JP2017032024A - Hydraulic pressure chamber structure in pulley - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent leakage of a hydraulic pressure in a hydraulic pressure chamber.SOLUTION: In a hydraulic pressure chamber structure in a pulley in which a hydraulic pressure chamber R is composed of a cylinder 4 in which a movable pulley 3 externally inserted to a shaft portion 21 of a fixed pulley 2, is disposed movably in a rotating shaft X1 direction, a face at one side in the rotating shaft X1 direction, of a movable-side sheave portion 32 is applied as a sheave face 321 forming a V-groove 8 on which a belt V is wound, a face at the other side is applied as a hydraulic pressure action face 322 for making the movable-side sheave portion 32 generates clamping force acting on the belt V, and a joining portion 42 formed by bending one end of a cylindrical portion 41 to an inner diameter side, is joined to the hydraulic pressure action face 322 from the rotating shaft X1 direction, and the hydraulic pressure action face 322, and which is constituted to displace the movable pulley 3 in a direction to narrow a width of the V-groove 8 by a hydraulic pressure P supplied to the hydraulic pressure chamber R, a projection 324 having the ring shape when observed from the rotating shaft X1 direction, is formed on the hydraulic pressure action face 322, and the joining portion 42 is provided with a ring-shaped groove 421 to which the projection 324 is fitted.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a hydraulic chamber structure in a pulley.

  Patent Document 1 discloses a belt-type continuously variable transmission that includes a variator configured by winding a belt around a pair of pulleys (a primary pulley and a secondary pulley). In this belt-type continuously variable transmission, A desired gear ratio is realized by changing the belt winding radius in the primary pulley and the secondary pulley.

JP 2014-185702 A

FIG. 4 is a diagram illustrating a hydraulic chamber structure in a pulley according to a conventional example.
As shown in FIG. 4, the primary pulley 90 that constitutes the variator includes a fixed pulley 91 and a movable pulley 92 that is extrapolated to the shaft portion 911 of the fixed pulley 91, and the movable pulley 92 is a fixed pulley 91. In a state in which the relative rotation is restricted, and is movable in the direction of the rotation axis X1.
The fixed pulley 91 and the movable pulley 92 have sheave portions 912 and 922 extending in the radial direction of the rotation axis X1, and the opposing surfaces of the sheave portions 912 and 922 are inclined with respect to the rotation axis X1. Sheave surfaces 913 and 923 are formed.
The sheave surfaces 913 and 923 are provided in such a direction that the distance D between the sheave surfaces 913 and 923 increases toward the outer side in the radial direction from the rotation axis X1, and the belt V is wound between the sheave surfaces 913 and 923. A V-shaped groove 901 is formed.

  In the primary pulley 90, a hydraulic chamber R to which the hydraulic pressure P is supplied is formed on the opposite side of the movable pulley 92 from the fixed pulley 91, and the hydraulic pressure P is supplied to the hydraulic chamber R through the oil path 96. When the movable pulley 92 pushed by the hydraulic pressure P is displaced in the direction of narrowing the V groove 901 (leftward in the figure) and the supply of the hydraulic pressure P to the hydraulic chamber R is interrupted, Due to the pressing force acting from the belt V, the V groove 901 is displaced in the direction of widening (rightward in the figure).

  Here, the hydraulic chamber R has a disk-like piston 94 fixed to the shaft portion 911 of the fixed pulley 91 through the opening of the cylindrical cylinder 93 fitted to the outer diameter side of the sheave portion 922 of the movable pulley 92. It is formed by sealing.

Here, the cylinder 93 is configured such that a ring-shaped fitting portion 932 provided at one end of the cylindrical base portion 931 is externally fitted to a step portion 924 provided on the outer peripheral side of the sheave portion 922 from the direction of the rotation axis X1. The movable pulley 92 is fixed.
Therefore, when the movable pulley 92 moves in the direction of the rotation axis X1, the cylinder 93 moves together with the movable pulley 92 in the direction of the rotation axis X1.

