JP2001153152A - Motive power transmission mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a stable motive power transmission mechanism having no influence by a change in an ambient temperature, capable of preventing an entrance of foreign matter, capable of preventing abrasion, capable of preventing rust and capable of surely maintaining a cutoff state after cutting off the transmission of torque once. SOLUTION: When generating torque exceeding a preset value by an accident of a compressor 1, one taper surface (either one according to the rotational direction of a pulley) of respective radial directional tapered recessed parts 8a of a pulley 4 side inner ring 8 presses respective balls 9 to be moved to respective radial directional and rotary shaft directional recessed parts 10b of a hub 10. Since there is the slight possibility of returning the respective balls to the radial directional outside in a state after this movement, the respective one taper surfaces and an inclined face 12a of a ball pressing ring 12 move the respective balls further to the respective rotary shaft directional inmost recessed parts 10c, so that the respective balls are surely checked from returning to the radial directional outside. Thus, since the inner ring and the respective balls separate from each other, rotation of the pulley is not transmitted to a rotary shaft 2 of the compressor.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission mechanism having a function of a torque limiter, and can be widely used in fields such as compressors and general industrial equipment.

[0002]

2. Description of the Related Art A number of power transmission mechanisms of this type have been proposed, and as an example, a power transmission mechanism described in Japanese Patent Application Laid-Open No. 8-135575 will be described with reference to FIG.

[0003] As shown in FIG.
The inner cylinder protrusion 22A of the front housing 22
The inner ring of the ball bearing 24 is fixed, and the outer ring of the ball bearing 24 has
The rotor 25 is fixed. A pulley 26 is fixed to the rotor 25, and a first holding member 28 is fixed to the pulley 26 by a rivet 27.

A hub 29 is attached to a shaft 23 of the compressor 21.
Are fixed by a nut 30, and a second holding member 32 is fixed to the hub 29 by a rivet 31.

An elastic ring 33 made of synthetic resin or rubber is press-fitted between the first holding member 28 and the second holding member 32.

As shown in FIG. 19A, the elastic ring 33 has a petal shape, and a plurality of convex portions 33A and concave portions 33B are formed on the inner and outer peripheral surfaces of the elastic ring 33. . On the outer peripheral surface of the first holding member 28, a plurality of concave portions 28A and convex portions 28B are formed corresponding to the plural convex portions 33A and concave portions 33B of the elastic ring body 33, respectively. Further, on the inner peripheral surface of the second holding member 32, a plurality of concave portions 32A and convex portions 32B are formed corresponding to the plural convex portions 33A and concave portions 33B of the elastic ring body 33, respectively.

The shaft 23 of the compressor 21 is moved from the pulley 26 to the shaft 23 of the compressor 21.
When transmitting a normal torque to the elastic ring 33, the plurality of protrusions 33A and the plurality of recesses 33B of the elastic ring body 33 are respectively formed by the plurality of recesses 28A and the protrusions 28B of the first holding member 28 and the plurality of It compresses and deforms between the concave portion 32A and the convex portion 32B, and transmits torque by its reaction force. And
When a torque exceeding the set value is generated due to a seizure accident of the compressor 21 or the like, the elastic ring body 33 is deformed,
Its radial thickness is reduced. As a result, the elastic ring 3
3 slips with respect to the concave portion 32A and the convex portion 32B of the second holding member 32, so that transmission of torque is interrupted.

[0008]

In the conventional power transmission mechanism, since the first holding member and the second holding member are provided with a plurality of concave portions and convex portions, respectively, along the rotation direction, the elastic ring body is not provided. Even if the vehicle slips once and the protrusions and recesses escape from the recesses and protrusions of the second holding member, the second
There is a possibility that the retaining member may be fitted into the adjacent concave portion and convex portion and transmit the torque again.

Further, in the conventional power transmission mechanism, the function of the torque limiter is unstable because the elastic modulus of the elastic ring body fluctuates due to the rise and fall of the surrounding temperature.

