JPH10184826A - Auto-tensioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an auto-tension by which a clearance between a tension pulley and an engine block can be reduced and compactification can be accomplished. SOLUTION: An auxiliary reservoir chamber is arranged on the side of a plunger in a direct acting type hydraulic damper 28, and the hydraulic damper 28 is arranged between a tension pulley 21 and an engine block 27 so as to be stored inside a bevel of the tension pulley 21 while the plunger is brought into contact with a pin of an eccentric wheel 23, and as a result, a clearance W1 between the tension pulley 21 and the engine block 27 is reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an auto-tensioner used for adjusting the tension of a timing belt of an automobile, and more particularly to an auto-tensioner which is reduced in size as a whole.

[0002]

2. Description of the Related Art FIGS. 12 (a) and 12 (b) show an auto-tensioner proposed by the present applicant in Japanese Utility Model Laid-Open No. 2-56950, which has a unit structure in which a hydraulic damper and a tension pulley are integrated. The use of the damper has an advantage that the damping ability is excellent.

In this automatic tensioner, a tension pulley 1 is rotatably mounted around an eccentric wheel 2 via a bearing 3, and a fixing bolt 5 penetrating through an eccentric hole 4 of the eccentric wheel 2.
Is fastened to the wall of the engine block 6, the hydraulic damper 7 is fixedly arranged in the gap between the tension pulley 1 and the engine block 6, and the tip mounting portion 8 of the hydraulic damper 7 is mounted on the fixing bolt 5, and the upper end of the plunger 9 Abuts on a projection 10 provided on the eccentric wheel 2, one end of a torsion coil spring 11 disposed between the eccentric wheel 2 and the hydraulic damper 7 is locked on the eccentric wheel 2, and the other end is locked on the hydraulic damper 7. doing.

The hydraulic damper 7 includes a damper cylinder 12
The plunger 9 is inserted movably in the axial direction so as to form the pressure chamber 13 at the lower part of the liquid chamber in the internal liquid chamber, and the lower part of the plunger 9 is connected with the chamber in the plunger 9 and the lower part of the pressure chamber 13. A communication hole 14 for communication and a check valve 15 located at the lower end of the communication hole 14 are provided, and a return coil spring 16 for pushing up the plunger 9 in the pressure chamber 13 is contracted.

The chamber in the plunger 9 is a reservoir chamber 17, the upper half is an air chamber, the lower half is filled with hydraulic oil, and when the plunger 9 is pushed by the tension of the belt A, the operation in the pressure chamber 13 is started. The oil is supplied to the damper cylinder 12 and the plunger 9
When the plunger 9 is raised due to the loosening of the belt A, the check valve 15 is opened, and the operating oil flows from the reservoir chamber 17 to the pressure chamber 13 when the plunger 9 is raised due to the loosening of the belt A. become.

[0006]

The conventional hydraulic damper 7 described above has a structure in which the reservoir chamber 17 is provided inside the plunger 9, so that if the total length of the hydraulic damper is shortened, the volume of the reservoir chamber is reduced. Becomes very small,
The air in the reservoir chamber 17 may enter the pressure chamber 13.

For this reason, the total length of the hydraulic damper 7 cannot be shortened, and as shown in FIG. 12, the hydraulic damper 7 protrudes from the umbrella of the tension pulley 1 to the outside. Clearance W of tension pulley 1
In order to arrange the hydraulic damper 7 in the
About 5 mm is required, and there is a problem that the height of the tension pulley 1 from the engine block is required to some extent.

Also, the torsion coil spring 11 is
And the eccentric wheel 2, even if the hydraulic damper 7 is downsized,
Can not be stored inside the umbrella.

Accordingly, an object of the present invention is to provide an auto-tensioner in which the size of a hydraulic damper can be accommodated in the umbrella of a tension pulley by reducing the size of the hydraulic damper, and the gap between the engine block and the tension pulley can be reduced. To provide.

[0010]

In order to solve the above-mentioned problems, the invention of claim 1 applies a spring force of a tension adjusting spring to an eccentric wheel of a tension pulley, and rotates the eccentric wheel when the belt tension increases. A direct-acting hydraulic damper formed by engaging a plunger or rod with a part of an eccentric ring and providing a check valve located between a pressure chamber and a reservoir chamber in a damper cylinder for buffering It adopts a configuration housed in a pulley umbrella.

