JP2003240020A - Two way clutch unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a two way clutch unit capable of switching a rotating direction of an output side with a simple means without switching a rotating direction of an input side. <P>SOLUTION: The two way clutch unit is provided with a rotatably arranged outer ring 1, a center axis 2 coaxially arranged therein, a sun ring 3 coaxially arranged between the sun ring 3 and the center axis 2, a two way clutch 4 existing between the sun ring 3 and the center axis 2 and capable of engaging with and disengaging from the sun ring 3 and the center axis 2 in both of regular and reverse rotation directions, a planetary roller 6 arranged in an annular space 5 formed between the outer ring 1 and the sun ring 3 rotatably under a pressed condition at even intervals in a circumference direction, and a carrier 7 retaining the planetary roller 6 rotatably at even intervals in a circumference direction and capable of restricting and releasing revolution of the planetary roller 6 by arranging the outer ring 1 and the sun ring 3 in such a manner that the same can be connected and disconnected. <P>COPYRIGHT: (C)2003,JPO

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, and more particularly, to a two-way clutch unit having a structure capable of switching the output side rotation direction without switching the input side rotation direction.

[0002]

2. Description of the Related Art As a conventional two-way clutch unit, there is, for example, a structure disclosed in Japanese Patent Application Laid-Open No. 9-25946.

This two-way clutch unit is interposed between an input system rotary member, an output system rotary member, and an input system rotary member and an output system rotary member, and torque transmission capable of engaging / disengaging with these rotary members. Member, a retainer that holds the torque transmission member, and controls engagement / disengagement of the torque transmission member through relative rotation with respect to the input system rotating member, and is interposed between the retainer and the stationary system member to prevent friction. The main components are a switching mechanism that causes relative rotation of the cage by a force, and a coupling means that couples the cage and the input system rotary member in the rotational direction with a predetermined rotational gap.

When the input system rotary member starts to rotate, the cage receives frictional force from the switching mechanism and tries to maintain its stop position, and as a result, the cage is opposite to the input rotation with respect to the input system rotary member. Rotate relative to the direction. As a result, the torque transmission member held by the retainer engages with both the input system rotating member and the output system rotating member. On the other hand, since the cage is connected to the input system rotating member via the connecting means, when the cage rotates relative to the input system rotating member by the amount corresponding to the predetermined gap in the rotation direction, the cage receives the rotational torque from the input system rotating member and is connected to the switching mechanism. It follows and rotates with the input system rotating member while making sliding contact. The rotation of the cage at this time is always delayed with respect to the rotation of the input system rotation member by an amount corresponding to the rotation direction clearance, and therefore,
Rotational torque from the input system rotating member is transmitted to the output system rotating member via the torque transmitting member.

[0005]

In the two-way clutch unit disclosed in Japanese Patent Laid-Open No. 9-25946 mentioned above, the rotation of the output system rotary member is changed by switching the forward and reverse rotation directions of the input system rotary member. I was trying to switch directions. When a two-way clutch unit of this type is incorporated in a motor drive unit of a hybrid vehicle, for example, a switching mechanism for switching the rotation direction of the motor is required when switching between forward and reverse movements of the vehicle, and an ordinary vehicle. Even when it is mounted on the transmission of, the mechanism for switching between forward and reverse of the vehicle is complicated.

Therefore, the present invention has been proposed in view of the above problems, and an object thereof is to switch the rotation direction on the output side by a simple means without switching the rotation direction on the input side. To provide a two-way clutch unit.

[0007]

As a technical means for achieving the above-mentioned object, the present invention provides an outer ring rotatably arranged, and a central shaft concentrically arranged inside thereof.
A sun ring concentrically arranged between the outer ring and the central shaft, and a sun ring interposed between the sun ring and the central shaft and engaging with the sun ring and the central shaft in both forward and reverse rotation directions.
A detachable two-way clutch, a planetary rotor rotatably arranged in an annular space formed between the outer ring and the sun ring in a pressure contact state at equal circumferential intervals, and a planetary rotor thereof. Is rotatably held at equal intervals in the circumferential direction and is arranged so as to be connectable to and disconnectable from the outer ring and the sun ring, thereby providing a carrier capable of restraining / releasing the rotation of the planetary rotor. To do.

