JPH11166604A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance the reliability of a centrifugal oil pressure canceling mechanism in a continuously variable transmission and to reduce its manufacturing cost. SOLUTION: This transmission is provided with a primary pulley and a secondary pulley 6 with a metallic belt (laid across) between. The primary pulley and the secondary pulley 6 are made up of a fixed sheave and a movable sheave 9. Behind the movable sheave 9, there is a working oil chamber 15, which moves the movable sheave 9, and a canceling oil chamber 16, which is separated from the working oil chamber 15 by a plunger 17 and which cancels the centrifugal oil pressure produced within the working oil chamber 15 accompanying the rotation of the movable sheave 9. In order to form the canceling oil chamber 16, a chamber cover 19 is fixed to a cylinder 20, which forms the working oil chamber 15 outside a moving area A of the plunger 17.

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 for a vehicle, and more particularly to a structure of a cancel oil chamber for canceling a centrifugal hydraulic pressure.

[0002]

2. Description of the Related Art Generally, a continuously variable transmission for a vehicle generally has a continuously variable transmission mechanism which is a main transmission mechanism for continuously adjusting a gear ratio according to a running state, and a starting device for controlling power transmission from an engine. And a forward / reverse switching mechanism for changing the drive rotation direction of the continuously variable transmission mechanism in accordance with the forward and backward movement of the vehicle. FIG. 8 is a skeleton diagram showing a configuration of a drive system of a conventional continuously variable transmission having such a structure.

The continuously variable transmission shown in FIG. 8 uses a torque converter 1 as the starting device, and an oil pump 3 and a forward / reverse switching mechanism 4 are arranged between the torque converter 1 and the main transmission mechanism 2. The configuration is as follows. In this case, the main transmission mechanism 2 is mounted on a primary shaft (input shaft) 12 to which rotational driving force is input from the engine via the torque converter 1 and a secondary pulley 5 (output shaft). Secondary pulley 6 that outputs rotational driving force to wheel 14 side
And a metal belt (drive belt) 7 that transmits rotation from the primary pulley 5 to the secondary pulley 6.

The primary pulley 5 and the secondary pulley 6 are fixed sheaves 31, 32 integrated with the primary shaft 12 and the secondary shaft 13, respectively.
And movable sheaves 8 and 9 incorporated so as to be movable in the axial direction. In addition, movable sheave 8,
Hydraulic cylinders 10 and 11 are provided on the back side of 9, and by appropriately controlling the pressure in the hydraulic cylinders 10 and 11, the movable sheaves 8 and 9 slide in the axial direction, and the primary pulley 5 and the secondary pulley 5 The pulley groove width of the pulley 6 can be changed. As a result, the winding diameter of the metal belt 7 changes, and an arbitrary speed ratio can be obtained in a stepless manner.

[0005] To the hydraulic cylinders 10 and 11, a primary pressure and a secondary pressure obtained by regulating a source pressure generated by the oil pump 3 by a control valve (not shown) are applied. In this case, the secondary pulley 6
On the side, a line pressure corresponding to the gear ratio is applied as a secondary pressure, and a necessary tension is applied to the metal belt 7. On the other hand, the hydraulic cylinder 10 on the primary pulley 5 side
Has a larger cross-sectional area than the hydraulic cylinder 11 on the secondary pulley 6 side, to which a hydraulic pressure reduced in line pressure is applied as a primary pressure. In this case, the primary pressure is adjusted by the engine speed and the depression depth of the accelerator pedal. When the primary pressure is increased and oil is supplied, the groove width of the primary pulley 5 becomes narrow, the diameter on the drive side becomes large, and the speed is shifted to the high speed side (overtop side). When oil is drained with the primary pressure lowered, the groove width is widened, the diameter on the drive side is reduced, and the speed is shifted to the low speed side (low side).

