JPH07332401A - Two-way clutch unit - Google Patents

Abstract

PURPOSE:To improve durability, further stabilize functions and improve assemblability of an automatic lock for normal/reverse rotation of a rotary shaft. CONSTITUTION:A two-way clutch unit is made by engaging an outer ring 1a of the two-way clutch unit 1 with a bearing housing 3, which accommodates a rolling bearing 2, and integrating them together. As its principal elements, the two-way clutch unit 1 is composed of an outer ring 1a, which has a plurality of cam grooves 1a1 in circumferential positions equally arranged in the inner circumference, a roller 1b, which is arranged in the inside diameter of respective cam grooves 1a1, a cage 1c, which is equipped with a pocket for accommodating respective roller 1b, a rubber ring material, for example, an O ring 1e, which is fitted to the inner circumference of one of the ends of the cage 1c, and a control pin 1f which is fixed to the other end of the cage 1c.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a two-way clutch unit capable of automatically controlling idling / locking of forward / reverse rotation of a rotary shaft. For example, a rotation for controlling rotation of a washing / dehydrating tub in a fully automatic washing machine. It can be used as a control mechanism.

[0002]

2. Description of the Related Art For example, in a fully automatic washing machine, washing, rinsing (washing) and dehydration of laundry are performed in one washing / dehydrating tub, so that the washing / dehydrating tub is stopped during washing and rotated only during dewatering. It has become. The rotation control of the washing / dehydrating tub is performed by controlling the rotation of the tubular tub shaft extending downward from the center of the bottom of the tub. That is, as shown in FIG. 8, a fan shaft 32, which is rotatably connected to a rotation source, is inserted through the tubular tub shaft 31, and is used for washing (usually, the switching lever 34 for washing / dewatering is (Washing position), the spring clutch 33 is turned off (at this time, the spring 33a of the spring clutch 33 expands in diameter, and the tubular tub shaft 31 becomes free), and the brake belt 36 is turned on.
The tubular tank shaft 31 in the one-way roller clutch 3
5 and the brake belt 36 are restrained in both rotation directions to rotate only the fan shaft 32 in the forward and reverse directions, and at the time of dehydration, the switching lever 34 is switched to the dehydration position to turn on the spring clutch 33 (at this time, the spring clutch 33
(The spring 33a is reduced in diameter and becomes tight with the tubular tank shaft 31), and the fan shaft 32 is rotated in the idling direction of the one-way roller clutch 35 with the brake belt 36 turned off, so that the tubular tank shaft 31 is rotated. 31 is rotated in synchronization with the fan shaft 32. When the dehydration is completed, the switching lever 3
By switching 4 to the washing position, the spring clutch 33 is turned off and the brake belt 36 is operated (ON) to stop the rotation of the tubular tub shaft 31. The cylindrical tank shaft 3
1 is a pair of rolling bearings 37, 38, which is a washing housing 39.
It is rotatably supported with respect to.

[0003]

In the fully automatic washing machine, the one-way roller clutch 35 and the brake belt 36 are used together to prevent the cylindrical tub shaft 31 from rotating along with the brake belt 36. Wear is expected to deteriorate due to long-term use (prevention of accompanying rotation of the washing / dehydrating tank and brake stop). On the other hand, it is difficult to adopt an improvement means that complicates the control mechanism and increases the cost.

In view of the above-mentioned circumstances, the present applicant has already proposed a two-way clutch suitable for use in a fully automatic washing machine (see Japanese Patent Laid-Open No. 5-209637). The two-way clutch according to the previously proposed structure is configured such that a leaf spring-shaped drag strip is connected to an inner diameter portion of a retainer that accommodates a roller (roller) and the drag strip is brought into contact with the outer circumference of a rotary shaft with a tightening margin. By using the frictional force generated at the contact area between the drag strip and the rotating shaft, the forward / reverse rotation lock can be automatically switched according to the change in the rotating direction of the rotating shaft. It was

The present invention relates to the previously proposed two-way clutch, which has been improved from the viewpoints of improving durability, further stabilizing the function, and improving the assembling property.

[0006]

According to another aspect of the present invention, there is provided a two-way clutch unit including a plurality of torque transmission members interposed between an inner circumference of an outer ring and an outer circumference of a rotary shaft, and a cage for holding the torque transmission members. A two-way clutch having a friction member interposed between the inner circumference of the cage and the outer circumference of the rotary shaft, a rolling bearing that rotatably supports the rotary shaft, and a bearing housing that houses the rolling bearing. That is, the outer ring of the two-way clutch and the bearing housing are integrally engaged with each other with a gap in the radial direction and the axial direction.

