JPH06201040A - Transmission gear for vehicle - Google Patents

Abstract

PURPOSE:To heighten conformability between a seal ring groove and a disposed member so as to suppress oil spill by forming a seal ring, disposed between oil feed passages to each hydraulic servo, of synthetic resin and forming a member, disposed in a seal ring groove, of iron in double piston structure having an inner cylinder in common. CONSTITUTION:An input shaft 15 is connected to a connecting member 16 through a first clutch C1 and to a sun gear S through a second clutch C2. A third clutch C3 and a one-way clutch F0 are interposed between the connecting member 16 and the ring gear R1 of a planetary gear 10, and a fourth clutch CO is interposed between the connecting member 16 and a ring gear R2. As to the clutches C0, C3 in such a transmission gear, pistons are fittingly mounted between inner and outer cylinders respectively, and pressure oil is fed/discharged to/from oil chambers partitioned by the respective pistons through oil holes. In this case, a seal ring groove is formed at each oil hole, and a synthetic resin made seal ring with a cut part of tapered cross section is fittingly mounted into this seal ring groove to aim at sealing.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle transmission, and more particularly to a hydraulic pressure supply structure for a hydraulic servo of a clutch device used in the vehicle transmission.

[0002]

2. Description of the Related Art Conventionally, a clutch cylinder is arranged on an aluminum case supporting device, a seal ring groove is arranged in the case, and cast iron is formed in the groove to form an oil passage for a hydraulic servo. It is known that a seal ring made of metal is provided.

Although the cast iron seal ring has good compatibility with the aluminum case, it may cause a pressure drop in the hydraulic servo due to oil leakage.

Therefore, before preventing oil leakage, it is desired to employ a seal ring for synthetic resin made of Teflon or Vespel material, for example.

However, in terms of the compatibility with the aluminum case and the movement performance in the groove of the seal ring for forming a plurality of oil passages, the performance deteriorates.

To solve this problem, a synthetic resin seal ring is used to improve the conformability with the aluminum case and to improve the movability of the seal ring required as the number of seal rings is reduced. It is an object of the present invention to provide a vehicular transmission having an oil supply structure for the hydraulic servo.

[0007]

In order to solve the above-mentioned problems, the present invention provides an iron shaft 101 connected to a first rotating member 15 and an iron shaft 101 rotatably disposed on the shaft. A first clutch device C ₀ and a second clutch device C ₃ disposed in the first clutch device, wherein the first clutch device C ₀ is the shaft 15
A first inner cylinder 102 that is rotatably disposed on the upper side; a first outer cylinder 103 that is concentrically disposed with the first inner cylinder 102; and the first inner and first inner cylinders 102. A first side wall 104 for connecting the outer cylinder, a first piston 105 slidably disposed in the axial direction between the first inner and outer cylinders, the first inner cylinder, the first inner cylinder, Of the outer cylinder, the first side wall and the first piston, the first oil chamber 106, and the second clutch device C ₃ is formed on the outer diameter side of the first piston. A second outer cylinder 107, a second piston 108 axially slidably disposed between the first inner cylinder and the second outer cylinder, and the first inner cylinder Over, the second outer cylinder,
The first and second oil chambers 109 are formed by the first piston and the second piston, and the hydraulic pressure is supplied to the outer diameter side of the shaft to the first and second oil chambers. Second oil holes 110 and 111 are formed, and seal ring grooves 112 to 114 are formed to seal the first and second oil holes.
And a synthetic resin seal ring having a cut portion 115 having a tapered cross section is disposed in a groove formed between the first and second oil holes. It has a structure in which

Further, a seal ring having a cut portion 117 having a vertical cross section is disposed in the grooves formed on both sides of the first and second oil holes, respectively. It has a structure in which the vehicle transmission described in the section is arranged.