In the continuously variable transmission having such a configuration, the hydraulic cylinders 10, 11 are fixed to the movable sheaves 8, 9, so that when the pulley rotates, the hydraulic cylinders 10, 11 also rotate. . Therefore, the oil filled in the hydraulic cylinders 10 and 11 also rotates, and centrifugal force acts on the oil. As a result, the clamping force of the adjusted hydraulic pressure and the clamping force of the centrifugal hydraulic pressure act on the pulleys 5 and 6, and the sum of these clamp forces acts on the pulleys 5 and 6 as shown in FIG. 9. Becomes

In this case, the required clamping force changes according to the input torque, but the clamping force due to the centrifugal hydraulic pressure changes according to the number of revolutions and the cylinder size regardless of the input torque. Therefore, as the number of rotations of the pulley increases, the ratio of the clamping force by the centrifugal hydraulic pressure to the required clamping force increases. For this reason, when the rotational speed of the primary pulley 5 and the secondary pulley 6 is large, such as during high-speed running (at the time of overdrive) or at the time of starting (at the time of low), if the rotational speed is increased while the input torque is small, the centrifugal hydraulic pressure The ratio of the clamping force to the required clamping force increases. Eventually, even if the pressure adjustment hydraulic pressure is set to zero, the generated clamping force exceeds the required clamping force.

If such a situation occurs, the balance between the clamping force on the primary side and the clamping force on the secondary side will be lost, and a downshift or an upshift will occur. Therefore,
In order to maintain the pulley ratio, it is necessary to reduce the rotation speed to reduce the clamping force due to the centrifugal hydraulic pressure, or to increase the pressure adjustment hydraulic pressure supplied to the cylinder of the pulley having the lower rotation speed to increase the clamping force.

For this reason, if the influence of the centrifugal oil pressure is left as it is, the upper limit of the number of pulley rotations during overdrive or low is naturally determined, and the controllable shift range during high-speed running or starting is reduced. Becomes Therefore, the performance of the engine cannot be maximized and the advantage of the continuously variable transmission cannot be utilized. Further, if the pulley ratio is to be maintained by increasing the cylinder pressure, the tension of the belt and the stress generated in the pulley and the cylinder will increase, resulting in a problem of lowering the durability and reliability. Furthermore, an increase in the spin loss of the belt and an increase in the discharge pressure of the oil pump cause a reduction in the efficiency of the transmission and an increase in the drive torque of the oil pump.

Therefore, in the continuously variable transmission, a mechanism for canceling the centrifugal oil pressure is provided in order to solve such a problem caused by the centrifugal oil pressure. FIG. 10 is an explanatory diagram showing a configuration of a main part of the continuously variable transmission provided with a mechanism for canceling the centrifugal hydraulic pressure, and shows a configuration on the secondary pulley 6 side. As shown in FIG. 10, in the continuously variable transmission, a hydraulic oil chamber 15 and a cancel oil chamber 16 are provided behind the movable sheave 9, and the centrifugal oil pressure in the hydraulic oil chamber 15 is canceled by the cancel oil chamber 16. It is supposed to be.

The hydraulic oil chamber 15 and the cancel oil chamber 16 are formed in a cylinder 18 which also serves as a cover for the cancel oil chamber 16, and are isolated by a plunger 17. Then, the cylinder portion 18a of the cylinder 18 and the movable sheave 9,
A hydraulic oil chamber 15 is formed by the plunger 17, and a cancel oil chamber 16 is formed by the chamber 18 b of the cylinder 18 and the movable sheave 9. A sealing member 17a such as a resin ring or a rubber lip is fitted around the outer periphery of the plunger 17, whereby the hydraulic oil chamber 1 is fitted.
5 and the cancel oil chamber 16 are isolated in a sealed state.

In such a continuously variable transmission, when the pulley rotates, the centrifugal oil pressure generated in the oil in the hydraulic oil chamber 15 pushes the movable sheave 9 to the left in the figure, and the plunger 1
7 is pushed rightward. On the other hand, the centrifugal oil pressure generated in the oil in the cancel oil chamber 16 pushes the plunger 17 to the left and pushes the cylinder 18 to the right. Thereby, the movable sheave 9 fixed to the cylinder 18 is pulled rightward. Therefore, the force for pulling the movable sheave 9 rightward and the force for pushing the movable sheave 9 leftward in the hydraulic oil chamber 15 cancel each other, and the centrifugal hydraulic pressure generated in the hydraulic oil chamber 15 is cancelled. This allows
The influence of the centrifugal oil pressure on the clamping force is reduced. The clamping force of the pulley can be optimally controlled, so that the shift range can be expanded, the load on the belt can be reduced, and the fuel efficiency can be improved.

