JP2023178115A - One-way clutch - Google Patents

Abstract

To provide a one-way clutch capable of easily and efficiently spreading lubricating fluid onto a frictional surface.SOLUTION: A one-way clutch 1 includes an inner clutch 2, an outer clutch 3, a clutch key 4 stored in a clutch key storage recessed part 11, and an elastic member 5 stored in the storage recessed part 11 together with the clutch key 4. In the storage recessed part 11, an inner clutch side supply groove 15 is formed to supply lubricating fluid stored in the storage recessed part 11 between the clutch 2 and the clutch 3, when the clutch key 4 sinks into the storage recessed part 11 against the energizing force of the elastic member 5.SELECTED DRAWING: Figure 3

Description

The present invention relates to a one-way clutch.

BACKGROUND ART One-way clutches (also referred to as "overrunning clutches") that supply lubricating oil (lubricating fluid) through holes provided in side plates are known (for example, see Patent Document 1).

Japanese Patent Application Publication No. 2002-310200

However, conventional one-way clutches have room for improvement in easily and efficiently spreading lubricating fluid against friction surfaces.

An object of the present invention is to provide a one-way clutch that can easily and efficiently spread lubricating fluid against a friction surface.

(1) The one-way clutch according to the present invention includes an inner clutch, an outer clutch, a clutch key accommodated in a clutch key accommodating recess provided in the inner clutch, and a clutch key accommodated in the clutch key accommodating recess together with the clutch key. a one-way clutch, the one-way clutch comprising: a one-way clutch in which the clutch key is inserted into the clutch key accommodating recess when the clutch key sinks into the clutch key accommodating recess against the biasing force of the elastic member; An inner clutch side supply groove is formed for supplying the lubricating fluid contained in the recess between the inner clutch and the outer clutch.

(2) In the one-way clutch described in (1) above, the inner clutch side supply groove is formed by a radial supply groove and an axial supply groove intersecting the radial supply groove. can do.

(3) In the one-way clutch described in (1) or (2) above, the radial supply groove and the axial supply groove may have the same groove depth.

(4) In the one-way clutch described in (1) or (2) above, the radial supply groove and the axial supply groove may have different groove depths.

(5) The one-way clutch described in any one of (1) to (4) above includes an outer clutch for supplying the lubricating fluid to the outer clutch between the inner clutch and the outer clutch. Preferably, a side supply groove is formed.

(6) In the one-way clutch described in (5) above, it is preferable that the outer clutch side supply groove includes a helical supply groove extending spirally in the axial direction.

(7) In the one-way clutch described in (6) above, the axial end of the spiral supply groove may be discontinuous with the axial end of the outer clutch.

(8) The one-way clutch described in any one of (1) to (7) above includes at least one clutch for suppressing leakage of the lubricating fluid supplied between the inner clutch and the outer clutch. Preferably, an annular seal member is provided. For example, the one-way clutch according to any one of the above inventions includes at least one annular seal member for suppressing leakage of the lubricating fluid supplied between the inner clutch and the outer clutch. I can do that.

According to the present invention, it is possible to provide a one-way clutch that can easily and efficiently spread lubricating fluid to a friction surface.

FIG. 1 is a half-sectional view schematically showing a yoke unit, in which a one-way clutch and a yoke of a universal joint according to an embodiment of the present invention are integrally constructed, from a side surface of the yoke unit. FIG. 2 is a front view schematically showing the yoke unit of FIG. 1 from the shaft connection side. 2 is a sectional view taken along line AA in FIG. 1. FIG. FIG. 2 is a front view schematically showing an example of an inner clutch applicable to the one-way clutch of FIG. 1 from the shaft connection side. 5 is a view taken in the direction of arrow D in FIG. 4. FIG. 5 is a sectional view taken along line BB in FIG. 4. FIG. 6 is a sectional view taken along the line CC in FIG. 5. FIG. FIG. 2 is a front view schematically showing an example of an outer clutch applicable to the one-way clutch of FIG. 1 from the shaft connection side. 9 is a sectional view taken along line DD in FIG. 8. FIG. 5 is a diagram showing another example of an inner clutch applicable to the one-way clutch of FIG. 1, as viewed in the direction of arrow D in FIG. 4. FIG. 11 is a sectional view taken along the line CC in FIG. 10. FIG.

