JP3801786B2 - Gear transmission mechanism of automatic transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a gear transmission mechanism of an automatic transmission, and more particularly to a gear transmission mechanism that enables shortening of a control valve that controls the shift of the mechanism.
[0002]
[Prior art]
An automatic transmission usually includes a plurality of planetary gear sets, and a transmission path (speed stage) between the input and output shafts passing through the planetary gear sets is switched by selectively operating a plurality of multi-plate hydraulic clutches and multi-plate hydraulic brakes. It is normal to configure as follows.
[0003]
Then, the multi-plate hydraulic clutch and the multi-plate hydraulic brake are selectively operated by being supplied with operating hydraulic pressure from a control valve.
By the way, the supply of working hydraulic pressure to the working piston of the multi-plate hydraulic brake can be performed from anywhere including the outer peripheral portion of the transmission case, but the multi-plate hydraulic clutch itself rotates as a whole, The hydraulic pressure is supplied to the clutch operating piston from its inner periphery.
[0004]
Therefore, except for the multi-plate hydraulic clutch that can be installed adjacent to the end wall of the transmission case, the other multi-plate hydraulic clutch has a clutch operating piston fitted on the clutch support that is installed horizontally in the transmission case. It is customary to provide it.
[0005]
[Problems to be solved by the invention]
By the way, a so-called front engine / rear wheel drive vehicle (FR vehicle) in which the input / output shafts are arranged in a coaxial butting relationship with each other, and a plurality of planetary gear sets are arranged sequentially from the input shaft side to the output shaft side. In the automatic transmission for
Since the planetary gear set is often arranged in front of the input shaft, the operating piston of the multi-plate hydraulic clutch is often arranged relatively behind the automatic transmission, so the clutch support is also compared with the automatic transmission. Many are installed behind the target.
[0006]
Therefore, the hydraulic pressure is supplied to the clutch operating piston fitted on the clutch support by guiding the operating hydraulic pressure from the control valve to the inner periphery of the clutch operating piston through the radial hole formed in the clutch support. Therefore, the control valve needs to extend to the clutch support in the transmission axial direction.
For this reason, in the case of the conventional general automatic transmission in which the clutch support is located relatively behind the automatic transmission, there has been a problem that the control valve tends to be long in the transmission axial direction.
[0007]
The first aspect of the present invention is to propose a gear transmission mechanism of an automatic transmission capable of shortening the control valve in the transmission axial direction.
[0008]
The second aspect of the present invention is to propose an automatic transmission which is advantageous in terms of cost by reducing the number of parts of the gear transmission mechanism.
[0009]
The third aspect of the present invention is to propose a simpler and more reliable positioning structure of the clutch support for the transmission case using the snap ring.
[0010]
The fourth aspect of the present invention is to propose a gear transmission mechanism for an automatic transmission that can reliably prevent the snap ring from coming off in the third aspect of the invention.
[0011]
The fifth aspect of the present invention is to propose a gear transmission mechanism for an automatic transmission that realizes a shortened structure and increased strength at the rearmost end portion.
[0012]
[Means for Solving the Problems]
For these purposes, first, the gear transmission mechanism of the automatic transmission according to the first invention is:
A plurality of planetary gear sets are coaxially arranged from the input shaft side to the output shaft side provided in abutment thereto, and include a plurality of multi-plate hydraulic clutches and a multi-plate hydraulic brake that respond to the hydraulic pressure supplied from the control valve, In the automatic transmission configured to switch the transmission path between the input / output shafts via the planetary gear set by selectively operating a plurality of multi-plate hydraulic clutches and multi-plate hydraulic brakes,
Out of the multi-plate hydraulic brake, an output-side hydraulic brake for fixing the constituent members of the planetary gear set to which the output shaft is coupled is arranged behind the control valve and at the rear end of the automatic transmission. ,
The multi-plate hydraulic clutch is disposed in front of the output-side hydraulic brake , and is interposed between the multi-plate hydraulic clutch and the output-side hydraulic brake , and a clutch support disposed above the control valve. Fitting the operating piston of the plate hydraulic clutch,
The plurality of planetary gear sets are arranged in front of the multi-plate hydraulic clutch.
