JP3381633B2 - Friction wheel type continuously variable transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a friction wheel type continuously variable transmission represented by a toroidal type continuously variable transmission.

[0002]

2. Description of the Related Art A friction wheel type continuously variable transmission includes an input disc, an output disc, a plurality of power rollers sandwiched between opposing surfaces of both discs and capable of tilting, and a power roller around a rotation axis of the power roller. A trunnion that is rotatable and that is freely stroked in the swing axis direction orthogonal to the power roller rotation axis, a fluid pressure cylinder device that strokes the trunnion in the swing axis direction, a fluid pressure cylinder device, and other fluids. And a control valve device for adjusting the fluid pressure supplied to the pressure device. And
When a spool contained in the control valve device is operated to generate a control fluid of a predetermined pressure based on the gear ratio command,
This control fluid is supplied to the fluid chamber of the fluid pressure cylinder device, and the servo piston moves in the swing axis direction, whereby the trunnion makes a stroke so as to be offset in the swing axis direction, and the power roller divides the input / output disk. Since the force tilts in a direction corresponding to the swing axis line, the rotational force of the input disk is set to a stepless speed change ratio and output to the output disk.

During shift control, the reaction force of the control fluid pressure acting on the servo piston of the fluid pressure cylinder device acts on the cylinder body accommodating the servo piston. Since the valve body accommodating the spool of the control valve device is integrally connected, the reaction force acts on the valve body from the cylinder body to deform the spool hole accommodating the spool. As a result, the smooth operation of the spool is hindered and a valve stick of the control valve device is apt to occur.

When the power roller is squeezed between the input disk and the output disk during the shift control, the power roller receives the thrust force in the direction pushed out from between the input and output disks and supports the power roller. Since the trunnion is deformed, the sliding portion of the servo piston provided in the cylinder body may be inclined in a direction deviated from the swing axis direction and the cylinder body may be deformed. Therefore, when the cylinder body and the valve body are integrally connected, the deformation of the cylinder body acts on the valve body, and the valve stick of the control valve device is likely to occur.

As a means for solving this problem, for example, there is a prior art disclosed in Japanese Patent Laid-Open No. 4-29659. In this prior art, a cylinder body accommodating a servo piston (piston) of a fluid pressure cylinder device (hydraulic cylinder device) and a valve body accommodating a spool of a control valve device are separately configured, and both are directly coupled to each other. Even if the cylinder body is deformed by the reaction force of the fluid pressure acting on the servo piston, the reaction force is not transmitted to the valve body, which is a separate body from the cylinder body. Since the spool hole of the body is not deformed, the valve stick of the control valve device can be reliably prevented.

[0006]

However, when the cylinder body and the valve body are separately fixed to the casing as described above, the length of the fluid passage for supplying the control fluid from the valve body to the fluid chamber of the cylinder body is newly increased. Occurs as a serious problem.

That is, for example, in the toroidal continuously variable transmission disclosed in Japanese Patent Laid-Open No. 5-39833, the cylinder body and the valve body have separate structures, and in FIG. 4 of this publication, control is performed from the valve body to the fluid chamber of the cylinder body. A fluid passage for supplying a fluid is specifically shown. According to this, a fluid passage (in the publication, referred to as an oil passage) is provided on an inner wall of a casing (in this publication, referred to as a transmission case).
The control fluid is supplied from the valve body to the fluid chamber of the cylinder body through this fluid passage. As described above, when the fluid passage is formed in the casing, the fluid passage becomes long. Therefore, at a low temperature where the fluid viscosity becomes high, there is a possibility that the shift stability and the shift responsiveness deteriorate due to the response delay of the pressure of the control fluid.

The present invention has been made in view of the above circumstances, and the shift stability is achieved even if the cylinder body and the valve body are separate bodies in order to prevent a valve stick of the spool housed in the valve body. An object of the present invention is to provide a friction wheel type continuously variable transmission that does not reduce the shift responsiveness.

[0009]

For these purposes, a friction wheel type continuously variable transmission according to claim 1 is provided with an input disk,
An output disc, a plurality of power rollers sandwiched between opposing surfaces of both discs and capable of tilting, the power roller being rotatable about a power roller rotation axis, and a swing axis direction orthogonal to the power roller rotation axis. A trunnion that freely strokes, a servo piston that strokes the trunnion in the swing axis direction, a cylinder body that houses the servo piston, and a supply / discharge control of the working fluid pressure to stroke the servo piston. In a friction wheel type continuously variable transmission including a valve body that accommodates a spool, the cylinder body and the valve body are fixed to the device casing without being in close contact with each other and are formed on the lower surface of the cylinder body. Working fluid receiving port and the working fluid receiving port A working fluid supply port formed on the upper surface of the valve body, and connected via an elastic deformable hydraulic fluid delivery tube.

