JP2005249126A - Automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an automatic transmission of high degree of freedom in layout without radial enlargement in axially arranging two clutches in series. <P>SOLUTION: In this automatic transmission, a first clutch and a second clutch are axially arranged in series in a state that only the first clutch is radially overlapped to a second planetary gear, and a cylinder chamber of the first clutch and a cylinder chamber of the second clutch are arranged concentrately at one side with respect to the secondary planetary gear as an axial baseline. A piston of the first clutch is accommodated in an area surrounded by a radially-extended part supporting a first clutch drum and a bottom part of the first clutch drum to constitute a first centrifugal cancel chamber, and a piston of the second clutch is mounted at an inner diameter side with respect to the first clutch piston to constitute a second centrifugal cancel chamber. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an automatic transmission that achieves a plurality of shift speeds by fastening / release of a fastening element, and more particularly to arrangement of a clutch.

As a conventional automatic transmission, for example, a technique disclosed in Patent Document 1 is disclosed. In the automatic transmission described in this publication, two reduction rotation input clutches C-1 and C-3 are arranged so as to surround the front and rear and the outer periphery of the reduction planetary gear G1.
Japanese Patent Laid-Open No. 2002-349683 (see page 5, lower left, FIG. 3).

However, when the two clutches C-1 and C-3 are arranged in series in the axial direction as in the above prior art,
1) The clutch hub of the two clutches is provided on the outer peripheral side of the speed reduction planetary gear G1 and expands in the radial direction according to the required performance of the clutch.
2) Since the cylinder chambers, which are the hydraulic servos of the two clutches, are arranged opposite to each other via the reduction planetary gear G1, the oil passage for supplying hydraulic pressure to one cylinder chamber has a reduction planetary gear G1 compared to the other oil passage. It is necessary to lengthen by minutes.
3) When a speed change gear set or the like is configured via another planetary gear and a connecting member, it is surrounded by the piston, so that the degree of freedom in layout is restricted.
4) When the centrifugal cancel chamber is constituted by two clutches, it is necessary to provide the cylinder chamber at a position facing the cylinder chamber via the piston in the axial direction, and a plurality of cylinder chambers and centrifugal cancel chambers are continuously arranged in the axial direction. Longer dimensions.
There was a problem.

  The present invention has been made paying attention to the above problems, and an object thereof is to provide an automatic transmission having a high degree of freedom in layout without expanding in the radial direction when two clutches are arranged in series in the axial direction. .

  In order to achieve the above object, according to the present invention, the first clutch and the second clutch are arranged in series in the axial direction, and only the first clutch is arranged so as to overlap the second planetary gear in the radial direction. The chamber and the cylinder chamber of the second clutch were concentrated on one side with the second planetary gear as the axial reference. Further, the piston of the first clutch is accommodated in a region surrounded by a radially extending portion that supports the first clutch drum and a bottom surface portion of the first clutch drum, and the cylinder chamber of the first clutch and the first clutch A first centrifugal cancel chamber is formed between a first accumulator plate provided on the opposite side in the axial direction via the piston of the first piston and the inner periphery of the first clutch piston, and the piston of the second clutch is used as the first clutch piston. Between the cylinder chamber of the second clutch and the second accumulator plate provided on the side facing the axial direction via the piston of the second clutch and the inner periphery of the second clutch piston. A second centrifugal cancellation chamber was constructed.

  Therefore, by arranging the cylinder chambers in a concentrated manner, it is possible to improve the manageability of the oil passage. In addition, by arranging only one of the fastening elements so as to overlap the planetary gear in the axial direction, it is possible to enlarge the clutch plate and the like on the inner diameter side in order to change the fastening capacity, and to make the radial direction compact. be able to. Also, considering that the centrifugal cancellation chamber is configured in the first clutch and the second clutch, it is necessary to provide the cylinder chamber at a position facing the axial direction, which may cause an increase in the axial direction. One clutch requires a large engagement capacity. In view of these points, securing the fastening capacity by arranging the piston of the first clutch on the outer diameter side, and arranging the piston of the second clutch on the inner diameter side, the first and second centrifugal cancellation chambers have a diameter. It is possible to arrange the offset in the direction, and the axial dimension can be shortened while securing the fastening capacity of the first clutch.

  Hereinafter, the best mode for realizing an automatic transmission according to the present invention will be described based on a first embodiment shown in the drawings.

