JP2000035109A - Lubricating device for continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve miniaturization of an oil pump while the supply of lubricating oil to a forward-reverse switching device in a continuously variable transmission is sufficiently ensured. SOLUTION: In a lubricating device of a continuously variable transmission provided with a primary pulley and a secondary pulley, the distance between the pulleys is variable, and a driving belt laid over between these pulleys, oil pressure for varying the distance between the pulleys is supplied from an oil pump 47 driven by a pump-side case 3 of a torque converter 2. Oil leaking from the oil pump 47 is dropped-supplied to a forward-reverse switching device 11 through a guide oil passage 91 and a guide pipe 92. Like the case of the idle running of an engine, even when sufficient quantity of discharge from the oil pump 47 is not ensured, lubrication of the forward-reverse switching device 11 can thus be performed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubricating device for a continuously variable transmission for supplying lubricating oil to a forward / reverse switching device assembled in a belt type continuously variable transmission for a vehicle.

[0002]

2. Description of the Related Art As a continuously variable transmission for vehicles, a metal drive belt is mounted between a primary pulley provided on a drive shaft and a secondary pulley provided on a driven shaft, and the diameter of the pulley is reduced by hydraulic pressure. In some cases, the rotation speed of the driven shaft is changed steplessly by changing the rotation speed. In such a continuously variable transmission, between the output shaft driven by the engine and the drive shaft, the rotation of the output shaft is switched between the forward direction and the reverse direction and transmitted to the drive shaft. Is provided with a forward / reverse switching device.

The forward / reverse switching device has components such as a sun gear, a planetary pinion gear, and a bearing, and supplies lubricating oil to these components. For example, Japanese Unexamined Patent Publication No. 7-259944 discloses that an orifice is provided in an oil passage formed in communication with an oil pump, and lubricating oil is guided to a central shaft portion of the forward / reverse switching device through the orifice, and the periphery of the shaft is provided. Discloses an oil passage structure for forcibly lubricating components such as a planetary pinion gear.

[0004]

In such a lubrication system, the vehicle is in a running state, and if the oil pump discharges sufficiently, the amount of oil supplied to the lubricating oil passage is also sufficient. The lubricating oil is sufficiently supplied to each part by the centrifugal force applied to the lubricating oil by the rotation of the operating member constituting the forward / reverse switching device. However, in the idling operation, the discharge amount of the oil pump is considerably reduced. Even in this state, it is necessary to always maintain the functional parts such as the pulley operating cylinder and the torque converter which constitute the continuously variable transmission. For this reason, lubricating oil flow balance,
That is, a sufficient amount of lubrication for the amount of discharge from the oil pump cannot be secured.

[0005] It is desirable to reduce the size of the oil pump as much as possible in consideration of the improvement of fuel efficiency and the like. However, since the oil pressure from the oil pump is required to be as high as about 50 kg / cm ² , the size of the oil pump is reduced. Then, the lubricating oil becomes insufficient at the time of idling, and there is a limit to the size reduction of the oil pump.

SUMMARY OF THE INVENTION It is an object of the present invention to ensure a sufficient supply of lubricating oil to a forward / reverse switching device in a continuously variable transmission.
An object of the present invention is to reduce the size of an oil pump.

[0007]

According to the present invention, there is provided a lubricating apparatus for a continuously variable transmission, wherein a drive belt is stretched between a primary pulley mounted on a drive shaft and a driven shaft and mounted on the driven shaft. A lubricating device for a continuously variable transmission, comprising: a secondary pulley that is driven by the engine; and a forward / reverse switching device that switches the rotation of an output shaft that is rotationally driven by an engine to one of a forward direction and a reverse direction and transmits the rotation to the drive shaft. And lubricating oil guide means for guiding oil leaked from an oil pump rotationally driven by the engine to the forward / reverse switching device.

In the present invention, the oil leaked from the oil pump is guided to the forward / reverse switching device, so that the hydraulic pressure for changing the pulley width of each of the primary pulley and the secondary pulley is changed as in an idling state. Even when it is not possible to secure a sufficient discharge oil amount from the oil pump to be generated, lubrication of the forward / reverse switching device can be performed using the leak oil. Thus, even when the oil pump is downsized, lubrication during idling can be reliably performed.

