JPH0451246Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Field of Industrial Application) The present invention relates to a refueling device for a belt type continuously variable transmission used in a power transmission system or the like in a vehicle or the like.

(Prior art and its problems) As this type of oil supply device, the present applicant proposed the one shown in FIG. 4 (Japanese Patent Application No. 60-047374). In such a device, one end of the supply pipe 101 is connected to the sealing member 1.
02 into the hollow part 104 of the pulley shaft 103, and the other end is inserted into the hole 106 of the base body 105.
It penetrates in a sealed state with a ring 107. The base body 105 is provided with a connection port 106a that is continuous with the hole 106, and the connection port 106a is connected to the hole 106.
The opening surface of 6a is liquid-tightly closed by a lid 108, and one end of an oil supply path 108a is communicated with the supply pipe 101 via the lid 108 and the connection port 106a. The other end of the oil supply path 108a is connected to a hydraulic pressure supply source (not shown). and,
A collar 10 is provided at the other end of the supply pipe 101 to prevent the supply pipe 101 from being displaced toward the side opposite to the lid body 108.
9, and a claw portion 109a is provided on the outer periphery of the collar 109 to prevent misalignment between the supply pipe 101 and the pulley shaft 103. However, as the pulley shaft 103 moves in the radial direction due to vibrations or the like, the pulley shaft 103 and the supply pipe 101 are not necessarily coaxial, so misalignment between the two axes is absorbed. In order to prevent the supply pipe 101 from being bent, the claw portion 109a and the lid body 108 are
A clearance C corresponding to the expected amount of misalignment is provided between the two. Therefore, when the actual amount of misalignment Y is large with respect to the clearance C (see FIG. 5), bending stress acts on the supply pipe 101, causing knitting wear on the seal member 102. On the other hand, if the clearance C is too large, as shown in FIG. By repeating the movement in the axial direction, the O-ring 1
07 is worn out. Therefore, in any of the above cases, a problem may arise in that the sealing performance of the supply pipe 101 is poor. Furthermore, as described above, the clearance C must be set appropriately with respect to the expected amount of misalignment, and high accuracy is required in its dimensional control.

(Purpose of the invention) The present invention was made in order to solve the problems of the prior art described above, and is a lubricating device for a belt-type continuously variable transmission that can improve sealing performance and reduce costs. The purpose is to provide

(Means for Solving the Problems) In order to achieve the above object, the present invention includes a fixed pulley half integrally formed on the outer periphery of a pulley shaft rotatably supported on a base body, and a A movable pulley half that is slidably but non-rotatably fitted to the outer periphery of the pulley shaft facing each other, a pressure chamber provided on the side of the movable pulley half opposite to the belt engagement groove, and a pressure chamber inside the pulley shaft. and a fitting hole for an oil supply passage communicating with the pressure chamber formed along the axis thereof, and the width of the belt can be changed by the hydraulic pressure in the pressure chamber between the fixed pulley half and the movable pulley half. In a lubricating device for a belt-type continuously variable transmission in which an engagement groove is configured, sealing means is interposed in the fitting hole of the lubricating passage on one end side and in the hole of the base body on the other end side, respectively, to ensure liquid tightness. an oil supply pipe that is fitted and whose other end side faces a connection port of a hydraulic power supply source that is continuous with the hole of the base body; and an oil supply pipe that is provided on the outer circumferential surface of the other end side of the supply pipe so as to be able to abut against the base body. and a biasing member interposed between the stopper and a lid that closes the hydraulic pressure supply source side of the connection port to bias the supply pipe toward the oil supply passage side, The present invention provides a lubricating device for a belt-type continuously variable transmission, characterized in that a relative rotational difference occurs between the pulley shaft and the supply pipe during rotation.

(Function) The end of the supply pipe on the base side is biased toward the pulley shaft by the biasing member through the stopper, so that even if the axis misalignment occurs between the pulley shaft and the supply pipe, Also, since the movement of the base side end of the supply pipe is not restricted, excessive bending stress does not occur on the supply pipe, and even when the pulley shaft and the supply pipe are coaxial, the supply pipe does not bend in its axial direction. Do not move indiscriminately. Furthermore, for the same reason, there is no need for highly accurate dimensional control of the clearance between the base-side end surface of the supply pipe and the lid.