As the planetary rotating body, either a planetary roller or a planetary gear can be applied. Further, the two-way clutch is interposed between the sun ring and the central shaft, holds a torque transmitting member that is engageable with and disengageable from the sun ring and the central shaft, and holds the torque transmitting member. A structure including a retainer that controls engagement / disengagement of the torque transmission member through relative rotation with respect to the central axis is desirable.

When the outer ring is the input side, the central axis is the output side, and conversely, when the central axis is the input side, the outer ring is the output side. In the former case, that is, when the outer ring is on the input side, in the two-way clutch unit according to the present invention, the carrier is connected to and disconnected from the outer ring and the sun ring to restrain and release the rotation of the planetary rotor. The rotation direction of the output side central axis is switched with.

That is, when the carrier is joined to the outer ring and the sun ring, the carrier and the outer ring and the sun ring are integrated. When the outer ring is rotationally driven by the drive source, the carrier and the sun ring are integrated into the outer ring,
The rotation of the planetary rotating body held by the carrier is restrained, the carrier and the sun ring rotate in the same direction together with the outer ring, and the rotating torque of the outer ring is transmitted from the sun ring to the central axis through the 2-way clutch. The central axis is driven to rotate in the same direction as the outer ring.

On the contrary, when the carrier is separated from the outer ring and the sun ring, the carrier is released from the outer ring and the sun ring to release the state in which the rotation of the planetary rotor is restrained. When the outer ring is rotationally driven by the drive source, the sun ring rotates in the opposite direction to the outer ring via the planetary rotor by the rotation of the planetary rotor held by the carrier. Due to the rotation of the sun ring, the rotation torque of the outer ring is transmitted from the sun ring to the central shaft via the two-way clutch, and the central shaft is rotationally driven in the opposite direction to the outer ring.

As a structure of the carrier, the carrier is arranged so as to be slidable in the axial direction in an annular space formed between the outer ring and the sun ring, and is fitted by concavity and convexity between the abutting surfaces of the outer ring and the sun ring. It is possible to have a structure in which there is a meshing portion that mates with each other and can be joined to the outer ring and the sun ring through the meshing portion. Engagement of the carrier with the outer ring and sun ring at this meshing part
When the carrier is disengaged, the carrier connects and disconnects with the outer ring and the sun ring, and the rotation direction of the output side central shaft is switched.

Further, as another structure of the carrier, the carrier is arranged in an annular space formed between the outer ring and the sun ring, and wing bodies are respectively provided on the opposing surfaces of the outer ring and the sun ring and the carrier, A structure in which a sealed space surrounded by an outer ring, a sun ring and a carrier is filled with a fluid is possible. When the outer ring on the input side is rotating at low speed, the outer ring and the sun ring are separated from the carrier due to the slip of the fluid, and when the outer ring is rotating at high speed, the fluid flow is spiraled by the blades. Since the rotating motion is uniform, the sun ring and the carrier rotate following the rotation of the outer ring. When the fluid is used as described above, the carrier is connected to and disconnected from the outer ring and the sun ring due to the low rotation and high rotation of the outer ring, and the rotation direction of the output side central shaft is switched.

[0014]

1 to 3 show an embodiment of a two-way clutch unit according to the present invention. Note that FIG.
1A is a sectional view taken along line ZZ in FIG.
(B) is a sectional view taken along line YY of FIG. 1 (a), FIG. 2 is a sectional view taken along line WW of FIG. 1 (a), and FIG. 3 is seen from the X direction of FIG. 1 (a). FIG. By providing this 2-way clutch unit in the motor drive section of the hybrid vehicle, the rotation direction of the output shaft can be switched between the forward and reverse directions without switching the rotation direction of the motor. Also,
By assembling the transmission of an ordinary vehicle, it is possible to easily switch between forward and reverse traveling of the vehicle.