[0009]

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

FIG. 1 is a skeleton diagram showing a drive system of a continuously variable transmission for a vehicle using a belt. A crankshaft 1 driven by an engine (not shown) is driven by a pump side case 3 of a torque converter 2. A turbine runner 5 that is directly connected via a plate 4 and that faces the pump impeller 3 a provided in the pump side case 3.
Are directly connected to the turbine shaft, that is, the output shaft 6. A stator 7 is arranged between the pump impeller 3 a and the turbine runner 5, and is supported by a one-way clutch 8. A lock-up clutch 9 is directly connected to the output shaft 6 so as to be able to engage and disengage with the torque converter case on the drive plate 4 side. Engine power is transmitted to the output shaft 6 via the torque converter 2 or the lock-up clutch 9. Is transmitted.

The output shaft 6 is transmitted to a drive shaft 13 of a continuously variable transmission 12 via a forward / reverse switching device 11. A primary pulley 14 is provided on the drive shaft 13, and a movable sheave 14 a on the primary side is opposed to the primary pulley 14.
Are mounted slidably in the axial direction on the drive shaft 13 by a ball spline or the like, and the primary pulley 14 has a variable pulley interval. A secondary pulley 16 is provided on a driven shaft 15 arranged in parallel with the drive shaft 13, and a movable sheave 16 a on the secondary side is opposed to the driven pulley 15 in an axial direction similar to the movable sheave 14 a. And the secondary pulley 16 has a variable pulley spacing.

A drive belt 17 is stretched between the primary pulley 14 and the secondary pulley 16, and by changing the groove width of both pulleys 14, 16,
By changing the ratio of the winding diameter to each of the pulleys 14 and 16, the rotation speed of the driven shaft 15 is continuously variable.

In order to change the groove width of the primary pulley 14, a cylinder 19 forming an oil chamber 18 with the movable sheave 14a is attached to the drive shaft 13, and in order to change the groove width of the secondary pulley 16, Movable sheave 16
and a cylinder 22 forming an oil chamber 21 with the driven shaft 1
5.

The driven shaft 15 is connected to an intermediate shaft 25 via gears 23 and 24. A gear 26 mounted on the intermediate shaft 25 meshes with a final gear 28 of a differential device 27 and is connected to the differential device 27. Wheels 31a and 31b are attached to the axles 29a and 29b. In the case of a front wheel drive vehicle, the wheels 31
a and 31b are front wheels.

The forward / reverse switching device 11 includes an annular clutch cylinder 32 having a forward clutch drum portion fixed to the output shaft 6 and a clutch hub 33 fixed to the drive shaft 13 with a spline portion. With clutch cylinder 3
2 and the clutch hub 3
3, a multi-plate type forward clutch 34 is provided, and a hydraulic piston 35 for operating the forward clutch 34 is incorporated in the clutch cylinder 32. Therefore, the oil chamber 32 in the clutch cylinder 32
When the forward clutch 34 is connected by supplying hydraulic pressure to the drive shaft 13a, the rotation of the output shaft 6 is transmitted to the drive shaft 13 through the clutch hub 33 and the clutch cylinder 32, and the drive shaft 13 is the same as the output shaft 6. Rotate in the forward direction.

A ring gear 37 is rotatable outside a sun gear 36 fixed to the drive shaft 13 via a spline portion, and a carrier 39 fixed to the clutch cylinder 32 meshes with the carrier 39 to form a pair. Planetary pinion gears 41 and 42 are rotatably mounted, one planetary pinion gear 41 meshes with a sun gear 36, and the other planetary pinion gear 42 is a ring gear 3.
7, and these gears constitute a double pinion type planetary gear.

Each planetary pinion gear 41,
Although 42 are shown separately in FIG. 1 for the sake of drawing convenience, they are meshed in pairs, and a plurality of planetary pinion gears 41 and 42 may be provided. A multi-plate reverse brake 43 is provided between the ring gear 37 and the case 10. A hydraulic piston 44 for operating the reverse brake 43 is incorporated in a brake cylinder 45 formed in the case 10. ing.

