainer and the centrifugal cancel plate are combined, it is not necessary to align the caulking hole and the through hole. Therefore, it is possible to provide a highly productive clutch excellent in assembling workability.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is an enlarged cross-sectional view showing the upper half of the drum clutch 100 of the automatic transmission according to the first embodiment of the present invention from the side. FIGS. 2 (a) and 2 (b) are a rear view and a sectional view taken along line XX, respectively, showing a later-described centrifugal cancel plate 140 according to the present invention.

  In FIG. 1, reference numeral 10 denotes a first rotating shaft (rotating member) integrally provided with the sun gear S of the planetary gear mechanism G, and in this embodiment forms an input rotating element. The first rotary shaft 10 is a hollow shaft, and holds a second rotary shaft 20 constituting an output rotary element in a relatively rotatable manner.

  Reference numeral 110 denotes a hollow connecting plate whose inner periphery is welded to one end 11 of the first rotary shaft 10. Reference numeral 111 denotes a clutch hub fixed to the outer edge of the connecting plate 110. A spline is formed on the outer surface of the clutch hub 111, and a plurality of drive plates (friction elements) C1 that are slidably held along the axis O of the clutch drum 100 are provided on the spline. In this embodiment, the clutch hub 111 is configured separately from the connecting plate 110, but may be configured integrally.

  Reference numeral 120 denotes a clutch drum whose inner peripheral portion is welded to one end 21 of the second rotary shaft 20. The clutch drum 120 has a bottom portion 121 whose inner peripheral portion is welded to the shaft end portion 21, and an annular peripheral wall 122 that surrounds the shaft end portion 21 is integrally formed inside the clutch drum 120. Further, the bottom portion 121 is formed integrally with a cylindrical portion 123 that is folded back along the rotating shaft 220 (axis O) to surround the drum peripheral wall 122 and has a seal ring 24 on the outer peripheral surface thereof. The inner surface of the drum cylindrical portion 123 is disposed opposite to the outer surface of the clutch hub 110, and further, a spline is formed on the inner surface, and is slidably held along the axis O on the spline. A plurality of driven plates (friction elements) C2 are provided alternately with the drive plate C1.

  Reference numeral 130 denotes a clutch piston that forms a cylinder chamber R1 with the clutch drum 120 and slides in the clutch drum 120 by the pressure (clutch pressure) of hydraulic oil charged and discharged into the cylinder chamber R1. .

  The clutch piston 130 includes a cylindrical inner sliding portion 131 that is slidably held on the seal ring 24 on the outer surface of the second rotary shaft end portion 21, and a drum that is integrally connected to the piston inner sliding portion 131. A first pressure receiving portion 132 disposed to face the inner surface of the bottom portion 121, a second pressure receiving portion 133 that is integrally connected to the first pressure receiving surface 132 and can come into contact with the top portion of the drum peripheral wall 122, and the second pressure receiving portion 133. And an outer sliding portion 134 slidably held on the seal ring 124 of the drum peripheral wall 122. As a result, a cylinder chamber R1 is formed between the clutch drum 120 and the clutch piston 130. The cylinder chamber R1 is filled and discharged from the oil passage 22 provided at the shaft end 21. The outermost diameter position r1 of the cylinder chamber R1 from the axis O is the inner peripheral surface position of the outer sliding portion 134.

  The piston outer sliding portion 134 is integrally connected with a pressing portion 135 that extends along a radial axis perpendicular to the axis O and bends toward the driven plate C2. When the pressing portion 135 presses the driven plate C2, the drive plate C1 and the driven plate C2 that are separated from each other and in the released state are fastened. In this way, the axial dimension is shortened by arranging the cylinder chamber R1 so as to overlap in the radial direction inside the pressing portion 135 of the clutch piston 130 in the axial direction.