By the way, in the case of FIG.
Although the cover 8 also serves as the cover of the cancel oil chamber 16, the cylinder 18 and the cover of the cancel oil chamber 16 may not be integrally formed depending on the structure of the continuously variable transmission. That is, when the plunger is fixed to the movable sheave side and the cylinder is fixed to the shaft side, if the cover of the hydraulic oil chamber and the cover of the cancel oil chamber are formed integrally, the plunger cannot be assembled. Even when the cylinder is fixed to the movable sheave side and the plunger is fixed to the shaft side, if the inner diameter of the cylinder is larger than the outer diameter of the movable sheave, the plunger cannot be assembled. Therefore, in the continuously variable transmission having such a structure, the chamber cover (cover member) 19 is formed separately from the cylinder 20 as shown in FIG.
After installing the plunger 17 in the chamber cover 1
9 is attached.

In this case, the chamber cover 19 is formed thinner than the cylinder 20, and is fixed to the cylinder 20 by caulking its end to the end of the cylinder 20. At the end of the chamber cover 19, a cylindrical flange 21 formed by bending the edge is provided. A groove 22 is formed on the outer periphery of the cylinder 20, and the flange 21 is caulked in the groove 22.
That is, the flange 21 is provided on the end of the cylinder 20, and a tool is applied to the edge of the flange 21 while rotating the two, and the tool is pressed toward the center of rotation. As a result, the edge of the flange 21 is bent radially inward along the side wall 22 a of the groove 22, and the chamber cover 19 is fixed to the end of the cylinder 20. According to this fixing method, a component for connecting the both is unnecessary, and the chamber cover 19 can be fixed to the cylinder 20 easily and reliably.

[0015]

However, when the chamber cover 19 and the cylinder 20 are fixed in this manner, the cylinder 20 is bent by the impact at the time of caulking, and the inner wall of the cylinder 20 and the outer edge of the plunger 17 come into contact with each other. As a result, the seal member 17a may be damaged. In particular, when the plunger 17 is located at the swaged portion, there is a high possibility of such a situation. In this case, since the plunger 17 slides while sealing the high-pressure oil in the cylinder 20, there is a problem that if the seal member 17a is damaged, an operation failure due to oil leak may occur. Further, if deformation occurs in the cylinder 20 due to the impact at the time of caulking, there is also a problem that the plunger 17 sticks at that portion and causes malfunction.

On the other hand, in order to prevent such an obstacle, the rigidity of the cylinder 20 may be increased so that bending or deformation due to caulking does not occur. However, in order to increase the rigidity of the cylinder 20, it is necessary to increase the thickness of the cylinder 20, which raises a new problem that the manufacturing cost increases and the weight of the device increases.

An object of the present invention is to improve the reliability of a centrifugal hydraulic pressure canceling mechanism in a continuously variable transmission and reduce the manufacturing cost.

[0018]

SUMMARY OF THE INVENTION Among the inventions disclosed in the present application, the outline of a representative one will be briefly described.
It is as follows.

That is, the continuously variable transmission according to the present invention has a variable pulley groove width in which a driving belt is stretched between a primary pulley mounted on an input shaft and a variable pulley groove and a primary pulley mounted on an output shaft. And a primary pulley and a secondary pulley are composed of a fixed sheave and a movable sheave. A continuously variable transmission having a cancel oil chamber for canceling the centrifugal oil pressure generated in the hydraulic oil chamber with the rotation of the sheave, wherein the cover member forming the cancel oil chamber is moved outside the moving range of the plunger. In which the hydraulic oil chamber is fixed to a cylinder forming a hydraulic oil chamber.

In a similar continuously variable transmission, a flange portion extending in a radial direction is formed at an end of a cylinder forming a hydraulic oil chamber, and a cover member forming a cancel oil chamber is added in an axial direction. The cover member may be fixed to the cylinder by fixing to the flange portion by pressure.