Therefore, when the forward clutch 34 is released, the oil chamber 45 in the brake cylinder 45 is released.
When the reverse brake 43 is brought into the braking state by supplying the hydraulic pressure to the a, the ring gear 37 is fixed to the case 10, so that the rotation of the carrier 39 integrated with the output shaft 6 becomes a pair of planetary The power is transmitted to the sun gear 36 via the pinion gears 41 and 42, and the drive shaft 13 rotates in the reverse rotation direction opposite to the output shaft 6. Thus, the reverse brake 43 is disposed on the primary pulley 14 side, and the forward clutch 34 is disposed on the torque converter 2 side.
To reduce the overall length of the transmission, a brake cylinder 45 is disposed outside a bearing 46 that supports the shaft of the primary pulley 14.

In order to operate hydraulic operating devices such as the brake cylinder 45 and the clutch cylinder 32, the case 1
An oil pump 47 as a hydraulic pressure source is disposed in the oil pump 0. The oil pump 47 is driven by the crankshaft 1 via the drive plate 4 and the sleeve of the pump side case 3 of the torque converter 2. I have.

FIG. 2 is a diagram showing a hydraulic circuit for controlling the operation of the drive system shown in FIG.
Has a rotor driven by the engine and a pump housing on the case 10 side, and has two discharge ports 48a, 48b.
And two suction ports 49a and 49b, and an inflow-side oil passage 52 connected to an oil pan 51 is connected to the suction ports 49a and 49b.

The discharge-side oil passages 53a and 53b connected to the respective discharge ports 48a and 48b join the line pressure oil passage 54, and the line pressure oil passage 54 operates the movable sheave 16a on the secondary pulley 16 side. The transmission control valve 55 and the line pressure control valve 56
Line pressure port. These control valves 5
Reference numerals 5 and 56 denote proportional electromagnetic relief valves, each having a solenoid operated by electric power from the control unit 57.

The line pressure control valve 56 controls the pressure of the line pressure oil passage 54 corresponding to the current supplied from the control unit 57 to the solenoid to control the line pressure supplied to the oil chamber 21 of the secondary pulley 16, ie, the secondary pressure. The pressure Ps is controlled. A lubrication pressure oil passage 58 is connected to a lubrication port of the line pressure control valve 56, and a lubrication pressure Pc for lubrication lower than the line pressure is set by the line pressure control valve 56.

The primary port of the transmission control valve 55 is connected to a primary oil passage 59 communicating with the oil chamber 18 for operating the movable sheave 14a on the primary pulley 14 side. The transmission control valve 55 is connected to the solenoid by the control unit 57 from the control unit 57. The primary pressure Pp corresponding to the supplied current is applied to the oil chamber 1
8 Since this primary pressure is set by adjusting the line pressure, it does not exceed the line pressure. However, oil chamber 1
8 is set larger than the cross-sectional area of the oil chamber 21, the force for pinching the belt can be made larger than that of the secondary pulley.

When the engine output such as climbing a hill or sudden acceleration is large, the line pressure is increased to prevent the belt 17 from slipping, and when the engine output is small, the line pressure is reduced to improve the loss and transmission efficiency of the oil pump 47. Is achieved. One discharge-side oil passage 53b of the oil pump 47
And the discharge-side oil passage 53b is connected to the inflow-side oil passage 5
A switching valve 61 is provided in these oil passages so as to be operated at a position where the lubricating oil passage 58 and the control port of the switching valve 61 are connected.
The operation is performed by an electromagnetic valve 62 provided at a. Therefore, when preventing the loss of the oil pump 47, the discharge oil passage 53b is brought into a rest state by energizing the solenoid valve 62, and the oil pressure can be supplied to the line pressure oil passage 54 only from the discharge oil passage 53a. .

In order to control the on / off operation of the lock-up clutch 9 shown in FIG. 1, the lock-up control valve 63 and the lock-up operation solenoid valve 64 are provided in the hydraulic control circuit as shown in FIG. The solenoid valve 64 is turned on / off by a control signal from the control unit 57.

When the vehicle speed exceeds a predetermined value, a lock-up ON signal is sent from the control unit 57 to the solenoid valve 64,
The lubricating pressure oil passage 58 and the oil passage 65 are in communication with each other, and the lubricating pressure acts on the control port of the lock-up control valve 63 via the oil passage 65. At this time, the control pressure also acts on the first relief valve 66 connected between the oil passage 65 and the lubrication pressure oil passage 58, so that the lubrication pressure Pc is set to a lower pressure Po. As a result, the spool of the lock-up control valve 63 slides to the right in FIG. 2, and the lubricating pressure oil path 58 flows through the oil path 67 connected to the apply chamber 9b, and this lubricating pressure flows into the apply chamber 9b. Supplied. As a result, the lock-up clutch 9 is pushed to the left to enter a lock-up state, that is, a directly connected state, and the pressure in the release chamber 9a is returned to the oil pan 51 via the oil passage 68.