A friction wheel type continuously variable transmission according to a second aspect of the present invention includes an input disk, an output disk, a plurality of power rollers that are tilted by being sandwiched between opposing surfaces of both disks, and the power rollers. A trunnion rotatably supported around the power roller rotation axis and rotatably supported in a swing axis direction orthogonal to the power roller rotation axis, a servo piston that strokes the trunnion in the swing axis direction, and the servo piston. A friction wheel type continuously variable transmission including a cylinder body for accommodating and a valve body for accommodating a spool for performing supply / discharge control of a working fluid pressure for causing a stroke of the servo piston, wherein the cylinder body and the valve body While fixing the and to the device casing without sticking to each other,
A body internal flow path communicating with another piston fluid chamber is formed near the first piston fluid chamber accommodating the servo piston of the cylinder body, and the first piston fluid chamber is formed on the lower surface of the cylinder body. A first working fluid receiving port that communicates from immediately below and a second working fluid receiving port that communicates from immediately below the body internal flow path are formed at positions close to each other, and these first and second working fluid receiving ports are formed. On the other hand, the working fluid port is formed on the upper surface of the valve body so as to closely face and oppose from below, one end is connected to the working fluid port, and the other end is the first and second working fluid receiving ports. An elastically deformable working fluid delivery pipe is arranged so as to be connected to both.

Furthermore, the invention according to claim 3 is the same as claim 1.
Or the friction wheel type continuously variable transmission according to 2, wherein the working fluid delivery pipe is constituted by a lip-type seal member having an axial cross section of a V shape or a U shape, and the radial direction of the lip type seal member. Expansion was regulated by a regulating portion provided on the lower surface of the cylinder body or the upper surface of the valve body.

[0012]

According to the friction wheel type continuously variable transmission of the first aspect, even if the cylinder body is deformed by the reaction force of the working fluid pressure supplied to the piston fluid chamber in the cylinder body during the shift control. Alternatively, even if the cylinder body is deformed by the thrust force being applied to the power roller by the power roller being clamped by the input disk and the output disk, the valve body is arranged inside the device casing without being in close contact with the cylinder body. In addition, since the working fluid delivery pipe connecting between the working fluid supply port and the working fluid receiving port absorbs the deformation of the cylinder body due to its own elastic deformation, the valve can be removed from the spool housed in the valve body. Does not have a bad effect such as sticks.

Further, according to the present invention, a working fluid transfer pipe is connected between the working fluid receiving port of the cylinder body and the working fluid supplying port of the valve body which are close to each other, so that the cylinder body and the valve body are connected to each other. Since the fluid path of the working fluid is formed, the length of the fluid path is significantly shortened compared with the case where a long fluid path is formed in the casing as in the conventional device, and the working fluid pressure due to the viscosity change of the working fluid at low temperature is It is possible to improve gear shift stability and gear shift responsiveness without causing a response delay or the like.

Further, according to the friction type continuously variable transmission of the second aspect, the same effect as that of the first aspect can be obtained, and the first working fluid receiving port is formed immediately below the first piston fluid chamber. Therefore, the fluid path for receiving the working fluid from the working fluid supply port can be shortened. Also,
A second working fluid receiving port, which communicates with another piston fluid chamber via a body internal flow path, is formed in the immediate vicinity of the first working fluid receiving port, and the first and second working fluids are supplied from the working fluid supply port. Since the working fluid is delivered to the receiving port at the same time via the working fluid delivery pipe, the structure is such that the fluid path length is further shortened, and the shift stability and the shift responsiveness can be enhanced.

Further, according to the friction type continuously variable transmission of the third aspect, the lip seal member as the working fluid delivery pipe is provided with a high pressure working fluid from the working fluid supply port of the cylinder body. While the expansion in the radial direction is restricted by the restricting portion provided on the lower surface or the upper surface of the valve body, the axial length becomes longer and elastically deforms so that the V-shaped or U-shaped cross section is corrected, and the upper surface operates. Since the lower surface is in close contact with the periphery of the fluid receiving port and the lower surface is in close contact with the periphery of the working fluid supply port, it is possible to reliably prevent leakage of the working fluid to the outside even with a member having a simple structure. it can.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows the internal structure of a toroidal-type continuously variable automatic transmission according to the present invention.