In the two-way clutch unit of this embodiment, an outer ring 1 which is an input side rotating member rotatably arranged, a central shaft 2 which is an output side rotating member concentrically arranged inside the outer ring 1, and A sun ring 3 concentrically arranged between the outer ring 1 and the central shaft 2, and the sun ring 3
Formed between the outer ring 1 and the sun ring 3, and a two-way clutch 4 that is interposed between the sun ring 3 and the center shaft 2 and is engageable / disengageable with the sun ring 3 and the center shaft 2 in both forward and reverse rotation directions. A planetary roller 6 which is a planetary-type rotating body rotatably arranged in an annular space 5 at equal intervals in a circumferential direction in a pressed state.
A carrier 7 which holds the planetary rollers 6 rotatably at equal intervals in the circumferential direction and is arranged so as to be connectable to and disconnectable from the outer ring 1 and the sun ring 3 so that the rotation of the planetary rollers 6 can be restrained and released. It is equipped with a main part consisting of and.

Of the above-mentioned constituent members, the central shaft 2 is rotatably supported by the stationary member 8 via a rolling bearing 9 so as to rotate in the forward and reverse directions. The stationary member 8 is attached to a motor drive unit of a hybrid vehicle or a transmission of an ordinary vehicle. A two-way clutch 4 is provided on the central shaft 2.

The two-way clutch 4 of this embodiment exemplifies the one using the sprag 11 as the torque transmitting member, but it may be a type using a roller as another torque transmitting member. The two-way clutch 4 includes a sun ring 3 as an input side rotating member, a central shaft 2 as an output side rotating member, an inner peripheral surface of a large diameter portion 3 a of the sun ring 3, and a large diameter portion 2 a of the central shaft 2. A plurality of sprags 11, which are torque transmission members interposed between the outer peripheral surface, and an outer cage 12 and an inner cage 13 for accommodating and holding the sprags 11 at equal intervals in the circumferential direction are main elements. .
A rolling bearing 15 is interposed between the inner circumference of the sun ring 3 and the outer circumference of the central shaft 2, and a rolling bearing 16 is interposed between the inner circumference of the inner cage 13 and the outer circumference of the central shaft 2. Ring 3
And the central shaft 2 are coaxially supported so as to be rotatable relative to each other.

The outer retainer 12 is fixed to the inner circumference of the sun ring 3 by appropriate means and rotates integrally with the sun ring 3. The inner cage 13 includes, for example, a pin 17 and a slit hole 1
It is connected to the outer cage 12 via a connecting means composed of 8 and 8. In this embodiment, the pin 17 is fixed to the inner cage 13 by an appropriate means, and the tip of the pin 17 is inserted into the slit hole 18 formed through the outer cage 12 with a predetermined rotational gap. The inner cage 13 is rotatable relative to the sun ring 3 and the outer cage 12 fixed to the sun ring 3, but the range of relative rotation is within the gap in the rotational direction between the pin 17 and the slit hole 18. Limited to range.

The sprag 11 has cam surfaces on both sides of the outer diameter side portion and both sides of the inner diameter side portion, the outer diameter side portion is housed in the pocket of the outer cage 12, and the inner diameter side portion is the inner cage 13. It is accommodated in a pocket of 1 through a pair of elastic bodies, for example, leaf springs 19. In the neutral position shown in FIG. 2, the sprag 11 separates from both the inner peripheral surface of the large diameter portion 3a of the sun ring 3 and the outer peripheral surface of the large diameter portion 2a of the central shaft 2 to generate rotational torque from the sun ring 3. When it is shut off but tilted in either the forward or reverse rotation direction, its cam surface engages with both the inner peripheral surface of the large diameter portion 3a of the sun ring 3 and the outer peripheral surface of the large diameter portion 2a of the central shaft 2. Rotational torque from the sun ring 3 is transmitted to the central shaft 2.

The rotational torque is transmitted in the sprag 1
It is the friction plate 14 which is fixed to a part of the casing (not shown) and which is determined by the tilting direction of 1, and controls the tilting and the direction. The friction plate 14 is slidably attached to the outer periphery of the end of the inner cage 13, and the sliding friction force generated between the friction plate 14 and the inner cage 13 is used to move the inner cage 13 to the outside. The rotation is delayed with respect to the cage 12.