In the primary pulley 90, when the highest gear ratio is realized, the winding radius of the belt V in the primary pulley 90 is maximized. At this time, the element E that supports the belt V is a sheave on the fixed pulley 91 side. On the outer diameter side of the surface 913 and the sheave surface 923 on the movable pulley 92 side, both sides in the direction of the rotation axis X1 are supported.
Here, a force in a direction of narrowing the winding radius acts on the belt V wound around the primary pulley 90, and the sheave surface 913, the fixed pulley 91 and the movable pulley 92 around which the belt V is wound, The pressing force in the direction of widening the groove width of the V-groove 901 between 923 is acting.

In the sheave portion 922, the thickness W in the direction of the rotation axis X1 on the outer diameter side of the step portion 924 is thinner than the inner diameter side, and the rigidity strength on the outer diameter side of the step portion 924 is lower than the inner diameter side. It has become.
Therefore, deformation may occur on the outer diameter side of the step portion 924 of the sheave portion 922 due to the pressing force acting from the belt V (element E) (see FIG. 3B).

  Here, since the fitting portion 932 of the cylinder 93 is only fitted to the step portion 924 of the sheave portion 922, when the outer diameter side of the step portion 924 of the sheave portion 922 is deformed, the fitting portion 932 is fitted. A gap S may be generated between the portion 932 and the sheave portion 922. In such a case, the hydraulic pressure P in the hydraulic chamber R leaks from the portion of the generated gap.

  Therefore, it is required to prevent leakage of hydraulic pressure in the hydraulic chamber.

The present invention
A movable pulley externally attached to the shaft portion of the fixed pulley is provided so as to be movable in the rotational axis direction, and one surface of the sheave portion of the movable pulley in the rotational shaft direction has a V groove around which the belt is wound. The sheave surface to be formed, and the other surface is a hydraulic working surface that generates a narrow pressure acting on the belt at the sheave portion,
A hydraulic chamber is formed from a cylinder in which a disk portion formed by bending one end of a cylindrical portion toward the inner diameter side is joined to the hydraulic operation surface from the direction of the rotation axis, and the hydraulic operation surface,
The movable pulley is a hydraulic chamber structure in a pulley configured to be displaced in a direction of narrowing the width of the V-groove by the hydraulic pressure supplied to the hydraulic chamber;
Among the oil pressure action surface and the disk portion joined together in the rotation axis direction, the oil pressure action surface is provided with a ring-shaped protrusion when viewed from the rotation axis direction, and
The pulley has a hydraulic chamber structure in which a ring-shaped groove into which the protrusion is fitted is provided in the disk portion.

According to the present invention, even if a gap is generated on the joint surface between the hydraulic acting surface of the sheave portion of the movable pulley and the disk portion of the cylinder due to the deformation of the sheave portion of the movable pulley on the outer diameter side, Since the protrusion provided on the hydraulic pressure acting surface is fitted in the groove provided in the plate portion, there is no gap between the inside and the outside of the hydraulic chamber.
Thereby, leakage of the hydraulic pressure in the hydraulic chamber can be prevented.
In particular, since a protrusion is provided on the hydraulic pressure acting surface of the sheave part of the movable pulley, this protrusion functions as a rib that suppresses deformation on the outer diameter side of the sheave part of the movable pulley. A gap communicating with the outside can be prevented more reliably.

It is a figure explaining the hydraulic chamber structure in the pulley concerning an embodiment. It is a figure explaining the effect | action of the hydraulic chamber structure in the pulley concerning Embodiment. It is a figure explaining the generation | occurrence | production mechanism of a clearance gap in the hydraulic chamber structure in the pulley concerning a prior art example. It is a figure explaining the hydraulic chamber structure in the pulley concerning a prior art example.