The two-way clutch unit according to claim 2 has two
A clutch housing for accommodating a directional clutch and a bearing housing are integrally engaged with each other with a gap in the radial and axial directions.

In the two-way clutch unit of claim 3, a rubber ring member, which is attached to one of the inner circumference of the retainer and the outer circumference of the rotary shaft and is in contact with the other with an interference, is used as the friction member. It is a thing.

The two-way clutch unit according to claim 4 is 2
As a directional clutch, the inner ring has a plurality of cam grooves, and the outer ring forms a symmetrical wedge space between the outer circumference of the rotating shaft and the outer circumference of the rotating shaft at each cam groove portion, and the cam groove of the outer ring and the rotating shaft. Made of rubber that is mounted on one of the inner periphery of the retainer and the outer periphery of the rotary shaft, and the other of which is interposed between the rollers and the outer periphery of the retainer, and which retains the rollers. A two-way roller clutch having a ring member is used.

A fifth aspect of the present invention has a plurality of cam grooves on the inner circumference,
An outer ring that forms a symmetrical wedge space in both the forward and reverse rotation directions between each cam groove portion and the outer circumference of the rotating shaft, and a plurality of rollers interposed between the cam groove of the outer ring and the outer circumference of the rotating shaft. The present invention relates to a two-way roller clutch having a retainer for accommodating and holding a roller, and a rubber ring member attached to one of an inner periphery of the retainer and an outer periphery of a rotary shaft and contacting the other with a tight margin.

[0011]

For example, if the rotary shaft rotates in the forward rotation direction, 2
The retainer of the directional clutch receives the frictional force of the friction member interposed between the inner circumference of the directional clutch and the outer circumference of the rotary shaft, and swings in the forward rotation direction. Due to the swinging of the cage, the torque transmission member housed and held in the cage moves or tilts in the forward rotation direction (when a roller or a ball is used as the torque transmission member, the roller or the ball moves in the swinging direction of the cage). When the sprag is used as the torque transmission member, the sprag tilts in the swinging direction of the cage).
The rotation shaft is locked in the forward rotation direction. Conversely, when the rotation shaft rotates in the reverse rotation direction, the cage swings in the reverse rotation direction, and the rotation shaft is locked in the reverse rotation direction. That is, the forward / reverse rotation direction lock of the rotary shaft is automatically switched.

By unitizing the two-way clutch and the rolling bearing by the engaging structure of the outer ring of the two-way clutch and the bearing housing for accommodating the rolling bearing, centering adjustment of the two is unnecessary, and the assembling work is simplified. Can be converted. Moreover, the presence of the radial and axial gaps in the engaging portion allows the two-way clutch to move relative to the rolling bearing within the range of the gap. Therefore, when the rotary shaft is tilted or eccentric due to an attachment error or the like, the two-way clutch is radially and axially moved in accordance with the movement of the rotary shaft, and the two-way clutch with respect to the rotary shaft is moved. Maintain alignment.

The two-way clutch and the rolling bearing may be unitized by an engaging structure of a clutch housing accommodating the two-way clutch and the bearing housing, and in that case, the same operation is performed.

Since the friction member is formed of a rubber ring member which is mounted on one of the inner circumference of the cage and the outer circumference of the rotary shaft and contacts the other with an interference, the wear resistance of the friction member is improved. Can be improved. Also, since the tightening margin with the other member in contact can be set freely,
It is possible to easily finely adjust the automatic lock timing (delay angle until automatic lock) in the forward and reverse rotation directions of the rotary shaft. Further, depending on the mounting position of the friction member, a sealing function can be added.

[0015]

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

The two-way clutch unit shown in FIG.
The outer ring 1a of the directional clutch 1 and the bearing housing 3 that houses the rolling bearing 2 are engaged and integrated with each other.

The two-way clutch 1 has an outer ring 1a having a plurality of cam grooves 1a1 (see FIG. 2) at evenly distributed positions on the inner circumference.
A roller 1b arranged in the inner diameter of each cam groove 1a1, a cage 1c having a pocket for accommodating each roller 1b,
A rubber ring material such as an O-ring 1e mounted on the inner circumference of one end of the cage 1c and a control pin 1f fixed to one end of the cage 1c are main elements. The rotary shaft 4 is inserted through the inner diameter of the roller 1b.