Hereinafter, a one-way clutch according to an embodiment of the present invention will be described with reference to the drawings.

Here, in the present disclosure, the "axial direction" refers to a direction extending along the central axis O1 of the yoke unit 100, which will be described later. In addition, in the present disclosure, the "axis-perpendicular direction" refers to a direction perpendicular to the axial direction (so-called circular radial direction). In particular, in the present disclosure, among the axial directions, the direction approaching the center axis O1 is referred to as the axially inner side, and the direction moving away from the center axis O1 is referred to as the axially outer side. Furthermore, in the present disclosure, the "circumferential direction" refers to the circumferential direction around the central axis O1.

In FIG. 1, reference numeral 100 denotes a yoke unit including one yoke 101 of two yokes constituting a universal joint (the overall view is omitted). The yoke unit 100 extends along the central axis O1 of the yoke unit 100. In the present disclosure, one side of the yoke unit 100 in the direction in which the central axis O1 extends is the shaft side, and the other side in the direction in which the central axis O1 extends is the universal joint side. In the present disclosure, a drive shaft (not shown) can be connected to the shaft side of the yoke unit 100, and the other yoke (not shown) of the universal joint can be connected to the universal joint side. .

In the present disclosure, the yoke unit 100 includes the one-way clutch 1 according to an embodiment of the present invention, which is integrally configured with the yoke 101.

The one-way clutch 1 includes an inner clutch 2, an outer clutch 3, a clutch key 4 accommodated in a clutch key accommodating recess 11 provided in the inner clutch 2, and an elastic clutch 4 accommodated in the clutch key accommodating recess 11 together with the clutch key 4. A member 5 is provided.

In the present disclosure, the inner clutch 2 is a cylindrical inner clutch. In the present disclosure, the center axis of the inner clutch 2 is the same as the center axis O1 of the yoke unit 100. In the present disclosure, a plurality of spline grooves 2s are formed on the inner peripheral surface of the inner clutch 2 to connect the drive shaft. The spline groove 2s extends along the central axis O1. As shown in FIG. 2, the spline grooves 2s are arranged at intervals in the circumferential direction around the central axis O1. In the present disclosure, the drive shaft is formed with, for example, a spline protrusion (not shown) that fits into the spline groove 2s, and can be fitted into the spline groove 2s of the inner clutch 2.

Furthermore, in the present disclosure, as shown in FIG. 1, the inner clutch 2 is formed with a through hole 2h extending in the axial direction. A ball B is arranged in the through hole 2h. The inner opening in the axial direction of the through hole 2h opens into the spline groove 2s, exposing a portion of the ball B. On the other hand, the outer opening in the axially perpendicular direction of the through hole 2h opens to the outer circumferential surface of the inner clutch 2, and is closed by an annular set cover C. The set cover C is urged toward the shaft in the axial direction by a coil spring S between the backup ring R1 and the L-shaped ring R2. However, in the present disclosure, the backup ring R1 is held on the axial universal joint side by the step of the inner clutch 2, and the L-shaped ring R2 is held on the axial shaft side by the stopper ring R3.

The clutch key housing recess 11 is a recess formed in the inner clutch 2 and recessed inward in the axial direction. The clutch key housing recess 11 extends in the axial direction. In the present disclosure, the shaft side end of the clutch key storage recess 11 is closed by the shaft side partition member 6 . The shaft-side partition member 6 is an annular shaft-side partition member that extends in the circumferential direction around the central axis O1. The shaft side partition member 6 is fixed to the outer peripheral surface of the inner clutch 2. On the other hand, in the present disclosure, the universal joint side end of the clutch key storage recess 11 is partitioned by the universal joint side partition member 7. The universal joint side partition member 7 is coupled to the outer clutch 3 and the yoke 101, respectively, as described later.

