JPH10141459A - Lubrication device for belt type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To supply lubricating oil to a friction and heat generation part of a belt surely and efficiently even when a running position of the belt is deviated due to the change of change gear ratio. SOLUTION: Oil supply nozzles 10, 11 which supply lubricating oil to a belt are arranged on each side of an input pulley 1 side and an output pulley 2 side, respectively, and lubrication pipes 12, 13 which supply lubricating oil from an oil pressure supply means to each oil supply nozzle 10, 11 are provided. A position in the direction of pulley shaft of the oil supply nozzle 10 on the input pulley 1 side is set in the vicinity of a central part C of a belt running position when change gear ratio is the maximum LO, and a position in the direction of pulley shaft of the oil supply nozzle 11 on the output pulley 2 side is set in the vicinity of a central part C' of a belt running position when change gear ratio is the maximum HI.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission used for vehicles and the like, and more particularly to an improvement in a lubricating device for a belt-type continuously variable transmission.

[0002]

2. Description of the Related Art A belt-type continuously variable transmission is conventionally known as a vehicle transmission, and as a lubricating device for such a continuously variable transmission, for example, Japanese Patent Application No. Hei 10 (1994) -207, which was proposed by the present applicant. No. 7-58517.

In this lubricating device for a belt-type continuously variable transmission, an oil supply nozzle for supplying lubricating oil toward the belt is provided on each of an input pulley side and an output pulley side. Lubricating oil can be reliably and efficiently supplied to both the input side and output side belts and pulleys, as compared to the case where only one of the pulleys is provided.

[0004]

However, in the conventional lubricating device for a belt-type continuously variable transmission, the position of the oil supply nozzle on the input pulley side and the position of the oil supply nozzle on the output pulley side are set in the axial direction of the pulley. When the gear ratio changes and the running position of the belt shifts with respect to the axial direction of the pulley, the lubricating oil hits only one side of the belt, and efficient lubrication is achieved. There was a problem that it could not be performed.

Accordingly, the present invention has been made in view of the above-mentioned problems, and ensures that lubricating oil is reliably and efficiently applied to the frictional heat generating portion of the belt even when the running position of the belt is shifted due to a change in the gear ratio. The purpose is to supply.

[0006]

According to a first aspect of the present invention, an oil supply nozzle for supplying lubricating oil to a belt is provided on each of an input pulley side and an output pulley side, and the lubricating oil from a hydraulic pressure supply means is supplied to each of the above-mentioned belts. In a lubricating device for a belt-type continuously variable transmission provided with a lubrication passage for supplying to a refueling nozzle, the position of the refueling nozzle on the input pulley side in the pulley axial direction is near the center of the belt traveling position when the gear ratio is the maximum LO. On the other hand, the gear ratio of the oil supply nozzle on the output pulley side in the pulley axial direction
It is set near the center of the belt running position at the time of I.

In a second aspect based on the first aspect, each of the refueling nozzles is disposed in a space surrounded by an input pulley, an output pulley, and a belt, and the ejection direction of these refueling nozzles is changed to the input pulley side. And the output pulley side are set so as to be near the pulley biting portion of the belt.

[0008] In a third aspect based on the second aspect, each of the refueling nozzles is intensively arranged between an input pulley and an output pulley.

[0009]

Therefore, according to the first aspect, the position of the oil supply nozzle on the input pulley side in the axial direction of the pulley is set near the center of the belt running position at the time of the lowest LO, and the pulley of the oil supply nozzle on the output pulley side is set. Since the axial position is set near the center of the belt running position at the time of the maximum HI, even if the gear ratio changes and the running position of the belt shifts, lubricating oil is reliably supplied to the small-diameter pulley side, which is the frictional heating part of the belt. And efficiently supplied.

In the second invention, the position of each refueling nozzle is set in a space surrounded by both the pulley and the belt on the input side and the output side, and the ejection direction of the refueling nozzle is set on the input pulley side and the output pulley side. The lubricating oil can be reliably and efficiently supplied to the heat generating portion of the belt because it is set in the vicinity of the pulley biting portion of the belt.

According to the third aspect of the present invention, since each oil supply nozzle is disposed intensively between the input pulley and the output pulley, the lubricating oil can be reliably and efficiently supplied to the heat generating portion of the belt with a simple configuration. Therefore, the degree of freedom in design can be improved.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the accompanying drawings.

Referring to FIG. 1, the belt-type continuously variable transmission mainly includes an input pulley 1, an output pulley 2, and a belt 3.