Hereinafter, the hydraulic chamber structure of the primary pulley according to the embodiment will be described.
FIG. 1 is a diagram for explaining a hydraulic chamber composition of the primary pulley 1 according to the embodiment, and is an enlarged view showing the periphery of the primary pulley 1 constituting the variator of the belt type continuously variable transmission.

  As shown in FIG. 1, the primary pulley 1 includes a fixed pulley 2 and a movable pulley 3 that is extrapolated to a shaft portion 21 of the fixed pulley 2. The movable pulley 3 and the fixed pulley 2 are connected by spline coupling, and the movable pulley 3 is restricted from rotating relative to the fixed pulley 2 in the circumferential direction around the rotation axis X1 in the shaft portion 21 of the fixed pulley 2. Thus, it is provided so as to be movable in the direction of the rotation axis X1.

The fixed pulley 2 includes a shaft portion 21 arranged along the rotation axis X1 and a fixed-side sheave portion 22 extending from the outer periphery of the shaft portion 21 to the radially outer side of the rotation shaft X1.
The fixed sheave portion 22 is provided over the entire circumference in the circumferential direction around the rotation axis X1 of the shaft portion 21, and the surface of the fixed sheave portion 22 on the movable pulley 3 side is inclined with respect to the rotation axis X1. Sheave surface 221 is formed.

  The movable pulley 3 has a cylindrical base portion 31 that is extrapolated to the shaft portion 21 of the fixed pulley 2, and a movable-side sheave portion 32 that extends from the outer periphery of the base portion 31 to the radially outer side of the rotation axis X <b> 1. .

  The movable sheave portion 32 is also provided over the entire circumference in the circumferential direction around the rotation axis X1 of the base portion 31, and the surface of the movable sheave portion 32 on the fixed pulley 2 side is inclined with respect to the rotation axis X1. Sheave surface 321 is formed.

  The sheave surface 321 of the movable sheave portion 32 and the sheave surface 221 of the fixed sheave portion 22 are provided in such a direction that the separation distance D increases from the rotation axis X1 toward the radially outer side. A region between the sheave surfaces 221 and 321 facing each other in the X1 direction is a V groove 8 around which the belt V is wound.

In the movable pulley 3, one surface of the movable sheave portion 32 in the direction of the rotation axis X <b> 1 is a sheave surface 321, and the other surface is a hydraulic pressure acting surface 322 of the hydraulic pressure P supplied to the hydraulic chamber R. . The hydraulic action surface 322 is a flat surface orthogonal to the rotation axis X1.
In the movable sheave portion 32, a step portion 323 to which the ring-shaped joint portion 42 of the cylinder 4 is fitted is provided on the outer diameter side of the hydraulic acting surface 322, and the outer diameter side of the step portion 323 is located on the outer diameter side. 4 is a joint surface 322a with the joint portion 42.
The joint surface 322a is provided in a direction perpendicular to the rotation axis X1, and has a ring shape when viewed from the direction of the rotation axis X1.

The hydraulic acting surface 322 and the joining surface 322a are separated by a predetermined length L1 in the direction of the rotation axis X1, and the joining portion 42 of the cylinder 4 is formed with the same thickness in the direction of the rotation axis X1 as this length L1.
Therefore, when the joint portion 42 of the cylinder 4 is externally fitted to the step portion 323 of the movable sheave portion 32, the inner side surface 42 c of the joint portion 42 is provided flush with the hydraulic action surface 322.

  The joint surface 322a is provided with a ring-shaped protrusion 324 when viewed from the direction of the rotation axis X1. The protrusion 324 is provided so as to be centered on the rotation axis X1 when viewed from the direction of the rotation axis X1, and extends in a direction away from the movable sheave portion 32 along the rotation axis X1.

  In the joint portion 42 of the cylinder 4 joined to the joint surface 322a, a ring-shaped groove 421 into which the ring-shaped protrusion 324 fits is opened on a surface facing the joint surface 322a (joint surface 42a).