An input shaft 2 connected to a rotary drive source such as an engine (not shown) is provided in the transmission case 1.
And a rotary shaft 3 concentrically connected to the right side of the input shaft 2, and an oil pump 5 attached to the end of the transmission case 1 via a bolt 4 on the input shaft 2 side. Adjacent to the right side of the oil pump 5, a forward / reverse switching mechanism 9 for switching forward / backward to the first and second toroidal speed change mechanisms 10 and 11 via a planetary gear mechanism 8 by operating a forward clutch 6 and a reverse clutch 7. The first toroidal speed change mechanism 10 is located near the rotary drive source, and the second toroidal speed change mechanism 11 is located farther from the rotary drive source on the rotary shaft 3 side. ing.

A sun gear 13 which is rotatably supported on the input shaft 2 through a needle bearing 12 and constitutes a planetary gear mechanism 8 of a forward / reverse switching mechanism 9 is provided between the shafts 2 and 3, and the sun gear 13 is provided on the sun gear 13. Loading cam 14 which is engaged with the fixed claw portion 13a and is rotatably supported by the rotating shaft 3.
And an input disk 17 connected to the loading cam 14 via an engagement roller and supported on the rotating shaft 3 via a ball spline 16. The rotating force from the input shaft 2 is transmitted to the rotating shaft 3 via the forward / reverse switching mechanism 9 from the claw portion 13a of the sun gear 13 through the loading cam 14, the engaging roller 15, the input disk 17, and the ball spline 16 in sequence. It has become so.

Loading cam 14 and input disk 1
Wave-shaped cam surfaces with which the engagement roller 15 engages are formed on the opposing surfaces of No. 7 respectively .

The first toroidal speed change mechanism 10 has an input disk 17 having a toroidal surface 17a formed on a surface thereof separated from the engagement roller 15 and a toroidal surface 18a formed on an opposite surface of the input disk 17 for rotation. An output disk 18 rotatably supported on the shaft 3 and both disks 17, 1
A pair of power rollers 44 contacting tiltably with respect to both discs in a toroidal groove formed by the toroidal surfaces 17a, 18a of No. 8, and these power rollers 44 are rotatable about the power roller rotation axis O _2. A trunnion 46 that supports and makes a stroke in a swing axis O ₃ direction orthogonal to the power roller rotation axis O ₂ , and a trunnion 4.
6 is operated to change the radial contact position of the power roller 44 with respect to the input disk 17 and the output disk 18, thereby continuously changing the rotational speed ratio between the input disk 17 and the output disk 18, that is, the gear ratio. And a hydraulic servo mechanism.

The second toroidal speed change mechanism 11 has an input disk 19, an output disk 20, a power roller 44, a trunnion 46 and a hydraulic servo mechanism like the first toroidal speed change mechanism 10, but has a ball spline 21 on the rotary shaft 3. The input disk 19 externally fitted through is arranged on the side far from the first toroidal transmission mechanism 10, and the output disk 20 is arranged on the side close to the first toroidal transmission mechanism 10.

Shaft cylinder portions 18b and 20b are provided on the back surfaces of the output disks 18 and 20 facing each other, and an output gear 22 is spline-coupled to the shaft cylinder portions 18b and 20b. The output gear 22 is provided with a bearing 24 in a gear housing 23 fixed to the inner peripheral wall of the transmission case 1.
Is supported through. The output gear 22 meshes with a counter gear 25, and the counter gear 25 is rotatably supported by a gear housing 23 via a bearing 26. At the center of the counter gear 25, a counter shaft 27 is splined at one end so as to rotate integrally, and the other end of the canter shaft 27 is rotatably supported by the transmission case 1 via a bearing . . Here, the output that has a predetermined gear ratio by the above-described tilting operation of the friction roller is output by the output gear 2.
The two are combined and transmitted to the output shaft (not shown) via the counter gear 25, the counter shaft 27, and the gear train 28 in order. Further, the forward / reverse switching of the output shaft is performed by the forward / reverse switching mechanism 9 switching the forward / backward movement with respect to the first and second toroidal transmission mechanisms 10 and 11.