Therefore, the present invention improves on the drawbacks of the conventional power transmission mechanism, is not affected by changes in the surrounding temperature, can prevent foreign substances from entering, can prevent wear and rust, and An object of the present invention is to provide a stable power transmission mechanism that reliably maintains the interrupted state after torque transmission is interrupted once.

[0011]

The present invention employs the following means to solve the above-mentioned problems.

1. A driving-side rotating member having a plurality of radially tapered recesses, a driven-side rotating member connected to a rotating shaft, and having a plurality of radially and rotationally-shaped recesses, and It is composed of each ball that can move to the concave portion in the radial direction and the rotation axis direction, a spring attached to the driven-side rotating member, and a ball pressing ring urged by the spring. An inclined surface formed on a ring presses each of the balls against each of the radially tapered recesses of the driving-side rotating member and the driven-side rotating member, and when the torque is cut off, the respective balls of the driving-side rotating member. A power transmission mechanism in which one tapered surface of the directional tapered recess and the inclined surface of the ball pressing ring move each of the balls to the radially and rotationally axially recessed portions.

2. The driven-side rotating member has a rotating shaft-direction recessed portion that is continuous with the rotating shaft-direction recessed portions. When torque is cut off, the balls move to the rotating shaft-direction recessed portions to move in the radial direction. 2. The power transmission mechanism according to 1 above, wherein

3. The drive-side member includes a pulley, an outer ring fixed to the pulley, an inner ring pressed against each of the balls, and an elastically deformable rubber member coupling between the outer ring and the inner ring. 2. The power transmission mechanism according to the above 1, wherein

4. The power transmission mechanism according to claim 1, wherein the spring is a disc spring, and a biasing force is set on the ball pressing ring by a screw.

5. Between the inner peripheral surface of the driving-side rotating member and the outer peripheral surface of the driven-side rotating member, and between the inner peripheral surface of the driving-side rotating member and the outer peripheral surface of the ball pressing ring,
2. The power transmission mechanism according to the above 1, wherein each of the power transmission mechanisms is sealed by a seal member.

6. The inner peripheral surface of the rubber member and the outer peripheral surface of the driven-side rotating member, and the inner peripheral surface of the rubber member and the outer peripheral surface of the ball pressing ring were sealed by pressing each other. 3. The power transmission mechanism according to 3.

[7] Between the ring-shaped seal member fixed to the inner ring and the outer peripheral surface of the driven-side rotating member,
4. The power transmission mechanism according to 3, wherein the inner peripheral surface of the rubber member and the outer peripheral surface of the ball pressing ring are hermetically sealed by pressing each other.

8. Pressure contact between the inner peripheral surface of the rubber member and the outer peripheral surface of the driven-side rotating member, and between the ring-shaped seal member fixed to the inner ring and the outer peripheral surface of the ball pressing ring, respectively. 4. The power transmission mechanism according to the above 3, wherein the power transmission mechanism is hermetically sealed.

9. When a gap is generated between the outer ring and the pulley, the seal can be maintained even when the outer ring, the rubber member, and the inner ring are moved to the pulley side. 8. The power transmission mechanism according to 8.

10. When a gap is generated between the driven-side rotating member and the rotation shaft, the hermetic seal can be maintained even when the driven-side rotating member, each of the balls and the ball pressing ring are moved to the pulley side. Said 6,7
Or the power transmission mechanism according to 8.

11. The power transmission mechanism according to any one of 5 to 10, wherein a rust preventive material or a lubricating material is sealed in the sealed space.

12. After each of the balls starts moving from each of the radial tapered recesses to each of the radial and rotational axis recesses by the one tapered surface, the angle of the inclined surface of the ball pressing ring contacted by each of the balls is 2. The power transmission mechanism according to claim 1, wherein each of the balls is formed to be smaller than an angle of an inclined surface of the ball pressing ring that comes into contact before the balls start moving.