The cylinder 4 has a cylindrical tubular portion 41 and a joining portion 42 (disc portion) formed by bending one end of the tubular portion 41 on the movable pulley 3 side toward the inner diameter side.
The cylinder 4 joins the joint surface 42a of the joint portion 42 provided at one end of the cylindrical portion 41 to the joint surface 322a of the hydraulic acting surface 322 in the movable sheave portion 32 from the direction of the rotation axis X1 to move the movable side. The sheave portion 32 is fixed to the hydraulic action surface 322. And when joining the joining surface 42a of the joining part 42 to the joining surface 322a of the hydraulic action surface 322, the protrusion 324 of the joining surface 322a fits in the groove | channel 421 of the joining surface 42a.

  In this state, the cylinder 4 follows the movement of the movable pulley 3 in the direction of the rotation axis X1, and moves in the direction of the rotation axis X1 integrally with the movable pulley 3.

An outer peripheral portion 51 of the piston 5 fixed to the shaft portion 21 of the fixed pulley 2 is in contact with an inner periphery 41 a of the cylindrical portion 41 of the cylinder 4, and the cylinder 4 rotates integrally with the movable sheave portion 32. When moved in the X1 direction, the outer peripheral portion 51 of the piston 5 slides on the inner periphery of the cylindrical portion 41 of the cylinder 4.
A seal ring 52 is fitted on the outer peripheral portion 51 of the piston 5 so as to seal a gap between the outer peripheral portion 51 of the piston 5 and the cylindrical portion 41 of the cylinder 4. doing.

In the embodiment, the opening of the cylindrical tubular portion 41 of the cylinder 4 is sealed with the disk-shaped piston 5, and the hydraulic acting surface 322 of the movable sheave portion 32 and the piston are located inside the cylinder 4. 5 is formed with a hydraulic chamber R.
The hydraulic chamber R is supplied with hydraulic pressure through an oil passage 21 a provided in the shaft portion 21 of the fixed pulley 2 and an oil hole 21 b, and when the hydraulic pressure P is supplied to the hydraulic chamber R. Due to the hydraulic pressure P, the joining portion 42 of the cylinder 4 is pushed toward the movable sheave portion 32, and the joining surface 42 a of the joining portion 42 is brought into pressure contact with the hydraulic acting surface 322 of the movable sheave portion 32. Then, the movable pulley 3 pushed by the hydraulic pressure P is displaced in the direction of narrowing the groove width of the V groove 8 (left direction in the figure).

Next, the operation of the hydraulic chamber structure in the primary pulley 1 according to the embodiment will be described in comparison with the case of the hydraulic chamber structure in the primary pulley according to the conventional example.
2A and 2B are views for explaining the action of the hydraulic chamber structure in the primary pulley 1 according to the embodiment. FIG. 2A is an enlarged view around the hydraulic chamber R attached to the movable pulley 3, and FIG. These are figures explaining the effect | action of the processus | protrusion 324 when a deformation | transformation arises in the outer diameter side of the movable sheave part 32 with the pressing force which acts from the element E. FIG.
FIG. 3 is a view for explaining a mechanism for generating the gap S in the hydraulic chamber structure in the pulley according to the conventional example. FIG. 3A is an enlarged view around the hydraulic chamber R attached to the movable pulley 92. ) Is a diagram illustrating a case where the pressing force acting from the element E causes a deformation on the outer diameter side of the movable sheave portion 922. FIG.

The belt V wound around the V groove 8 between the sheave surfaces 221 and 321 is subjected to a pressing force in the direction of narrowing the winding radius of the primary pulley 1 of the belt V, and the element E that supports the belt V A pressing force F1 is applied to the element E to move the element E in the radial direction.
Therefore, a pressing force F2 in the direction of widening the groove width of the V-groove 8 acts on the fixed sheave portion 22 and the movable sheave portion 32 of the primary pulley 1 from the element E that supports the belt V. A pressing force F <b> 2 that constantly urges the movable sheave portion 32 in the direction separating the fixed sheave portion 22 from the fixed sheave portion 22 (rightward in the drawing) is constantly acting on the sheave portion 32.