Next, FIG. 2 shows a trunnion 46 that rotatably supports the power roller 44, and a hydraulic servo mechanism that displaces the trunnion 46 so as to offset it toward the swing axis O ₃ direction in accordance with a gear ratio command. Is shown.

A shaft insertion hole 46a having a circular cross section is formed at a lower portion of the trunnion 46 to which the lower link 52 is connected.
Is formed downward. This shaft fitting hole 4
The trunnion shaft 70 is fitted into the 6a from below, and the upper end of the trunnion shaft 70 is bar-tethered by the pin 56.

Further, a wire pulley is provided around the reduced diameter portion 46c formed on the outer periphery of the lower portion of the shaft fitting hole 46a so that the wire 72 is hung for synchronizing the tilt rotation between the power rollers of the first and second toroidal transmission mechanisms 10 and 11. 74 is externally fitted. Further, on the trunnion shaft 70, a pulley disengagement washer 76 is externally fitted at a lower position of the wire pulley 74.

A cylindrical piston boss portion 78c of the servo piston 78 and a recess cam 66 are provided below the pulley slip-out prevention washer 76 and the trunnion shaft 70.
The nut 82 is screwed onto the male screw formed on the lower end of the trunnion shaft 70 and the upper member is tightened up, so that the servo piston 78 moves to the trunnion shaft 7.
It is integrated with the trunnion 46 through 0.

Here, the reference numeral 85 indicates a hydraulic cylinder device, which is composed of the servo piston 78 and a cylinder body 84 for accommodating the servo piston 78. The cylinder body 84 has an insertion hole 61 that opens in the direction of the swing axis O ₃ and a piston oil chamber 63.
4a and a lower cylinder body 84b that has an insertion hole coaxial with the insertion hole 61 and closes the upper cylinder body 84a from the lower side. The bolt inserted from the lower cylinder body 84b side is It is fixed to the transmission case 1 by being screwed into the transmission case 1 through the lower cylinder body 84b and the upper cylinder body 84a. Note that FIG.
The piston oil chamber 63 on the right side of the first piston is a first oil chamber 63a above the servo piston 78 and a second oil chamber 63a below the servo piston 78.
The oil chamber 63b is defined, and the piston oil chamber 63 on the left side of FIG.
c, the second oil chamber 63d is defined below the servo piston 78.

Further, reference numeral 86 is a valve body, and a control valve device 87 is constituted by a spool (not shown) movably arranged in the valve body 86, and the valve is moved by the movement of the spool. By switching the fluid passage in the valve of the body 86, the hydraulic cylinder device 8
5, the hydraulic pressure supply / discharge control is performed.

The valve body 86 is composed of an upper valve body 86a and a lower valve body 86b, and a bolt inserted from the lower valve body 86b side passes through the lower cylinder body 86b and the upper cylinder body 86a. By being screwed into the transmission case 1 at the lower position of the cylinder body 84, it is fixed separately from the cylinder body 84. This allows
The valve body 86 and the cylinder body 84 are arranged in a vertically stacked state without being in close contact with each other.

In the present embodiment, the valve body 8
A plurality of oil passages 88 for supplying the hydraulic oil generated in 6 to each piston oil chamber 63 in the cylinder body 80 are provided above and below the valve body 86 and the cylinder body 84.

These oil passages 88 are, as shown in FIG.
Hydraulic oil supply port 9 opened on the upper surface of the valve body 86
0 and the hydraulic oil supply port 90 from the lower surface of the cylinder body 84.
And a lip seal member 94 that communicates the hydraulic oil supply port 90 and the hydraulic oil receiving port 92 while maintaining liquid tightness.

The hydraulic oil supply port 90 is provided in the valve body 8
6 communicates with the hydraulic oil supply port, and hydraulic oil of a predetermined pressure is supplied when the spool of the shift control valve moves to a predetermined position. Around the hydraulic oil supply port 90, an annular projecting portion 96 that projects toward the lower surface of the cylinder body 84 is formed. Further, the hydraulic oil receiving port 92 communicates with a predetermined piston oil chamber 63 via a body internal oil passage 93 formed in the cylinder body 84.

The lip seal member 94 is a cylindrical elastic member made of synthetic resin having a V-shaped or U-shaped cross section in the axial direction, and its upper surface has a hydraulic oil receiving port 92.
And the lower surface thereof is in contact with the periphery of the hydraulic oil supply port 90 and is axially pressed. Also,
The lower portion of the lip seal member 94 is inserted into the annular protrusion 96 of the valve body 86, and the outer diameter of the lip seal member 94 is enlarged by the passage of high-pressure hydraulic oil, and the lip seal member 94 is orthogonal to the axial direction. It prevents it from shifting in the direction of.