The sun ring 3 has a stepped portion 3b at one end of the large diameter portion 3a, and a small diameter portion 3c via the stepped portion 3b.
Is integrally formed with a stepped cylindrical shape. As described above, the outer retainer 12 of the two-way clutch 4 is fixed to the inner circumference of the large diameter portion 3a of the sun ring 3, and the rolling bearing 15 is interposed between the outer retainer 12 and the central shaft 2. Further, the small diameter portion 3c provided via the step portion 3b extending from the large diameter portion 3a of the sun ring 3 is externally inserted on the outer periphery of the central shaft 2 with a minute gap.

The outer ring 1 includes a thick portion 1a located on the outer side of the sun ring 3 on the side corresponding to the large diameter portion 3a.
The thin portion 1c located on the outer side of the sun ring 3 on the side corresponding to the small diameter portion 3c, and the outer portion provided between the thick portion 1a and the thin portion 1c and corresponding to the step portion 3b of the sun ring 3. It has a cylindrical shape integrally formed with the step portion 1b located on one side. The step portion 1b of the outer ring 1 and the step portion 3b of the sun ring 3 are arranged so that both axial end surfaces thereof are flush with each other, and in particular, the step portion 1b of the outer ring 1 is arranged.
A meshing portion 20 with the carrier 7 is formed on the end surface of the thin portion 1c on the side of and the end surface of the step portion 3b of the sun ring 3 on the side of the small diameter portion 3c as described later. Rolling bearings 21 and 22 are interposed between the inner circumference of the thick portion 1a of the outer ring 1 and the outer circumference of the large diameter portion 3a of the sun ring 3, and the outer ring 1 is rotatably supported by the sun ring 3. There is.

In the annular space 5 formed between the small-diameter portion 3c of the sun ring 3 and the thin-walled portion 1c of the outer ring 1, a plurality of (four in the figure) planet rollers 6 are arranged at equal intervals in the circumferential direction. Has been done. These planetary rollers 6 can rotate by being pressed against the outer circumference of the small diameter portion 3c of the sun ring 3 and the inner circumference of the thin portion 1c of the outer ring 1. Along with these planetary rollers 6, a carrier 7 is axially slidably arranged in an annular space 5 between the small diameter portion 3c of the sun ring 3 and the thin portion 1c of the outer ring 1 so that the planetary rollers 6 can be circumferentially moved. It is held so that it can rotate at equal intervals. The planetary rollers 6 are accommodated in the accommodating portions 23 provided at equal intervals in the circumferential direction of the carrier 7 with a minute gap.

Further, the axial end surface of the carrier 7, that is,
A concave portion is formed on an end surface of the planetary roller 6 opposite to the end surface on which the accommodating portion 23 is formed, and an elastic body such as a coil spring 24 is fitted into the concave portion to face the carrier 7 of the stationary member 8. Is stretched in parallel with the axial direction. The elastic force of the coil spring 24 causes the carrier 7 to move the end surface of the step portion 3b of the sun ring 3 and the outer ring 1.
Is urged in the direction of abutting the end face of the stepped portion 1b.

The end face of the step portion 3b of the sun ring 3 and the end face of the step portion 1b of the outer ring 1 and the end face of the carrier 7 opposite to both end faces thereof are filled with the carrier 7 as shown in FIG. 3 and the outer ring 1 are formed with concavities and convexities 25, and the concavities and convexities 25 form a meshing portion 20 for fitting the sun ring 3 and the outer ring 1 and the carrier 7 together. A coil spring 24 is provided at a portion of the stationary member 8 facing the carrier 7.
An electromagnetic brake 26 is embedded for adsorbing the carrier 7 against the elastic force of the carrier 7 and separating it from the sun ring 3 and the outer ring 1 to restrict the rotation of the carrier 7 in the circumferential direction.

Instead of the irregularities 25, wing bodies are respectively provided on the facing surfaces of the outer ring and the sun ring and the carrier, and the sealed space surrounded by the outer ring, the sun ring and the carrier is filled with fluid, A fluid clutch or the like for transmitting or shutting off may be provided.