Further, a flange portion having a U-shaped cross section is formed at the end of the cover member forming the cancel oil chamber, and the end of the cylinder forming the hydraulic oil chamber is inserted into the flange portion. The cover member may be fixed to the cylinder by fixing the edge to the cylinder.

Further, the cover member forming the cancel oil chamber may be fixed to the joint between the cylinder forming the hydraulic oil chamber and the movable sheave. In addition, the end of the cover member forming the cancel oil chamber may be fixed. The cover member may be fixed to the cylinder by cutting out a part of the part to form an uneven part and fixing the convex part of the uneven part to the end of the cylinder forming the hydraulic oil chamber.

[0023]

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

(Embodiment 1) FIG. 1 is a sectional view showing a configuration of a continuously variable transmission according to Embodiment 1 of the present invention, showing a configuration in which the present invention is applied to a secondary pulley 6 side. ing. The basic structure of the continuously variable transmission is shown in FIGS.
It is the same as that of the eleventh embodiment, and the same reference numerals are given to the same members and the details are omitted.

The continuously variable transmission shown in FIG. 1 is also similar to that shown in FIGS.
A hydraulic oil chamber 15 and a cancel oil chamber 16 are formed on the rear side. Here, the hydraulic oil chamber 15 is provided with the movable sheave 9.
And a cylinder 20 fixed to the rear side of the movable sheave 9 by caulking, and a plunger 17 disposed inside the cylinder 20 and sliding on the inner peripheral surface of the cylinder 20 in a sealed state. And 23. In this case, the oil passage 23 is connected to a control valve (not shown) by a hydraulic circuit, and the plunger 17 moves within a range A in the figure by appropriately applying hydraulic pressure to the hydraulic oil chamber 15. As a result, the metal belt 7 (see FIG. 8) in which the movable sheave 9 is on the conical surface 9a is pressed to generate a clamping force.

On the other hand, a cancel oil chamber 16 is formed on the right side of the hydraulic oil chamber 15 in the drawing with a plunger 17 interposed therebetween. The cancel oil chamber 16 is a portion surrounded by the plunger 17, the cylinder 20, and a chamber cover 19 fixed to an end of the cylinder 20, and communicates with the oil passage 24. When the pulley rotates, this oil passage 2
The inside of the cancel oil chamber 16 is filled with the oil supplied from the hydraulic oil chamber 4, and the hydraulic oil chamber 1 is filled with centrifugal force generated therein.
The centrifugal oil pressure acting on 5 is canceled. That is, the centrifugal oil pressure generated in the cancel oil chamber 16 causes the chamber cover 1
9 is pushed rightward in the figure, and pulls the cylinder 20 and the movable sheave 9 rightward. For this reason, the centrifugal oil pressure of the hydraulic oil chamber 15 acting in the direction of pushing the movable sheave 9 to the left in the drawing is canceled correspondingly.

Incidentally, the continuously variable transmission also has a structure in which the chamber cover 19 is fixed to the end of the cylinder 20 by caulking, as in the case of FIG. However, as shown in FIG. 1, in the continuously variable transmission according to the present invention, the swaging position between the chamber cover 19 and the cylinder 20 is provided outside the movement range A of the plunger 17,
It has a different configuration from the conventional one located within the movement range of the plunger 17. That is, FIG.
In the cylinder 20 of FIG.
Is formed, and the chamber cover 19 is caulked there.

In this case, a cylindrical flange portion 19a is formed at the end of the chamber cover 19. Then, this flange portion 19a is provided on the end of the cylinder 20, and the edge of the flange portion 19a is bent inward in the radial direction. As a result, the flange portion 19a is swaged and fixed to the groove 20a. At this time, the swaged portion is out of the movement range A of the plunger 17, and the plunger 17 is not positioned below the processing portion. Therefore, when the tool is pressed against the flange portion 19a, it is possible to prevent the inner wall of the cylinder 20 from colliding with the outer edge of the plunger 17 to damage the seal member 17a. In addition, since the deflection of the cylinder 20 in the movement range of the plunger 17 is reduced,
The damage of the seal member 17a due to the bending can be prevented.