Then, the hydraulic oil generated in the valve body 86 is supplied to the cylinder body 84 side through the oil passage 88, and the hydraulic pressure in the second oil chamber 63b on the right side and the first oil chamber 63c on the left side is increased. Then, when the pressures of the first oil chamber 63a on the right side and the second oil chamber 63d on the left side are lowered to generate a differential pressure,
The left and right servo pistons 78 stroke in the swing axis O3 direction, for example, the tilting operation of the power roller 44 is performed so that the actual speed ratio shifts to the High side, and conversely, the first oil chamber 63a on the right side and the first oil chamber 63a on the left side. When the hydraulic pressure in the second oil chamber 63d is increased and the pressures in the second oil chamber 63b on the right side and the first oil chamber 63c on the left side are reduced to generate a differential pressure, the actual speed ratio shifts to the Low side. The tilting motion is performed.

Next, the function and effect of this embodiment will be described. During the shift control, the cylinder body 84 may be deformed by the reaction force of the hydraulic pressure supplied to each piston oil chamber 63, but the cylinder body 84 may be deformed between the hydraulic oil supply port 90 and the hydraulic oil receiving port 92 of the oil passage 88. The installed lip seal member 94
Since the deformation of the cylinder body 84 is absorbed by the elastic deformation, the valve body 86 is not adversely affected by deformation and the valve stick does not occur.

When the power roller 44 is pinched by the input / output disks 17 and 18 during the shift control, the power roller 44 receives a thrust force in the direction of being pushed out from between the input / output disks 17 and 18, which causes , Power roller 4
The trunnion 46 supporting 4 receives the thrust force and deforms with the position connected to the upper link 50 and the lower link 52 as a fulcrum. Then, the trunnion shaft 70 and the piston boss portion 78c are also inclined in a direction deviated from the swing axis O ₃ direction, and the cylinder body 84 is deformed. Also at this time, the lip seal member 94 arranged between the hydraulic oil supply port 90 and the hydraulic oil receiving port 92 of the oil passage 88 absorbs the deformation of the cylinder body 84 due to its own elastic deformation. The valve stick does not occur without adversely affecting 86 such as deformation.

Since the oil passage 88 of the present embodiment has a significantly shorter oil passage length as compared with the case where a long oil passage is formed in the casing as in the conventional apparatus, the oil passage 88 is affected by the viscosity change of the operating oil at low temperature. Since the response delay of the hydraulic pressure does not occur, the shift stability and the shift response can be improved.

The outer diameter of the lip seal member 94 forming the oil passage 88 is restricted by the projection 96 of the valve body 86, and high-pressure hydraulic oil is supplied from the hydraulic oil supply port 90. Then, the V-shaped or U-shaped cross-section is corrected to elastically deform while the axial length is increased, the upper surface is further in close contact with the periphery of the hydraulic oil receiving port 92, and the lower surface is the hydraulic oil supply port. Since the state of being closer to the periphery of 90 is achieved, it is possible to reliably prevent the hydraulic oil from leaking to the outside.

Next, FIG. 4 shows a valve body 8
6 and the second oil passage provided between the upper and lower sides of the cylinder body 84.
1 shows an embodiment. The oil passage 97 of this embodiment is
A body internal oil passage 95 communicating with another piston oil chamber (not shown) is formed near the piston oil chamber 63 of the upper cylinder body 84a, and the piston oil chamber 63 is formed in the lower cylinder body 84b. A first oil hole 98a communicating with the second oil hole 98 communicating with the body internal oil passage 95.
b are formed at positions close to each other. In addition, the upper cylinder body 84 located on the outer periphery of the piston oil chamber 63
An annular groove is formed on the lower surface of a, and an O-ring 99 is mounted in this groove. The first oil hole 9
8a is referred to as a first hydraulic oil receiving port 98a, and a second oil hole 98
b is referred to as a second hydraulic oil receiving port 98b.

A hydraulic oil supply port 100 is formed in the upper portion of the valve body 86 so as to be located below the first and second hydraulic oil receiving ports 98a and 98b, and the hydraulic oil supply port 100 A circular recess 102 having a larger diameter than the position where the first and second hydraulic oil receiving ports 98a and 98b are formed is formed around the periphery.