13. The configuration is such that the torque at which each of the balls starts moving from each of the radial tapered recesses to the radial and rotational axial recesses by the one tapered surface is substantially equal to the torque at the time of complete interruption. Said 1
The power transmission mechanism described in the above.

14. When the torque is cut off, the driven-side rotating member and the ball pressing ring are connected to each other so that the biasing force of the spring acts on each of the balls even in a state in which each of the balls has moved to each of the recesses in the rotational axis direction. 3. The power transmission mechanism according to claim 2, wherein a gap is formed between the power transmission mechanisms.

15. When the torque is cut off, the depth of each of the rotation shaft direction recesses is set so that the biasing force of the spring acts on each of the balls even in a state where each of the balls has moved to the rotation shaft direction recess. 3. The power transmission mechanism according to the above item 2.

16. 5. The power transmission mechanism according to the item 4, wherein the screw is used in combination with a means for preventing loosening.

[0028]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Four embodiments of the present invention will be described below.

First, a compressor using a power transmission mechanism according to a first embodiment of the present invention will be described with reference to FIGS. 1 is a front view, FIG. 2 is an axial sectional view of the compressor when torque is transmitted, FIG. 3 is an axial sectional view of the compressor when torque is cut off, and FIG. 4 is a line A in FIG. FIG. 5 is a sectional view taken along line B- in FIG.
It is sectional drawing by B.

An inner ring of the ball bearing 3 is fixed to a housing of the compressor 1, and a pulley 4 is fixed to an outer ring of the ball bearing 3. An outer ring 5 is provided on the side surface of the pulley 4.
An inner ring 8 is fixed to the inner ring 8 via a vulcanized and bonded elastically deformable rubber ring 7. The rubber ring 7 has a buffer function. The inner ring 8 has a radially tapered concave portion 8a for accommodating one ball 9,
Several places are formed on the same diameter at equal intervals. A pair of tapered surfaces 8b are formed symmetrically in each radially tapered recess 8a.

A shaft mounting portion 10 a of a hub 10 is fixed to a rotating shaft 2 of the compressor by a nut 11. Hub 1
In 0, several radial and rotational axis recesses 10b for accommodating one ball 9 are formed at equal intervals at the same diameter. In addition, each radial and rotational axis direction recess 10b
, Each recess 10c in the direction of the rotation axis is formed.

When transmitting the torque, each of the balls 9 moves as shown in FIG.
As shown in FIG. 4, each radial direction tapered concave portion 8a and each radial and rotational axis direction concave portion 10b are located. However, when the torque is cut off, each ball 9 moves to each radial direction and rotation axis direction recess 10b as shown in FIGS.
Go to The movement of each ball 9 will be described later.

A ball pressing ring 12 and a disc spring 13 are fitted to the protruding cylindrical portion 10 d of the hub 10, and fixed by a nut 14. By adjusting the degree of tightening of the nut 14, the disc spring 13 against the ball pressing ring 12 is adjusted.
Can be set. Ball pressing ring 1
2 has an inclined surface 12a for pressing each ball 9 against the inner ring 8 arranged radially outward and the hub 10 arranged in the rotation axis direction. A ring-shaped sealing member 15 is provided between the inner ring 8 and the protrusion 10 e of the hub 10, and a ring-shaped sealing member 16 is provided between the inner ring 8 and the ball pressing ring 12. I do. Inner ring 8, hub 10, ball pressing ring 12, and respective ring-shaped seal members 15, 1
A rust preventive material or a lubricating material is sealed in the space enclosed by 6.