The clutch key 4 is accommodated in the clutch key accommodating recess 11 . In the present disclosure, the clutch key 4 is a flat clutch key. Specifically, as shown in FIG. 1, the clutch key 4 is a long member extending in the axial direction, and has a flat cross-sectional shape as shown in FIG. In the present disclosure, the clutch key 4 includes a distal end portion 4a that can be engaged with a notch 3a, which will be described later, and a rear end portion 4b that serves as a reference point when the clutch key 4 is swung in the direction perpendicular to the axis. Furthermore, in the present disclosure, the clutch key 4 includes a stepped surface 4c directly below the tip portion 4a. The step surface 4c is provided on the side facing the bottom surface 12 of the clutch key accommodating recess 11 when the clutch key 4 is accommodated in the clutch key accommodating recess 11. In the present disclosure, the stepped surface 4c is continuous with each of the two axial ends 4e (see FIG. 1) of the clutch key 4, and is open to each of the two axial ends 4e.

Further, as shown in FIG. 1, an elastic member 5 is interposed between the clutch key 4 and the bottom surface 12 of the clutch key accommodating recess 11. In the present disclosure, as shown in FIG. 1, the elastic member 5 locally contacts the bottom surface 12 of the clutch key storage recess 11 and the stepped surface 4c of the clutch key 4. It has a part. As a result, the clutch key 4 is urged (pressed) outward in the axial direction while being accommodated in the clutch key accommodating recess 11 . In the present disclosure, the elastic member 5 is a leaf spring. However, the elastic member 5 is not limited to a leaf spring, and may be any member that biases the clutch key 4 radially outward.

In addition, as shown in FIG. 3, the elastic member 5 is accommodated in the stepped surface 4c of the clutch key 4. Thereby, the clutch key 4 can be swung in the direction perpendicular to the axis using the rear end portion 4b of the clutch key 4 as a base point. As shown in FIG. 3, in the initial state, the elastic member 5 moves the tip 4a of the clutch key 4 outward in the axial direction so that the tip 4a of the clutch key 4 is exposed from the outer peripheral surface of the inner clutch 2. It is energizing. As a result, the tip 4a of the clutch key 4 can be hooked onto the notch 3a provided in the outer clutch 3 and locked in the notch 3a, and the clutch key 4 can be held in contact with the inner circumferential surface of the outer clutch 3. The tip portion 4a can be pushed into the clutch key accommodating recess 11 against the urging force (pressing force) of the elastic member 5.

The outer clutch 3 is also a cylindrical outer clutch. The outer clutch 3 accommodates the inner clutch 2 inside thereof. The center axis of the outer clutch 3 is also the same as the center axis O1 of the yoke unit 100. As shown in FIG. 3, in the present disclosure, the clutch key 4 is exposed outward in the axial direction from the outer peripheral surface of the inner clutch 2 by being urged outward in the axial direction by the elastic member 5. A notch 3a is formed on the inner circumferential surface of the outer clutch 3 for locking the clutch key 4 urged outward in the axial direction by the elastic member 5.

A plurality of clutch key accommodating recesses 11 are formed on the outer peripheral surface of the inner clutch 2 at intervals in the circumferential direction. As shown in FIG. 4, in the present disclosure, the inner clutch 2 includes two clutch key accommodating recesses 11. The two clutch key accommodating recesses 11 are formed at positions at an angle of 180° in the circumferential direction around the central axis O. That is, the two clutch key accommodating recesses 11 are arranged at opposing positions with the central axis O interposed therebetween. In other words, in the present disclosure, the one-way clutch 1 includes two clutch keys 4, and the two clutch keys 4 are arranged at opposing positions across the central axis O.