The hydraulic oil supply port 100 of the valve body 86 and the first and second hydraulic oil receiving ports 98a and 98b of the cylinder body 84 are communicated with each other between the upper and lower sides of the cylinder body 84 and the valve body 86. A lip seal member 104 is provided.

The lip seal member 104 is also a cylindrical elastic member made of synthetic resin having a V-shaped or U-shaped cross section in the axial direction, and its upper surface has first and second hydraulic oil receiving ports 98a, The lower surface of the cylinder body 84 is arranged so as to surround 98b at the same time, and the lower surface is arranged in contact with the periphery of the hydraulic oil supply port 100 and pressed in the axial direction. Further, the lower portion of the lip seal member 104 is inserted into the circular recess 102 of the valve body 86, and the outer diameter of the lip seal member 104 is enlarged by the passage of high-pressure hydraulic oil, and the lip seal member 104 is orthogonal to the axial direction. It prevents it from shifting in the direction.

Here, what is shown in FIG. 5 is the first and the second.
1 schematically shows an example of a servo mechanism of the toroidal speed change mechanisms 10 and 11, that is, an example of a servo piston 78 that tilts the power roller 44 and an oil passage that supplies hydraulic oil to the piston oil chamber 63. The oil passage 97 is provided, for example, at a position for supplying the upshift shift hydraulic pressure P _U of the valve body 86 and at a position for supplying the downshift shift hydraulic pressure P _D.

Then, the valve from the valve body 86
Shift speed hydraulic P_UBecomes higher, and the downshift gearshift hydraulic pressure P
_D, The servo piston 78 moves in the direction of the solid arrow.
And the power roller 44 tilts to the High side.
Upshift gearshift hydraulic pressure P _ULowers and downshifts
Shift hydraulic pressure P_DBecomes higher, each servo piston 78 breaks.
Stroke in the direction of the arrow and the power roller 44 goes low.
The vehicle is tilted to the side and stepless speed change control is performed.

According to the above construction, even if the cylinder body 84 is deformed by the reaction force of the working oil pressure supplied to the piston oil chamber 63 during the shift control, or the power roller 44 is squeezed between the input / output disks 17 and 18. Even if the cylinder body 84 is deformed by receiving the thrust force, the hydraulic oil supply port 100 and the first and second hydraulic oil receiving ports 98a,
Since the lip seal member 104 disposed between 98b absorbs the deformation of the cylinder body 84 by elastic deformation, the valve body 86 is not adversely affected by deformation and the valve stick does not occur.

Further, the lip seal member 104 is constrained from expanding in outer diameter by the circular recess 102 of the valve body 86, and when the high-pressure hydraulic oil is supplied from the hydraulic oil supply port 100, it has a V-shaped cross section, Alternatively, the U-shape is corrected so that the axial length becomes longer and elastically deformed, the upper surface further surrounds the first and second hydraulic oil receiving ports 98a and 98b, and the lower surface surrounds the hydraulic oil supply port 100. Since it is in a state in which the working oil is further closely contacted with, it is possible to surely prevent the hydraulic oil from leaking to the outside.

An O-ring 99 is mounted so as to surround the oil chamber 63 between the contact surfaces of the upper cylinder body 84a and the lower cylinder body 84b which form the cylinder body 84. The liquid tight sealing property can be sufficiently maintained.

In the present embodiment, the first hydraulic oil receiving port 98a is formed immediately below the oil chamber 63 to form the hydraulic oil supply port 1.
The hydraulic oil passage from 00 is short. Also, the first
A second hydraulic oil receiving port 98b is formed in the immediate vicinity of the hydraulic oil receiving port 98b, and the first and second hydraulic oil receiving ports 100 are provided.
Since the lip seal member 104 is connected so that the hydraulic oil can be supplied to the hydraulic oil receiving ports 98a and 98b at the same time, the oil passage length is shorter than that of the first embodiment. . As a result, even if the viscosity of the hydraulic oil changes at low temperatures, the shift stability and the shift responsiveness can be further improved.

[Brief description of drawings]

FIG. 1 is a sectional view showing a toroidal type continuously variable transmission according to the present invention.

FIG. 2 is a sectional view showing a trunnion and a hydraulic servo mechanism according to the present invention.

FIG. 3 is a sectional view of an essential part showing the oil passage structure of the first embodiment between the cylinder body and the valve body according to the present invention.