According to a second aspect of the present invention, in the first aspect of the present invention, the direct-acting hydraulic damper is provided with a sub-reservoir chamber at a side of a damper cylinder accommodating a plunger or a rod and a plunger so as to be movable in the axial direction. Is provided so as to communicate with the reservoir chamber.

According to a third aspect of the present invention, in the first or second aspect, the air space is left in the reservoir chamber or the auxiliary reservoir chamber of the direct acting hydraulic damper.

According to a fourth aspect of the present invention, in the first aspect of the present invention, a straight line connecting the center of the fulcrum shaft of the eccentric wheel and the linear hydraulic damper to the center of the pulley and a projecting direction of the plunger or rod of the hydraulic damper. The configuration is such that the angle is within 30 ° to 90 °.

[0014]

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

In the first embodiment shown in FIGS. 1 and 2, a tension pulley 21 is attached via a rolling bearing 22 so as to be rotatable around an eccentric ring 23, and an eccentric hole provided in the eccentric ring 23 is provided. 24 is fixed to the engine block 27 through a sliding bearing 25, and between the eccentric wheel 23 and the facing surface of the engine block 27,
A direct-acting hydraulic damper 28 is disposed so as to fit inside the umbrella of the tension pulley 21.

As shown in FIG. 2, the direct-acting type hydraulic damper 28 is provided with a liquid chamber 3 provided in a damper cylinder 29 in an oblique vertical direction.
The sub-reservoir chamber 33 and a mounting portion 34 are provided on the projection 32 connected to one side of the damper cylinder 29. The sub-reservoir 33 is accommodated in the plunger 31 so as to be movable in the axial direction. .

The plunger 31 has a lower end of a reservoir chamber 35 provided along the axis and communicates with a pressure chamber 36 formed at a lower end of the liquid chamber 30 through a passage 37. A check valve 38 and a pressure chamber 3
6, a return coil spring 39 for the plunger 31 is contracted.

A circumferential groove 40 communicating with the reservoir chamber 35 is provided on the outer peripheral surface of the intermediate portion of the plunger 31, and the sub-reservoir chamber 3 is provided.
3 is provided at a right angle to the liquid chamber 30, communicates with the circumferential groove 40 through the passage 41, and the open end of the sub-reservoir chamber 33 is in close contact with the rubber cap 42.

The plunger 31 has a head 4 at its upper end.
3, the upper end of the reservoir chamber 35 is sealed by an O-ring 44, and the upper end of the liquid chamber 30 is sealed by an oil seal 45.

The direct-acting hydraulic damper 28 is filled with hydraulic oil (oil) in an amount that fills the entire reservoir chamber 35 and the pressure chamber 36 and a part of the sub-reservoir chamber 33. The upper space is arranged to be an air chamber.

As shown in FIGS. 1B and 2, the direct-acting hydraulic damper 28 has a fixing bolt 26 that penetrates the mounting portion 34 and a fixing pin 46 that has the projection 32 penetrated by an engine block. 27, the sub-reservoir chamber 33 is fixed so as to be inclined obliquely upward, and the hydraulic oil is left in an air space above the sub-reservoir chamber 33 so that the oil level does not contact the rubber cap 42. And the head 43 of the plunger 31 is in contact with a pin 47 protruding from the eccentric wheel 23.

The direct-acting hydraulic damper 28 includes a liquid chamber 30.
By providing the sub-reservoir chamber 33 on the side of the hydraulic pressure damper 28, the entire length of the plunger 31 can be shortened, whereby the entire hydraulic damper 28 can be downsized and housed in the umbrella of the tension pulley 21. 21
And it is possible to reduce the gap W ₁ between the engine block 27.

On the other hand, the eccentric wheel 23 supporting the tension pulley 21 has a window hole 4 into which a fixing pin 46 is loosely fitted.
A tension adjusting spring 51, whose tip abuts a fixing pin 46 via a spring seat 50, is contracted in a horizontal hole 49 provided to communicate with the window hole 48, and is fixed to the eccentric wheel 23. The rotational force in the tensioning direction of the belt A with the bolt 26 as a fulcrum is urged.