On the other hand, as shown in FIG. 8, a plurality of notches 3a are formed on the inner peripheral surface of the outer clutch 3 at intervals in the circumferential direction. In the present disclosure, the outer clutch 3 includes four notches 3a. The four notches 3a are arranged at 90° angles in the circumferential direction. That is, the four notches 3a are arranged at equal intervals in the circumferential direction. As a result, the two clutch keys 4 are simultaneously locked in the two notches 3a arranged at opposite positions across the central axis O, or are simultaneously passed through the two notches 3a.

Referring to FIG. 3, in the one-way clutch 1, when the inner clutch 2 is about to rotate to one side in the circumferential direction with respect to the outer clutch 3, the clutch key 4 engages with the notch 3a of the outer clutch 3, while the inner clutch When the clutch key 2 attempts to rotate toward the other side in the circumferential direction with respect to the outer clutch 3, the clutch key 4 resists the urging force of the elastic member 5 and sinks into the clutch key accommodation recess 11, causing the inner clutch 2 to rotate idly.

Specifically, as shown in FIG. 3, when the counterclockwise rotation when viewed from the axial shaft side is defined as a forward rotation (rotation on one side in the circumferential direction), the rotational speed of the inner clutch 2 in the forward rotation is equal to that of the outer clutch 2. When the rotation speed is equal to or higher than the normal rotation speed of the clutch 3, the inner clutch 2 rotates the outer clutch 3 integrally by engagement of the clutch key 4 and the notch 3a. That is, in the present disclosure, the yoke unit 100 transfers the input rotation from the drive shaft to the universal joint when the rotation speed of the drive shaft in the forward rotation is equal to or higher than the rotation speed of the universal joint (yoke 101) in the forward rotation. to communicate. On the other hand, when the forward rotational speed of the inner clutch 2 is less than the forward rotational speed of the outer clutch 3, the inner clutch 2 disengages the clutch key 4 from the notch 3a, thereby causing the outer clutch Clutch 3 is idling. That is, in the present disclosure, in the yoke unit 100, when the rotational speed of the drive shaft in the forward rotation is less than the rotational speed of the forward rotation of the universal joint (yoke 101), the input rotation from the universal joint is prevent communication.

On the other hand, as shown in FIG. 3, when the clockwise rotation when viewed from the axial shaft side is reverse rotation (rotation on the other side in the circumferential direction), the rotational speed of the reverse rotation of the inner clutch 2 is the rotation speed of the outer clutch 3. When the rotational speed is equal to or higher than the rotation speed of the reverse rotation, the inner clutch 2 idles relative to the outer clutch 3 by disengaging the clutch key 4 from the notch 3a. That is, in the present disclosure, in the yoke unit 100, when the rotational speed of the reverse rotation of the drive shaft is equal to or higher than the rotational speed of the reverse rotation of the universal joint (yoke 101), the input rotation from the drive shaft is prevent communication. On the other hand, when the rotational speed of the inner clutch 2 in the reverse rotation is less than the rotational speed of the outer clutch 3 in the reverse rotation, the inner clutch 2 is integrally connected to the outer clutch 3 by engagement between the clutch key 4 and the notch 3a. Rotate to . That is, in the present disclosure, when the rotational speed of the reverse rotation of the drive shaft is less than the rotational speed of the reverse rotation of the universal joint (yoke 101), the yoke unit 100 transfers the input rotation from the universal joint to the drive shaft. to communicate.

Here, when the clutch key 4 sinks into the clutch key accommodating recess 11 against the biasing force of the elastic member 5, the lubricating fluid accommodated in the clutch key accommodating recess 11 is transferred to the inner An inner clutch side supply groove 15 is formed between the clutch 2 and the outer clutch 3 for supplying the fluid.