[0013]
A gear transmission mechanism of an automatic transmission according to a second invention is the above-described first invention,
The output-side hydraulic brake is arranged so that the operating piston is stroked toward the clutch support during operation, and the brake plate of the output-side hydraulic brake is received in the piston stroke direction by the clutch support. Is.
[0014]
A gear transmission mechanism of an automatic transmission according to a third invention is the first invention or the second invention,
The clutch support is positioned in the input / output axis direction with the inner peripheral step of the transmission case and the snap ring engaged in the transmission case, and the end surface of the snap ring that receives the clutch support is moved toward the inner periphery. It is made to incline so that it may approach.
[0015]
A gear transmission mechanism of an automatic transmission according to a fourth aspect of the present invention is the third aspect of the invention,
The clutch support is prevented from rotating with respect to the transmission case.
[0016]
A gear transmission mechanism of an automatic transmission according to a fifth invention is any one of the first invention to the fourth invention,
When there are two output side hydraulic brakes, the operating piston of one output side hydraulic brake is fitted in the outer peripheral wall of the operating piston of the other output side hydraulic brake fitted in the rear end wall of the transmission case. In addition, the operating hydraulic pressure is supplied to the one output side hydraulic brake from the inner peripheral portion of the rear end wall via an oil passage provided in the rear end wall of the transmission case. is there.
[0017]
【The invention's effect】
The automatic transmission selectively operates a plurality of multi-plate hydraulic clutches and a multi-plate hydraulic brake that respond to the hydraulic pressure supplied from the control valve , thereby transmitting a transmission path between the input / output shafts via a plurality of planetary gear sets. Can be switched.
[0018]
By the way, in the first invention, among the multi-plate hydraulic brakes, the output-side hydraulic brake for fixing the constituent members of the planetary gear set to which the output shaft is coupled alone is located behind the control valve and automatically shifts. Placed at the rear end of the machine,
The multi-plate hydraulic clutch is disposed in front of the output-side hydraulic brake, and the operating piston of the multi-plate hydraulic clutch is interposed between the multi-plate hydraulic clutch and the output-side hydraulic brake, and is located above the control valve. Mated with the clutch support located at
Since a plurality of planetary gear sets are arranged in front of the multi-plate hydraulic clutch,
Even with the planetary gear set arranged in the forward direction, the clutch support is located relatively far from the rear end of the automatic transmission,
As described above, since the hydraulic pressure is supplied to the multi-plate hydraulic clutch through the radial path of the clutch support to the inner periphery of the clutch, the transmission shaft of the control valve needs to be extended to the clutch support. The length in the line direction can be shortened.
[0019]
In the second invention, the output-side hydraulic brake is arranged so that the operating piston is stroked toward the clutch support during operation, and the brake plate of the output-side hydraulic brake is received by the clutch support in the piston stroke direction. In addition,
Parts such as a snap ring for receiving the brake plate of the output-side hydraulic brake in the piston stroke direction are not required, and the number of parts of the gear transmission mechanism can be reduced to provide a cost-effective automatic transmission.
Further, in this case, an axial space for engaging a snap ring or the like in the transmission case becomes unnecessary, and in this respect, the automatic transmission can be shortened.
[0020]
According to a third aspect of the present invention, the clutch support is positioned in the input / output axis direction with the inner circumferential step of the transmission case and the snap ring engaged in the transmission case, and the end surface of the snap ring that receives the clutch support is Because it is inclined to approach the clutch support as it goes around,
The inclined end surface of the snap ring provides easy and reliable positioning of the clutch support with respect to the transmission case, and rattling of the clutch support in the axial direction can be prevented.
[0021]
In the fourth invention, when positioning the clutch support with the snap ring as in the third invention, the clutch support is prevented from rotating with respect to the transmission case.
The clutch support is prevented from rotating, and this rotation can reliably prevent the snap ring from expanding and coming off the transmission case.