In FIG. 1A, the tension adjusting spring 51 is used.
Is a single coil spring, but in the second embodiment shown in FIG. 3, a double coil spring is used as the tension adjusting spring 51.

In the third embodiment shown in FIGS. 4A and 4B, a torsion coil spring is used as the tension adjusting spring 51. The torsion coil spring is provided around the fixing bolt 26 on the outer surface of the eccentric wheel 23. A torsion coil spring is externally fitted to the projection 52 provided, and one end 51a is locked to the projection 52, and the other end 51b is locked to the fixing pin 46.
The turning force in the direction of stretching is urged.

In each of the above embodiments, the tension adjusting spring 51 is housed inside the eccentric ring 23 or arranged on the outer surface side of the eccentric ring 23, so that the space for the tension adjusting spring 51 is limited to the tension pulley 21 and the engine. not a failure to reduce the gap W ₁ of the block 27.

In each of the embodiments, 53 in FIG.
Indicates a hexagonal hole for resetting provided in the eccentric wheel 23, applies a torque to the eccentric wheel 23 with a hexagon wrench, pushes the plunger 31, and hangs the belt A on the pulley 21 in this state, and releases the hex wrench. The pulley 21 moves in the direction of pressing the belt A, and is set.

The auto-tensioners according to the first to third embodiments of the present invention have the above-described structure. When the tension of the belt A increases in the state shown in FIG. 2, the tension pulley 21 and the eccentric wheel 23 The plunger 31 is pushed in by the pin 47 with the fixing bolt 26 pivoting counterclockwise in FIG.

When the plunger 31 is pushed, the pressure chamber 3
The hydraulic oil in 6 moves from the leak gap between the plunger 31 and the inner peripheral surface of the liquid chamber 30 to the peripheral groove 40 to buffer the operation of the plunger 31. The hydraulic oil that has moved to the circumferential groove 40 is
1 enters the sub reservoir chamber 33.

The plunger 31 stops at the balance point between the tension of the belt A and the spring force of the tension adjusting spring 51.

On the other hand, when the tension of the belt A decreases, the tension pulley 21 and the eccentric wheel 23 rotate clockwise in FIG. 2, and the tension pulley 21 swings at the balance point between the tension adjusting spring 51 and the tension of the belt A. Motion stops.

At this time, since the pin 47 of the eccentric wheel 23 moves away from the plunger 31, the plunger 3
1 rises following the movement of the pin 47 due to the pressing of the return coil spring 39.

In this case, since the check valve 38 opens the communication passage 37, the hydraulic oil in the reservoir chamber 35 is released from the pressure chamber 36.
And the working oil in the sub reservoir chamber 33 flows into the reservoir chamber 35, and the plunger 31 immediately follows the movement of the pin 47.

FIGS. 5 to 7 show the first to third examples shown above.
The fourth embodiment in which the plunger of the embodiment of the present invention is constituted by separate parts of the rod and the plunger, and the linear motion type hydraulic damper is further miniaturized.
Is shown. Note that the same parts as those in the first to third examples are denoted by the same reference numerals, and description thereof will be omitted. The same applies to the following examples.

The direct acting hydraulic damper 28 shown in the fourth embodiment has a plunger 6 in a damper cylinder 29.
1 is slidably accommodated in the axial direction.
The rod 62 located on the opening end side in 9 has a straight shape, which improves the manufacturability and assemblability, and is guided by a wear ring 63 provided inside the cylinder 29 so as to be movable in the axial direction.

The inner end of the rod 62 comes into contact with a tapered recess provided on the inner diameter of the plunger 61.
Two or more oil grooves 64 communicating with the passage 37 are formed, and a space between the plunger 61 and the wear ring 63 is formed in the reservoir chamber 35.
It has become.

The above-mentioned wear ring 63 is press-fitted.
Inserted loosely into cylinder 29 so that shavings from cylinder 29 and wear ring 63 do not mix into the oil,
The open end of the cylinder 29 is sealed by an oil seal 65 whose inner periphery is in close contact with the rod 62.