Referring to FIG. 3, the clutch key housing recess 11 is filled with the lubricating fluid. This allows the clutch key 4 and the elastic member 5 to move smoothly. On the other hand, when the inner clutch 2 and the outer clutch 3 rotate relative to each other, the clutch key 4 may be pressed inward in the axial direction by the outer clutch 3. In this case, the clutch key 4 sinks into the clutch key accommodating recess 11 against the biasing force of the elastic member 5. As a result, the lubricating fluid accommodated in the clutch key accommodating recess 11 is compressed between the clutch key 4 and the clutch key accommodating recess 11 as the clutch key 4 sinks. The lubricating fluid compressed between the clutch key 4 and the clutch key accommodation recess 11 is fed under pressure between the inner clutch 2 and the outer clutch 3 through the inner clutch side supply groove 15. Thereby, the lubricating fluid accommodated in the clutch key accommodating recess 11 can be easily and efficiently spread between the inner clutch 2 and the outer clutch 3. Therefore, according to the one-way clutch 1, the lubricating fluid can be spread easily and efficiently onto the friction surface.

On the other hand, even when the inner clutch 2 and the outer clutch 3 rotate relative to each other, the clutch key 4 may be separated from the bottom surface 12 of the clutch key storage recess 11 due to the urging force of the elastic member 5. Further, when the inner clutch 2 and the outer clutch 3 rotate integrally, the clutch key 4 is locked in the notch 3a. Also in this case, the clutch key 4 is separated from the bottom surface 12 of the clutch key accommodating recess 11 by the urging force of the elastic member 5. In this case, the lubricating fluid pressure-fed between the inner clutch 2 and the outer clutch 3 returns to the space formed between the clutch key 4 and the clutch key accommodating recess 11 through the inner clutch side supply groove 15. can be done.

Referring to FIG. 7, the clutch key accommodating recess 11 is formed by a bottom surface 12 and two circumferential side surfaces 13. The two circumferential side surfaces 13 are spaced apart from each other in the circumferential direction and are connected to the bottom surface 12 . In the present disclosure, the clutch key housing recess 11 further includes two circumferential outer edge surfaces 14 . The axially inner end of the circumferential outer edge surface 14 is continuous with the circumferential side surface 13 adjacent to the circumferential outer edge surface 14 . On the other hand, the axially outer end of the circumferential outer edge surface 14 is continuous with the outer circumferential surface of the inner clutch 2 . In the present disclosure, the circumferential outer edge surfaces 14 of the clutch key accommodating recess 11 are tapered surfaces that move away from each other in the circumferential direction as they go outward in the axially perpendicular direction.

On the other hand, the inner clutch side supply groove 15 includes a radial supply groove 16. The radial supply groove 16 is formed in the circumferential side surface 13 of the clutch key accommodating recess 11 . The radial supply groove 16 extends in the axial direction. Thereby, the lubricating fluid accommodated in the clutch key accommodation recess 11 can be efficiently supplied between the inner clutch 2 and the outer clutch 3 through the radial supply groove 16.

Further, in the present disclosure, the radial supply groove 16 is formed in a range from the circumferential side surface 13 to the circumferential outer edge surface 14. In the present disclosure, the inner end of the radial supply groove 16 in the axial direction is spaced apart from the bottom surface 12 of the clutch key storage recess 11 and is discontinuous with the bottom surface 12 . However, the inner end of the radial supply groove 16 in the axial direction can be made to contact the bottom surface 12 of the clutch key storage recess 11 by making it continuous with the bottom surface 12 . On the other hand, the axially outer end of the radial supply groove 16 is continuous with the circumferential outer edge surface 14 of the clutch key storage recess 11 and is open to the circumferential outer edge surface 14 . The circumferential outer edge surface 14 of the clutch key accommodating recess 11 forms a gap between the inner clutch 2 and the outer clutch 3. Since the clutch key 4 extends along the central axis O1, this gap extends along the central axis O1. Therefore, the circumferential outer edge surface 14 of the clutch key accommodating recess 11 is effective for spreading the lubricating fluid over a wider range. However, the circumferential outer edge surface 14 of the clutch key accommodating recess 11 can be omitted.