Next, an example of the operation of the two-way clutch unit in this embodiment will be described in detail below. In this 2-way clutch unit, for example, the outer ring 1 is used as an input side and the rotation direction (forward / reverse rotation) of the central shaft 2 is changed through the planetary roller 6, the sun ring 3 and the 2-way clutch 4 without switching the rotation direction. You can switch. That is, in the conventional two-way clutch unit, the rotation direction on the output side is switched between the forward and reverse directions by switching the rotation direction on the input side as shown in FIG. 6B. In the 2-way clutch unit, the rotation direction on the output side can be switched between the forward and reverse directions without switching the rotation direction on the input side as shown in FIG.

First, when the electromagnetic brake 26 is off due to non-conduction, as shown in FIGS. 4A and 4B, the annular space 5 between the small diameter portion 3c of the sun ring 3 and the thin portion 1c of the outer ring 1 is formed.
The carrier 7, which is disposed so as to be slidable in the axial direction, is urged toward the step portions 3b and 1b of the sun ring 3 and the outer ring 1 by the elastic force of the coil spring 24. As a result, the end face of the carrier 7 and the end faces of the step portions 3b, 1b of the sun ring 3 and the outer ring 1 collide with each other and the concavities and convexities 25 of the meshing portion 20 formed on both end faces are fitted to each other, and the carrier 7 The sun ring 3 and the outer ring 1 are integrated.

When the outer ring 1 is rotated in this state, since the carrier 7 and the sun ring 3 are integrated with the outer ring 1, the carrier 7 and the sun ring 3 are integrated together with the rotation of the outer ring 1. Rotate in the same direction. The rotation torque of the sun ring 3 is transmitted to the central shaft 2 via the 2-way clutch 4, and the central shaft 2
Rotates in the same direction as the sun ring 3, that is, the outer ring 1.

Here, in the two-way clutch 4, the outer cage 12 rotates integrally with the sun ring 3 due to the rotation of the sun ring 3, but the inner cage 13 receives a frictional force from the friction plate 14 and stops. Attempts to maintain the position, which results in the inner cage 13 rotating behind the outer cage 12. As a result, the leaf springs 19 arranged in the pockets of the inner cage 13 bend and the sprags 11 tilt.
On the other hand, the inner cage 13 has a pin 17 and a slit hole 18.
Since it is connected to the outer retainer 12 via, the range of the delayed rotation is restricted to the range corresponding to the rotational gap (one side) between the pin 17 and the slit hole 18, and the inner retainer 13 When the delayed rotation reaches the maximum range, the sprag 11 tilts by a predetermined amount, and the sun ring 3 and the central shaft 2 are completely locked via the sprag 11.

When the sun ring 3 further rotates from this state, the inner cage 13 receives the rotational torque from the sun ring 3 via the outer cage 12 and follows the sun ring 3 while slidingly contacting the friction plate 14. To do. At this time, the rotation of the inner cage 13 is always delayed with respect to the rotation of the sun ring 3 by the gap in the rotation direction (one side), so that the rotation torque from the sun ring 3 is transmitted via the sprag 11 to the central shaft 2
The central shaft 2 rotates integrally with the sun ring 3. Such torque transmission is automatically performed regardless of whether the sun ring 3 is rotated in the forward or reverse direction.

Next, when the electromagnetic brake 26 is turned on by energization, the carrier 7 is attracted by the action of the electromagnetic brake 26 as shown in FIGS. By the attraction by the electromagnetic brake 26, the carrier 7 is slid toward the electromagnetic brake 26 side in the axial direction against the elastic force of the coil spring 24. As a result, the end surface of the carrier 7 is disengaged from the both end surfaces of the sun ring 3 and the outer ring 1, and the fitting state of the concavities and convexities 25 in the meshing portion 20 formed on both end surfaces is released. As a result, the rotation of the carrier 7 in the circumferential direction is restricted and the carrier 7 is fixedly arranged together with the stationary side member 8, so that the planetary roller 6 can rotate.

When the outer ring 1 is rotated in this state, the planetary roller 6 is pressed against the inner circumference of the thin portion 1c of the outer ring 1 and the sun ring 3 is attached to the planetary roller 6.
Since the outer circumference of the small diameter portion 3c is in pressure contact, the sun ring 3 rotates in the opposite direction to the outer ring 1 via the planetary roller 6 that rotates. The rotation torque of this sun ring 1 is
The torque is transmitted to the central shaft 2 by the same two-way clutch 4 as when the electromagnetic brake 26 is turned off, and the central shaft 2 rotates in the same direction as the sun ring 3, that is, in the opposite direction to the outer ring 1.