First, the configuration will be described.
FIG. 1 is a schematic diagram illustrating the overall configuration of the first embodiment. The rotation output from the engine 1 is input to the torque converter 2 via the engine output shaft E1, and the rotation with the increased torque is input to the transmission mechanism via the input shaft Input. The torque converter 2 includes a lock-up clutch mechanism, and when the torque transmission efficiency decreases, the engine output shaft E1 and the input shaft Input are directly connected.

  The speed change mechanism is composed of a first planetary gear G1 and a planetary gear set GS, and outputs rotation input from the input shaft Input from the output gear Output.

  The first planetary gear G1 is a single pinion planetary gear serving as a reduction gear having a first sun gear S1, a first ring gear R1, and a first carrier C1 that supports a first pinion P1 that meshes with both gears S1 and R1. It is.

The planetary gear set GS includes a second planetary gear G2 and a third planetary gear G3.
The second planetary gear G2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier C2 that supports a second pinion P2 that meshes with both the gears S2 and R2.
The third planetary gear G3 includes a third sun gear S3 and a fourth sun gear S4, a third pinion P3 that meshes with each of the third and fourth sun gears S3 and S4, and a third axial pinion that supports the third pinion P3. A double sun gear planetary gear having a carrier C3, a center member CM connected to the third carrier C3 and disposed between the two sun gears S3 and S4, and one third ring gear R3 meshing with the third pinion P3 It is. The center member CM is coupled to the third carrier C3 at a spatial position with a plurality of third pinions P3 adjacent on the circumference of the third carrier PC3.

  The input shaft Input is connected to the first ring gear R1 and inputs the rotational driving force from the engine 1 as a driving source via the torque converter 2.

  The output gear Output is connected to the second carrier C2, and transmits the output rotational driving force to the driving wheels via a final gear or the like not shown.

  The second sun gear S2 and the third sun gear S3 are integrally connected by a first connecting member M1. The second carrier C2 and the third ring gear R3 are integrally connected by a second connecting member M2.

  The low clutch L / C (first clutch described in claims) selectively connects and disconnects the first carrier C1 and the second ring gear R2. The 3-5 reverse clutch 3-5R / C (second clutch described in claims) selectively connects and disconnects the first carrier C1 and the second sun gear S2. A high clutch H / C (third clutch described in claims) selectively connects and disconnects the input shaft Input and the center member CM.

  The low reverse brake L & R / B (first brake described in claims) selectively stops the rotation of the third carrier C3. The 2-6 brake 2-6 / B (second brake described in claims) selectively stops the rotation of the fourth sun gear S4.

  The clutches L / C, 3-5R / C, H / C and brakes L & R / B, 2-6 / B have 6 forward speeds, 1 reverse speeds as shown in the engagement operation table of FIG. A shift hydraulic pressure control device (not shown) that generates a fastening pressure (◯ mark) and a release pressure (no mark) at the gear position is connected. Note that a hydraulic control type, an electronic control type, a hydraulic pressure + electronic control type, and the like are employed as the transmission hydraulic pressure control device.

  FIG. 3 is a collinear diagram showing a rotation stop state of members at each of the sixth forward speed and the reverse first speed in the automatic transmission according to the first embodiment. 1st to 6th speed and 1st reverse speed are achieved according to the fastening operation table shown in FIG.

  FIG. 4 is an enlarged cross-sectional view of the low clutch L / C and the 3-5 reverse clutch 3-5R / C of the first embodiment. The first carrier C1 of the first planetary gear G1 is connected to the rotating shaft 10.

  The rotary shaft 10 includes a first piston support portion 11 (a radially extending portion described in claims) that supports the first piston 30 of the low clutch L / C, and a piston wall support that supports the piston wall 60. The part 12 and the 2nd piston support part 13 which supports the 3-5R / C 2nd piston 40 are provided. A clutch drum 20 is connected to the outer peripheral end 14 of the rotary shaft 10.

  The clutch drum 20 has a first spline portion 21 that is spline-fitted with the drive-side clutch plate of the low clutch L / C, and a second spline-fitted with the drive-side clutch plate of the 3-5 reverse clutch 3-5R / C. A spline portion 22 is provided. A first cylinder chamber 35 for low clutch L / C is provided at the bottom of the clutch drum 20 adjacent to the output gear Output. A first centrifugal cancellation chamber 36 defined by a first accumulation plate 36 a and an inner periphery of the first piston 30 is provided on the side facing the first cylinder chamber 35 via the first piston 30.