(Example) Hereinafter, an example of the present invention will be described with reference to the drawings. FIG. 1 is a block diagram showing a part of a belt type continuously variable transmission equipped with a lubricating device according to a first embodiment of the present invention. In the figure, 1 is a case (base body), and the case 1
A driven shaft (pulley shaft) 2 is rotatably supported inside, and a driven pulley (pulley) 3 is installed on the driven shaft 2.

The driven pulley 3 and a drive pulley (pulley) installed on the drive shaft (pulley shaft) 32 (not shown)
An endless V-belt 4 having a V-block 4a having a trapezoidal cross section is wound between the two. The rotational power of an output shaft (all not shown) of an internal combustion engine is transmitted to the drive shaft 32 via a starting clutch (not shown) or the like.

The driven pulley 3 includes a disk-shaped fixed pulley half 5 integrally formed on the outer periphery of the driven shaft 2;
It consists of a movable pulley half 6 which faces the fixed pulley half 5 and is fitted to the outer periphery of the driven shaft 2 along its axial direction so as to be slidable but non-rotatable. Note that the movable pulley half 6 in FIG. 1 shows a state in which the upper half and lower half of the figure have different axial positions. That is, the upper half of the figure shows the state in which the movable pulley half 6 has moved toward the fixed pulley half 5, and the lower half shows the state in which the movable pulley half 6 has moved toward the side opposite to the fixed pulley half 5. are shown respectively.

The fixed pulley half 5 is the movable pulley half 6.
The side surface is an inclined surface 5a. The movable pulley half 6 is composed of a cylindrical shaft portion 6a, a disc-shaped portion 6b, and a cylindrical peripheral wall portion 6c. The cylindrical shaft portion 6a is fitted onto the driven shaft 2 so as to be slidable in the axial direction thereof. Moreover, the cylindrical shaft portion 6a
Ball engaging grooves 7 and 8 are formed in the inner circumferential surface of the driven shaft 2 and the outer circumferential surface of the driven shaft 2, respectively, along the axial direction and facing each other in the radial direction. A plurality of balls 9 fitted between opposing surfaces of the movable pulley half 6
is not rotatable with respect to the driven shaft 2.

The disk-shaped portion 6b is integrally provided on the outer periphery of the end of the cylindrical shaft portion 6a on the side of the fixed pulley half 5. The side surface of the disk-shaped portion 6b on the fixed pulley half 5 side is an inclined surface 6d.
d and the inclined surface 5a of the fixed pulley half 5, a V groove (belt engagement groove) 10 is defined, and the V groove 1
The V-belt 4 is wrapped around the V-belt 4.

The cylindrical peripheral wall portion 6c is the disc-shaped portion 6b.
It protrudes integrally with the disc-shaped portion 6b along the axial direction on the opposite side of the fixed pulley half 5 near the outer peripheral end of the pulley half 5.

A fixed member 11 is fitted into the movable pulley half 6. The fixing member 11 has its cylindrical shaft portion 1
1a is fitted onto the outer periphery of the driven shaft 2 so as to be non-rotatable and non-movable in the axial direction. Further, the outer circumferential surface of the flange portion 11b of the fixed member 11 is fluid-tightly and slidably fitted into the inner circumferential surface of the cylindrical circumferential wall portion 6c of the movable pulley half 6. 6, a pressure chamber 12 is formed between the two.
Driving oil is supplied to the pressure chamber 12 from a driving oil supply source (not shown) via an oil supply passage 18 (described later), and the axial position of the movable pulley half 6 is controlled by the oil pressure in the pressure chamber 12. That is, the width of the V-groove 10 is drive-controlled.

A coil-shaped first spring 13 is interposed between the opposing surfaces of the disk-shaped portion 6b of the movable pulley half 6 and the flange portion 11b of the fixed member 11,
The movable pulley half 6 is biased toward the fixed pulley half 5 by the first spring 13 . The first
The spring 13 is used to prevent the V-belt 4 from loosening suddenly if the pressure inside the pressure chamber 12 should drop.