[0034]

According to the present invention, the rotation direction of the two-way clutch can be switched by a simple means without switching the rotation direction on the input side. For example, when provided in the motor drive unit of a hybrid vehicle, the rotation direction of the output shaft can be switched between the forward and reverse directions without switching the rotation direction of the motor, and the transmission becomes unnecessary,
Further, even when mounted on a transmission of an ordinary vehicle, the forward and backward movements of the vehicle can be easily switched, which is of great practical value.

[Brief description of drawings]

1A and 1B show a structure of a two-way clutch unit according to an embodiment of the present invention, in which FIG. 1A is a sectional view taken along line ZZ of FIG. 1B, and FIG. 1B is taken along line YY of FIG. FIG.

FIG. 2 is a cross-sectional view showing a structure of a two-way clutch according to the embodiment of the present invention, taken along line WW of FIG.

FIG. 3 is a partially enlarged cross-sectional view of the embodiment of the present invention viewed from the X direction in FIG.

4A and 4B are sectional views showing a state in which an electromagnetic brake is turned off, and FIG. 4B is a sectional view taken along line Y-Y of FIG. 4A, showing an outer ring, a planetary roller, and Indicates the direction of rotation of the sun ring.

5A and 5B are cross-sectional views showing a state in which an electromagnetic brake is turned on, and FIG. 5B is a cross-sectional view taken along the line YY of FIG. 5A, showing an outer ring, a planetary roller, and Indicates the direction of rotation of the sun ring.

FIG. 6A is a characteristic diagram showing the relationship between the input rotation direction and the output rotation direction in the embodiment of the present invention, and FIG.
FIG. 6 is a characteristic diagram showing a relationship between an input rotation direction and an output rotation direction in a conventional example.

[Explanation of symbols] 1 Outer ring 2 central axis 3 sun rings 4 2-way clutch 5 annular space 6 Planetary type rotating body (planetary roller) 7 career 11 Torque transmission member (sprag) 12 Cage (outer cage) 13 Cage (inner cage) 20 Interlocking part 25 unevenness

Claims (5)

[Claims] 1. An outer ring rotatably arranged,
A central axis concentrically arranged inwardly, a sun ring concentrically arranged between the outer ring and the central axis, and a sun ring interposed between the sun ring and the central axis. A two-way clutch that can be engaged and disengaged in both forward and reverse rotation directions, and a planetary type that is rotatably arranged in an annular space formed between the outer ring and the sun ring in a pressure contact state at equal circumferential intervals. The rotating body and its planetary rotating body are rotatably held at equal intervals in the circumferential direction, and are arranged so that they can be connected to and disconnected from the outer ring and the sun ring, so that the rotation of the planetary rotating body can be restrained and released. A two-way clutch unit including a carrier. 2. The planetary rotating body is one of a planetary roller and a planetary gear.
2 way clutch unit described in. 3. The two-way clutch is interposed between a sun ring and a central shaft, holds a torque transmitting member that is engageable with and disengageable from the sun ring and the central shaft, and holds the torque transmitting member. The two-way clutch unit according to claim 1 or 2, further comprising: a retainer that controls engagement / disengagement of the torque transmission member through relative rotation with respect to a sun ring or a central axis. 4. The carrier is axially slidably arranged in an annular space formed between the outer ring and the sun ring, and is fitted with concave and convex portions between the abutting surfaces of the outer ring and the sun ring. The two-way clutch unit according to any one of claims 1 to 3, wherein the two-way clutch unit has a meshing portion that engages with the outer ring and the sun ring through the meshing portion. 5. The carrier is disposed in an annular space formed between the outer ring and the sun ring, and wings are provided on the surfaces of the outer ring and the sun ring facing the carrier, respectively. 4. The structure according to claim 1, wherein the closed space surrounded by the ring and the carrier is filled with a fluid.
Way clutch unit.