JPH06337048A - Epicyclic gear transmission for vehicle - Google Patents

Abstract

PURPOSE:To carry out reverse running, even when a synchronous mechanism fails to operate at an extremely low temperature, by providing the second fixing means fixing the first speed member in a stationary part. CONSTITUTION:A lock pole 62 is supported in a case 40 by a pin 66 freely slidably, and a point end part 64 of the lock pole 62 can gear with a spline 60 of a sleeve 24. By the first link 72 and the second link 74, the lock pole 62 is moved, a roller 98 is brought into contact with a piston 70. When a hydraulic piston 70 is operated and moves upward, the lock pole 62 is moved by the first link 72 and the second link 74 to engage with the spline 60 of the sleeve 24. The first link 72 and the second link 74 are usually held in a non-operation condition by a return spring 76 arranged in the second link 74. The hydraulic piston 70 is also usually held in a non-operation condition by a piston spring 78 arranged inside a piston case 71. An oil pressure sensor detects a fact that a temperature is below the fixed value, and an oil pressure operating a fixing means 99 works at an extremely low temperature.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle planetary gear transmission used in an automatic transmission such as an automobile.

[0002]

2. Description of the Related Art The present inventor has disclosed in Japanese Patent Application No. 5-111254 a planetary gear transmission for a vehicle used for an automatic transmission such as an automobile, in which a friction element such as a multi-plate clutch causes drag when not operating. A device for reducing resistance was proposed. This device is a member (hereinafter referred to as a first speed member) fixed to a stationary part such as a case of a transmission during forward first speed and in reverse in order to reduce drag resistance due to a non-actuated friction element and improve power transmission efficiency. Say)
Is configured to be selectively connectable to the stationary portion and the input shaft via a clutch and a dog clutch.

That is, a first-speed member usually has two friction elements, a clutch for connecting to an input shaft and a brake for fixing to a stationary portion. Generally, a one-way clutch (OWC) is provided for a first-speed member. The dog clutch, which is provided and focuses on the fact that this one-way clutch (OWC) functions to fix the first-speed member to the stationary part during normal D-range travel, allows switching by using only one clutch as the friction element. It is configured so that the required functions can be satisfied by combining with.

According to this device, the brake for fixing the first speed member, which has the largest drag resistance at the high speed stage, is substantially the same as when it is eliminated, and it is possible to expect a great improvement in the transmission efficiency.

[0005]

However, in this vehicle planetary gear transmission, in order to smoothly switch the dog clutch, it is necessary to provide a so-called synchromesh synchronization mechanism. That is,
The dog clutches having different rotations are engaged with each other after eliminating the rotation difference by the synchronizing mechanism.

However, when a wet multi-plate clutch generally used in an automatic transmission is combined with a synchronizing mechanism,
The drag resistance of the wet multi-plate clutch becomes extremely large at an extremely low temperature of about 30 ° C. or lower, so that the synchronizing mechanism cannot exert a sufficient function, and as a result, the dog clutch cannot be switched. In that case, even if the first speed member cannot be connected to the input shaft, the vehicle can travel forward at the first speed, but if the first speed member cannot be fixed to the stationary portion,
There was a problem that it became impossible to run backwards.

The present invention has been made in view of the above-mentioned conventional problems, and the second fixing means for fixing the first speed member to the stationary portion allows the synchronizing mechanism to operate at an extremely low temperature. An object of the present invention is to provide a planetary gear transmission for a vehicle, which is capable of traveling in reverse even when it becomes impossible.

[0008]

In order to achieve the above object, the present invention is a planetary gear transmission for a vehicle, wherein a plurality of planetary gears are combined to obtain a gear ratio of four or more forward gears.
A planetary gear transmission for a vehicle, wherein a member that is fixed to a stationary portion at the first forward speed and in reverse is fixed to the stationary portion via a friction clutch and a switchable dog clutch. It is characterized by having a second fixing means for fixing to the stationary portion in addition to the fixing means to the.

According to the present invention, the second fixing means is
A lock pole that is swingably provided on the stationary portion and has a tip end that can mesh with a spline formed in the sleeve of the dog clutch; and a hydraulic piston that swings the lock pole via a link. To do.

[0010]

According to the vehicular planetary gear transmission of the present invention having such a structure, since the second fixing means for fixing to the stationary portion during reverse running at extremely low temperature is provided, that is, by the hydraulic piston. Since the lock pole is swung via the link so that the tip of the lock pole is engaged with the spline formed on the sleeve of the dog clutch, 1
The high speed member can be fixed to the stationary portion, and the vehicle can travel backward.