The outer circumference of one end portion of the outer ring 1a has a slightly larger diameter to form a step portion 1a2, and a plurality of (for example, three) notch portions 1a3 are provided at equidistant positions on the circumference of the step portion 1a2. There is. When a press-molded product is used as the outer ring 1a, the step portion 1a2 may be a flange.

The rolling bearing 2 for rotatably supporting the rotating shaft 4 is arranged with its axis aligned with the two-way clutch 1, and is fitted and fixed to the inner circumference of the bearing housing 3. At the other end of the bearing housing 3, a plurality of (for example, three) claw portions 3a protruding toward the inner diameter side are provided at circumferentially equidistant positions. The claw portions 3a are cutout portions 1a3 of the outer ring 1a, respectively.
In addition, a radial clearance S1, an axial clearance S2, and a rotational clearance S3 are adapted to be engageable with each other. These gaps S1, S2, S3 are, for example, about 0.5 mm. Due to the existence of the radial clearance S1 and the axial clearance S2, the two-way clutch 1 can move in the radial direction and the axial direction with respect to the rolling bearing 2. Therefore, even if the rotary shaft 4 is tilted due to an installation error or the like, the two-way clutch 1 is displaced within the range of the clearances (S1, S2, S3) according to the tilt of the rotary shaft 4, and the two-way clutch 1 The misalignment of the axis with the rotary shaft 4 is automatically adjusted.

The outer circumference of one end of the cage 1c has a slightly larger diameter to form a stepped portion 1c1, which is the outer ring 1a.
The retainer 1c is restrained from coming off in the axial direction by fittingly engaging the concave step portion 1a4 provided on the inner circumference of the one end portion. The control pin 1f fixed to one end of the cage 1c penetrates the outer ring 1a and the stopper holes 1a5 and 3b provided in the bearing housing 3 and projects from the bearing housing 3 to the outer diameter side. . Each of the stopper holes 1a5 and 3b has an elongated hole shape in the circumferential direction, and in the cage 1c, the control pin 1f has the stopper holes 1a5 and 3b.
It is possible to swing and move in the circumferential direction with respect to the outer ring 1a within the range of contacting the side wall in the circumferential direction. The cage 1c
May be made of metal or resin.

As shown enlarged in FIG. 2, a symmetrical wedge space is formed between the cam groove 1a1 of the outer ring 1a and the outer periphery of the rotary shaft 4 in both forward and reverse rotational directions. The roller 1b is disposed so as to be engageable with and disengageable from these wedge spaces, and is housed and held in the pocket of the cage 1c via the springs 1g arranged on both sides in the circumferential direction. The O-ring 1e is fitted and fixed in an annular groove 1c2 provided on the inner circumference of one end of the cage 1c, and contacts the outer circumference of the rotary shaft 4 with a tightening margin t.

For example, when the rotary shaft 4 rotates in the clockwise direction in FIG. 2, the retainer 1c swings in the clockwise direction by the frictional force of the O-ring 1e that comes into contact with the outer periphery of the rotary shaft 4 with an interference. Then, the roller 1b is engaged with the wedge space on the right rotation direction side of the cam groove 1a1. As a result, the rotary shaft 4 is automatically locked in the right rotation direction. The swinging of the cage 1c is restricted by the control pin 1f fixed to the cage 1c contacting the side walls of the stopper holes 1a5 and 3b on the right rotation direction side. Conversely, when the rotary shaft 4 rotates counterclockwise, the rotary shaft 4 is automatically locked in the left rotary direction in the same manner. The swinging of the cage 1c is restricted by the control pin 1f fixed to the cage 1c contacting the side walls of the stopper holes 1a5 and 3b on the left rotation direction side. The timing at which the two-way clutch 1 automatically switches to the lock (the delay angle until switching to the lock) is the O-ring 1e.
By finely setting the tightening margin t of, the fine adjustment can be easily performed.

As described above, the two-way clutch 1 has a function of automatically locking the forward and reverse rotations of the rotary shaft 4, but by controlling the control pin 1f appropriately, the two-way clutch 1 can be rotated in one direction. Locking and idling in both directions are also possible. For example, if the control pin 1f is held at the position where it abuts against the side wall of the stopper holes 1a5 and 3b on the right rotation direction side, the rotary shaft 4 is locked in the right rotation and left rotation free, and the control pin 1f is locked in the stopper holes 1a5 and 3b. When it is held at a position where it abuts against the side wall on the left rotation direction side, the rotation shaft 4 becomes left rotation locked and right rotation free. Then, when the control pin 1f is held at the neutral position, the rotary shaft 4 becomes free from both rotations.