Further, deformation of the cylinder 20 in the range of movement of the plunger 17 can be prevented, and malfunction of the plunger 17 due to deformation of the cylinder 20 can be avoided. In addition, it is not necessary to increase the thickness of the cylinder 20 in order to secure the rigidity of the cylinder 20, so that it is possible to suppress an increase in cost and reduce the weight of parts.

(Second Embodiment) Next, a continuously variable transmission according to a second embodiment of the present invention will be described. FIG. 2 is a cross-sectional view illustrating a configuration of the continuously variable transmission according to the second embodiment of the present invention. In the following embodiments, the first embodiment
The same reference numerals are given to the same members as those of the continuously variable transmission described above, and the details are omitted.

In the continuously variable transmission, the present invention is applied to the primary pulley 5 side. The continuously variable transmission shown in FIG. 2 also has a hydraulic oil chamber 15 and a cancel oil chamber 16 formed behind the conical surface 8 a of the movable sheave 8. In this case, a portion surrounded by the movable sheave 8, the cylinder 20, and the plunger 17 becomes the hydraulic oil chamber 15. Also, plunger 17
And a portion surrounded by the cylinder 20 and the chamber cover 19 fixed to the cylinder 20 becomes the cancel oil chamber 16. The centrifugal oil pressure acting on the hydraulic oil chamber 15 is canceled by the centrifugal force generated in the cancel oil chamber 16.

In the case of the continuously variable transmission shown in FIG. 2, the chamber cover 19 is fixed to the side portion 20b of the cylinder 20 by caulking. The chamber cover 19 has an edge 19b.
Is fixed to the side portion 20b of the cylinder 20 at the left end side in the drawing. At this time, the swaged portion is out of the movement range A of the plunger 17, and as described above, the plunger 17 is not damaged by the swage or the operation of the plunger 17 is not hindered by the deformation of the cylinder 20. Further, since it is not necessary to provide a groove for caulking the chamber cover 19 in the cylinder 20 as shown in FIG. 1, the man-hour required for the groove processing can be reduced and the cost can be reduced.

(Embodiment 3) FIG. 3 is a sectional view showing a configuration of a continuously variable transmission according to Embodiment 3 of the present invention. The continuously variable transmission shown in FIG. 3 has substantially the same configuration as that of the first embodiment. However, in the case of the continuously variable transmission shown in FIG. 3, the chamber cover 19 is caulked and fixed to a flange portion 20c formed at the end of the cylinder 20. I have.

As shown in FIG. 3, a flange 20c is formed at the end of the cylinder 20 toward the outside in the radial direction. On the other hand, a cylindrical flange portion 19c is also formed at the end of the chamber cover 19, and the flange portion 19c is provided outside the flange portion 20c of the cylinder 20. Then, the flange portion 19c is folded so as to sandwich the flange portion 20c of the cylinder 20, and both are fixed by caulking.

At this time, the caulking operation is performed by applying pressure in the axial direction. Therefore, radial force does not act on the cylinder 20 due to caulking, and damage to the plunger 17 and deformation of the cylinder 20 can be prevented. In addition,
Also in this case, the caulking portion may be provided outside the moving range of the plunger 17 so that the influence of the bending of the cylinder 20 can be avoided more reliably.

(Embodiment 4) FIG. 4 is a sectional view showing a configuration of a continuously variable transmission according to Embodiment 4 of the present invention. The continuously variable transmission of FIG. 4 has substantially the same configuration as that of the first embodiment, but in the case of FIG. 4, the end of the chamber cover 19 is formed in a double cylindrical shape, and the cylinder 20 is provided therewith. The end is fixed by caulking.

As shown in FIG. 4, the chamber cover 19
Is formed with a double cylindrical fitting flange (flange) 19d having a U-shaped cross section. On the other hand, a groove 20a is formed at the end of the cylinder 20. Then, after the fitting flange 19d of the chamber cover 19 is press-fitted into the end of the cylinder 20, the end of the fitting flange 19d is bent into the groove 20a and both are fixed by caulking.

In the case of the structure shown in FIG.
Since the inner wall 19e can receive the force at the time of caulking, the bending and deformation of the cylinder 20 at the time of caulking can be prevented. Further, inside the fitting flange portion 19d,
By inserting the caulking jig 25 as shown by the one-dot chain line, it is also possible to suppress the bending of the cylinder 20 during caulking. In FIG. 4, the caulking portion is provided outside the movement range of the plunger 17, so that the influence of the bending of the cylinder 20 can be avoided more reliably.