One of the pair of tapered surfaces 8b of the radially tapered recess 8a of the inner ring 8 (either one according to the rotation direction of the pulley 4), each ball 9, and the inclined surface 12a of the ball pressing ring 12 The relationship between the force and the movement of the ball will be described. The inclined surface 12a presses the ball 9 with a force P1 in a direction perpendicular to the inclined surface 12a by the urging force of the disc spring 13. As shown in FIG. 10, the force P1 is a component force P1r that pushes the ball 9 radially outward.
And a component force P1h pushing rightward in the rotation axis direction. The one tapered surface 8b pushes the ball 9 with a force P2 in a direction perpendicular to the tapered surface 8b. As shown in FIG. 11, the force P2 is divided into a component force P2r for pushing the ball 9 inward in the radial direction and a component force P2h for pushing the ball 9 rightward in the rotation axis direction (in FIG. 4, when the inner ring 8 rotates rightward). can do. When P1r> P2r, the torque is transmitted because the pair of tapered surfaces 8b are in pressure contact with the ball 9, and when P1r <P2r, the one tapered surface 8b moves the ball 9 radially inward, so that the torque is transmitted. Is shut off.

The operation of this embodiment when transmitting torque will be described with reference to FIGS. Since each ball 9 is in pressure contact with a pair of tapered surfaces 8 b of each radial tapered recess 8 a of the inner ring 8, the protruding portion 10 e of the hub 10, and the inclined surface 12 a of the ball pressing ring 12, the pulley 4 Rotation of three bolts 6, outer ring 5, rubber ring 7, inner ring 8, each ball 9,
Projecting portion 10e of hub 10 and shaft mounting portion 10a of hub 10
And transmitted to the rotary shaft 2 of the compressor.

When a torque exceeding the set value is generated due to a seizure accident of the compressor 1 or the like, the state shown in FIGS. One of the tapered surfaces 8b of the concave portion 8a (either one according to the rotation direction of the pulley 4) presses each ball 9, and as shown in FIG. 3 and FIG. It moves to the concave part 10b. In the state after this movement, each ball 9 may slightly return to the outside in the radial direction, so that each one of the tapered surface 8b and the inclined surface 1 of the ball pressing ring 12
In 2a, each ball 9 is further moved to each rotation axis direction deep recess 10c. As a result, each ball 9 is reliably prevented from returning radially outward. At this time, the ball pressing ring 12 is restored by temporarily moving slightly leftward in FIG. 2 while resisting the disc spring 13 by the inclined surface 12 a being pressed by each ball 9. Therefore,
Since the inner ring 8 and each ball 9 are separated from each other, the rotation of the pulley 4 is not transmitted to the rotary shaft 2 of the compressor.

Next, a power transmission mechanism according to a second embodiment of the present invention will be described with reference to FIG. Since the second embodiment is a partial improvement of the first embodiment, only the improvements will be described.

When the torque is cut off, even if each ball 9 is moved to the corresponding recess 10c in the rotation axis direction, the disc spring 1
The receiving portion 10f of the ball pressing ring 12 is set to an appropriate length in the rotation axis direction of the hub 10 so that the pressing force in the rotation axis direction of 3 acts. Then, loosening of the nut 14 can be prevented. The reason why loosening can be prevented is that nut 1
4, the pressing force in the direction of the rotation axis of the disc spring 13 is still acting after the torque is cut off. To loosen the nut 14, a torque corresponding to the pressing force in the direction of the rotation axis is applied to the nut 14. Need to work. Ball pressing ring 12
Between the ball receiving ring 10f and the receiving portion 10f of the hub 10.
It is appropriate to form a minimum gap c such that the second inclined surface 12a does not hinder the generation of a force for pushing each ball 9 outward in the radial direction.

Further, a power transmission mechanism according to a third embodiment of the present invention will be described with reference to FIGS. Third
In the embodiment, since the first embodiment is partially improved, only the improvements will be described.