In the embodiment shown in FIG. 3, the O-ring 1e is fitted and fixed in an annular groove 1c3 provided at the inner circumference of the other end of the cage 1c, and this is brought into contact with the outer circumference of the rotary shaft 4 with a tightening margin. It is a thing. The O-ring 1e serves as a friction member as described above, and also serves to prevent grease leakage from the two-way clutch 1 and foreign matter from entering the two-way clutch 1. In this embodiment, the retaining ring 1h fitted to the inner periphery of the other end of the outer ring 1a restricts the retainer 1c from coming off in the axial direction.

In the embodiment shown in FIG. 4, the O-ring 1e is fitted and fixed in an annular groove 4a provided on the outer circumference of the rotary shaft 4, and this is brought into contact with the inner circumference of the other end of the retainer 1c with a tightening margin. It is a thing. It has the same effects as those shown in FIG.

In the embodiment shown in FIG. 5, an annular groove 1 in which a rubber seal member 1e 'is provided on the inner circumference of the other end of the cage 1c.
It is fitted and fixed to c3 and is brought into contact with the outer periphery of the rotary shaft 4 with an interference. The seal member 1e ′ serves as a friction member as described above, and also serves to prevent grease leakage from the two-way clutch 1 and foreign matter from entering the two-way clutch 1.

The embodiment shown in FIG. 6 is a combination of the structure shown in FIG. 1 and the structure shown in FIG.

In the embodiment shown in FIG. 7, the outer ring 1a of the two-way clutch 1 is fitted and fixed to the inner circumference of the clutch housing 5,
The clutch housing 5 and the bearing housing 3 are integrally engaged. The outer circumference of one end of the clutch housing 5 has a slightly larger diameter to form a step 5a.
A plurality of (for example, three) notches 5b are arranged at evenly distributed positions on the circumference of
Is provided. When a press-molded product is used as the clutch housing 5, the step portion 5a may be a flange. In addition, at the other end of the bearing housing 3,
A plurality of (for example, three) claw portions 3a protruding toward the inner diameter side are provided at circumferentially equidistant positions. The claw portion 3a is adapted to be engageable with the cutout portion 5b with a radial gap S1, an axial gap S2, and a rotational gap S3.
A stopper hole 5c having an elongated hole shape in the circumferential direction is provided in the clutch housing 5.

In the embodiment described above, a roller clutch (a roller is used as a torque transmitting member) is used as a two-way clutch, but a combination structure of a ball and a cam groove, or both forward and reverse rotation directions is used. It is also possible to adopt a sprag structure having a cam surface, and in that case as well, the same operational effect is obtained. Combination structure of ball and cam groove,
A publicly known structure may be adopted as the sprag structure. However, when the sprag structure is adopted, for example, the outer ring having a cylindrical inner circumference and the inner and outer circumferences of the outer ring are arranged on both the inner and outer sides. The structure includes a sprag having a cam surface in the rotational direction, an inner retainer that accommodates the inside of the sprag, and an outer retainer that accommodates the outside of the sprag. And
One of the inner cage and the outer cage is fixed, and the above-mentioned friction member is interposed between the inner circumference of the other cage and the outer circumference of the rotary shaft or the inner circumference of the outer ring.

As the friction member, in addition to the O-ring 1e and the seal member 1e 'described above, a leaf spring-shaped metal member, a resin ring member, or the like can be used.

[0031]

As described above, according to the present invention,
Since the directional clutch has a function of automatically switching the forward / reverse rotation direction lock of the rotation shaft, for example, in the rotation control mechanism of the fully automatic washing machine shown in FIG. By using it, it is possible to prevent the cylindrical tank shaft 31 from rotating along with the two-way clutch unit. Therefore, the brake belt 3
6 can be used only for stopping the brake, and the fear of wear deterioration is eliminated.