That is, when the drag resistance of the wet clutch increases at extremely low temperatures, even if the sleeve is not engaged with the stationary portion due to insufficient operation of the synchronizer, the sleeve engaged with the first speed member is used as the synchronizer. By fixing to the stationary part by the second fixing means which is not provided, the first speed member is fixed to the stationary part to enable the backward traveling.

[0012]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 5 are views showing an embodiment of the present invention.
FIG. 4 is a skeleton diagram of a planetary gear train which is a base of one embodiment of the present invention. In FIG. 4, 100 denotes a first planetary gear set which is a simple planetary gear, and the first planetary gear set 100
Has a first sun gear 102, a first ring gear 106, and a first carrier 108. Reference numeral 200 denotes a double-pinion type double-row second planetary gear set, and the second planetary gear set 20.
0 is the second sun gear 202, the long pinion 204, the pinion 204A, the second ring gear 206, the second carrier 2
08 and the third sun gear 302.

The first sun gear 102 is a second carrier 208.
, And can be fixed to the stationary portion 604 by the second brake 502 via the second carrier 208. The first ring gear 106 is connected to the output shaft 602 and is also connectable to the second ring gear 206 by the first clutch 400. The first carrier 108 is a first speed member,
The one-way clutch 40 can be selectively fixed or connectable to the stationary portion 604 or the input shaft 600 via the second clutch 402 and the dog clutch 606.
It can be fixed to the stationary portion 604 via 6.

The second sun gear 202 is connected to the input shaft 600 and meshes with the long pinion 204 via the pinion 204A. The second carrier 208 is
As described above, it can be fixed to the stationary portion 604 by the second brake 502 while being connected to the first sun gear 102. The first ring gear 1 via the first clutch 400
The second ring gear 206, which can be connected to 06, meshes with the long pinion 204, and the long pinion 204 meshes with the third sun gear 302. The third sun gear 302 can be fixed to the stationary portion 604 by the first brake 500.

By operating each friction element as shown in FIG. 5, a gear ratio of 6 forward gears and 1 reverse gear is obtained. ○ in Figure 5
The marks indicate the operation (fastening, etc.) of each element. Also,
The arrow of the dog clutch 606 indicates the meshing direction of the dog clutch 606. That is, the fourth, fifth, and sixth speeds mesh with the input shaft 600 (on the left side in FIG. 4), and the values in parentheses () are not related to power transmission. It can be seen that no switching is required in the "D" range.

The mark * indicates that the dog clutch 606 can be switched in either direction. "L" represents a range used when the engine is braked, etc., and in many cases, the position of the operation lever is usually displayed as a number such as "2" or "1". The first portion of the "L" range and the reverse of the "R" range engage with the stationary portion 64 (right side in FIG. 4).

Next, the D range 4, 5, which is frequently used,
6th power transmission will be described. In the case of the fourth speed in the D range, the first clutch 400 and the second clutch 402
Is concluded. When the second clutch 402 and the dog clutch 606 are engaged, the entire planetary gear is integrated, so that a gear ratio of 1: 1 can be obtained. Next, in the case of the fifth speed in the D range, the second clutch 402 and the first brake 500
Is concluded.

When the second clutch 402 and the dog clutch 606 are engaged, the input shaft 600 moves to the first carrier 1
08, the first carrier 108 is rotationally driven by the input shaft 600. When the first brake 500 is engaged, the third sun gear 302 is fixed to the stationary portion 604 by the first brake 500, so the long pinion 204
The second carrier 208 connected to is decelerated, and the first sun gear 102 is also decelerated. Deceleration of the first sun gear 102 and the first
By rotating the carrier 108, the first ring gear 10
6 is accelerated, and the output shaft 602 is accelerated from the input speed of the input shaft 600.

Next, in the 6th speed of the D range, the second clutch 402 and the second brake 502 are engaged. Second
When the clutch 402 and the dog clutch 606 are engaged, the input shaft 600 is connected to the first carrier 108,
The first carrier 108 is rotationally driven by the input shaft 600.

When the second brake 502 is engaged, the second brake
The carrier 208 holds the stationary portion 60 by the second brake 502.
4 and the first sun gear 102 is fixed. Therefore, the speed of the first ring gear 106 is increased as compared with the case of the fifth speed, and the output shaft 602 is also increased as compared with the case of the fifth speed. As described above, in the high-speed stage that is frequently used, there is substantially no brake for fixing the first carrier 108, which is the first speed member having a large drag resistance, and the power loss due to the drag resistance is greatly reduced. Therefore, the transmission efficiency of the transmission can be improved, and as a result, it can be expected to contribute to the reduction of the fuel consumption rate of the automobile.