When transmitting the torque, each of the balls 9 moves as shown in FIG.
As shown in FIG. 4 and FIG.
Taper surface 8b and inclined surface 12a of ball pressing ring 12.
It is pressed. When the torque is interrupted, each ball 9
7, up to the inner diameter 8c of the inner ring 8.
It can move radially inward and in the direction of the rotation axis. This
In this state, each ball 9 is recessed in the direction of the rotation axis of the hub 10.
Whether to move to 10c is determined by pressing the ball in FIG.
The angle θ between the inclined surface 12a of the ring 12 and the radial direction
_sAnd each ball 9 and the ball receiving edge portion 10g of the hub 10
Angle θ between the tangent and the radial direction at the point of contact_aLarge with
Depends on small relationship. FIG. 9 shows the ball pressing ring in FIG.
Design changes were made to the 12 inclined surfaces 12a, and
An inclined surface 12b which is continuous and has a small inclination angle is formed.
1 shows the ball pressing ring 12 shown in FIG. Slope 12b and diameter
Angle θ ′_sAnd Angle θ_aIs the angle θ_sor
Is θ ' _sIf larger, each ball 9 extends radially inward.
And move in the direction of the rotation axis. Each ball 9 has one tapered surface
8b radially inward from each radial tapered recess 8a
After starting the movement in the direction of the rotation axis, each ball 9
The angle of the inclined surface of the ball pressing ring 12
Angle θ of inclined surface 12a at the start of transmission_sFormed smaller than
Then, each ball 9 moves more reliably.

When the torque is cut off, even if each ball 9 is moved to the corresponding recess 10c in the rotation axis direction, the disc spring 1
If the depth of each recess 10c in the rotation axis direction is set so that the pressing force in the rotation axis direction of 3 acts, the nut 14 can be prevented from loosening. If the nut 14 and the screw lock material are used together, the nut 14 can be more securely prevented from being loosened. However, by appropriately setting the depth of each of the recesses 10c in the axial direction, the screw lock material and the like can be eliminated. can do.

When the breaking torque is set low, the disc spring 1
3, the pressing force in the direction of the rotation axis must be reduced. In this case, the risk of the nut 14 becoming loose increases. Therefore, by using a screw lock material or the like, malfunction of the power transmission mechanism due to loosening of the nut 14 can be prevented.

When the torque is cut off, each ball 9 starts moving radially inward and in the direction of the rotation axis by one tapered surface 8b of each radial tapered recess 8a of the inner ring 8. With the movement of each ball 9, as shown in FIGS. 10 and 11, the angular deviation (θ) between each radial tapered recess 8a and each radial and rotational axis recess 10b of the hub 10 is obtained.
_r ) occurs, and the force for moving each ball 9 inward in the radial direction and in the rotation axis direction increases. When this tendency of increase in force and the tendency of increase of the movement inhibiting force of each ball 9 due to the inclined surfaces 12a and 12b of the ball pressing ring 12 are substantially matched, the driving torque from the start of interruption to the complete interruption is reduced. It can be kept almost constant.

In FIGS. 10 and 11, the angle between the radial direction and the center line of the radial tapered recess 8a is θ _r , and the angle between the center line of the radial tapered recess 8a and one tapered surface 8b. The angle is θ _t , and one tapered surface 8b from the center of the hub 10
Let l be the radial distance to the point where the ball 9 presses the ball 9 with the force P2, and let T be the transmission torque. P2r = P2h × tan (θ _r + θ _t ) T = P2h × 1 Therefore, the following equation (1) is established. I do.

[0045]

(Equation 1) Here, if P2r = P1r, P1r = P1h × t
Since an (θ _s ), the following equations (2) and (3) hold.

[0046]

(Equation 2)

(Equation 3) The value that fluctuates due to the movement of the ball 9 due to the angle shift is:
1 and P1h. If the increase in P1h due to the change in 1 is appropriate, T will be substantially constant with respect to the angle shift (θ _r ).

FIG. 12 is a graph showing the relationship between the transmission torque and the angle shift. When the difference between the torque at the start of shutoff and the torque at the time of complete shutoff is small, the transmitted torque is nearly flat with respect to the change in the angle shift, and when the difference between the torques is large, the transmitted torque is No longer flat with changes.

Further, a power transmission mechanism according to a fourth embodiment of the present invention will be described with reference to FIGS. The fourth embodiment is a partial improvement of the first embodiment, and only the points of improvement will be described.