Further, an input shaft 15 for locking the engine driving force, a case having a boss portion 118 for hindering the input shaft, an oil reservoir groove 119 formed on the outer diameter side of the boss portion, An iron sleeve 120 disposed on the outer diameter side of the boss to cover the oil sump groove, and a plurality of seal ring grooves 121 to 12 formed on the outer diameter side of the iron sleeve.
4 and a third clutch device C ₁ connected to the input shaft and rotatably arranged on the iron sleeve, the third clutch device being the first rotating member. A second inner cylinder having an iron shaft 101 connected to the input shaft 15, and a third outer cylinder 125 concentrically arranged on the second inner cylinder.
And a second side wall 126 for connecting the second inner cylinder and the third outer cylinder, and an axially slidable arrangement between the second inner cylinder and the third outer cylinder. Third piston 127
And a third oil chamber 128 formed by the second inner cylinder, the third outer cylinder, and the third piston, and the iron shaft includes the third oil chamber, the first and second oil chambers. A third oil hole 129 which is connected to the oil hole,
A fourth oil hole 130 and a fifth oil hole 131 are formed, and four seal ring grooves 132 to 135 are provided to seal the third to fifth oil holes, and four cut sections 115 having a tapered cross section. A structure is provided in which the transmission for vehicle according to claim 2 is arranged in which a resin seal ring having the above is arranged.

[0010]

According to the present invention, a seal ring made of synthetic resin having a tapered cut portion is disposed between the oil supply passages to the oil chambers of the two clutches, so that two clutches can be selectively used. When the oil pressure is supplied to the oil chamber, or when the oil pressure is supplied to the two oil chambers at the same time but there is a difference in the oil supply pressure of each oil, the oil pressure between the seal rings does not leak and the oil pressure is servo-controlled. It can be supplied inside.

Further, since the member, which is relatively rotatably disposed inside the inner cylinder of the clutch and has the groove for arranging the seal ring, is made of iron, friction is generated between the inner ring and the synthetic resin seal ring. Can be prevented.

Further, since seal rings having cut portions having a vertical cross section are arranged on both sides of the oil supply holes to the two oil chambers, oil leakage from both sides can be surely prevented.

Further, by disposing the iron sleeve on the case and disposing the seal ring having the tapered cut section between the inner sleeve of the third clutch and the inner cylinder of the third clutch,
Despite the large relative rotation with the iron sleeve, a sufficient amount of lubricating oil can be supplied to the seal ring and, on the other hand, the amount of oil leakage that occurs is a seal having a vertical sectional view. It can be reduced with a ring.

[0014]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a sectional view showing an essential part of the invention relating to a vehicle transmission of the invention, FIG. 2 is a diagram showing a skeleton of the vehicle transmission of the invention, and FIG. 3 is a vehicle transmission of the invention. Is an operation table of.

First, the structure of the vehicle transmission will be described with reference to FIG.

A four-speed automatic transmission A to which the present invention is applied has a torque converter 5 via a lockup clutch L / C.
It has 0- and 4-speed transmission gear mechanism 1, a reduction mechanism 51, and a differential device 52.

The four-speed transmission gear mechanism 1 has a planetary gear unit 12 formed by combining a single planetary gear 10 and a dual planetary gear 11, and the sun gears S ₁ and S _{2 of the} gear unit 12 are integrally formed. It is composed of the formed sun gear S.

Further, the pinions P ₁ and P ₁ 'which mesh with the sun gears S ₁ and S ₂ have a common carrier CR, and
A carrier CR that supports a pinion P ₂ that meshes with a ring gear (hereinafter referred to as a “large ring gear”) R ₂ of the pinion and dual planetary gear 11 is also integrally formed.

The input shaft 15 extending from the output member of the torque converter 50 is connected to the connecting member 16 via the first clutch C ₁ and to the sun gear S via the second clutch C _2. is doing.

Further, a ring gear (hereinafter referred to as "small ring gear") R of the connecting member 16 and the single planetary gear R
_A third clutch C ₃ and a second one-way clutch F ₀ are interposed between the first clutch C ₁ and the _first clutch C _1, and a fourth clutch C ₀ is interposed between the connecting member 16 and the large ring gear R ₂ . .

The sun gear S is constructed so that it can be locked by a _first brake B ₁ which is a band brake, and a second brake is provided between the large ring gear R ₂ and the case 17. B ₂ and the first one-way clutch F ₁ are interposed. Further, the carrier CR is an output gear 1 which is an output shaft located substantially in the center of the transmission gear mechanism 1.
It is linked to 3.