[0022]
In a fifth aspect of the present invention, when there are two output-side hydraulic brakes, the operating piston of one output-side hydraulic brake is fitted in the rear end wall of the transmission case. The hydraulic pressure is supplied to the one output side hydraulic brake from the inner peripheral portion of the rear end wall through an oil passage provided in the rear end wall of the transmission case. From
First, since it is a double piston in which the operating pistons of both output side hydraulic brakes are fitted to each other, it is possible to shorten the structure of the rearmost end portion of the automatic transmission in which the output side hydraulic brake is disposed. Can
Furthermore, a bulge caused by an oil passage provided in the rear end wall of the transmission case for supplying the hydraulic pressure to the one output side hydraulic brake constitutes a reinforcing rib for reinforcing the rear end wall, and the automatic transmission It is possible to increase the strength of the rearmost end portion.
[0023]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 schematically shows a transmission gear mechanism according to an embodiment of the present invention, which includes an input shaft 1, an output shaft 3, three planetary gear sets 5, 7, and 9, which will be described later. It consists of a number of friction elements such as hydraulic clutches and hydraulic brakes.
The input shaft 1 and the output shaft 3 are provided so as to face each other coaxially, and the planetary gear sets 5, 7, 9 are disposed coaxially with the input / output shafts 1, 3.
[0024]
The first planetary gear set 5 on the most input shaft 1 side, the second planetary gear set 7 on the center, and the planetary gear set 9 on the most output shaft 3 side are respectively the first, second, and third sun gears 5s, 7s, and 9s. And simple planets comprising first, second, and third ring gears 5r, 7r, and 9r, and planetary pinions meshed between these gears, which are rotatably supported by the first, second, and third carriers 5c, 7c, and 9c. A gear set.
[0025]
The first ring gear 5r is coupled to the input shaft 1, and the second carrier 7c is coupled to the output shaft 3. The first ring gear 5r can be coupled to the second ring gear 7r and the third carrier 9c via the input clutch I / C, and the second ring gear 7r and the third carrier 9c are connected to the transmission case by the reverse brake R / B. In addition to being able to be fixed, it is possible to couple to the third sun gear 9s by the direct clutch D / C.
[0026]
The first sun gear 5s is supported by the third one-way clutch 3rd / OWC so as not to rotate in the direction opposite to the engine rotation, and can be fixed to the transmission case by the front brake Fr / B.
The first carrier 5c is coupled to the third ring gear 9r so as to rotate integrally, and the second sun gear 7s is prevented from rotating in the direction opposite to the engine rotation by the forward one-way clutch F / OWC when the forward brake Fwd / B is engaged. At the same time, it is appropriately fixed by engaging the low coast brake LC / B so that the forward one-way clutch F / OWC cannot rotate appropriately in the idling direction.
[0027]
Further, the second sun gear 7s and the third sun gear 9s can be coupled by a high & low reverse clutch H & LR / C, and the engine can be rotated from the third sun gear 9s to the second sun gear 7s via the first one-way clutch 1st / OWC. It can be transmitted.
[0028]
Such a gear transmission train is a combination of forward (D range) first speed to fifth speed and reverse (R range) by the combination of engagement (indicated by a circle) and release (no mark) of the friction element shown in FIG. Each shift stage can be selected.
[0029]
FIG. 2 is an actual configuration diagram of the gear transmission train schematically shown in FIG. 1, and the input shaft 1 and the output shaft 3 are coaxially abutted and fitted so that they can be rotated relative to each other so that they can rotate relative to each other. The first planetary gear set 5 is arranged on the input shaft 1 and the second planetary gear set 7 and the planetary gear set 9 are arranged on the output shaft 3, respectively. The case 10 is positioned relatively near the front end.
The first ring gear 5r is coupled to the input shaft 1 by the member 11 and the clutch drum 12 of the input clutch I / C, and the second carrier 7c is serrated to the output shaft 3 and directly coupled.
The clutch drum 12, that is, the first ring gear 5r can be coupled to the third carrier 9c via the input clutch I / C, and the second ring gear 7r is integrally formed with the third carrier 9c.
Here, the input clutch I / C is disposed on the outer periphery of the second planetary gear set 7, and the inner peripheral portion of the input clutch drum 12 is coupled to the input shaft 1 between the first and second planetary gear sets 5 and 7, The operating piston 13 of the input clutch I / C is fitted to the inner periphery of the drum 12.