Inside the driven shaft 2, there is a first shaft extending from a substantially middle portion in the axial direction to an end portion on the opposite side of the fixed pulley half 5.
A driving oil conduit (fitting hole) 14 is provided.
The first driving oil guide passage 14 is coaxial with the driven shaft 2, and one end thereof (fixed pulley half 5
side) communicates with the pressure chamber 12 via a first port 15 bored along the radial direction of the driven shaft 2.

One end of a first driving oil supply pipe (supply pipe) 17 is fitted into the first driving oil guide passage 14 via a cylindrical first seal member 16 so as to be relatively rotatable. The first drive oil supply pipe 17 and the first drive oil introduction passage 14 constitute a supply passage 18 for the drive oil of the movable pulley half 6. A gap exists between the outer peripheral surface of the first driving oil supply pipe 17 other than the portion where the first seal member 16 is disposed and the inner peripheral surface of the first driving oil guide passage 14. The other end of the first driving oil supply pipe 17 extends outward from the first driving oil guide path 14 and is attached to the case 1 .

FIG. 2 is a detailed view of the attachment portion of the first driving oil supply pipe 17 to the case 1. As shown in the figure, the case 1 is entered from the driven shaft 2 side.
A hole 50 and a connection port 51 are successively arranged concentrically with the driven shaft 2 in order toward the outer surface of the shaft. The hole portion 50 is a small diameter portion 50 located on the driven shaft 2 side.
a, and a large diameter portion 50b located on the side opposite to the driven shaft 2. The connection port 51 has a small diameter portion 51a located on the hole 50 side and having a larger diameter than the large diameter portion 50b of the hole 50, and a large diameter portion 5 located on the side opposite to the hole 50.
1b.

The other end side of the first driving oil supply pipe 17 passes through the hole 50 of the case 1 in a tight fit state in the small diameter part 50a and in a loose fit state in the large diameter part 50b. It extends into the small diameter part 51a of the connection port 51, and a stopper 17a is provided on the outer periphery of the extension part.
is integrally provided so as to protrude in the radial direction. The collar 17a is connected to the large diameter portion 50 of the hole 50 of the case 1.
b and the small diameter portion 51a of the connection port 51.
0c, the displacement of the first driving oil supply pipe 17 toward one end side (left side in FIG. 2) is prevented. The collar 17a also has the function of stopping the first driving oil supply pipe 17 from rotating with respect to the case 1. A gap exists between the outer peripheral surface of the collar 17a and the inner peripheral surface of the small diameter portion 51a of the connection port 51. An O-ring 19 is interposed between the outer circumferential surface of the first driving oil supply pipe 17 and the inner circumferential surface of the large diameter portion 50b of the hole 50 to provide a fluid-tight seal between the two.

The opening surface of the connection port 51 of the case 1 is connected to the lid body 20.
It is blocked by. The lid body 20 is formed by providing a flange portion 20b on the outer peripheral surface of one end side (right side in the figure) of a main body 20a having a short-axis cylindrical shape. The outer peripheral surface of the main body 20a of the lid body 20 is fitted into the inner peripheral surface of the small diameter portion 51a of the connection port 51, and the flange portion 20
The outer circumferential surface of b is fitted into the inner circumferential surface of the large diameter portion 51b of the connection port 51, and the inner surface of the flange portion 20b is fitted into the small diameter portion 51a of the connection port 51.
and the large diameter portion 51b. The lid body 20 is fixed to the case 1 so as not to come off by a snap spring 21 that is engaged with an annular groove 51d provided on the inner peripheral surface of the large diameter portion 51b of the connection port 51. Further, an O-ring 22 is fitted in an annular groove 20c provided on the outer peripheral surface of the main body 20a of the lid 20.
The ring 22 provides a fluid-tight seal between the outer peripheral surface of the lid 20 and the inner peripheral surface of the connection port 51 of the case 1.

The lid body 20 has a spring fitting hole 20d in order from the drive shaft 2 side to the outer surface side of the case 1;
The annular step portion 20e and the pipe connection hole 20f are connected to the lid body 20.
They are connected concentrically.