Further, the reduction mechanism 51 has a counter shaft 54 rotatably supported by the case, and the shaft 54 has a large gear 53 and a small gear 55 which are constantly meshed with the output gear 13. It is fixed. In addition, the differential device 52 includes a differential pinion 5 that meshes with each other.
6 and the left and right side pinions 57a and 57b are fixed to the left and right front axles 59a and 59b, respectively.
The diff pinion 56 is supported by a diff carrier 60 that is rotatably supported by the case, and the diff carrier 60 is provided with a ring gear 61 that is constantly meshed with the small gear 55.

Next, the structure of the essential part of the invention will be described with reference to FIG.

The first rotating member 15 is an input shaft to which the engine drive of the transmission is transmitted. The iron shaft 101 is
The input shaft 15 is spline-connected and hindered.

The first clutch device C ₀ includes an iron shaft 101.
Of the first inner cylinder 102 is rotatably disposed on the outside of the spline coupling portion and further spline-coupled on the outer side of the spline coupling portion.
The first outer cylinder 103 is concentrically arranged on the outer side in the radial direction, and they are connected to each other through the first side wall 104.

Further, a first piston 105 is slidably arranged between the first inner cylinder 102 and the first outer cylinder 103.

The first oil chamber 106 is formed by the first inner cylinder 102, the first outer cylinder 103, the first side wall 104, and the first oil chamber 106.

The second clutch C ₃ is the first piston 10
5, the outer cylinder formed on the outer diameter side, the first inner cylinder 102, and the second outer cylinder 103.
Second piston 10 disposed between the two so as to be slidable in the axial direction
8 and a second oil chamber 109 formed by the first inner cylinder 102, the second outer cylinder 103, the first piston 105 and the second piston 108.

The iron shaft 101 is provided with first and second oil holes 110 and 111 so that hydraulic pressure can be supplied to the first oil chamber 106 and the second oil chamber 109.

Further, three seal ring grooves 112 to 114 are engraved on the outer side to seal the first and second oil holes.

A seal ring 117 made of Teflon having a cut section with a vertical cross section is provided in the grooves 112 and 114, and a seal ring having a tapered cut section is provided in the groove 115. The boss portion 118 is connected to the case so that the input shaft 15 is supported by the bearing 136 on the radially inner side and the oil reservoir groove 119 is formed on the radially outer side.

The iron sleeve 120 has a plurality of seal ring grooves 121 to 124 which are arranged radially outside the groove 119 to form an oil sump.

The third clutch device C ₁ is an iron sleeve 1
20 is arranged on the outer side in the radial direction of 20 so as to be rotatable relative to each other, and via a shaft 101 made of iron. The second inner cylinder 101 and the third outer cylinder 125 arranged concentrically with the second inner cylinder 101.
And inner cylinder 101 and outer cylinder 12
5, a second side wall 126 for connecting 5 and a third piston 127 which is axially slidably arranged between the second inner cylinder 101 and the third outer cylinder 125,
It is formed by the second inner cylinder 101, the third outer cylinder 125, and the third piston 127, and has a third oil chamber 128.

The iron shaft 101 has a third oil chamber 128,
Third to third communicated with the first and second oil chambers 106 and 109
Fifth oil holes 129 to 131 are provided.

The four seal ring grooves 132 to 135 are arranged to seal these oil holes. A seal ring made of Teflon having a tapered cross section 115 is arranged between these grooves.

The shaft supply oil passage 137 is formed in the case 17 and is connected to the oil sump groove 119.

The return springs 139 and 140 are C
_{It is provided for one-} clutch device and C ₁ , C ₃ clutch device.

The seal ring groove 133 'is provided in parallel with the groove 133, and the grooves 133, 133' are provided for the oil reservoir oil passage 138.

Next, referring to FIG. 3, the operation of each gear stage will be described with reference to the operation table of the transmission of the present invention.

During parking and neutral, all brakes and clutches are released.

In reverse, when the vehicle speed is higher than a predetermined value, the C ₂ clutch and the B ₂ brake are engaged, and when the vehicle speed is lower than the predetermined value, only the C ₂ clutch is engaged.

In the D range, only the C ₁ clutch is engaged at the 1st speed. Moreover, the first and second one-way clutches F ₁ and F ₀ are engaged, and the rotation of the input shaft 15 causes the first clutch C ₁ and the second one-way clutch F _{0 to} rotate.
It is transmitted to the small ring gear R ₁ through, and by the first one-way clutch F ₁ in this state, the carrier CR while idly sun gear S since the rotation of the large ring gear R ₂ is blocked is decelerated greatly The decelerated rotation is taken out from the output gear 13. Then, the rotation of the output gear 13 is reduced by the reduction mechanism 51, and the differential device 52 further causes the left and right accelerator shafts 59a and 59b to be rotated.
Be transmitted to.