[0030]
The second ring gear 7r and the third carrier 9c configured integrally as described above can be fixed to the transmission case 10 by the multi-plate hydraulic brake type reverse brake R / B, and the multi-plate hydraulic clutch type direct clutch D / In order to be able to be coupled to the third sun gear 9s by C,
First, the clutch drum 14 of the direct clutch D / C is coupled to the third carrier 9c and extended from the third planetary gear set 9 toward the rear of the transmission, and this extended end is horizontally mounted in the transmission case 10. A reverse brake R / B hub is supported on the clutch support 15 so as to be rotatable.
Therefore, the reverse brake R / B is arranged so as to surround the rear extension end of the clutch drum 14, and the operating piston 16 is fitted in the clutch support 15.
[0031]
On the other hand, the operating piston 17 of the direct clutch D / C is fitted into the rear extension end of the clutch drum 14 and extends toward the front of the transmission, and a multi-plate hydraulic pressure is provided on the inner periphery of the direct clutch D / C. A clutch type high & low reverse clutch H & LR / C is installed.
The clutch drum 18 of the high & low reverse clutch H & LR / C is coupled to the third sun gear 9s by the member 19 and is mounted on the output shaft 3 via the hollow shaft 20 extending from the second sun gear 7s toward the rear of the transmission. It is supported so that it can rotate freely, and also functions as a clutch hub of the direct clutch D / C.
[0032]
The high & low reverse clutch H & LR / C appropriately connects between the clutch drum 18 and the clutch hub 21 connected to the hollow shaft 20, that is, between the second sun gear 7s and the third sun gear 9s. The operating piston 22 is fitted into the clutch drum 18.
A first one-way clutch 1st / OWC is interposed between the third sun gear 9s and the hollow shaft 20, through which engine rotation can be transmitted from the third sun gear 9s to the second sun gear 7s.
[0033]
The first sun gear 5s is supported by the third one-way clutch 3rd / OWC so as not to rotate in the direction opposite to the engine rotation, and can be fixed to the transmission case by a band brake type front brake Fr / B.
The first carrier 5c is integrally coupled to the third ring gear 9r by the member 23 so that the first carrier 5c and the third ring gear 9r rotate integrally.
[0034]
The hollow shaft 20 formed integrally with the second sun gear 7 s extends through the clutch support 15 to the rear end portion of the transmission case 10, and between the extended rear end of the hollow shaft 20 and the transmission case 10. A forward one-way clutch F / OWC and a forward brake Fwd / B are interposed, and a low coast brake LC / B arranged in parallel to these is interposed.
When the forward brake Fwd / B is engaged, the forward one-way clutch F / OWC prevents the second sun gear 7s (hollow shaft 20) from rotating in the direction opposite to the engine rotation with respect to the transmission case 10, and the low coast brake LC. / B serves to fix the second sun gear 7s (hollow shaft 20) so that it cannot rotate in the idling direction of the forward one-way clutch F / OWC by fastening.
[0035]
Here, each of the forward brake Fwd / B and the low coast brake LC / B is an output side multi-plate for fixing the constituent member (second sun gear 7s) of the second planetary gear set 7 to which the output shaft 3 is coupled. Make up hydraulic brake,
The forward brake Fwd / B and the low coast brake LC / B are arranged in such a direction that the respective operating pistons 24 and 25 stroke toward the clutch support 15 when operating, and the operating piston 24 is arranged at the rear end of the transmission case 10. The working piston 25 is fitted into the wall 10 a and the working piston 25 is fitted into the outer peripheral wall of the working piston 24.
[0036]
The brake discs of the forward brake Fwd / B and the low coast brake LC / B are rotationally engaged with a common spline 10b in the transmission case 10, and are prevented from coming off by a common snap ring 26, and are operated pistons 24, 25. The pressing force from is assumed to be received.
Since the oil passage for the operating piston 24 of the forward brake Fwd / B is fitted in the rear end wall 10a of the transmission case 10, a combination of a plurality of holes 31 shown in FIG. The hydraulic oil from the control valve 32 is supplied from the outer periphery of the piston 24.
Therefore, since the oil passage for the operating piston 25 of the low coast brake LC / B is fitted into the outer peripheral wall of the operating piston 24, the hole 33 provided in the transmission case 10 as clearly shown in FIG. The oil passage 34 is provided in the rear end wall 10 a of the transmission case 10, and hydraulic oil from the control valve 32 is supplied from the inner peripheral side of the piston 25.