Next, FIG. 3 is a cross-sectional view of an essential part according to an embodiment of the present invention. In FIG. 3, reference numeral 402 denotes the second clutch, the second clutch 402 is a wet clutch, and the first clutch 108, which is a first speed member, is connected to the second clutch 402. In the clutch case 80 that constitutes the second clutch 402, the clutch piston 82
Is housed slidably, a return spring 86 is interposed between a retainer 84 provided on the clutch case 80 and the clutch piston 82, and a hydraulic chamber 88 is formed between the clutch case 80 and the clutch piston 82. .

One friction plate 11 is assembled to the spline 81 of the clutch case 80, and the other friction plate 12 is assembled to the spline 15 of the clutch hub 14.
By pressing these friction plates 11 and 12 with the clutch piston 82, the second clutch 402 is engaged.
A spline 16 is formed on an extension of the clutch hub 14, and a synchro hub 18 is fitted to the spline 16. A spline 20 is also formed on the outer peripheral portion of the synchro hub 18, and a sleeve 24 is fitted to the spline 20 by the spline on the inner peripheral portion thereof. That is, the sleeve 24 is slidably engaged with the synchro hub 18 by the spline 20.

Reference numeral 600 denotes the cone surface 36 and the spline 3.
4 is an input shaft, and 42 is a flange fixed to the case 40 and having a cone surface 46 and a spline 44. The input shaft 600 and the cone surface 3 of the flange 42.
The cone surfaces of the synchronizer rings 38 and 48 provided between the synchronizer hubs 6 and 46 are in contact with the synchronizer hub 18.

The sleeve 24 can be selectively connected to the spline 34 of the input shaft 600 or the spline 44 of the flange 42 by sliding leftward or rightward. A groove 28 is formed on the outer circumference of the sleeve 24, and a shift fork (not shown) is fitted in the groove 28 to move the sleeve 24 in the left-right direction. A fixing spline 60 is formed on the outer periphery of the sleeve 24, and the lock pole 6 is swingably supported by the case 40.
The tip portion 64 of the second member is capable of meshing.

Next, FIG. 1 is a sectional view taken along line AA of FIG.
2 shows the operating state of the second fixing means, and FIG. 2 shows the non-operating state of the second fixing means. In FIGS. 1 and 2, 62
Is the lock pole, and the lock pole 62 is pin 6
6 is swingably supported by the case 40, and the tip 64
Is engageable with the spline 60 of the sleeve 24. The lock pole 62 is connected to the first link 72 by the pin 90, and the first link 72 is connected by the pin 92 to the second link 74.
Connected to. One end of the second link 74 is rotatably supported on the case 40 by a pin 94, and the other end of the second link 74 is supported by a pin 96 on the hydraulic piston 70.
A roller 98 that comes into contact with is rotatably provided.

When the hydraulic piston 70 is operated and moves upward, the lock pole 62 is moved by the first and second links 72 and 74, and the spline 60 of the sleeve 24 is moved.
And the rotation of the sleeve 24 is fixed to the case 40. A return spring 76 is provided on the second link 74, one end of the return spring 76 is fixed to the case 40, and the other end abuts on the first link 72. Therefore, the return spring 76 always keeps the first and second links 72 and 74 in the inoperative state.

Further, the hydraulic piston 70 is always in contact with the inner wall of the cylinder chamber 73 of the piston case 71 and the hydraulic piston 70.
It is held in the non-actuated position by a piston spring 78 interposed between the two. Lock pole 62, first and second links 72, 74, return spring 76, hydraulic piston 70, piston case 71, piston spring 78
And the like constitute second fixing means 99 for fixing the sleeve 24 to the case 40.

Since the spline 60 of the sleeve 24 is formed on the outer peripheral end surface of the sleeve 24, the sleeve 2
4 moves from the neutral position to the left side in FIG. 3 and meshes with the input shaft 600, even if the lock pole 62 moves,
The tip 64 of the lock pole 62 only contacts the outer circumference of the sleeve 24 and does not mesh with the spline 60.

That is, when the sleeve 24 meshes with the input shaft 600, the sleeve 24 holds the second fixing means 99.
Is not fixed by. Further, the second fixing means 9 is provided in the cylinder chamber 73 into which the hydraulic piston 70 is inserted.
The hydraulic pressure to operate 9 acts. Although not shown, this hydraulic pressure is created by the reverse hydraulic pressure in the case of "reverse". Furthermore, the temperature sensor (not shown) indicates that the lubricating oil of the transmission or the temperature of the transmission itself has fallen below a certain value. Is detected and the hydraulic pressure is applied only when the temperature is extremely low.