The two-way clutch and the rolling bearing are
Since it is unitized by the engaging structure of the outer ring or clutch housing and the bearing housing, centering adjustment of both is unnecessary, and the assembling work is simplified. Moreover, the presence of the radial and axial gaps in the engaging portion allows the two-way clutch to move relative to the rolling bearing within the range of the gap. Therefore, when the rotating shaft is tilted or eccentric due to an attachment error or the like, the two-way clutch is radially and axially moved in accordance with the movement of the rotating shaft, so that the two-way clutch moves to the two
The aligned state of the directional clutch is maintained.

Further, since the friction member is formed of a rubber ring member which is attached to one of the inner circumference of the cage and the outer circumference of the rotary shaft, and contacts the other with an interference, the wear resistance of the friction member is improved. It is possible to improve the sex. Further, since the tightening margin with the other member in contact can be freely set, it is possible to easily finely adjust the timing of automatic lock in the forward and reverse rotation directions of the rotary shaft (delay angle until automatic lock). it can. Moreover, depending on the mounting position of the friction member, a sealing function can be added.

[Brief description of drawings]

FIG. 1 is a cross-sectional view (FIG. A: aa cross section in FIG. B) and a front view (FIG. B: b direction arrow in FIG. A) showing an embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view showing the periphery of a cam groove of an outer ring.

FIG. 3 is a sectional view showing another embodiment of the present invention.

FIG. 4 is a sectional view showing another embodiment of the present invention.

FIG. 5 is a cross-sectional view showing another embodiment of the present invention.

FIG. 6 is a sectional view showing another embodiment of the present invention.

FIG. 7 is a sectional view (FIG. A: FIG. B) showing another embodiment of the present invention.
Section aa), front view (FIG. B: b in FIG. A)
Direction arrow).

FIG. 8 is a sectional view showing a rotation control mechanism of the fully automatic washing machine.

[Explanation of symbols]

 1 2-way clutch 1a Outer ring 1a1 Cam groove 1b Roller 1c Retainer 1e O-ring 1e 'Seal member 2 Rolling bearing 3 Bearing housing 4 Rotating shaft 5 Clutch housing S1 Radial gap S2 Axial gap t Tightening margin

Claims (5)

[Claims] 1. A plurality of torque transmission members interposed between an inner circumference of an outer ring and an outer circumference of a rotary shaft, a retainer for holding these torque transmission members, and an inner circumference of the retainer and an outer circumference of the rotary shaft. A two-way clutch having an intervening friction member, a rolling bearing rotatably supporting a rotary shaft, and a bearing housing accommodating the rolling bearing, wherein the outer ring of the two-way clutch and the bearing housing are radiused. A two-way clutch unit characterized by being integrally engaged with a gap in the axial and axial directions. 2. A plurality of torque transmission members interposed between the inner circumference of the outer ring and the outer circumference of the rotating shaft, a retainer for holding these torque transmitting members, and a retainer between the inner circumference of the retainer and the outer circumference of the rotating shaft. A two-way clutch having an intervening friction member, a clutch housing that houses the two-way clutch, a rolling bearing that rotatably supports a rotating shaft, and a bearing housing that houses the rolling bearing, the clutch comprising: A two-way clutch unit characterized in that a housing and a bearing housing are integrally engaged with each other with a gap in a radial direction and an axial direction. 3. The friction member is a rubber ring member mounted on one of the inner circumference of the cage and the outer circumference of the rotary shaft and contacting the other with a tight margin.
Or a two-way clutch unit of 2. 4. A two-way clutch is provided with a plurality of cam grooves on its inner circumference, and an outer ring that forms a symmetrical wedge space in each of the cam groove portions with respect to the outer circumference of the rotating shaft in both forward and reverse rotation directions, and an outer ring. A plurality of rollers interposed between the cam groove and the outer circumference of the rotating shaft,
A two-way roller clutch having a retainer for accommodating and holding these rollers, and a rubber ring member attached to one of the inner periphery of the retainer and the outer periphery of the rotary shaft and contacting the other with a tightening margin. Claim 1 or 2 according to claim 2
Directional clutch unit. 5. An outer ring having a plurality of cam grooves on its inner circumference, and forming a symmetrical wedge space in each of the cam groove portions with respect to the outer circumference of the rotary shaft in both forward and reverse rotation directions, and a cam groove of the outer ring. A plurality of rollers interposed between the outer circumference of the rotary shaft, a retainer for accommodating and holding these rollers, one of the inner circumference of the retainer and the outer circumference of the rotary shaft, and contacting the other with a tightening margin. A two-way roller clutch having a rubber ring member.