  In addition, an annular peripheral wall 136 surrounding the shaft end portion 21 is integrally connected to the back surface of the piston outer sliding portion 134. Reference numeral 140 denotes a centrifugal cancel plate that is slidably held with respect to the clutch piston 130 by an annular recess defined by the outer surface of the second rotary shaft end 21 and the inner surface of the piston rear peripheral wall 136. . The centrifugal cancel plate 140 has a rib 141 integrally protruding from the side surface to the other side in the axial direction, and the rib 141 restricts the radial expansion of the snap ring S1, thereby restricting the movement to the other side in the axial direction. . Further, the centrifugal cancel plate 140 includes a seal ring 142 at an outer edge portion thereof, and on the side facing the cylinder chamber R1, no oil pressure is applied from an oil passage 23 provided in the shaft end portion 21, for example, lubricating oil. Centrifugal cancellation chamber R2 to be filled and discharged is formed. The outermost diameter position r2 of the centrifugal cancel chamber R2 from the axis O is the position of the inner peripheral surface of the peripheral wall 136 and is on the outer diameter side of the cylinder chamber R1.

  A spring retainer assembly 150 is assembled in the centrifugal cancel chamber R2. The spring retainer assembly 150 is coaxially disposed around the axis O of the first pressure receiving portion 132 of the clutch piston 130, and includes a plurality of return springs 151 that urge the clutch piston to one side, and a portion corresponding to the center of the return spring 151 And the return spring 151 is caulked together to be fixed and held, and an annular spring retainer 152 constituting a seat portion of the centrifugal cancel plate 140 is formed.

  For this reason, the spring retainer assembly 150 is configured such that one end of the return spring 151 is seated on the inner bottom surface of the recess provided on the back surface of the clutch piston 130, that is, the back surface of the first pressure receiving portion 132, while the back surface of the spring retainer 152 is One side surface of the cancel plate 140 is brought into contact with, and the axial movement is restricted by the snap ring S1 through the centrifugal cancel plate 140.

  Thus, the drum clutch 100 supplies the hydraulic oil through the passage 22 into the cylinder chamber R1 while operating the clutch piston 130 toward the driven plate C2 in order to fasten the drive plate C1 and the driven plate C2. If oil is also supplied into the cancel chamber R2 through the passage 23, the centrifugal hydraulic pressure generated in the cylinder chamber R1 due to the rotation of the clutch drum 120 can be offset or reduced by the centrifugal hydraulic pressure generated in the centrifugal cancel chamber R2.

  However, when the outermost diameter position of the centrifugal cancel chamber R2 is on the outer diameter side of the outermost diameter position of the cylinder chamber R1 as in this embodiment, the centrifugal hydraulic pressure generated in the centrifugal cancel chamber R2 becomes excessive, The clutch engagement pressure generated in the cylinder chamber R1 required for the engagement operation of the clutch piston 130 may be affected, and the responsiveness may deteriorate.

  Therefore, in this embodiment, paying attention to the fact that the caulking hole 1 is formed in the spring retainer 152 when the plurality of coil springs 151 are integrally caulked by punching, the oil in the centrifugal cancel chamber R2 is discharged, and the centrifugal cancel plate A long hole 2 is connected to the 140 caulking hole 1 in a radial direction corresponding to the axial center Os of the coil spring 151 to allow the inside of the centrifugal cancel chamber R2 to communicate with the outside (outside of the centrifugal cancel chamber R2). Provide. The caulking hole 1 and the long hole 2 constitute the through hole of the present invention.

  According to such a configuration, since the structure for releasing the centrifugal cancel oil in the centrifugal cancel chamber R2 is not the conventional notch groove but the long hole 2 aligned with the caulking hole 1, the stress concentration is smaller than that of the notch groove. Therefore, it is easy to secure the strength of the centrifugal cancel plate 140. In addition, in this embodiment, the oil in the centrifugal cancel chamber R2 is discharged from the existing caulking hole 1 formed in the spring retainer 152 through the long hole 2 provided in the centrifugal cancel plate 140. Only 140 is required, and the entire drum clutch 100 need not be redesigned. In addition, it is not necessary to form a through hole in a narrow area on the inner peripheral side of the centrifugal cancel plate 140 and avoiding a rib 141 for holding the snap ring, a protruding portion for preventing the spring from falling, It can be formed relatively easily.