(Embodiment 5) FIG. 5 is a sectional view showing a configuration of a continuously variable transmission according to Embodiment 5 of the present invention. The continuously variable transmission of FIG. 5 has substantially the same configuration as that of the first embodiment, but in the case of FIG. 5, the end of the chamber cover 19 is extended to the joint between the cylinder 20 and the movable sheave 9. The end of the chamber cover 19 is fixed by swaging.

As shown in FIG. 5, the cylinder 20 is fixed by caulking at a left end thereof in a groove 9b provided in the movable sheave 9, and a groove 20d is formed in that portion. On the other hand, a cylindrical flange portion 19f is formed on the chamber cover 19. This flange portion 19f
When it is packaged in the cylinder 20, the cylinder 20
And the movable sheave 9 extends to the swaged portion, that is, the groove 20d. Therefore, the cylinder 20
After covering the chamber cover 19 with the flange 19f
By crimping the end of the cylinder 2 into the groove 20d.
The chamber cover 19 is fixed by caulking to 0.

In this case, the force applied to the cylinder 20 when caulking the chamber cover 19 is controlled by the groove 9 b of the movable sheave 9.
Therefore, bending and deformation of the cylinder 20 at the time of caulking can be prevented. Further, since it is not necessary to provide a groove for caulking the chamber cover 19 in the cylinder 20, the number of steps required for forming the groove can be reduced and cost can be reduced. In the case of FIG. 5, the caulking portion is located at a position outside the range of movement of the plunger 17, so that in addition to the above-described effects, the same effects as in the first embodiment can be obtained.

(Embodiment 6) FIG. 6 is a sectional view showing the structure of a continuously variable transmission according to Embodiment 5 of the present invention.
FIG. 7 is an explanatory diagram showing an appearance of the continuously variable transmission of FIG. 6. FIG.
The continuously variable transmission according to the third embodiment has substantially the same configuration as that of the first embodiment, but in the case of FIG. 6, the end of the chamber cover 19 is formed with unevenness, and the end of the cylinder 20 is caulked. It is fixed.

As shown in FIGS. 6 and 7, at the end of the chamber cover 19, a cylindrical concave-convex flange portion 19g formed by partially cutting off the end is formed. On the other hand, a groove 20a is formed at the end of the cylinder 20. Then, after embossing the uneven flange portion 19g at the end of the cylinder 20, the convex portion 19h of the uneven flange portion 19g is inserted into the groove 20a.
Fold it inside and fix it by caulking.

In the case of the structure shown in FIG.
Of the convex portions 19h, the force applied at the time of caulking can be reduced. Therefore, the bending and deformation of the cylinder 20 at the time of caulking can be suppressed as compared with the case where the entire circumference is caulked. Further, since the convex portion 19h existing with a gap is bent, wrinkles do not occur in the bent portion unlike when the entire periphery of the continuous edge is bent. In this case as well, it is a matter of course that the caulking portion may be provided at a position outside the moving range of the plunger 17.

Although the invention made by the inventor has been specifically described based on the embodiment, the invention is not limited to the embodiment and can be variously modified without departing from the gist of the invention. Needless to say,

For example, in Embodiments 3 to 6,
Although the example in which the present invention is applied to the secondary pulley is shown,
It goes without saying that this can be applied to the primary pulley side. In this case, a different configuration may be appropriately adopted for each pulley.

[0047]

Advantageous effects obtained by typical ones of the inventions disclosed in the present application will be briefly described.
It is as follows.

(1) Since the chamber cover forming the cancel oil chamber is fixed to the cylinder outside the range of movement of the plunger, the swaged portion does not come out of the range of movement of the plunger, and the plunger is not positioned below the processing portion. .
Therefore, it is possible to prevent the seal member from being damaged due to collision between the inner wall of the cylinder and the outer edge of the plunger during processing. In addition, since the bending of the cylinder in the movement range of the plunger is reduced, damage to the seal member due to the bending of the cylinder can be prevented. Further, deformation of the cylinder in the movement range of the plunger can be prevented, and malfunction of the plunger due to deformation of the cylinder can be avoided. In addition, it is not necessary to increase the thickness of the cylinder in order to secure the rigidity of the cylinder, so that it is possible to suppress an increase in cost and reduce the weight of parts.