  Therefore, when the element E that supports the belt V is located on the outer diameter side of the step portion 323 of the movable sheave portion 32 (for example, when the gear ratio is the highest), the thickness in the direction of the rotation axis X1 is The pressing force F2 from the element E acts on a thin area (area where the bonding surface 322a is provided).

  Here, the joint surface 322a of the movable sheave portion 32 is provided with a ring-shaped protrusion 324, and the rigidity strength of the region on the outer diameter side of the step portion 323 (region where the joint surface 322a is provided) is increased. Since it is raised by the projection 324, it is not easily deformed by the pressing force F2 acting from the element E.

In addition, when the entire region on the outer diameter side of the step portion 323 (region where the joint surface 322a is provided) is deformed by the pressing force F2 from the element E, the boundary between the step portion 323 and the joint surface 322a. The region on the outer diameter side with respect to the stepped portion 323 tilts with P1 as a fulcrum (see FIG. 2B, arrow a).
Then, the protrusion 324 fitted in the groove 421 provided in the joint portion 42 is pressed against the inner periphery of the groove 421 and the joint portion 42 moves in a direction away from the hydraulic acting surface 322 of the movable sheave portion 32. Is regulated.
In particular, since a step portion 323 to which the joint portion 42 is fitted is provided on the outer diameter side of the hydraulic acting surface 322, when the outer diameter side of the movable sheave portion 32 is deformed to the hydraulic chamber R side, the joint portion 42. The protrusion 324 fitted in the groove 421 is displaced in the direction of sandwiching the inner diameter side of the joint portion 42 with the stepped portion 323 (see arrow b in the figure), and the end portion 42b on the inner diameter side of the joint portion 42 Is held in a state where it is pressed against the stepped portion 323 without any gap (see arrow c in the figure).

  Thereby, even if the region on the outer diameter side of the step portion 323 of the movable sheave portion 32 (the region where the joining surface 322 a is provided) is deformed by the pressing force F <b> 2 acting from the element E, the movable sheave portion 32. No gap is formed between the outer diameter side region (region where the joint surface 322a is provided) and the joint portion 42 (joint surface 42a) of the cylinder 4.

On the other hand, as shown in FIG. 3, in the case of the fitting mode of the movable sheave portion 922 and the fitting portion 932 of the cylinder 93 according to the conventional example, the sheave portion 922 of the movable pulley 92 The thickness W of the region on the outer diameter side of the portion 924 is thinner than the thickness of the region on the inner diameter side of the step portion 924.
Therefore, the rigidity strength of the outer diameter side region from the step portion 924 is lower than the rigidity strength of the inner diameter side region, and the pressing force F from the element E causes the rigidity strength of the sheave portion 922 on the outer diameter side. As a result, the outer diameter side of the sheave portion 922 is deformed in a direction away from the element E (see FIG. 3B).

Then, since the ring-shaped fitting portion 932 of the cylinder 93 is only fitted and attached to the step portion 924 of the sheave portion 922, if the region on the outer diameter side of the step portion 924 is deformed, the deformation As a result of the fitting portion 932 being pushed by the region thus formed, there may be a gap S between the sheave portion 922 and the fitting portion 932 that communicates the inside and the outside of the hydraulic chamber R.
In such a case, the hydraulic pressure P in the hydraulic chamber R leaks out from the gap S between the sheave portion 922 and the fitting portion 932.