When a lock-up off signal is sent to the solenoid valve 64, the communication between the lubrication pressure oil passage 58 and the oil passage 65 is broken, and the oil passage 65 is closed. Thereby, the lock-up control valve 63
No control pressure is applied to the control port of
The relief valve 66 is less likely to drain, and the lubrication pressure is adjusted to a higher pressure. As a result, the lock-up control valve 63 is actuated by the lubrication pressure acting on the port connected to the lubrication pressure oil passage 58.
Of the lubricating oil passage 58 and the oil passage 67
Communication with is interrupted. At this time, the second lubricating pressure PL lower than the lubricating pressure Po is controlled by the second relief valve 69 connected to the drain port of the first relief valve 66.
Is set, the lubricating oil having the lubricating pressure PL flows through the oil passage 70 connected to the drain port, and the oil pressure is supplied to the release chamber 9a via the oil passage 68.

As a result, the lock-up clutch 9 is turned off, that is, released, and the release hydraulic pressure is changed to the oil passage 6.
After being cooled by the oil cooler 72 via the oil passage 71 and the oil passage 71, the oil returns to the oil pan 51. In addition, a relief valve 73 is connected to the oil passage 67, and the lubricating oil is returned to the oil pan 51 when the pressure of the lubricating oil supplied into the apply chamber 9 a becomes equal to or higher than a predetermined value.

As described above, when the vehicle is moved forward, the oil chamber 3 in the clutch cylinder 32 of the forward clutch 34 is moved.
The hydraulic pressure is supplied to the oil chamber 2a, and when the vehicle is moved backward, the oil pressure is supplied to the oil chamber 45a in the brake cylinder 45 of the reverse brake 43.
The supply of the hydraulic pressure is stopped at 45a. The lubricating pressure from the lubricating oil passage 58 is supplied to the oil chamber 32a, and a line pressure higher than the lubricating pressure is supplied to the oil chamber 45a.

In order to operate the forward clutch 34 and the reverse brake 43 in this manner, the lubricating oil passage 58 communicates with the oil chamber 32a through the clutch oil passage 75, the line pressure oil passage 54 and the oil chamber 45a. A brake oil passage 76 for communication is provided, and these oil passages 75, 76 are opened and closed by a manual valve 77. The manual valve 77 is operated by a select lever provided in the vehicle interior.

The manual valve 77 is operated to a P range, an R range, an N range, and a D range by a selector lever. When the vehicle is operated in the R range for reversing the vehicle, the brake oil passage 76 is in communication with the line pressure oil passage 54, and when the vehicle is operated in the D range for moving the vehicle forward, the clutch oil passage 75 is in communication with the lubricating oil passage 58. When the manual valve 77 is operated at a position other than these, the clutch oil passage 75 and the brake oil passage 76 are both closed.

The clutch oil passage 75 and the brake oil passage 76
Are connected to accumulators 78 and 79, respectively, so as to absorb a switching shock when switching between the forward state and the backward state.

A safety lock valve 81 is provided in the clutch oil passage 75 and the brake oil passage 76. An electromagnetic valve 83 provided in an oil passage 82 connecting a control port of the safety lock valve 81 and the lubricating oil passage 58 is provided. By operating, the communication between the clutch oil passage 75 and the lubrication pressure oil passage 58 is cut off, and the brake oil passage 76 and the line pressure oil passage 54
Communication with is interrupted.

FIG. 3 shows the torque converter 2 shown in FIG.
FIG. 3 is an enlarged cross-sectional view showing a portion of the forward / reverse switching device 11. The output shaft 6 to which the rotation of the crankshaft 1 is transmitted via the torque converter 2 is connected to the oil passage 68 shown in FIG. A passage 85 is formed. A lubricating oil passage 86 communicating with the oil passage 85 via the outer peripheral surface of the output shaft 6 is formed on the output shaft 6, and a lubricating oil passage 87 communicating with the lubricating oil passage 86 is formed on the drive shaft 13. ing.