That is, the second fixing means 99 operates when the synchronizing function becomes inoperable at a very low temperature. Next, the operation will be described. When the sleeve 24 is slid rightward by a not-shown fork to be engaged with the flange 42 and the wet clutch 402 is fastened, the first carrier 108, which is the first speed member, is fixed to the case 40 via the wet clutch 402.

Further, when the sleeve 24 is slid to the right by a not-shown fork to be engaged with the input shaft 600 and the wet clutch 402 is engaged, the first carrier 108, which is a first speed member, receives the input shaft 600 through the wet clutch 402. Connected to 600. That is, when the sleeve 24 slides left and right by a not-shown fork and meshes with the input shaft 600 or the case 40, the first carrier 108 of the first speed member is coupled with the input shaft 600 or the case 40 together with the coupling of the wet clutch 402. Selectively connect.

At that time, the synchronizer ring 3 is used.
The action of 8,48 meshes smoothly. However, at extremely low temperatures, the drag resistance of the friction plates 11 and 12 of the wet clutch 402 at the time of idling becomes large and exceeds the synchronizing capacity of the synchronizer rings 38 and 48. Can no longer engage.

In this case, the vehicle can travel forward without engaging with the input shaft 600, but cannot travel backward unless engaging with the flange 42. Therefore, when the automatic transmission is operated to the reverse gear "R range" while the temperature is below a certain temperature, the reverse hydraulic pressure acts on the cylinder chamber 73 and the hydraulic piston 70 operates against the piston spring 78.

When the hydraulic piston 70 operates, the roller 9
8 rotates and moves on the hydraulic piston 70,
The tip portion 6 of the lock pole 62 via the links 72 and 74
4 meshes with the spline 60 of the sleeve 24. Thereby, as shown in FIG. 1, even if the sleeve 24 does not engage with the spline 44 of the flange 42 fixed to the case 40, the lock pole 62 fixes the sleeve 24 to the case 40.

After that, if the necessary hydraulic pressure is applied to the wet clutch 402 to put the wet clutch 402 into the engaged state, it is possible to travel backward. The state where the second fixing means 99 does not operate is shown in FIG.
It is not fixed at 0.

[0036]

As described above, according to the present invention, even if the synchronization mechanism becomes inoperable at a very low temperature,
Since the 1st speed member can be fixed to the case by the operation of the lock pole which is the second fixing means, it is possible to avoid that the reverse traveling is disabled.

[Brief description of drawings]

FIG. 1 is a sectional view of an essential part showing an embodiment of the present invention.

FIG. 2 is an explanatory view showing a state in which a second fixing means does not operate.

FIG. 3 is a diagram showing a synchronization mechanism and a wet clutch.

FIG. 4 is a skeleton diagram of a planetary gear train.

[Fig. 5] Operation explanatory diagram

[Explanation of symbols]

 11, 12: Friction plate 14: Clutch hub 15, 16: Spline 18: Synchronous hub 20: Spline 24: Sleeve 28: Groove 34, 44: Spline 36, 46: Cone portion 38, 48: Synchronizer ring 40: Case 42 : Flange 60: Spline 62: Lock pole 64: Tip part 66: Pin 70: Hydraulic piston 71: Piston case 72: First link 73: Cylinder chamber 74: Second link 76: Return spring 78: Piston spring 80: Clutch case 81: Spline 82: Clutch Piston 84: Retainer 86: Return Spring 88: Hydraulic Chamber 90, 92, 94, 96: Pin 98: Roller 99: Second Fixing Means 100: First Planetary Gear Set 102: Second Sun Gear 106 : First ring gear 10 : First carrier (first speed member) 200: Second planetary gear set 202: Second sun gear 204: Long pinion 204A: Pinion 206: Second ring gear 208: Second carrier 302: Third sun gear 400: First clutch 402: Second clutch 406: One-way clutch 500: First brake 502: Second brake 600: Input shaft 602: Output shaft 604: Stationary part 606: Dog clutch

Claims (2)

[Claims] 1. A planetary gear transmission for a vehicle, wherein a plurality of planetary gears are combined to obtain a gear ratio of four or more forward gears, wherein a member fixed to a stationary portion at the first forward speed and the reverse gear is provided.
In a planetary gear transmission for a vehicle, which can be fixed to a stationary portion via a friction clutch and a switchable dog clutch, in addition to a fixing means for fixing the member to the stationary portion by the dog clutch, A planetary gear transmission for a vehicle, comprising a fixing means. 2. A lock pole, wherein the second fixing means is swingably provided on the stationary portion, and a tip end portion of the lock pole is meshable with a spline formed on a sleeve of the dog clutch, and the lock pole is a link. The planetary gear transmission for vehicles according to claim 1, further comprising a hydraulic piston that is swung through the gear.