Thus, in the case of the hydraulic chamber structure in the primary pulley 1 according to the embodiment,
The rigidity strength of the outer diameter side region (the region where the joint surface 322a is provided) of the movable sheave portion 32 from the step portion 323 is enhanced by the protrusion 324, so that the pressing force F2 acting from the element E can be used easily. There is no deformation. Further, even if the region on the outer diameter side of the step portion 323 of the movable sheave portion 32 (the region where the joint surface 322a is provided) is deformed by the pressing force F2 acting from the element E, the ring shape of the joint portion 42 is obtained. The projection 42, which is fitted in the groove 421, holds the end 42 b on the inner diameter side of the joint portion 42 in a state where it is pressed against the stepped portion 323 without any gap, and thus the outer diameter of the movable sheave portion 32. A gap is not generated between the side region (region where the joint surface 322a is provided) and the joint portion 42 (joint surface 42a) of the cylinder 4, and the hydraulic pressure in the hydraulic chamber R does not leak out.

As described above, in the embodiment,
(1) The movable pulley 3 extrapolated to the shaft portion 21 of the fixed pulley 2 is provided so as to be movable in the direction of the rotation axis X1, and the rotation side X1 direction of the movable sheave portion 32 (sheave portion) of the movable pulley 3 is provided. One surface is a sheave surface 321 that forms a V-groove 8 around which the belt V is wound, and the other surface is a hydraulic acting surface 322 that generates a narrow pressure acting on the belt V on the movable sheave portion 32 ( Hydraulic working surface)
A cylinder 4 in which one end of the cylindrical portion 41 on the movable pulley 3 side is bent toward the inner diameter side and a ring-shaped joining portion 42 (disc portion) is joined to the hydraulic acting surface 322 from the direction of the rotation axis X1; A hydraulic chamber R is formed from the working surface 322;
The movable pulley 3 has a hydraulic chamber structure in a pulley configured to be displaced by a hydraulic pressure P supplied to the hydraulic chamber R in a direction in which the width of the V groove 8 is reduced.
Of the hydraulic acting surface 322 joined to each other in the direction of the rotation axis X1 and the joining portion 42 of the cylinder 4, the hydraulic acting surface 322 is provided with a ring-shaped protrusion 324 when viewed from the direction of the rotation axis X1 and the joining portion 42. Further, a ring-shaped groove 421 into which the protrusion 324 is fitted is provided.

With this configuration, the rigidity strength of the outer diameter side region (the region where the joint surface 322a is provided) of the movable sheave portion 32 is enhanced by the protrusion 324, so that the pressing force F2 acting from the element E is used. There is no easy deformation.
Furthermore, the outer diameter side region of the movable sheave portion 32 (the region where the joining surface 322a is provided) is deformed by the pressing force F2 acting from the element E, and the hydraulic acting surface 322 and the joining portion 42 of the cylinder 4 Even if a gap is generated between the joint surfaces of the two, the protrusions 324 provided on the hydraulic action surface 322 are fitted in the grooves provided on the joint portion 42, thereby There is no gap to communicate.
As a result, it is possible to suitably prevent the belt from slipping due to insufficient clamping force of the belt V (element E) by the sheave surface 221 of the fixed sheave portion 22 and the sheave surface 321 of the movable sheave portion 32. Thus, it is possible to prevent a situation in which the planned gear ratio cannot be realized in the variator.

(2) The joining portion 42 of the cylinder 4 has one surface in the direction of the rotation axis X1 as a joining surface 42a with the hydraulic acting surface 322 of the movable sheave portion 32, and the hydraulic pressure P supplied to the hydraulic chamber R is When acting on the other surface, the joining surface 42a is configured to come into pressure contact with the hydraulic acting surface 322 of the movable sheave portion 32 from the direction of the rotation axis X1, and the outer diameter side of the movable sheave portion 32 is the hydraulic chamber R. When deformed to the side, the ring-shaped protrusion 324 fitted in the groove 421 is pressed against the inner periphery of the groove 421 to move the joint portion 42 in the direction away from the hydraulic acting surface 322 of the movable sheave portion 32. The configuration is regulated.