Further, the inner clutch side supply groove 15 may be formed by a radial supply groove 16 and an axial supply groove 17 that intersects with the radial supply groove 16. In this case, the lubricating fluid accommodated in the clutch key accommodating recess 11 passes through the radial supply groove 16 and the axial supply groove 17 and can be efficiently spread throughout the axial direction.

As shown in FIG. 5 , the inner clutch side supply groove 15 includes an axial supply groove 17 in addition to a radial supply groove 16 . The axial supply groove 17 is formed in the circumferential side surface 13. The axial supply groove 17 extends in the axial direction and merges with the radial supply groove 16 . Thereby, the lubricating fluid accommodated in the clutch key accommodating recess 11 passes through the axial supply groove 17 in addition to the radial supply groove 16, and can be efficiently spread throughout the axial direction. In the present disclosure, the axial end of the axial supply groove 17 is opened to the axial end of the clutch key accommodating recess 11 by being continuous with the axial end of the clutch key accommodating recess 11 . However, the axial end of the axial supply groove 17 can be made discontinuous with the axial end of the clutch key accommodating recess 11 by separating it from the axial end of the clutch key accommodating recess 11 .

As shown in FIG. 5, the radial feed groove can be a plurality of radial feed grooves 16. The plurality of radial supply grooves 16 are arranged at intervals in the axial direction. In this case, the lubricating fluid can be spread more efficiently in the entire axial direction. In the present disclosure, the radial supply grooves are two radial supply grooves 16, but a larger number of radial supply grooves 16 may be provided. Further, in the present disclosure, the axial supply groove is one axial supply groove 17. However, the axial feed groove can also be a plurality of axial feed grooves 17. In this case, the plurality of axial supply grooves 17 are arranged at intervals in the axial direction.

Further, in the present disclosure, the radial supply groove 16 and the axial supply groove 17 have the same groove depth. As shown in FIG. 7, the groove depth of the radial supply groove 16 and the groove depth of the axial supply groove 17 are equal. In this case, an equal amount of the lubricating fluid can be spread between the inner clutch 2 and the outer clutch 3 through the radial supply groove 16 and the axial supply groove 17.

Further, as shown in FIG. 6, in the present disclosure, the inner clutch 2 is formed of a large diameter portion 21, a medium diameter portion 22, and a small diameter portion 23 along the axial direction. The large diameter portion 21 is the portion of the inner clutch 2 that has the largest width in the axial direction (radial width). The small diameter portion 23 is a portion of the inner clutch 2 that has the smallest width in the axial direction (radial width). The medium diameter portion 22 has an axis-perpendicular width (radial width) that is intermediate between the axis-perpendicular width of the large-diameter portion 21 and the axis-perpendicular width of the small-diameter portion 23 . In the present disclosure, the middle diameter section 22 is formed by a first middle diameter section 22a and a second middle diameter section 22b. In the present disclosure, the first medium diameter portion 22a is a portion whose width in the axial direction (radial direction width) is larger than the width in the axial direction (radial direction width) of the second medium diameter portion 22b.

In the present disclosure, the clutch key accommodating recess 11 is formed by a notch formed in the large diameter portion 21 of the inner clutch 2. The notch is opened at each of the two axial ends of the large diameter portion 21 by being continuous with each of the two axial ends of the large diameter portion 21 . That is, in the present disclosure, each of the shaft-side axial end and the universal joint-side axial end of the clutch key accommodating recess 11 is open to the axial end of the large diameter portion 21 . However, in the present disclosure, an annular fixing groove 24 for fixing the shaft side partition member 6 is formed in the first medium diameter portion 22a. Referring to FIG. 1, the shaft-side axial end of the clutch key accommodating recess 11 is closed by the shaft-side partition member 6. As shown in FIG.