The spring fitting hole 20d and the pipe connection hole 20f are:
They communicate with each other via an opening in the inner peripheral surface of the annular step portion 20e. Spring fitting hole 20 of the lid 20
A coil-shaped second spring (biasing member) 23 is interposed between one end surface of the annular stepped portion 20e, which is the inner end surface of d, and the facing surface of the collar 17a of the first driving oil supply pipe 17. The first driving oil supply pipe 17 is biased toward one end thereof (the side opposite to the lid 20) by the second spring 23. Further, one end of a driving oil pipe (oil supply path) 24 that communicates with a driving oil (hydraulic) supply source (not shown) such as an oil pump is connected to the pipe connecting hole 20f of the lid 20.

A belt lubricating oil conduction path 25 is provided inside the driven shaft 2 from a substantially middle portion in the axial direction to an end portion on the side of the fixed pulley half 5 . (See Figure 1). The belt lubricating oil conduit 25 is coaxial with the driven shaft 2. Inside the driven shaft 2, the first driving oil passage 14 and the belt lubricating oil passage 25 are isolated from each other. Also,
The belt lubricating oil conduit 25 has a plurality of (two in the embodiment) second holes bored in the radial direction of the driven shaft 2.
It communicates with the V-groove 10 via a port 26. One end of the belt lubricating oil supply pipe 27 is fitted to the side of the fixed pulley half 5 from the second port 26 of the belt lubricating oil conduit passage 25 through a cylindrical second sealing member 28 so as to be relatively rotatable. has been done. The other end of the belt lubricating oil supply pipe 27 has almost the same configuration as the attachment part of the other end of the first drive oil supply pipe 17, that is, the collar 27a, the coiled third spring 2
9, via the lid body 30 and the snap spring 31, etc.
It is attached to the case 1. One end of a belt lubricating oil pipe (not shown) communicating with the drive oil supply source is connected to the belt lubricating oil supply pipe 27, and the belt lubricating oil supply pipe 27 and the belt lubricating oil conduit 25 , the second port 26, the V-groove 10, etc., and the lubricating oil is supplied to the V-belt 4 in this order.

In addition, numeral 33 in FIG. 1 is a second driving oil supply pipe (supply pipe) that communicates with the pressure chamber (both not shown) of the movable pulley half of the drive shaft 32;
The driving oil supply pipe 33 is attached to the case 1 and a second driving oil conduit (fitting hole) 34 coaxially provided in the drive shaft 32, and the configuration of the attachment part is the same as that of the second driving oil conduit (fitting hole) 34. 1 driving oil supply pipe 17. That is, the second driving oil supply pipe 33
has one end fitted into the second drive oil conduit 34 via a cylindrical third seal member (not shown), and the other end fitted with its collar (stopper) 33a and a coiled fourth seal member. Spring (biasing member) 3
5 and a plate-shaped lid 36 fixed to the case 1. The drive oil pipe 24 is connected to the other end of the second drive oil supply pipe 33 .

Further, numeral 37 in FIG. 1 is a clutch drive oil supply pipe, and the clutch drive oil supply pipe 37 has almost the same configuration as the first drive oil supply pipe 17, and the case 1 and the second drive oil It is attached to the conduction path 34. Between the inner peripheral surface of the clutch driving oil supply pipe 37 and the outer peripheral surface of the second driving oil supply pipe 33, one end thereof is connected to the pressure chamber of the starting clutch (not shown) via the second driving oil conduit 34. ), and a clutch drive oil pipe (not shown) is connected to the other end. Driving oil for driving the starting clutch is supplied to the clutch driving pipe, between the inner peripheral surface of the clutch driving oil supply pipe 37 and the outer peripheral surface of the second driving oil supply pipe 33, and in the second driving oil conduit. The driving oil is supplied from the drive oil supply pipe to the pressure chamber of the starting clutch via 34 and the like.

Next, the operation of the oil supply system for a belt type continuously variable transmission of the present invention having the above configuration will be explained.