Further, in the second speed state, the band of the first brake B ₁ is clamped.

The rotation of the input gear 15 depends on the first clutch C.
The rotation of the small ring gear R ₁ idles the large ring gear R ₂ because it is transmitted to the small ring gear R ₁ via the _first and second one-way clutches F ₀ and the sun gear S is locked by the first brake B _1. While from carrier CR 2
It is taken out as a fast rotation.

In the 1-2 shift, the first one-way clutch F ₁ is prevented from overrunning to prevent the occurrence of shift shock due to grip change.

Further, during the 2-3 shift, the timing for engaging the fourth clutch C ₀ and releasing the first brake B ₁ is properly performed.

In the third speed state in which the third clutch C ₃ and the fourth clutch C ₀ are engaged in addition to the _first clutch C ₁ and the first brake B ₁ is released, Axis 15
Is transmitted to the small ring gear R ₁ via the second one-way clutch F ₀ and the third clutch C ₃ and is transmitted to the large ring gear R 2 via the fourth clutch C ₀ so that the planetary gear unit 12 is integrated. The integrated rotation of the carrier CR is taken out to the output gear 13.

At this time, the fourth clutch C ₀ and the first brake B ₁ are replaced by another clutch. However, as described above, the proper timing is taken, and the gear shift through other gears is blocked so that the shift is performed. There is no shock.

The third clutch C ₃ is also engaged at the same time, but since the clutch C ₃ is in parallel with the second one-way clutch F ₀ , the engagement timing of the clutch C ₃ can be delayed.

Next, in the fourth speed state, the first clutch C
_In the fourth speed state in which the _first and fourth clutches C ₀ are engaged, the first brake B ₁ is switched to the locked state, and the third clutch C ₃ is switched to the released state. Since the rotation of the input shaft 15 is transmitted to the large ring gear R ₂ via the fourth clutch C ₀ and the sun gear S is locked by the first brake B ₁ , the rotation of the large ring gear R ₂ is prevented. The carrier CR is rotated at a high speed while idling the ring gear R ₁ , and this rotation is transmitted to the output gear 13.

At this time, the first brake B₁Locking of
Both release the third clutch C3, but the third clutch
Latch C₃Even if you release early, the second one-way
Chi F ₀The 3rd speed state is maintained by the
Brake B₁By controlling the locking of the
The occurrence of shift shock due to replacement is prevented.

Meanwhile, when the 4-3 speed downshift, with the first brake B ₁ is being released, the third clutch C ₃ is engaged, this time, the first brake B ₁ The second one-way clutch F ₀ is controlled by controlling the release.
Since the overrun is switched to the locking, the shift can be performed smoothly.

Further, in the 3-2 speed downshift, the release of the fourth clutch C ₀ is delayed with respect to the engagement of the first brake B ₁ , and the fourth clutch C ₀ and the first brake B ₁ are released. shifting _{the 1} via both released first speed state, i.e. the shift operation such as 3-1-2 speed is prevented.

The operation according to the present invention will be described below. In the 2-3 speed, the first clutch device C ₀
Is in the engaged state from the released state, and the engaged state of the C ₃ clutch device is maintained. At this time, the hydraulic pressure supplied to the oil chamber 106 of the C ₀ clutch device is higher than the hydraulic pressure supplied to the oil chamber 109 of the C ₃ clutch device. The modulator pressure is supplied to the oil chamber 106. Therefore, since the Teflon-made seal ring 115 arranged in the groove 113 has a tapered cut section, it does not expand radially outward even when high temperature hydraulic pressure is supplied, and smoothly in an overlapping state. It moves to the right in the drawing, and abuts on the right side surface of the groove 113 to ensure a reliable seal.

Further, in the third speed, both oil chambers 106,
Although the hydraulic pressure is supplied to both 109, the line pressure is supplied to the oil chamber 106 and the modulator pressure is supplied to the oil chamber 109, the seal ring 115 moves to the right in the figure in the same manner as described above, and the seal is surely made on the side surface. Done.