In FIG. 14, the flange 10 of the hub 10 is
The outer peripheral surface of h presses against the inner peripheral surface of the rubber ring 7, and the outer peripheral surface of the ball pressing ring 12 also presses against the outer peripheral surface of the rubber ring 7. Accordingly, no foreign matter enters the space sealed by the hub 10, the rubber ring 7, and the ball pressing ring 12, so that the interruption function of the power transmission mechanism is not affected. In addition, when a lubricating material such as grease or a rust preventive is sealed in a closed space, wear prevention and rust prevention of the shutoff structure in the power transmission mechanism can be achieved.

FIG. 15 shows a first modification of the power transmission mechanism according to the fourth embodiment of the present invention. In the first design modification example, the outer peripheral surface of the flange 10h of the hub 10 is pressed against a ring-shaped seal member 15 fixed on the inner peripheral surface of the inner ring 8 (on the side closer to the compressor). Same as 14.

FIG. 16 shows a second modification of the power transmission mechanism according to the fourth embodiment of the present invention. In the second design modification, the outer peripheral surface of the ball pressing ring 12 is
14 is pressed against a ring-shaped seal member 16 fixed to the outside of the inner peripheral surface (on the side far from the compressor), and the other points are the same as those in FIG.

Subsequently, in the power transmission mechanism of the fourth embodiment of the present invention shown in FIG.
FIG. 17 shows a state in which a gap has occurred between the motor and the pulley 4, and FIG. 18 shows a state in which a gap has occurred between the hub 10 and the rotary shaft 2 of the compressor.

In the state shown in FIG. 17, the outer ring 5
When the bolt 6 is inserted into the pulley 4 and screwed into the pulley 4, the outer ring 5, the rubber ring 7, and the inner ring 8 move to the pulley 4 side. At this time, the flange 10h of the hub 10
Can be maintained between the outer peripheral surface of the rubber ring 7 and the inner peripheral surface of the rubber ring 7, and between the outer peripheral surface of the ball pressing ring 12 and the inner peripheral surface of the rubber ring 7, respectively.

In the state of FIG. 18, the rotary shaft 2 of the compressor
When the nut 11 is screwed in, the hub 10, the ball 9, the ball pressing ring 12, the disc spring 13 and the nut 14 move to the pulley 4 side. At this time, the flange 10h of the hub 10
Can be maintained between the outer peripheral surface of the rubber ring 7 and the inner peripheral surface of the rubber ring 7, and between the outer peripheral surface of the ball pressing ring 12 and the inner peripheral surface of the rubber ring 7, respectively.

[0055]

As is apparent from the above description, the present invention has the following advantages.

1. A stable torque limiter can be obtained because it is not affected by a change in temperature around the power transmission mechanism.

2. Once the transmission of torque is interrupted,
The disadvantage that torque transmission and interruption are intermittently repeated as in the prior art does not occur.

3. Vibration, noise and heat generation do not occur in the power transmission mechanism.

4. Since the seal member is employed in the shut-off structure of the power transmission mechanism, foreign matter such as dust is prevented from entering, so that the characteristics of the torque limiter do not change.

5. Since the adoption of the seal member allows the sealing material to be filled with a rust preventive or lubricating material,
Since the rust prevention and wear prevention of the power transmission mechanism cutoff structure can be achieved, the characteristics of the torque limiter do not change.

6. When the power transmission mechanism is attached to the driven device, a shim or the like for adjusting the clearance in the rotation axis direction of the driven device is unnecessary.

7. After the transmission of torque is cut off, the ball transmission ring, spring and screw are attached to and detached from the hub without replacing the parts, and each ball is moved to the torque transmission position, thereby enabling the power transmission mechanism to operate. Can be restored.

8. By appropriately setting the angle of the inclined surface of the ball pressing ring, each ball moves more reliably, so that when a torque exceeding a set value is generated, transmission of the torque can be reliably shut off.

9. Since the torque at the start of shutoff and the torque at the time of complete shutoff are configured to be substantially equal, the reliability of the power transmission mechanism is improved.