  In addition, according to the present embodiment, the centrifugal hydraulic pressure acting on the centrifugal cancel chamber R2 is high even when the clutch drum 120 and the clutch hub 111 are at a high rotation speed or are used frequently in a high rotation area. Since the hydraulic pressure does not always exceed the centrifugal hydraulic pressure acting on the cylinder chamber R1, it is not necessary to apply a large hydraulic pressure as the hydraulic oil for the drum clutch 100, and the fuel consumption is not deteriorated.

  Therefore, according to the present embodiment, the degree of freedom in forming the oil passage that allows the centrifugal cancel chamber R2 to communicate with the outside world is ensured and the strength of the centrifugal cancel plate 140 is increased without causing major design changes or fuel consumption deterioration. Improvements can be made.

  Here, an outline of a general assembly sequence for the clutch drum will be described with reference to the present embodiment.

  (Working Step 1) The clutch piston 130 is inserted inside the clutch drum 120, and the clutch piston 130 is slidably fitted to the drum peripheral wall 122.

  (Working process 2) The spring retainer assembly 150 is assembled in a recess provided on the back surface of the clutch piston 130. On the back surface of the first pressure receiving portion 132, seat portions (not shown) for seating the return springs 151 are formed.

  (Working process 3) The centrifugal cancel plate 140 is inserted into the recess of the clutch piston while compressing the spring retainer assembly 150. In this case, the spring retainer assembly 150 must be assembled while being aligned so that the return spring 151 is seated on the seat.

  (Working Step 4) The snap ring S1 is fitted into a groove provided on the outer peripheral surface of the second rotary shaft 20, and the movement in the axis O direction with respect to the centrifugal cancel plate 140 is restricted.

  However, in the drum clutch provided with the long hole 2, the work hole 3 must be assembled while being aligned so that the long hole 2 is aligned with the caulking hole 1 formed in the spring retainer 152. There is room for improvement in terms of workability.

  Therefore, in the present embodiment, as shown in FIG. 2, the long hole 2 is a combination of the caulking holes 1 formed in the spring retainer 152 in a state where the centrifugal cancel plate 140 and the spring retainer assembly 150 are combined. The elongated hole extends around the axis O so as to overlap at least one.

  FIGS. 3A to 3C are rear views showing a state in which the spring retainer assembly 150 and the centrifugal cancel plate 140 are aligned at different phases θ in this embodiment. In FIG. 3, the phase θ is positive in the counterclockwise direction in the drawing, (a) shows the phase θ = 0, (b) shows the phase θ> 0, and (c) shows the phase θ <0.

  When the spring retainer assembly 150 is formed, the return springs 151 are caulked to the spring retainer 152 at the same pitch P1. Therefore, the long holes 2 provided in the centrifugal cancel plate 140 are formed so as to have a width L1 wider than the pitch P1. According to such a configuration, even if the spring retainer assembly 150 and the centrifugal cancel plate 140 are aligned without being aligned, at least one of the caulking holes 1 is always aligned with the long hole 2 as shown in FIG. Thus, the centrifugal cancel chamber R2 can be communicated with the outside world.

  In this case, when the spring retainer assembly 150 and the centrifugal cancel plate 140 are aligned, there is no need to align the caulking hole 1 and the long hole 2, thereby providing a highly productive clutch with excellent assembly workability. be able to.

  Since the long holes 2 need only be aligned with at least one caulking hole 1, the number of the long holes 2 may be at least one. Further, the width L1 of the long holes 2 should be wider than at least the pitch P1.