FIG. 4 is a cross-sectional view of essential parts showing an oil passage structure according to a second embodiment between a cylinder body and a valve body.

FIG. 5 is a schematic diagram showing an oil passage structure for the first and second toroidal transmission mechanisms according to the present invention.

[Explanation of symbols]

1 Transmission Case (Device Casing) 10 First Toroidal Speed Change Mechanism 11 Second Toroidal Speed Change Mechanism 17, 19 Input Disc 18, 20 Output Disc 44 Power Roller 46 Trunnion 63 Piston Oil Chamber (First Piston Oil Chamber) 78 Servo Piston 84 Cylinder Body 84a Upper cylinder body 84b Lower cylinder body 85 Hydraulic cylinder device 86 Valve body 86a Upper valve body 86b Lower valve body 87 Control valve device 90, 100 Hydraulic oil supply port (Operating fluid supply port) 92 Hydraulic oil receiving port (Operating fluid receiving port) Mouth) 94, 104 Lip seal member (lip type seal member, working fluid delivery pipe) 95 Body internal oil passage (body inner passage) 96 Projection part (regulating portion) 98a First working oil receiving port (first working fluid receiving) Mouth) 98b Second hydraulic oil receiving port (second working fluid receiving port) 102 Circular recess (regulating part) O ₂ Power roller rotation axis O ₃ Swing axis

─────────────────────────────────────────────────── ─── Continuation of the front page (56) Reference JP-A-58-194535 (JP, A) JP-A-9-250618 (JP, A) JP-A-9-292000 (JP, A) Actual development Sho-62- 202564 (JP, U) Actual Kaihei 6-69579 (JP, U) Actual Kohei 3-39650 (JP, Y2) Actual Kohei 4-16001 (JP, Y2) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16H 15 / 38,61 / 00 F15B 11/00 F16L 11 / 04,11 / 06,11 / 11

Claims (3)

(57) [Claims] 1. An input disk, an output disk, a plurality of power rollers sandwiched between opposing surfaces of both disks and capable of tilting, the power roller being rotatable about a power roller rotation axis, and the power roller. A trunnion that freely strokes in the swing axis direction orthogonal to the rotation axis, a servo piston that strokes the trunnion in the swing axis direction, a cylinder body that houses the servo piston, and a stroke for the servo piston. In a friction vehicle type continuously variable transmission including a valve body accommodating a spool for performing supply / discharge control of a working fluid pressure, the cylinder body and the valve body are fixed to an apparatus casing without being in close contact with each other. And a working fluid receiving port formed on the lower surface of the cylinder body. A working fluid supply port formed on the upper surface of the valve body in proximity to the working fluid inlet, a friction wheel continuously variable transmission, characterized in that connected via an elastic deformable hydraulic fluid delivery tube. 2. An input disk, an output disk, a plurality of power rollers sandwiched between opposing surfaces of both disks and capable of tilting, the power roller being rotatable about a power roller rotation axis, and the power roller. A trunnion that freely strokes in the swing axis direction orthogonal to the rotation axis, a servo piston that strokes the trunnion in the swing axis direction, a cylinder body that houses the servo piston, and a stroke for the servo piston. In a friction vehicle type continuously variable transmission including a valve body accommodating a spool for performing supply / discharge control of a working fluid pressure, the cylinder body and the valve body are fixed to an apparatus casing without being in close contact with each other. On the other hand, a first housing for accommodating the servo piston of the cylinder body A body internal flow path that communicates with another piston fluid chamber near the Ston fluid chamber, and a first working fluid receiving port that communicates with the lower surface of the cylinder body from directly below the first piston fluid chamber; A second working fluid receiving port that communicates from immediately below the internal flow path of the body is formed at a position close to each other, and the valve is provided so as to face the first and second working fluid receiving ports from below in close proximity. The working fluid port is formed on the upper surface of the body, one end is connected to the working fluid port, and the other end is the first and second working fluid ports.
A friction wheel type continuously variable transmission characterized in that an elastically deformable working fluid delivery pipe is arranged so as to be connected to both working fluid receiving ports. 3. The working fluid delivery pipe is constituted by a lip type seal member having a V-shaped or U-shaped cross section in the axial direction, and expansion of the lip type seal member in the radial direction of the cylinder body is performed. 3. The friction wheel type continuously variable transmission according to claim 1, wherein the frictional wheel type continuously variable transmission is regulated by a regulating portion provided on a lower surface or an upper surface of the valve body.