10. Form a gap between the ball pressing ring and the driven side rotating member such as a hub, appropriately set the depth of each recess in the rotation axis direction, or loosen the screw that biases the ball pressing ring. By using the prevention means together, the cutoff state of the transmission of torque can be reliably maintained.

[Brief description of the drawings]

FIG. 1 is a front view of a compressor using a power transmission mechanism according to a first embodiment of the present invention.

FIG. 2 is an axial sectional view at the time of transmitting torque of a compressor using the power transmission mechanism of the first embodiment of the present invention.

FIG. 3 is an axial cross-sectional view when a torque of a compressor using the power transmission mechanism of the first embodiment of the present invention is cut off.

FIG. 4 is a sectional view taken along line AA in FIG. 2;

FIG. 5 is a sectional view taken along line BB in FIG. 3;

FIG. 6 is an axial sectional view of a main part of a power transmission mechanism according to a second embodiment of the present invention when torque is transmitted.

FIG. 7 is a front view showing a relationship between an inner ring, a ball and a hub when torque of a power transmission mechanism according to a third embodiment of the present invention is completely cut off.

FIG. 8 is an axial sectional view of a main part of a power transmission mechanism according to a third embodiment of the present invention when torque is cut off.

FIG. 9 is an axial sectional view of a main part when torque is cut off in a modified example of the power transmission mechanism according to the third embodiment of the present invention.

FIG. 10 is an axial cross-sectional view of a main part for describing a dynamic relationship when torque is cut off in a power transmission mechanism according to a third embodiment of the present invention.

FIG. 11 is a front view illustrating a mechanical relationship between an inner ring, a ball, and a hub when torque is cut off in a power transmission mechanism according to a third embodiment of the present invention.

FIG. 12 is a graph showing a relationship between a transmission torque and an angle shift in a power transmission mechanism according to a third embodiment of the present invention.

FIG. 13 is a front view of a compressor using a power transmission mechanism according to a fourth embodiment of the present invention.

FIG. 14 is an axial sectional view at the time of transmitting torque of a compressor using a power transmission mechanism according to a fourth embodiment of the present invention.

FIG. 15 is an axial cross-sectional view at the time of transmitting torque of a compressor using a power transmission mechanism of a first design modification of the fourth embodiment of the present invention.

FIG. 16 is an axial sectional view at the time of transmitting torque of a compressor using a power transmission mechanism of a second design modification of the fourth embodiment of the present invention.

FIG. 17 is a schematic diagram showing a state in which a gap is generated between the outer ring and the pulley in FIG.

FIG. 18 is a schematic diagram showing a state in which a gap has occurred between the hub and the rotating shaft of the compressor in FIG.

19A and 19B show a compressor using a conventional power transmission mechanism, wherein FIG. 19A is a front view, and FIG. 19B is a line C-O in FIG.
It is sectional drawing by -C.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor 2 Compressor rotating shaft 3 Ball bearing 4 Pulley 5 Outer ring 6 Bolt 7 Rubber ring 8 Inner ring 8a Radial tapered recess 8b Tapered surface 8c Inner diameter 9 Ball 10 Hub 10a Shaft mounting portion 10b Radial and rotating shaft 10c Projection cylindrical part 10e Projection part 10f Receiving part 10g Ball receiving edge part 10h Flange 11 Nut 12 Ball pressing ring 12a Inclined surface 12b Inclined surface 13 Disc spring 14 Nut 15 Ring-shaped seal member 16 Ring shape Seal member

Claims (16)