A groove 66 for retaining the oil seal 65 is provided on the inner periphery of the portion of the cylinder 29 into which the oil seal 65 is press-fitted, so that the oil seal 65 is prevented from being detached simultaneously with the loosely inserted wear ring 63.

The damper cylinder 29 is made of steel, and the plunger return coil spring 39 in the pressure chamber 36 formed at the inner end of the cylinder 29 allows the air mixed in the pressure chamber 36 to quickly enter the reservoir chamber 35. It is formed in a tapered shape so that it can move.

The reservoir chamber 35 communicates with a sub-reservoir chamber 33 located on the side of the reservoir chamber 35 through a passage 41. The passage 41 is eccentric to the upper side of the sub-reservoir chamber 33, and is moved from the reservoir chamber 35 to the sub-reservoir chamber 33. The air can be moved quickly.

The damper cylinder 29 is provided with the fixing bolt 2
6 so as to be rotatable around the rod 6.
The tip of the pin abuts on a pin 47 provided on the eccentric wheel 23, and either or both the pin 47 and the rod 62 are subjected to a surface hardening treatment such as hard chrome plating or nitrocarburizing. As a measure against wear, as shown in FIG.
A rolling element 67 may be provided at a portion where the rolling element 67 is in contact with the rod 62 to make rolling contact.

In the arrangement of the damper cylinder 29 inside the pulley umbrella, as shown in FIG. 6B, a straight line a connecting the fixing bolt 26 serving as a fulcrum of rotation of the eccentric wheel 23 and the center of the pulley 21, and a damper cylinder The angle α between the rod 29 and the axis b along the moving direction of the rod 62 is set to be within 30 ° to 90 °. That is, the angle between the center of the belt winding angle (belt load) f and the angle between 0 ° and 60 ° is set, whereby the damper force c and the load on the fulcrum (the vector of the load from the belt and the damper force) are obtained. (Sum) d and the load e from the belt are distributed in three directions to reduce the load applied to the fixing bolt 26 serving as a fulcrum.

FIG. 7 (a) shows the eccentric ring 23 with the fixing bolt 2
6 shows a structure of a portion for urging a rotational force in the tension direction of the belt A with the fulcrum 6 as a fulcrum. A sliding member 71 formed of a synthetic resin in a cylindrical shape is provided in a concave hole 48a of the eccentric ring 23. A cap member 72 held so as to be movable in the axial direction with respect to the sliding member 71 is fitted into the distal end side of the tension adjusting spring 51 provided in the moving member 71, and the cap member 72 is fixed to the fixing pin 46. Is in contact with

The fifth type of the direct acting hydraulic damper 28 shown in FIG.
In this embodiment, the basic structure is the same as that of the fourth example, except that the damper cylinder 29 is made of an aluminum alloy, and a steel sleeve 73 is inserted into a portion of the cylinder 29 where the plunger 61 slides. , A pressure chamber 36.

The sixth embodiment shown in FIG. 10 has a structure in which the sub-reservoir chamber is omitted in order to further reduce the size of the damper cylinder 29. Basically, the sub-reservoir chamber of the fourth example is used. 33, the reservoir chamber 3 in the damper cylinder 29
The upper part of 5 is an air chamber.

Some auto tensioners for adjusting belt tension can be realized with a small amount of pulley movement. In this case, the stroke of the rod 62 of the hydraulic damper cylinder 29 may be small, and as shown in the sixth example, the auxiliary reservoir It can be put to practical use even with a structure without a room.

The operations of the fourth to sixth embodiments are basically the same as the operations of the first to third examples described above.

The seventh embodiment shown in FIGS. 11 (a) and 11 (b) shows a structure for adjusting the initial tension at the time of attachment to an engine. A part of the damper cylinder 29 is extended in a stay shape. A positioning stay 81 is provided, and an arc-shaped long hole 82 centering on the fixing bolt 26 is provided at the tip thereof.
The bolt 83 inserted through the screw 2 is screwed to the engine block 27.

The fixing pin 47 is connected to the damper cylinder 2
The length is set so as not to protrude toward the engine block 27 side from the mounting portion 34 of No. 9.