The lubricating oil supplied to the lubricating oil passage 87 is supplied to the sun gear 36 and the shaft portions of the planetary pinion gears 41 and 42 provided on the drive shaft 13 and the meshing portion between the gears 41 and 42 and the ring gear 37. It is supposed to be.

The oil pump 47 is a high-pressure pump, and the inner rotor of the pump is driven by an impeller sleeve 88 integrated with the pump-side case 3 of the torque converter 2. This impeller sleeve 88
Leaks from the bush 89 that supports the motor during the idling rotation of the engine.
A guide oil passage 91 is formed in the casing to guide the leak oil to the upper portion of the forward / reverse switching device 11, and a guide pipe 92 is attached to communicate with the guide oil passage 91. The lubricating oil flowing out of the guide pipe 92 is guided immediately above the planetary pinion gears 41 and 42 and is dropped on the respective gears 41 and 42.

With the lubricating device shown in FIG. 3, when the vehicle is running, the forward / reverse switching device 11 is connected via the lubricating oil passages 85-87.
In this case, a sufficient amount of lubricating oil is supplied to each of the gears described above. However, during forward running, the planetary pinion gears 41 and 42 do not perform planetary rotation with respect to the sun gear 36 and the ring gear 37, so that a small amount of lubricating oil is required.

However, when the vehicle is stopped and in the N range, the forward clutch 34 is disengaged, and the carrier 39 attached to the clutch cylinder 32 rotates. The planetary pinion gears 41 and 42 rotate in a planetary manner. In particular, in the idling state, the amount of oil supplied from the lubricating oil passage 87 decreases.

In this state, leak oil from the oil pump 47, that is, leak oil, is dropped onto the planetary pinion gears 41 and 42 from above the forward / reverse switching device 11 through the guide oil passage 91 and the guide pipe 92. At the time of idling, the carrier 39 and the planetary pinion gears 41 and 42 are idling at a low speed, so that lubricating oil can be supplied to a required lubricating point even when lubricating oil is dripped from above.

The present invention is not limited to the above-described embodiment, and it goes without saying that various modifications can be made without departing from the scope of the invention.

[0041]

According to the present invention, since the forward / reverse switching device is lubricated by utilizing the leak oil of the oil pump, the oil pump is in an idling state where a sufficient discharge oil amount cannot be secured from the oil pump. Also, lubrication of the forward / reverse switching device can be reliably performed. As a result, it is not necessary to increase the discharge amount from the discharge port of the oil pump during idling, and it is possible to achieve downsizing of the oil pump, improvement in function and durability, and further improvement in fuel efficiency. Becomes possible.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram showing a drive system of a continuously variable transmission having a lubrication device according to an embodiment of the present invention.

FIG. 2 is a hydraulic circuit diagram showing a hydraulic system for controlling the operation of the continuously variable transmission shown in FIG.

FIG. 3 is an enlarged sectional view showing a lubricating device for a continuously variable transmission provided in a portion of a torque converter and a forward / reverse switching device in FIG. 1;

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 crankshaft 2 torque converter 6 output shaft 9 lock-up clutch 11 forward / reverse switching device 12 continuously variable transmission 13 drive shaft 14 primary pulley 15 driven shaft 16 secondary pulley 17 drive belt 32 clutch cylinder 34 forward clutch 36 sun gear 37 ring gear 39 Carrier 43 Reverse brake 85 Oil passage 86, 87 Lubrication oil passage 91 Guide oil passage 92 Guide pipe

Continued on the front page F-term (reference) 3D039 AA13 AB01 AC34 AC36 AC45 AD43 3J050 AA02 AB03 BA03 CE10 DA01 3J063 AA01 AB02 AB12 AB22 AB43 AB52 AB62 AC03 AC11 BA11 BB11 BB23 BB41 BB50 CA02 CB02 CD01 XD03 XDX XD XD X

Claims (1)

[Claims] 1. A primary pulley mounted on a drive shaft, a secondary pulley mounted on a driven shaft and having a drive belt stretched between the primary pulley, and an output shaft rotated by an engine. A lubricating device for a continuously variable transmission having a forward / reverse switching device that switches to either the forward direction or the reverse direction and transmits the forward / reverse transmission to the drive shaft, wherein the oil leaked from an oil pump rotationally driven by the engine is provided. A lubricating device for a continuously variable transmission, comprising lubricating oil guiding means for guiding to a forward / reverse switching device.