Further, referring to FIG. 1, the universal joint side axial end of the clutch key housing recess 11 is closed by the universal joint side partition member 7. A yoke 101 is fixed to the inner peripheral side of the universal joint side partition member 7. Symbol M1 is an annular welded portion that fixes the universal joint side partition member 7 and the yoke 101. Furthermore, an outer clutch 3 is fixed to the outer peripheral side of the universal joint side partition member 7. Symbol M2 is an annular welded portion that fixes the universal joint side partition member 7 and the outer clutch 3.

Further, referring to FIG. 9, the outer clutch 3 is formed with an outer clutch side supply groove 30 for supplying the lubricating fluid between the inner clutch 2 and the outer clutch 3.

The outer clutch side supply groove 30 is formed on the inner circumferential surface of the outer clutch 3. The outer clutch side supply groove 30 cooperates with the inner clutch side supply groove 15 to spread the lubricating fluid. Thereby, the lubricating fluid is efficiently supplied between the inner clutch 2 and the outer clutch 3 through the outer clutch side supply groove 30 in addition to the inner clutch side supply groove 15 .

Specifically, in the present disclosure, the outer clutch side supply groove 30 includes a spiral supply groove 31 that extends spirally in the axial direction. The spiral supply groove 31 extends spirally around the central axis O1. Thereby, the lubricating fluid can be spread more efficiently throughout the axial direction through the spiral supply groove 31. Note that in the present disclosure, the groove depth of the spiral supply groove 31 is shallower than the groove depth of the notch 3a.

Further, in the present disclosure, the outer clutch 3 is provided with a lubricating fluid introducing portion (lubricating fluid introducing nipple) 33. The lubricating fluid introducing portion 33 penetrates the outer clutch 3 in the axially perpendicular direction, and allows the lubricating fluid to be introduced from the outer circumferential side to the inner circumferential side of the outer clutch 3. Thereby, the lubricating fluid can be supplied between the inner clutch 2 and the outer clutch 3 from the outside of the outer clutch 3 through the lubricating fluid introducing portion 33 .

Additionally, in the present disclosure, the outer clutch side supply groove 30 includes an annular supply groove 32 that extends in the circumferential direction around the center axis O1. In the present disclosure, the lubricating fluid introduction section 33 communicates with the annular supply groove 32 . Thereby, the lubricating fluid introduced from the outside of the outer clutch 3 through the lubricating fluid introducing portion 33 can be supplied to the entire circumferential direction around the central axis O1. Note that in the present disclosure, the groove depth of the annular supply groove 32 is shallower than the groove depth of the notch 3a.

Furthermore, in the present disclosure, the annular supply groove 32 merges with the spiral supply groove 31 . Thereby, the lubricating fluid introduced from the lubricating fluid introducing portion 33 can be supplied to the helical supply groove 31 through the annular supply groove 32 . Note that in the present disclosure, the groove depth of the annular supply groove 32 is shallower than the groove depth of the spiral supply groove 31. That is, in the present disclosure, the groove depth of the annular supply groove 32 is the shallowest, followed by the spiral supply groove 31 and the notch 3a.

In the present disclosure, the axial end 31a of the spiral supply groove 31 is spaced apart from the axial end 3b of the outer clutch 3 in the axial direction, and is discontinuous with the axial end 3b of the outer clutch 3. That is, in the present disclosure, the axial end 31a of the spiral supply groove 31 is not open to the axial end 3b of the outer clutch 3. Thereby, the lubricating fluid expanding through the spiral supply groove 31 can be prevented from leaking from the axial end 3b of the outer clutch 3.

Further, in the present disclosure, it is preferable that the one-way clutch 1 includes at least one annular seal member 8 for suppressing leakage of the lubricating fluid supplied between the inner clutch 2 and the outer clutch 3. . In this case, leakage of the lubricating fluid from the axial end 3b of the outer clutch 3 can be further suppressed.