(2) A flange is formed at the end of the cylinder, and the chamber cover is caulked and fixed to the flange by pressing the chamber cover in the axial direction. Without working, it is possible to prevent the plunger from being damaged and the cylinder from being bent or deformed.

(3) A fitting flange having a U-shaped cross section is formed at the end of the chamber cover, and the end of the flange is fixed to the cylinder with the end of the cylinder inserted therein. Thus, the force at the time of caulking can be received by the inner wall of the flange portion, and it becomes possible to prevent the cylinder from being bent or deformed at the time of caulking.

(4) Since the chamber cover is fixed to the connecting portion between the cylinder and the movable sheave, it is not necessary to provide a groove for caulking the chamber cover in the cylinder, and the man-hour required for groove processing can be reduced and cost can be reduced. be able to. Further, since the force applied to the cylinder when the chamber cover is swaged is received by the groove of the movable sheave, it is possible to prevent the cylinder from being bent or deformed during swaging.

(5) By forming a concave and convex flange portion by partially cutting off the end of the chamber cover and fixing the convex portion to the end of the cylinder, the force applied at the time of caulking can be reduced. . Therefore, the bending and deformation of the cylinder at the time of caulking are suppressed as compared with the case where the entire circumference is caulked, and the bending and deformation of the cylinder at the time of caulking can be reduced. Further, since the convex portion existing at the gap is bent, wrinkles do not occur in the bent portion unlike when the entire periphery of the continuous edge is bent.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view illustrating a configuration of a main part of a continuously variable transmission that is Embodiment 1 of the present invention.

FIG. 2 is a cross-sectional view illustrating a configuration of a main part of a continuously variable transmission according to a second embodiment of the present invention.

FIG. 3 is a cross-sectional view illustrating a configuration of a main part of a continuously variable transmission according to a third embodiment of the present invention.

FIG. 4 is a sectional view showing a configuration of a main part of a continuously variable transmission according to a fourth embodiment of the present invention.

FIG. 5 is a cross-sectional view illustrating a configuration of a main part of a continuously variable transmission according to a fifth embodiment of the present invention.

FIG. 6 is a sectional view showing a configuration of a main part of a continuously variable transmission according to a sixth embodiment of the present invention.

FIG. 7 is an explanatory diagram showing an appearance of a main part of the continuously variable transmission shown in FIG. 6;

FIG. 8 is a skeleton diagram showing a configuration of a drive system of a conventional continuously variable transmission.

FIG. 9 is an explanatory diagram showing a state of a clamping force applied to a pulley.

FIG. 10 is a sectional view showing a configuration of a centrifugal hydraulic pressure canceling mechanism in a conventional continuously variable transmission.

FIG. 11 is a cross-sectional view showing a configuration of another centrifugal hydraulic pressure canceling mechanism in a conventional continuously variable transmission.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Torque converter 2 Main transmission mechanism 3 Oil pump 4 Forward / reverse switching mechanism 5 Primary pulley 6 Secondary pulley 7 Metal belt (drive belt) 8 Movable sheave 8a Conical surface 9 Movable sheave 9a Conical surface 9b Groove 10 Hydraulic cylinder 11 Hydraulic cylinder 12 Primary Shaft (input shaft) 13 Secondary shaft (output shaft) 14 Drive wheel 15 Hydraulic oil chamber 16 Cancel oil chamber 17 Plunger 17a Seal member 18 Cylinder 18a Cylinder part 18b Chamber part 19 Chamber cover (cover member) 19a Flange part 19b Edge 19c Flange part 19d Fitting flange part (flange part) 19e Inner wall 19f Flange part 19g Irregular flange part (irregular part) 19h Convex part 20 Cylinder 20a Groove 20b Side surface 20c Flange part 20d Groove 21 Flange 22 Groove 22a Side wall 23 Oil passage 24 Oil passage 25 Caulking jig 31 Fixed sheave 32 Fixed sheave