  The first piston 30 is provided with a skewer-shaped arm portion 31 and a pressing portion 32 that presses the low clutch L / C at the tip of the arm portion 31. Here, the drive-side clutch plate of the 3-5 reverse clutch 3-5R / C is provided with a communication hole in a portion that is not spline-fitted with the clutch drum 20, and a skewered arm portion is formed in the communication hole. 31 is inserted. As a result, the stroke of the first piston 30 is transmitted to the low clutch L / C through the clutch plate of the 3-5 reverse clutch 3-5R / C.

  A first clutch hub 33 is provided on the outer periphery of the second ring gear R2 for spline fitting with the drive side clutch plate of the low clutch L / C. The first clutch hub 33 is supported by a first support portion 34 extending in the radial direction. The first support portion 34 is sandwiched between the second carrier C2 and the second clutch hub 42 (radially extending portion 42a) via a thrust bearing so as to be relatively rotatable.

  Between the piston wall 60 and the second piston 40, a second cylinder chamber 45 for the 3-5 reverse clutch 3-5R / C is provided. A second centrifugal cancel chamber 46 defined by the second accumulator plate 46 a and the inner periphery of the second piston 40 is provided on the side facing the second cylinder chamber 45 via the second piston 40.

  The second clutch hub 42 is provided with a radially extending portion 42a connected to the first connecting member M1, and a hub portion 42b that is spline-fitted with the drive side clutch plate of the 3-5 reverse clutch 3-5R / C. It has been. The hub portion 42 b is provided on the radially outer side of the second centrifugal cancel chamber 46 and on the radially inner side of the first clutch hub 33.

  Next, features in the arrangement of the low clutch L / C and the 3-5 reverse clutch 3-5R / C based on the above configuration will be described.

  1) The first cylinder chamber 35 for the low clutch L / C and the second cylinder chamber 45 for the 3-5 reverse clutch 3-5R / C are moved to the right in the figure with the second planetary gear G2 as the axial reference. It is concentrated. Thereby, the manageability of the oil path to the first cylinder chamber 35 and the second cylinder chamber 45 can be improved. In addition, when only the low clutch L / C is arranged so as to overlap the second planetary gear G2 in the axial direction, when changing the fastening capacity of the 3-5 reverse clutch 3-5R / C, a clutch plate is installed on the inner diameter side. It becomes possible to enlarge, and the radial compactization can be achieved. Considering that the centrifugal cancellation chamber is formed in the low clutch L / C and the 3-5 reverse clutch 3-5R / C, the first cylinder chamber 35 and the second cylinder 40 are connected via the first piston 30 and the second piston 40, respectively. It is necessary to provide the cylinder chamber 45 at a position facing the cylinder chamber 45 in the axial direction. Therefore, a plurality of hydraulic chambers are arranged in the axial direction, which may increase the axial direction. The low clutch L / C requires a large engagement capacity. In view of these points, the first piston 35 of the low clutch L / C is disposed on the outer diameter side to secure the fastening capacity, and the second piston 45 of the 3-5 reverse clutch 3-5R / C is disposed on the inner diameter side. By arranging, the first centrifugal cancellation chamber 36 and the second centrifugal cancellation chamber 46 can be arranged offset in the radial direction, and the axial dimension can be shortened while securing the fastening capacity of the low clutch L / C. (Corresponding to claim 1).

  2) When the low clutch L / C and the 3-5 reverse clutch 3-5R / C are arranged in series in the axial direction, as described in 1), the cylinder chambers 35 and 45 are arranged on one side, and the first The piston stroke directions of the second pistons 30 and 40 are the same.

  Therefore, one side of the two clutches can be released, and the degree of layout freedom can be improved. Specifically, a planetary gear constituting the planetary gear set GS having the first connecting member M1 and the second connecting member M2 as in the second planetary gear G2 can be arranged (corresponding to claim 2).

  3) A low clutch L / C is arranged on the outer diameter side of the second planetary gear G2, and a 3-5 reverse clutch 3-5R / C is arranged at a position offset to the second planetary gear G2 and the axial cylinder chamber side. ing. The outer diameter of the clutch drum 20 is the same in the outer circumference of the low clutch L / C and the 3-5 reverse clutch 3-5R / C. Further, the first cylinder chamber 35 for the low clutch L / C is disposed on the outer diameter side with respect to the second cylinder chamber 45 for the 3-5 reverse clutch 3-5R / C.