  FIG. 4 is a cross-sectional view of a main part showing a drum clutch 200 of the automatic transmission according to the second embodiment of the present invention from the side. In the present embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals and the description thereof is omitted.

  In this embodiment, the centrifugal cancel plate 140 is punched and each return spring 151 is directly caulked. That is, in this embodiment, the caulking portion of the centrifugal cancel plate 140 forms the seat portion 143 as it is, and only the long hole 2 forms a through hole that discharges the oil in the centrifugal cancel chamber to the outside. Therefore, according to this embodiment, the same effect as that of the first embodiment can be achieved with a small number of parts without using the spring retainer 152.

  Each form mentioned above is only what illustrates the drum clutch of this invention, and can add a various change in a claim. In the present invention, when the outermost diameter position of the centrifugal cancel chamber R2 is outside the outermost diameter position of the cylinder chamber R1, the centrifugal oil pressure in the centrifugal cancel chamber becomes excessive, and therefore the effective diameter of the centrifugal cancel chamber is large. It goes without saying that even if the (outermost diameter position—position where it communicates with the outside world) is reduced, the function necessary for canceling the centrifugal hydraulic pressure in the cylinder chamber can be secured.

  The drum clutch according to the present invention can be employed in an automatic transmission included in a power transmission device for vehicles, ships, and other general machines.

It is an expanded sectional view showing the upper half of the drum clutch of the automatic transmission which is the 1st form of the present invention from the side. (a), (b) is the rear view which shows the below-mentioned centrifugal cancellation plate based on this invention, and its XX sectional drawing, respectively. (a)-(c) is a rear view which respectively shows the state which match | combined the spring retainer assembly and the centrifugal cancellation plate by different phase (theta) in this form. It is principal part sectional drawing which shows the drum clutch 200 of the automatic transmission which is a 2nd form of this invention from the side.

Explanation of symbols

1 Caulking hole (through hole)
2 Long hole (through hole)
10 First rotating shaft (rotating member)
20 Second rotating shaft (other rotating member)
100 clutch drum
110 connecting plates
111 Clutch hub
120 clutch drum
121 Bottom
122 Drum wall
123 Drum cylinder
130 clutch piston
140 Centrifugal cancel plate
150 Spring retainer assembly
151 Return spring
152 Spring retainer (centrifugal cancel plate seat)

Claims (2)

A clutch drum having a bottom portion and a cylindrical portion extending in the axial direction from the bottom portion and coupled to the rotating member;
A clutch hub having an outer surface opposed to the inner surface of the cylindrical portion of the clutch drum and connected to another rotating member;
A friction element disposed between the outer surface of the clutch hub and the inner surface of the cylindrical portion of the clutch drum;
A clutch piston which is slidably disposed inside the clutch drum and forms a cylinder chamber with the bottom of the clutch drum;
A centrifugal cancel plate that forms a centrifugal cancel chamber between the clutch piston and the bottom of the cylinder chamber opposite to the axial direction and having an outermost diameter position outside the outermost diameter position of the cylinder chamber;
Arranged between the centrifugal cancel plate and the clutch piston, one end side is in contact with the clutch piston, the other end is seated on a seat provided on the centrifugal cancel plate, and the clutch piston is disposed in the cylinder chamber direction. A plurality of return springs that bias
In a drum clutch of an automatic transmission equipped with
The seat has a through hole that communicates the inside and the outside of the centrifugal cancel chamber at a position corresponding to the axial center of the return spring, and the oil in the centrifugal cancel chamber is discharged to the outside from the through hole. What I did,
A drum clutch of an automatic transmission characterized by The seat portion is provided with an annular spring retainer that punches out a portion corresponding to the center of the return spring and caulks the other end of the return spring integrally, and a back surface of the return spring is in contact with the centrifugal cancel plate.
2. The drum of an automatic transmission according to claim 1, wherein the through hole includes the caulking hole and a long hole extending in a radial direction so as to overlap at least one of the caulking holes. clutch.

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