When the internal combustion engine is operated and the output shaft and the drive shaft are connected via a starting clutch or the like and the drive shaft rotates, the driven shaft 2 is connected to the drive pulley,
The rotational power of the drive shaft is transmitted sequentially through the V-belt 4 and the driven pulley 3, and the drive shaft rotates. In addition, the pressure chamber 12 of the driven pulley 3 includes a driving oil pipe 24 and a first
Driving oil is supplied from the supply source through the driving oil supply pipe 17, the first driving oil conduit 14, and the first port 15 in order, and the oil pressure in the pressure chamber 12 is controlled, thereby controlling the driven pulley. 3 movable pulley half 6
is continuously driven and controlled in its axial direction. Accordingly, the fixed pulley half 5 and the movable pulley half 6
The width of the V-groove 10 formed by this changes, and the engagement radius of the V-belt 4 that engages with the V-groove 10 is also continuously controlled. For example, when the movable pulley half 6 moves toward the fixed pulley half 5, the width of the V-groove 10 becomes smaller and the engagement radius of the V-belt 4 becomes larger, as shown in the upper half of FIG. When the pulley half 6 moves toward the opposite side of the fixed pulley half 5, the width of the V-groove 10 becomes larger and the engagement radius of the V-belt 4 becomes smaller, as shown in the lower half of FIG. On the other hand, the pressure chamber of the movable pulley half of the drive pulley (not shown) also includes a drive oil pipe 24 and a second drive oil supply pipe 3.
Driving oil is sequentially supplied from the supply source through 3 and the second driving oil conduit 34, etc., and the hydraulic pressure in the pressure chamber is controlled, so that the movable pulley half of the driving pulley is connected to the movable pulley of the driven pulley 3. Like the half body 6, it is continuously driven and controlled in its axial direction. The transmission gear ratio changes as a result of changes in the engagement radius of the V-belt 4 on the drive pulley and the driven pulley 3, and by continuously controlling the engagement radius of the V-belt 4, the driving The gear ratio between the side and the driven side is controlled steplessly.

As the driven shaft 2 rotates, the driven shaft 2 may be displaced in the radial direction due to vibration or the like.
Accordingly, the first driving oil supply pipe 17 whose one end is fitted to the driven shaft 2 is also displaced in the radial direction. As mentioned above, the other end of the first driving oil supply pipe 17 is always urged toward the driven shaft 2 by the second spring 23 via the collar 17a, so that the driven shaft 2 and the first driving oil Even if an axis misalignment occurs between the first driving oil supply pipe 17 and the first driving oil supply pipe 17, the movement in the radial direction on the other end side of the first driving oil supply pipe 17 is not restricted, and the first driving oil supply pipe 17 Because excessive bending stress does not occur,
Uneven wear of the fitting portion with the driven shaft 2, that is, the first seal member 16, can be prevented to a minimum, thereby improving its sealing performance. Furthermore, since the first driving oil supply pipe 17 is always biased toward the driven shaft 2 by the second spring 23, the driven shaft 2 and the first driving oil supply pipe 17 are aligned on the same axis. In this case, the movement of the first driving oil supply pipe 17 in the axial direction is almost eliminated, and unnecessary wear of the O-ring 19 due to sliding on the outer peripheral surface of the first driving oil supply pipe 17 accompanying the movement is prevented. Therefore, its sealing performance can be improved. Furthermore, the first driving oil supply pipe 17
There is no need to manage the dimension of the clearance between the facing surfaces of the lid body 20 and the lid body 20, and the manufacturing cost can be reduced.

The operation of the first drive oil supply pipe 17 described above is exactly the same for the second drive oil supply pipe 33 on the drive pulley side, which has almost the same configuration and is attached as described above. Further, for the same reason, the belt lubricating oil supply pipe 27 and the clutch driving oil supply pipe 37 also have similar effects.

(Second Embodiment) FIG. 3 shows a second embodiment of the present invention, in which the same parts as in the above-mentioned first embodiment are given the same reference numerals. This embodiment differs from the first embodiment only in that leaf springs are used as biasing members for the first driving oil supply pipe 17 and the second driving oil supply pipe 33. It shows the configuration of the attachment part of the driving oil supply pipe 17 to the case 1. That is, an annular spring receiving portion 20g is protruded from the end surface of the lid body 20 on the first driving oil supply pipe 17 side, and a leaf spring is inserted between the opposing surfaces of the spring receiving portion 20g and the first driving oil supply pipe 17. (biasing member) 38 is interposed, and the leaf spring 3
8, the first drive oil supply pipe 17 is always biased toward its one end side (the side opposite to the lid body 20) 12. The outer peripheral surface of this leaf spring 38 and the small diameter portion 51 of the connection port 51
A gap exists between the inner circumferential surface of a. The second driving oil supply pipe 33 (not shown) has substantially the same configuration and is biased toward the drive shaft 32 by a leaf spring, and other configurations are the same as in the first embodiment.