The input pulley 1 includes an input shaft 1a connected to an output shaft 6a of an engine 6 via a torque converter 4 and a clutch 5, a fixed pulley 1b fixed to the input shaft 1a, and an input shaft 1a. The movable pulley 1c is slid in the axial direction and hydraulically controlled so that the relative distance from the input fixed pulley 1b is variable.

The output pulley 2 is connected to an output shaft 2a of the vehicle (not shown), a fixed pulley 2b is fixed to the output shaft 2a, and slides on the output shaft 2a in the axial direction. And a movable pulley 2c that is hydraulically controlled so that the relative distance from the output fixed pulley 2b is variable.

As shown in FIGS. 2 and 3, the belt 3 has a structure in which a large number of elements 3b are supported in a circumferential direction on a ring 3a having a laminated structure. With it wrapped around the pulley 2,
The rotational force is transmitted based on the contact friction force generated between both side surfaces of the element 3b and the conical surface of the pulley.

The gear ratio of the continuously variable transmission (= input shaft rotation speed /
The output shaft rotation speed) is changed by reciprocally changing the positions of the movable pulleys 1c and 2c by hydraulic control of the radius of the portion where the belt 3 contacts each of the input pulley 1 and the output pulley 2. .

That is, while increasing the distance between the pulleys 1b and 1c on the input side to reduce the contact radius of the belt 3,
As the contact radius is increased by reducing the distance between the output-side pulleys 2b and 2c, the gear ratio becomes larger = LO. On the contrary, the distance between the input-side pulleys 1b and 1c is reduced, and the output-side pulleys 2b and 2c are reduced. The gear ratio is smaller = H as the interval is increased
I side.

The distance between the pulleys on the input side and the output side, that is, the position of the movable pulleys 1c and 2c is adjusted so that the size changes reciprocally from the hydraulic pump 7 to the movable pulleys 1c and 2c. The hydraulic control is controlled by the hydraulic pressure supplied via the pressure means 8, and such hydraulic control is performed according to a predetermined gear shift pattern according to a predetermined gear shift pattern so as to achieve a predetermined gear ratio according to the driving state of the vehicle. The control means 9 instructs the pressure adjusting means 8 to be executed.

An oil supply nozzle 10 for supplying lubricating oil to the belt is provided near each of the input pulley 1 and the output pulley 2.
And 11 are independently arranged, and the hydraulic pump 7 and the respective oil supply nozzles 10 and 11 are connected to each other by lubrication pipes 12 and 13 via a pressure adjusting means 8, respectively.

Although the above points are the same as those of the conventional belt-type continuously variable transmission, in this embodiment, the position of the belt provided on the input pulley 1 side in the pulley axial direction of the oil supply nozzle 10 has the highest gear ratio. The position of the belt provided on the side of the output pulley 2 in the pulley axial direction of the refueling nozzle 11 is set at the gear ratio H,
It is set at the approximate center of the belt running position at the time of I, and the positional relationship between the two refueling nozzles 10 and 11 is offset from each other in the axial direction of the pulley.

FIG. 1 shows a state in which the gear ratio is the lowest LO, and these two refueling nozzles 10 and 1
4 and 5 show the positional relationship between the belt 1 and the input pulley 1 and the output pulley 2 in an enlarged manner.

FIG. 4 is a longitudinal sectional view showing a main part of this embodiment, and FIG. 5 is a transverse sectional view of the same main part.

The gear ratio in the state shown in FIGS. 4 and 5 is the lowest LO as described above, and the position of the belt 3 provided on the input pulley 1 side in the pulley axial direction of the oil supply nozzle 10 is roughly equivalent to the belt running position. It is located at the center C.

On the other hand, the position of the belt provided on the output pulley 2 side in the axial direction of the oil supply nozzle 11 is offset by a predetermined amount δ in the axial direction of the pulley with respect to the oil supply nozzle 10 on the input pulley 1 side.

In FIG. 5, the positional relationship between the refueling nozzles 10 and 11 is set on the inner peripheral side of the space surrounded by the input pulley 1, the output pulley 2 and the belt 3, and
The direction in which the lubricating oil is ejected from 0 and 11 depends on the pulley engagement portions 3 of the belt 3 on the input pulley 1 side and the output pulley 2 side.
1, 32.

FIG. 6 shows that when the gear ratio is the maximum HI,
It is a longitudinal cross-sectional view which shows the same principal part as the above.

On the HI side, the approximate center of the traveling position of the belt 3 is shifted from C to C 'on the LO side by the shift.
The position of the oil supply nozzle 11 of the belt 3 provided on the output pulley 2 in the axial direction of the pulley is located at the approximate center C 'of the belt traveling position on the HI side because the belt is provided on the output pulley 2 side by δ in the axial direction of the pulley. Will be located.