  That is, since the low clutch L / C is a starting element, a large torque is applied. Therefore, in order to ensure the area (capacity) of the first cylinder chamber 35, the first cylinder chamber 35 is disposed on the outer diameter side. On the other hand, the second cylinder chamber 45 for the 3-5 reverse clutch 3-5R / C is arranged on the inner diameter side, but no planetary gear or the like is arranged on the inner diameter side like the low clutch L / C. Therefore, the clutch plate is enlarged in the inner diameter direction, thereby securing the fastening capacity. At this time, by enlarging the clutch plate in the inner diameter direction, there is no need to expand in the outer diameter direction in order to secure the fastening capacity. That is, the outer diameter of the clutch drum 20 can be set to the same diameter on the outer periphery of the low clutch L / C and the 3-5 reverse clutch 3-5R / C, and the radial expansion can be prevented ( (Corresponding to claim 3).

  As mentioned above, although the automatic transmission of this invention has been demonstrated based on Example 1, it is not restricted to these Examples about concrete structure, The summary of the invention which concerns on each claim of a claim As long as they do not deviate, design changes and additions are permitted.

1 is a schematic diagram illustrating an overall configuration of an automatic transmission according to a first embodiment. 2 is an engagement operation table at each gear stage of the automatic transmission according to the first embodiment. FIG. 3 is a collinear diagram at each shift speed of the automatic transmission according to the first embodiment. It is an expanded sectional view showing the low clutch and 3-5 reverse clutch part of Example 1.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Engine 2 Torque converter 10 Rotating shaft 11 1st piston support part 12 Piston wall support part 13 2nd piston support part 14 Outer peripheral side edge part 20 Clutch drum 21 1st spline part 22 2nd spline part 30 1st piston 31 Arm part 32 pressing portion 33 first clutch hub 34 first support portion 35 first cylinder chamber 36 first centrifugal cancel chamber 40 second piston 41 pressing portion 42 second clutch hub 42a radially extending portion 42b hub portion 45 second cylinder chamber 46 Second centrifugal cancellation chamber

Claims (3)

An input unit for inputting rotation from a driving source;
An output unit for outputting the rotated rotation;
Three sets of planetary gears,
A plurality of members integrally connecting the plurality of rotating elements;
An input unit, an output unit, a member, and three clutches arranged between the rotating elements of the planetary gear, each having three clutches selectively connected and disconnected and two brakes selectively fixed,
One set of the three planetary gears is a first planetary gear having a first sun gear, a first ring gear, and a first carrier that supports a pinion meshing with both gears,
One set of the three planetary gears is a second sun gear, a second ring gear, and a single pinion type planetary gear having a second carrier that supports a pinion that meshes with both gears as a second planetary gear,
One set of the three planetary gears includes a third and fourth sun gear, a pinion that meshes with each of the two sun gears, and a center member that is disposed between the two sun gears and that inputs or outputs rotation. A double sun gear type planetary gear having a third carrier having a third ring gear meshing with the pinion gear is defined as a third planetary gear;
An input connected to the first ring gear;
An output connected to the second carrier;
A first connecting member that integrally connects the second sun gear and the third sun gear;
A second connecting member that integrally connects the second carrier and the third ring gear;
A first clutch that selectively connects and disconnects the first carrier and the second ring gear;
A second clutch for selectively connecting and disconnecting the first carrier and the first connecting member;
A third clutch that selectively connects and disconnects the third carrier and the input unit;
A first brake for selectively stopping rotation of the third carrier;
A second brake for selectively stopping the rotation of the fourth sun gear;
With
The first clutch and the second clutch are arranged in series in the axial direction,
Only the first clutch is disposed so as to overlap the second planetary gear in the radial direction,
The cylinder chamber of the first clutch and the cylinder chamber of the second clutch are concentrated on one side with the second planetary gear as an axial reference,
The piston of the first clutch is housed in a region surrounded by a radially extending portion that supports the first clutch drum and a bottom surface portion of the first clutch drum, and the cylinder chamber of the first clutch and the first clutch Forming a first centrifugal cancel chamber between a first accumulator plate provided on the side facing the axial direction via a piston of one clutch and an inner periphery of the first clutch piston;
The piston of the second clutch is arranged on the inner diameter side with respect to the first clutch piston, and is provided on the side facing the axial direction through the cylinder chamber of the second clutch and the piston of the second clutch. An automatic transmission characterized in that a second centrifugal cancel chamber is formed between a two accumulation plate and an inner periphery of the second clutch piston. The automatic transmission according to claim 1, wherein
The pistons of the first clutch and the piston of the second clutch have the same stroke direction from the cylinder chamber of the first clutch and the cylinder chamber of the second clutch toward the second planetary gear. transmission. The automatic transmission according to claim 1 or 2,
The first clutch and the second clutch have a common clutch drum,
2. The automatic transmission according to claim 1, wherein the outer diameter of the clutch drum is the same on the outer periphery of the first and second clutches.

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