[Claims] A driven rotary member having a plurality of radially tapered concave portions; a driven rotary member connected to a rotary shaft and having a plurality of radially and rotationally axial concave portions; And a ball mounted on the driven-side rotating member and a ball pressing ring urged by the spring to transmit torque. In some cases, the inclined surface formed on the ball pressing ring presses each of the balls into contact with each of the radially tapered recesses of the driving-side rotating member and the driven-side rotating member. One tapered surface of each of the radially tapered recesses of the member and the inclined surface of the ball pressing ring move each of the balls to the respective radially and rotationally axially recessed portions. Characteristic power transmission mechanism. 2. The method according to claim 1, wherein the driven-side rotating member has a recess in the rotating shaft direction that is continuous with the recess in the rotating shaft direction, and when the torque is cut off, the balls move to the recesses in the rotating shaft direction. The power transmission mechanism according to claim 1, wherein movement in a radial direction is prevented by the power transmission mechanism. 3. An elastically deformable coupling member in which the driving-side member is connected to a pulley, an outer ring fixed to the pulley, an inner ring pressed against each of the balls, and a connection between the outer ring and the inner ring. The power transmission mechanism according to claim 1, further comprising a rubber member. 4. The power transmission mechanism according to claim 1, wherein the spring is a disc spring, and a biasing force for the ball pressing ring is set by a screw. 5. An apparatus according to claim 1, wherein an inner peripheral surface of the driving-side rotating member and an outer peripheral surface of the driven-side rotating member, and an inner peripheral surface of the driving-side rotating member and an outer peripheral surface of the ball pressing ring. The power transmission mechanism according to claim 1, wherein each of the power transmission mechanisms is sealed by a seal member. 6. A pressure contact is made between an inner peripheral surface of the rubber member and an outer peripheral surface of the driven side rotating member, and between an inner peripheral surface of the rubber member and an outer peripheral surface of the ball pressing ring. The power transmission mechanism according to claim 3, wherein the power transmission mechanism is sealed. 7. A space between a ring-shaped seal member fixed to the inner ring and an outer peripheral surface of the driven-side rotating member, and between an inner peripheral surface of the rubber member and an outer peripheral surface of the ball pressing ring. The power transmission mechanism according to claim 3, wherein the power transmission mechanism is closed by being pressed against each other. 8. A space between an inner peripheral surface of the rubber member and an outer peripheral surface of the driven-side rotating member, and a space between a ring-shaped seal member fixed to the inner ring and an outer peripheral surface of the ball pressing ring. The power transmission mechanism according to claim 3, wherein the power transmission mechanism is closed by being pressed against each other. 9. When a gap is generated between the outer ring and the pulley, the hermetic seal can be maintained even when the outer ring, the rubber member, and the inner ring are moved toward the pulley. The power transmission mechanism according to claim 6, 7 or 8, wherein 10. When a gap is generated between the driven-side rotating member and the rotating shaft, the sealing is performed even if the driven-side rotating member, the balls, and the ball pressing ring are moved to the pulley side. The power transmission mechanism according to claim 6, 7 or 8, wherein 11. The power transmission mechanism according to claim 5, wherein a rust preventive material or a lubricating material is sealed in the closed space. 12. The inclination of the ball pressing ring with which each of the balls comes into contact after each of the balls starts moving from each of the radially tapered recesses to each of the radially and rotationally axial recesses by the one tapered surface. The power transmission mechanism according to claim 1, wherein an angle of the surface is formed smaller than an angle of an inclined surface of the ball pressing ring that contacts each of the balls before the ball starts moving. 13. The torque when each of the balls starts moving from each of the radially tapered recesses to the radially and rotationally axial recesses by the one tapered surface, and the torque at the time of complete interruption are substantially equal. The power transmission mechanism according to claim 1, wherein the power transmission mechanism is configured to be equal. 14. When the torque is cut off, the driven-side rotating member and the driven member are moved so that the biasing force of the spring acts on each of the balls even in a state in which each of the balls has moved to each of the recesses in the rotational axis direction. The power transmission mechanism according to claim 2, wherein a gap is formed between the power transmission mechanism and the ball pressing ring. 15. Each of the recesses in the rotation axis direction such that the biasing force of the spring acts on each of the balls even when the balls move to the recesses in the rotation axis direction when the torque is cut off. The power transmission mechanism according to claim 2, wherein a depth of the power transmission mechanism is set. 16. The power transmission mechanism according to claim 4, wherein said screw is provided with means for preventing loosening.