Next, before describing the operation of the present embodiment, the principle of generating frictional heat on the belt of the continuously variable transmission will be described.

FIGS. 2 and 3 show examples of the structure of the metal belt 3 used in the belt-type continuously variable transmission.

To explain this, the belt 3 is composed of a laminated ring 3a composed of a plurality of endless rings,
a number of elements 3 arranged without gaps in the longitudinal direction of a
b.

Each element 3b is allowed to bend inward as an element row by a tapered surface 3c formed in the lower half of the front surface, so that it can be wound around a pulley.

Incidentally, the contact point A between the elements 3b shown in FIG. 3 is radially inward from the contact surface B between the ring 3a and the element 3b by r.

The radius difference r is about 1 mm, but because of this radius difference r, the angular velocity of the ring 3a moving outward at the bent portion wound around the pulley is higher than that of the element 3b moving inside. It becomes smaller and slips.

For example, as shown in FIG. 7A, when the gear ratio is on the LO side where the gear ratio is large, the winding angle of the belt 3 or the circumference of contact with the pulley is smaller than that of the input pulley 1 with respect to the output pulley 2. Since the side is larger and the frictional force between the ring 3a and the element 3b is correspondingly larger, the slip occurs on the input pulley 1 side where the frictional force is relatively small.

On the other hand, as shown in FIG. 7B, when the transmission ratio is on the HI side where the gear ratio is small, the ring 3a and the element 3b are substantially separated from each other on the input pulley 1 side where the belt 3 is wound around at a large angle. It rotates integrally and the relative slip between the ring 3a and the element 3b mainly occurs on the output pulley 2 side.

That is, in such a metal belt for a continuously variable transmission, the ring 3a and the element 3b are connected to the input pulley 1 on the LO side where the speed ratio is larger than 1, and the HI is set to be lower than 1 on the input pulley side. On the side, relative slip occurs on the output pulley 2 side. And the ring 3
Friction heat is generated on the contact surface between the element a and the element 3b. FIG. 8 shows a belt circumference = 700 mm and a distance between pulley shafts = 160.
The figure shows the calculation result of the relative slip speed between the element 3b and the ring 3a generated when the speed ratio is changed by operating the input shaft rotation speed = 4000 rpm in the belt-type continuously variable transmission set to mm. is there. From this figure, it can be seen that the occurrence of slippage at the speed ratio = 1 is caused by the input pulley 1 and the output pulley 2.
It can be seen that the relative slip speed increases as the gear ratio shifts to the LO side or the HI side, and accordingly, the heat generation also increases.

Next, the operation of the present embodiment will be described.

First, assuming that the gear ratio is on the LO side (FIG. 4), the position of the oil supply nozzle 10 of the belt 3 provided on the input pulley 1 side in the pulley axial direction is located at the approximate center C of the belt traveling position. The position of the belt provided on the output pulley 2 side in the axial direction of the oil supply nozzle 11 is offset in the axial direction by a predetermined amount δ with respect to the oil supply nozzle 10 on the input pulley 1 side. The predetermined amount δ is set to the offset amount δ = 9.5 mm in the specifications of the belt-type continuously variable transmission shown in FIG.

When the speed ratio is on the LO side, as described above, the relative slippage between the ring 3a and the element 3b occurs on the input pulley 1 side, and the relative slip generates frictional heat on the contact surface. In the embodiment, the position of the oil supply nozzle 10 of the belt 3 provided on the input pulley 1 side in the pulley axial direction is
Since the belt 3 is set at the approximate center C of the belt traveling position, the friction heating portion of the belt 3 can be reliably and efficiently lubricated. However, on the other output pulley 2 side,
The lubricating oil is sprayed on one side offset by 9.5 mm from the center C of the belt 3, but frictional heat is relatively unlikely to be generated on the output pulley 2 side. Does not occur.

On the other hand, when the gear ratio is on the HI side, the relative slippage of the ring 3a and the element 3b occurs on the output pulley 2 side as described above, and the relative slippage of the ring 3a and the element 3b occurs. Friction heat is generated on the contact surface. At this time, the approximate center C 'of the running position of the belt is shifted by a predetermined amount δ to the left side in FIG.
The position of the oil supply nozzle 11 of the belt provided on the output pulley 2 side in the axial direction of the pulley is located at the approximate center C 'of the belt traveling position, so that the frictional heating portion of the belt is reliably and efficiently lubricated. be able to. However, even in this case, the lubricating oil is sprayed on the other input pulley 1 side at an offset of 9.5 mm to one side from the center of the belt, but frictional heat is relatively generated on the input pulley 1 side as described above. Since it does not easily occur, the problem that the belt 3 becomes hot does not occur.