Further, since the third clutch device C ₁ is arranged so as to be rotatable relative to the outer side of the iron sleeve 101, the seal ring 115 having the cross-section tapered cut portions arranged in the seal ring grooves 112 to 114. As a result, the seal ring 115 is movable in the groove and the lubricating oil is sufficiently supplied, so that the durability is improved.

On the other hand, the oil seals the seal ring 115 for lubrication.
It is necessary to prevent further loss of the amount of oil in order to prevent pressure drop because of leakage from the oil seals. When oil is supplied to the holes 110 and 111, oil leakage is surely prevented and a decrease in hydraulic pressure is reduced.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a main part of an oil supply structure for a hydraulic servo relating to a vehicle transmission of the invention.

FIG. 2 is a skeleton of the vehicle transmission according to the present invention.

FIG. 3 is an operation table of the vehicle transmission according to the present invention.

[Explanation of symbols]

15 First Rotating Member (Input Shaft) 101 Iron Shaft (Second Inner Cylinder) C ₀ First Clutch Device C ₃ Second Clutch Device 102 First Inner Cylinder 103 First Outer Cylinder 104 One side wall 105 First piston 106 First oil chamber 108 Second piston 109 Second oil chamber 110 First oil hole 111 Second oil hole 112-114 Seal ring groove 115 Seal ring (Cut section) (Having a taper shape) 117 Seal ring (having a vertical cross section) 118 Boss portion 119 Oil sump groove 120 Iron sleeve 121-124 Seal ring groove C ₁ Third clutch device 125 Third outer cylinder 126 Second Side wall 127 Third piston 128 Third oil hole 129-131 Third to fifth oil hole 132-135 Seal Ngumizo

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Fumitomo Yokoyama 10 Akane Takane, Anjo City, Aichi Aisin AW Co., Ltd.

Claims (3)

[Claims] 1. An iron shaft connected to a first rotating member,
A vehicle transmission including a first clutch device disposed on the shaft so as to be rotatable relative to the shaft, and a second clutch device disposed in the first clutch device, wherein The clutch device includes a first inner cylinder rotatably disposed on the shaft, a first outer cylinder concentrically disposed with the first inner cylinder, the first inner and the first inner cylinders. A first side wall connecting one outer cylinder, a first piston slidably arranged in the axial direction between the first inner and outer cylinders, the first inner cylinder, first An outer cylinder, a first side wall, and a first oil chamber formed by a first piston, and the second clutch device is a second outer member formed on the outer diameter side of the first piston. Cylinder and the front A second piston axially slidably disposed between the first inner cylinder and the second outer cylinder, the first inner cylinder, the second outer cylinder, the first piston And a second oil chamber formed by the second piston, and first and second oil holes through which hydraulic pressure is supplied to the first and second oil chambers on the outer diameter side of the shaft. And a seal ring groove for sealing the first and second oil holes, and a synthetic resin having a cut section with a tapered cross section in the groove formed between the first and second oil holes. A vehicle transmission characterized in that a manufactured seal ring is provided. 2. A seal ring having a cut portion having a vertical cross section is provided in each of the grooves formed on both sides of the first and second oil holes. The vehicle gearboxes listed. 3. An input shaft for locking an engine driving force,
A case having a boss portion that obstructs the input shaft, an oil reservoir groove formed on the outer diameter side of the boss portion, and an oil reservoir groove provided on the outer diameter side of the boss portion so as to cover the oil reservoir groove. An iron sleeve, a plurality of seal ring grooves formed on the outer diameter side of the iron sleeve, a third clutch device connected to the input shaft and relatively rotatably disposed on the iron sleeve. The third clutch device is provided with a second inner cylinder having an iron shaft connected to the input shaft, which is the first rotating member, and concentrically arranged on the second inner cylinder. A third outer cylinder, a second side wall connecting the second inner cylinder and the third outer cylinder, and an axial slide between the second inner cylinder and the third outer cylinder. Third freely arranged And a third oil chamber formed by the second inner cylinder, the third outer cylinder, and the third piston, the iron shaft includes the third oil chamber, the first and second pistons. To form a third oil hole, a fourth oil hole, and a fifth oil hole, which are connected to the oil holes, and four seal ring grooves are provided to seal the third to fifth oil holes. 3. The vehicular transmission according to claim 2, further comprising a resin seal ring having two cut portions each having a tapered cross section.