  With this configuration, even if the outer diameter side of the movable sheave portion 32 is deformed to the hydraulic chamber R side (FIG. 2B, right side), the ring-shaped protrusion 324 fitted into the groove 421 is formed into the groove. Since there is no gap between the protrusion 324 and the groove 421 in pressure contact with the inner circumference of the 421, leakage of the hydraulic pressure P in the hydraulic chamber R to the outside can be reliably prevented.

  (3) On the outer diameter side of the hydraulic acting surface 322, a step portion 323 to which the joining portion 42 (disk portion) of the cylinder 4 is fitted is provided, and the outer diameter is larger than the step portion 323 in the hydraulic acting surface 322. The side is configured as a joint surface 322a that is thinner in the direction of the rotation axis X1 than the inner diameter side.

With this configuration, when the outer diameter side of the movable sheave portion 32 is deformed to the hydraulic chamber R side ((b) in FIG. 2, the right side), the protrusion 324 fitted into the groove 421 is changed to the inner diameter side of the joint portion 42. End 42b is pressed from the radially outer side of the rotation axis X1 toward the step 323, so that the end 42b on the inner diameter side of the joint portion 42 is held in pressure contact with the step 323 without any gap. Become.
This reliably prevents a gap from being formed between the outer diameter side region of the movable sheave portion 32 (the region where the joint surface 322a is provided) and the joint portion 42 (joint surface 42a) of the cylinder 4. Therefore, leakage of hydraulic pressure from the hydraulic chamber R can be suitably prevented.

(4) When the outer diameter side of the movable sheave portion 32 is deformed to the hydraulic chamber R side, the projection 324 fitted in the groove 421 is pressed against the inner periphery of the groove 421 and is joined to the step portion 323. The structure is configured such that a pressing force in a direction to press the outer periphery of the step portion 323 is applied to the joint portion 42 to restrict the movement of the joint portion 42 in the direction away from the hydraulic acting surface 322 of the movable sheave portion 32.

With this configuration, the entire region on the outer diameter side of the stepped portion 323 of the movable sheave portion 32 (the region where the joining surface 322a is provided) is deformed to the hydraulic chamber R side by the pressing force F2 from the element E. In this case, the entire region on the outer diameter side of the step portion 323 is inclined with the boundary P1 between the step portion 323 and the joint surface 322a as a fulcrum (see the arrow a in FIG. 2B).
Then, the protrusion 324 fitted in the ring-shaped groove 421 of the joint portion 42 is displaced in a direction of sandwiching the inner diameter side of the joint portion 42 with the stepped portion 323 (see the arrow b in the figure). The end 42b on the inner diameter side of the portion 42 is held in pressure contact with the stepped portion 323 without any gap (see the arrow c in the figure), and the leakage of the hydraulic pressure P in the hydraulic chamber R to the outside is further increased. Certainty can be prevented.

  In the above-described embodiment, the case where the ring-shaped protrusion 324 is provided on the movable pulley 3 side and the ring-shaped groove 421 into which the protrusion 324 is fitted is provided on the cylinder 4 side is illustrated. However, the embodiment is not limited to this embodiment.

For example, a ring-shaped groove is provided in a region on the outer diameter side of the stepped portion 323 of the movable sheave portion 32, and the ring-shaped groove provided in the movable-side sheave portion 32 is fitted into the joint portion 42 of the cylinder 4. It is good also as a structure which provided the ring-shaped protrusion to match.
Also with this configuration, the outer diameter side region (region where the joint surface 322a is provided) of the movable sheave portion 32 and the joint portion 42 of the cylinder 4 are pressed against each other without a gap. Therefore, leakage of the hydraulic pressure in the hydraulic chamber R can be suitably prevented.