In the above embodiment, the oil supply nozzles 10 and 11 for supplying the lubricating oil to the input pulley 1 and the output pulley 2 are independently provided, and the hydraulic pump 7 and the oil supply nozzles 10 and 11 are provided independently. The lubricating pipes 11 and 12 are connected to each other by lubricating pipes 12 and 13 via the pressure adjusting means 8, but the lubricating pipes 12 and 13 can be shared by both refueling nozzles.

FIGS. 9 and 10 show a second embodiment, in which the oil supply nozzles 10 and 11 of the first embodiment are connected to the input pulley 1.
And the output pulley 2 are assembled. The other configuration is the same as that of the first embodiment.

FIG. 9 is a longitudinal sectional view showing a lubricating device for a belt-type continuously variable transmission, and FIG. 10 is a side sectional view of the same main part.

The gear ratios in FIGS. 9 and 10 are shown in FIG.
Similarly, the position of the lubrication nozzle 10 ′ of the belt 3 provided on the input pulley 1 side in the pulley axial direction is located at the approximate center C of the belt running position, and provided on one output pulley 2 side. The position of the refueling nozzle 11 ′ of the belt 3 in the pulley axial direction is offset by a predetermined amount δ in the pulley axial direction with respect to the refueling nozzle 10 on the input pulley 1 side.

The two oil supply nozzles 10 'and 11' are connected by a single lubrication pipe 14, and are connected to a hydraulic pump via a pressure adjusting means 8 similar to that of the first embodiment.

According to this configuration, the refueling nozzles 10 ', 1
1 'can be arranged in a concentrated manner, which reduces the space required for lubrication, improves the degree of freedom in the design of belt-type continuously variable transmissions, and reduces the friction of belt 3 with a simple component configuration. The heat generation part can be reliably and efficiently lubricated to promote cooling.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a lubrication device for a belt-type continuously variable transmission, showing one embodiment of the present invention.

FIG. 2 is also a cross-sectional view of the belt in the radial direction.

FIG. 3 is a sectional view of the belt in the circumferential direction.

FIG. 4 is a longitudinal sectional view showing a state of lubrication when the speed ratio is on the LO side.

FIG. 5 is a cross-sectional view showing a state of lubrication when the gear ratio is on the LO side.

FIG. 6 is a longitudinal sectional view showing a state of lubrication when the speed ratio is on the HI side.

FIGS. 7A and 7B are explanatory diagrams showing the principle of relative slippage occurring between the belt element and the ring. FIG. 7A shows a case where the speed ratio is LO, and FIG. 7B shows a case where the speed ratio is HI.

FIG. 8 is a graph showing a relationship between a relative slip speed generated between an element and a ring of a belt and a gear ratio.

FIG. 9 is a longitudinal sectional view of a main part of a lubricating device for a belt-type continuously variable transmission according to a second embodiment.

FIG. 10 is a cross-sectional view of a main part of a lubricating device of a belt-type continuously variable transmission, respectively.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Input pulley 2 Output pulley 3 Belt 7 Hydraulic pump 8 Pressure adjusting means 10, 11 Oil supply nozzle 12, 13 Lubrication pipe

Claims (3)

[Claims] An oil supply nozzle for supplying lubricating oil to a belt is provided on each of an input pulley side and an output pulley side,
In a lubricating device for a belt-type continuously variable transmission provided with a lubricating passage for supplying lubricating oil from a hydraulic pressure supply unit to each of the lubricating nozzles, the position of the lubricating nozzle on the input pulley side in the pulley axial direction is such that the gear ratio is the lowest LO. Wherein the position of the oil supply nozzle on the output pulley side in the axial direction of the pulley is set near the center of the belt traveling position when the gear ratio is the highest HI. Lubricating device for a continuously variable transmission. 2. The refueling nozzle is disposed in a space surrounded by an input pulley, an output pulley, and a belt,
2. A lubricating device for a belt-type continuously variable transmission according to claim 1, wherein the ejection directions of the oil supply nozzles are set so as to be near the engagement portion of the belt on the input pulley side and the output pulley side. . 3. The lubricating device for a belt-type continuously variable transmission according to claim 2, wherein each of the refueling nozzles is disposed intensively between an input pulley and an output pulley.