Therefore, in this embodiment, the same effects as in the first embodiment can be achieved, and in addition, a large number of coiled springs are installed in the space between the driving oil pipe 24 and the first driving oil supply pipe 17. Compared to the first embodiment, in which the cross sections are arranged side by side with a predetermined gap between them, the space is sparse, so that the driving oil can flow from the driving oil pipe 24 to the first driving oil supply pipe 17. can be supplied more stably without causing pressure loss.

(Effects of the invention) As detailed above, in the present invention, the end of the supply pipe on the base side is always urged toward the pulley shaft by the biasing member through the stopper, so that the pulley shaft and the supply pipe are connected to each other. Even if there is a misalignment of the axis between the pulley shaft and the supply pipe, the movement of the base side end of the supply pipe is not restricted (there is a degree of freedom), so excessive bending stress does not occur on the supply pipe, and the pulley shaft and supply Since the supply pipe does not move unnecessarily in the axial direction even when the oil supply pipe and the oil supply pipe are coaxial, wear on the sealing member of the supply pipe is suppressed to a minimum, and therefore the oil supply pipe and the oil supply It is possible to improve the sealing performance between the passage and the passage. In addition, for the same reason, there is no need for highly accurate dimensional control of the clearance between the end surface of the supply tube on the base side and the lid, which reduces processing accuracy and reduces costs. play.

[Brief explanation of the drawing]

1 and 2 show a first embodiment of the present invention, FIG. 1 is a cross-sectional view of the main part of a belt type continuously variable transmission equipped with the oil supply device of the present invention, and FIG. FIG. 3 is an enlarged view of the main part with a part of the circular part omitted. FIG. 3 is an enlarged view of the main part similar to FIG. 2 showing the second embodiment of the present invention. FIGS. 4 and 5 are different views of the conventional device. It is a sectional view showing an operating state. 1... Case (base body), 2... Driven shaft (pulley shaft), 3... Driven pulley (pulley), 10... V groove (belt engagement groove), 14... First driving oil guide path (fitting) hole filling), 17...first driving oil supply pipe (supply pipe), 1
7a...Tsuba (stopper), 20...Lid body, 23...
...Second spring (biasing member), 24...Driving oil piping (oil supply path), 32...Drive shaft (pulley shaft), 33...
...Second driving oil supply pipe (supply pipe), 33a... collar (stopper), 34... second driving oil conduit (fitting hole), 35... fourth spring (biasing member), 36... Lid body, 38... leaf spring (biasing member), 50... hole,
51...Connection port.

Claims (1)

[Scope of utility model registration request] a fixed pulley half integrally formed on the outer periphery of a pulley shaft that is rotatably supported on a base; and a fixed pulley half that is slidably but non-rotatably fitted on the outer periphery of the pulley shaft opposite to the fixed pulley half. Fitting of a movable pulley half, a pressure chamber provided on the side opposite to the belt engagement groove of the movable pulley half, and an oil supply passage formed in the pulley shaft along its axis and communicating with the pressure chamber. In the oil supply device for a belt type continuously variable transmission, the fixed pulley half and the movable pulley half constitute a belt engaging groove whose width can be changed by the hydraulic pressure in the pressure chamber. A hydraulic power source whose other end side is fluid-tightly fitted into the fitting hole of the oil supply passage with sealing means interposed in each hole of the base body, and whose other end side is continuous with the hole portion of the base body. an oil supply pipe facing the connection port; a stopper provided on the outer circumferential surface of the other end of the supply pipe so as to be able to abut against the base; a lid body that closes the hydraulic pressure supply source side of the connection port; and the stopper. and a biasing member interposed between the fuel supply pipe and the fuel supply pipe for biasing the supply pipe toward the oil supply passage, and a relative rotation difference is generated between the pulley shaft and the supply pipe when the pulley shaft rotates. A lubricating device for a belt-type continuously variable transmission.