When the auto tensioner is attached to the engine block 27, the fixing bolt 26 is temporarily fixed in the phase indicated by the dashed line in FIG. 11A, and the belt A is hung on the tension pulley 21 in this state. , The eccentric wheel 23 is rotated to press the tension pulley 21 against the belt A.

The adjustment of the initial tension of the belt, which absorbs the length of the belt A, the position error of the crank and the camshaft, etc., is performed by the slot 82 of the positioning stay 81, and as shown by the solid line in FIG. The bolt 83 may be tightened at a phase where A is set to an appropriate tension, the stay 81 may be fixed to the engine block 27, and then the fixing bolt 26 may be tightened.

[0052]

As described above, according to the present invention, the direct-acting hydraulic damper is reduced in size and accommodated in the umbrella of the tension pulley, so that the clearance between the tension pulley and the engine block is reduced. And the space saving of the auto tensioner can be achieved.

[Brief description of the drawings]

FIG. 1A is a front view showing a first embodiment of an auto-tensioner according to the present invention, and FIG. 1B is an arrow b in FIG.
Longitudinal sectional view taken along the ₁ -b ₁

FIG. 2 is a longitudinal sectional view showing the structure of a direct acting hydraulic damper in the above embodiment.

FIG. 3 is a longitudinal sectional view of a tension adjusting spring portion according to a second embodiment.

FIG. 4A is a front view showing a third embodiment,
(B) is a longitudinal sectional view along the arrow b ₂ -b ₂ of (a).

FIG. 5A is a front view showing a fourth embodiment,
(B) is a vertical side view of the above.

6 (a) is a cross-sectional plan view of FIG. 5 (a), and FIG. 6 (b) is a vertical cross-sectional view along an arrow VI-VI of FIG. 5 (b).

7A is a longitudinal sectional view taken along the arrow VII-VII of FIG. 5B, and FIG. 7B is a longitudinal sectional view of a direct acting hydraulic damper.

FIG. 8 is a longitudinal sectional view in which a rolling element is used in a portion where a rod of a hydraulic damper contacts.

FIG. 9 is a longitudinal sectional view showing a fifth embodiment of a direct acting hydraulic damper.

FIG. 10 is a longitudinal sectional view showing a sixth embodiment of a direct acting hydraulic damper;

FIG. 11A is a front view showing a seventh embodiment,
(B) is a cross-sectional plan view of the above.

12A is a longitudinal sectional view showing a conventional auto tensioner, and FIG. 12B is a lateral view showing a hydraulic damper portion of the same.

[Explanation of symbols]

 21 Tension Pulley 23 Eccentric Wheel 26 Fixing Bolt 27 Engine Block 28 Linear Hydraulic Damper 29 Damper Cylinder 30 Liquid Chamber 31 Plunger 33 Sub Reservoir Chamber 35 Reservoir Chamber 36 Pressure Chamber 38 Check Valve 39 Return Coil Spring 46 Fixing Pin 47 Pin 51 Spring for Tension Adjustment 61 Plunger 62 Rod 63 Wearing

Claims (4)

[Claims] 1. A spring for tension adjustment is applied to an eccentric wheel of a tension pulley, and a plunger or a rod is engaged with a part of the eccentric wheel so as to buffer the rotation of the eccentric wheel when the tension of the belt increases. An automatic tensioner in which a direct-acting hydraulic damper formed by providing a check valve located between a pressure chamber and a reservoir chamber in a damper cylinder is housed in a tension pulley umbrella. 2. A direct-acting hydraulic damper, wherein a sub-reservoir chamber is provided on a side of a plunger or a damper cylinder housing a rod and a plunger movably in an axial direction so as to communicate with the reservoir chamber. Auto tensioner according to 1. 3. The auto-tensioner according to claim 1, wherein an air space is left in a reservoir chamber or a sub-reservoir chamber of the direct acting hydraulic damper. 4. An angle between a straight line connecting the center of the fulcrum shaft of the eccentric ring and the linear motion type hydraulic damper and the center of the pulley, and a protruding direction of the plunger or rod of the hydraulic damper is 30 ° to 90 °.
The auto-tensioner according to claim 1, wherein the auto-tensioner is configured to be within the range of °.