Claims (5)

[Claims] A primary pulley having a variable pulley groove width mounted on an input shaft; and a secondary pulley having a variable pulley groove width mounted on an output shaft and having a drive belt stretched between the primary pulley and the primary pulley. The primary pulley and the secondary pulley are composed of a fixed sheave and a movable sheave, a hydraulic oil chamber for moving the movable sheave behind the movable sheave, and a rotation of the movable sheave separated by the hydraulic oil chamber and a plunger. And a cancel oil chamber for canceling the centrifugal oil pressure generated in the hydraulic oil chamber with the operation of the hydraulic oil chamber, wherein the cover member forming the cancel oil chamber is moved outside the movement range of the plunger. 3. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is fixed to a cylinder forming the hydraulic oil chamber. 2. A primary pulley having a variable pulley groove width mounted on an input shaft, and a secondary pulley having a variable pulley groove width mounted on an output shaft and having a drive belt stretched between said primary pulley and said primary pulley. The primary pulley and the secondary pulley are composed of a fixed sheave and a movable sheave, a hydraulic oil chamber for moving the movable sheave behind the movable sheave, and a rotation of the movable sheave separated by the hydraulic oil chamber and a plunger. And a cancel oil chamber for canceling the centrifugal oil pressure generated in the hydraulic oil chamber with the hydraulic oil chamber, wherein the continuously variable transmission radially extends to an end of a cylinder forming the hydraulic oil chamber. Forming a flange portion to be formed, and fixing the cover member forming the cancel oil chamber to the flange portion by pressing in the axial direction, CVT, characterized in that the cover member is fixed to the cylinder. 3. A primary pulley having a variable pulley groove width mounted on an input shaft, and a secondary pulley having a variable pulley groove width mounted on an output shaft and having a driving belt stretched between said primary pulley and said primary pulley. The primary pulley and the secondary pulley are composed of a fixed sheave and a movable sheave, a hydraulic oil chamber for moving the movable sheave behind the movable sheave, and a rotation of the movable sheave separated by the hydraulic oil chamber and a plunger. And a cancel oil chamber for canceling the centrifugal oil pressure generated in the hydraulic oil chamber with the hydraulic oil chamber, wherein the cross section of the end of the cover member forming the cancel oil chamber has a A flange portion having a V-shape is formed, and an end of the cylinder forming the hydraulic oil chamber is inserted into the flange portion, and an edge of the flange portion is moved forward. By fixing the cylinder, continuously variable transmission, characterized in that the securing said cover member to said cylinder. 4. A primary pulley having a variable pulley groove width mounted on an input shaft, and a secondary pulley having a variable pulley groove width mounted on an output shaft and having a drive belt stretched between said primary pulley and said primary pulley. The primary pulley and the secondary pulley are composed of a fixed sheave and a movable sheave, a hydraulic oil chamber for moving the movable sheave behind the movable sheave, and a rotation of the movable sheave separated by the hydraulic oil chamber and a plunger. And a cancel oil chamber for canceling a centrifugal oil pressure generated in the hydraulic oil chamber with the operation of the hydraulic oil chamber, wherein a cover member forming the cancel oil chamber forms the hydraulic oil chamber. A continuously variable transmission fixed to a joint between a movable cylinder and the movable sheave. 5. A pulley having a variable pulley groove width mounted on an input shaft, and a secondary pulley having a variable pulley groove width mounted on an output shaft and having a drive belt stretched between said primary pulley and said primary pulley. The primary pulley and the secondary pulley are composed of a fixed sheave and a movable sheave, a hydraulic oil chamber for moving the movable sheave behind the movable sheave, and a rotation of the movable sheave separated by the hydraulic oil chamber and a plunger. And a cancel oil chamber for canceling a centrifugal oil pressure generated in the hydraulic oil chamber with the operation of the hydraulic oil chamber, wherein an end of a cover member forming the cancel oil chamber is partially cut away. The cover member is moved forward by forming an uneven portion by fixing the convex portion of the uneven portion to an end of a cylinder forming the hydraulic oil chamber. CVT, characterized in that fixed to the cylinder.