  Further, the projection provided on one of the joint surfaces (joint surfaces 322a and 42a) of the movable sheave portion 32 and the cylinder 4 may be two or more projections having different outer diameters. In this case, a ring-shaped groove provided on the other of the joint surfaces (joint surfaces 322a, 42a) of the movable sheave portion 32 and the cylinder 4 is formed with an outer diameter with which each projection engages with the projection. By providing the same number, leakage of the hydraulic pressure in the hydraulic chamber R can be more reliably prevented.

Further, each of the joint surfaces (joint surfaces 322a and 42a) of the movable sheave portion 32 and the cylinder 4 is provided with a protrusion and a ring-shaped groove, and the protrusion of one joint surface 322a and the ring-shaped groove are provided. The groove may be configured to engage with the ring-shaped groove and the protrusion on the other joint surface 42a.
Also by doing in this way, leakage of the hydraulic pressure in the hydraulic chamber R can be suitably prevented.

DESCRIPTION OF SYMBOLS 1 Primary pulley 2 Fixed pulley 21 Shaft part 22 Fixed side sheave part 221 Sheave surface 3 Movable pulley 31 Base part 32 Movable side sheave part 321 Sheave surface 322 Hydraulic action surface 322a Joint surface 323 Step part 324 Protrusion 4 Cylinder 41 Cylindrical part 41a Peripheral 42 joint 42a joint 42b end 42c inner surface 421 groove 5 piston 51 outer periphery 52 seal ring 8 V groove 431 groove E element R hydraulic chamber V belt X1 rotating shaft

Claims (4)

A movable pulley externally attached to the shaft portion of the fixed pulley is provided so as to be movable in the rotational axis direction, and one surface of the sheave portion of the movable pulley in the rotational shaft direction has a V groove around which the belt is wound. The sheave surface to be formed, and the other surface is a hydraulic working surface that generates a narrow pressure acting on the belt at the sheave portion,
A hydraulic chamber is formed from a cylinder in which a disk portion formed by bending one end of a cylindrical portion toward the inner diameter side is joined to the hydraulic operation surface from the direction of the rotation axis, and the hydraulic operation surface,
The movable pulley is a hydraulic chamber structure in a pulley configured to be displaced in a direction of narrowing the width of the V-groove by the hydraulic pressure supplied to the hydraulic chamber;
Among the oil pressure action surface and the disk portion joined together in the rotation axis direction, the oil pressure action surface is provided with a ring-shaped protrusion when viewed from the rotation axis direction, and
A hydraulic chamber structure in a pulley, wherein the disk portion is provided with a ring-shaped groove into which the protrusion is fitted. In the disk portion, when one surface in the rotational axis direction is a joint surface with the hydraulic pressure acting surface of the sheave portion, and the hydraulic pressure supplied to the hydraulic chamber acts on the other surface, The joining surface is configured to be brought into pressure contact with the hydraulic acting surface of the sheave portion from the rotation axis direction, and
When the outer diameter side of the sheave portion is deformed to the hydraulic chamber side, the protrusion fitted into the groove is pressed against the inner periphery of the groove in a direction away from the hydraulic acting surface of the sheave portion. The hydraulic chamber structure in a pulley according to claim 1, wherein the hydraulic chamber structure is configured to restrict movement of the disc portion.   3. The hydraulic chamber structure in a pulley according to claim 1, wherein a step portion on which the disk portion is fitted is provided on an outer diameter side of the hydraulic pressure acting surface.   When the outer diameter side of the sheave portion is deformed to the hydraulic chamber side, the protrusion fitted into the groove is pressed against the inner periphery of the groove, and the disk portion externally fitted to the step portion is replaced with the step portion. A pressing force in a direction to press contact with the outer periphery of the disk portion is applied to the disk portion to restrict the movement of the disk portion in a direction away from the hydraulic acting surface of the sheave portion. The hydraulic chamber structure in a pulley according to claim 3, wherein the hydraulic chamber structure is a pulley.