[0037]
In the present embodiment configured as described above, the forward brake Fwd, which is an output-side hydraulic brake for fixing the second sun gear 7s, which is a component of the second planetary gear set 7 to which the output shaft 3 is coupled, as a single unit. / B and low coast brake LC / B at the rear end of the automatic transmission,
The direct clutch D / C, which is a multi-plate hydraulic clutch, is arranged in front of these output-side hydraulic brakes Fwd / B (LC / B), and the operating piston 17 of the multi-plate hydraulic clutch D / C is connected to these multi-plate hydraulic clutches. The clutch support 15 is interposed between the D / C and the output side hydraulic brake Fwd / B (LC / B),
Order to arranged the planetary gear set 5,7,9 forward from multiple disc hydraulic clutch D / C,
Even in the automatic transmission arranged in front of the planetary gear sets 5, 7, and 9, the clutch support 15 is located at a position relatively far away from the rear end of the automatic transmission,
Since it is rotating as a whole, the hydraulic pressure must be supplied to the multi-plate hydraulic clutch D / C through the radial passage 35 (see FIG. 2) of the clutch support 15 to the inner periphery of the clutch. Further, the length of the control valve 32 that needs to be extended to the clutch support 15 in the transmission axial direction can be shortened.
[0038]
Further, of the forward brake Fwd / B and the low coast brake LC / B which are output side hydraulic brakes, the forward brake in which the operating piston 25 of the low coast brake LC / B is fitted in the rear end wall 10a of the transmission case. Fwd / B is fitted into the outer peripheral wall of the actuating piston 24, and the low coast brake LC / B is operated from the inner peripheral portion of the rear end wall via an oil passage 34 provided in the rear end wall 10a of the transmission case. Because it was configured to supply hydraulic pressure,
First, since it is a double piston in which the operating pistons 24, 25 of both output side hydraulic brakes are fitted to each other, the structure of the rearmost end portion of the automatic transmission in which the output side hydraulic brake is arranged is shortened. Can be realized,
Furthermore, the bulge 10c resulting from the oil passage 34 provided in the rear end wall 10a of the transmission case for supplying the hydraulic pressure to the low coast brake LC / B constitutes a reinforcing rib that reinforces the rear end wall 10a. The strength of the rear end portion of the automatic transmission can be increased.
[0039]
As shown in FIG. 2, it is common sense that the clutch support 15 is positioned in the input / output axial direction by an inner circumferential step portion 10 d in the transmission case 10 and a snap ring 36 engaged in the transmission case 10. In Although,
At this time, as shown in FIGS. 5 and 6, the snap ring 36 is preferably inclined so that at least the end face of the snap ring 36 that receives the clutch support 15 approaches the clutch support 15 toward the inner periphery.
In this case, the inclined end surface of the snap ring 15 provides easy and reliable positioning of the clutch support 15 with respect to the transmission case 10, and rattling of the clutch support 15 in the axial direction can be prevented.
[0040]
Similarly, as shown in FIG. 5, the forward brake Fwd / B and the low coast brake LC / B, which are output side hydraulic brakes, are arranged so that the operating pistons 24 and 25 are stroked toward the clutch support 15 when operating. In addition, the brake plate of these output hydraulic brakes can be configured to be received in the piston stroke direction by the clutch support 15.
In this case, parts such as the snap ring 26 (see FIG. 2) for receiving the brake plate of the output-side hydraulic brake in the piston stroke direction are not necessary, and the number of parts of the gear transmission mechanism is reduced, resulting in a cost-effective automatic transmission. As well as
A space in the axial direction for engaging the snap ring and other parts in the transmission case becomes unnecessary, and in this respect, the automatic transmission can be shortened.
[0041]
Further, when positioning the clutch support 15 with the snap ring 36, the clutch support 15 is formed by a spline type protrusion 15a as shown in FIGS. 5 and 6 and a spline type notch 10e in the transmission case 10. It is advantageous to prevent rotation with respect to the transmission case 10 by engagement.
In this case, the clutch support 15 does not rotate, and it is possible to reliably prevent the snap ring 36 from being expanded and coming off the transmission case 10 by this rotation.
[Brief description of the drawings]
FIG. 1 is an explanatory diagram schematically showing a gear transmission mechanism of an automatic transmission according to an embodiment of the present invention, and also showing an engagement / release logic for each gear stage of an internal friction element.
FIG. 2 is a longitudinal side view showing an actual configuration embodying a gear transmission mechanism according to the embodiment;
FIG. 3 is an enlarged partial sectional view showing an output side multi-plate hydraulic brake at a rear end portion of the gear transmission mechanism together with an oil passage structure for one brake.
FIG. 4 is an enlarged partial sectional view showing an output-side multi-plate hydraulic brake at a rear end portion of the gear transmission mechanism together with an oil passage structure for the other brake.
FIG. 5 is a longitudinal sectional side view of an essential part showing another embodiment of the gear transmission mechanism according to the present invention.
FIG. 6 shows an attachment structure of a clutch support of the gear transmission mechanism according to the embodiment;
(A) is a longitudinal side view of the attachment structure,
(B) is an end view of the clutch support.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Input shaft 3 Output shaft 5 1st planetary gear set 7 2nd planetary gear set 9 3rd planetary gear set
Fr / B front brake
3rd / OWC third one-way clutch
I / C input clutch
H & LR / C High & Low Reverse Clutch
1st / OWC first one-way clutch
D / C direct clutch (multi-plate hydraulic clutch)
R / B reverse brake
LC / B low coast brake (hydraulic brake on output side)
Fwd / B forward brake (hydraulic brake on output side)
F / OWC forward one-way clutch
10 Transmission case
14 Direct clutch drum
15 Clutch support
15a Clutch support detent projection
17 Direct clutch operating piston
18 High & Low Reverse Clutch Drum (Direct Clutch Hub)
20 hollow shaft
21 high & low reverse clutch hub
22 High & Low Reverse Clutch Actuation Piston
24 Forward brake actuated piston
25 Low coast brake operating piston
31 Forward brake fluid hole
32 Control valve
33 Low coast brake fluid hole
34 Low coast brake hydraulic oil passage
36 Clutch support snap ring

Claims (5)

A plurality of planetary gear sets are coaxially arranged from the input shaft side to the output shaft side provided in abutment thereto, and include a plurality of multi-plate hydraulic clutches and a multi-plate hydraulic brake that respond to the hydraulic pressure supplied from the control valve, the automatic transmission in which the transmission path between the input and output shaft via the planetary gear set to switch by selective actuation of the plurality of multi-plate hydraulic clutches and multi-disc hydraulic brake,
Out of the multi-plate hydraulic brake, an output-side hydraulic brake for fixing the constituent members of the planetary gear set to which the output shaft is coupled is arranged behind the control valve and at the rear end of the automatic transmission. ,
The multi-plate hydraulic clutch is disposed in front of the output-side hydraulic brake , and is interposed between the multi-plate hydraulic clutch and the output-side hydraulic brake , and is provided on a clutch support disposed above the control valve. Fitting the operating piston of the plate hydraulic clutch,
A gear transmission mechanism for an automatic transmission, wherein the plurality of planetary gear sets are arranged in front of the multi-plate hydraulic clutch. 2. The output side hydraulic brake according to claim 1, wherein the operating piston is arranged to be stroked toward the clutch support during operation, and the brake plate of the output side hydraulic brake is received in the piston stroke direction by the clutch support. A gear transmission mechanism for an automatic transmission. In Claim 1 or 2, the clutch support is positioned in the input / output axial direction with the inner circumferential step of the transmission case and the snap ring engaged in the transmission case, and the end surface of the snap ring that receives the clutch support is A gear transmission mechanism of an automatic transmission, wherein the gear transmission mechanism is inclined so as to approach the clutch support toward the inner periphery. 4. A gear transmission mechanism for an automatic transmission according to claim 3, wherein the clutch support is prevented from rotating with respect to the transmission case. 5. When there are two output-side hydraulic brakes according to claim 1, the other output in which the operating piston of one output-side hydraulic brake is fitted in the rear end wall of the transmission case. The hydraulic pressure is applied to the one output-side hydraulic brake from the inner peripheral portion of the rear end wall through an oil passage provided in the rear end wall of the transmission case. A gear transmission mechanism of an automatic transmission, characterized by being configured to supply.

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