Referring to FIG. 1, in the present disclosure, an annular seal member 8 is provided between the outer clutch 3 and the shaft-side partition member 6, and extends in the circumferential direction around the central axis O1. Examples of the annular seal member 8 include elastic members made of rubber or resin, such as packing and O-rings. In the present disclosure, the annular seal member 8 seals between the inner peripheral surface of the outer clutch 3 and the outer peripheral surface of the shaft-side partition member 6. Thereby, the phenomenon in which the lubricating fluid leaks from the shaft-side axial end 3b of the outer clutch 3 can be further suppressed. In the present disclosure, leakage of the lubricating fluid can be suppressed by welding the universal joint side partition member 7 and the yoke 101 to the universal joint side axial end 3b of the outer clutch 3. Therefore, the arrangement of the annular seal member 8 on the universal joint side of the outer clutch 3 can be omitted.

As described above, in the one-way clutch 1, when the inner clutch 2 and the outer clutch 3 rotate relative to each other, the clutch key 4 sinks into the clutch key accommodating recess 11, so that the lubricant stored in the clutch key accommodating recess 11 is removed. The fluid is spread between the inner clutch 2 and the outer clutch 3 through the inner clutch side supply groove 15. Thereby, the frictional resistance between the inner clutch 2 and the outer clutch 3 during operation can be reduced. In this case, it is possible to suppress heat generation (reduce the amount of heat generated) and extend the operating life of the one-way clutch 1.

In particular, in the present disclosure, the inner clutch side supply groove 15 is formed by a radial supply groove 16 and an axial supply groove 17 that intersects with the radial supply groove 16. In this case, the lubricating fluid can be spread more efficiently between the inner clutch 2 and the outer clutch 3.

Further, in the present disclosure, the radial supply groove 16 and the axial supply groove 17 have the same groove depth. In this case, an equal amount of lubricating fluid can be spread between the inner clutch 2 and the outer clutch 3 through the radial supply groove 16 and the axial supply groove 17.

Further, in the present disclosure, the lubricating fluid pressure-fed by the clutch key 4 is also supplied between the inner clutch 2 and the outer clutch 3 through the outer clutch side supply groove 30 formed in the outer clutch 3. Thereby, the frictional resistance between the inner clutch 2 and the outer clutch 3 during operation can be further reduced. In this case, it is possible to further suppress heat generation (reduce the amount of heat generated) and extend the operating life of the one-way clutch 1.

In particular, in the present disclosure, the outer clutch side supply groove 30 includes a helical supply groove 31 that extends spirally in the axial direction. Thereby, the lubricating fluid can be spread more efficiently throughout the axial direction through the spiral supply groove 31.

Further, in the present disclosure, the axial end 31a of the spiral supply groove 31 is discontinuous with the axial end 3b of the outer clutch 3. This can prevent the lubricating fluid expanding through the spiral supply groove 31 from leaking from the axial end 3b of the outer clutch 3.

In particular, in the present disclosure, the one-way clutch 1 includes at least one annular seal member 8 for suppressing leakage of the lubricating fluid supplied between the inner clutch 2 and the outer clutch 3. In this case, the phenomenon that the lubricating fluid leaks from the axial end 3b of the outer clutch 3 can be further suppressed. However, this does not deny that the annular seal member 8 can be omitted. Further, the annular seal member 8 can be used alone instead of making the axial end 31a of the spiral supply groove 31 discontinuous with the axial end 3b of the outer clutch 3.

Incidentally, in the inner clutch 2, the radial supply groove 16 and the axial supply groove 17 may have different groove depths. In this case, by changing the groove depth of the radial supply groove 16 and the groove depth of the axial supply groove 17, more lubricating fluid can be supplied to a desired portion.

10 and 11 show main parts of a modification of the inner clutch 2 shown in FIGS. 4 to 7. However, the description of parts that are substantially the same as the above configuration will be omitted. As shown in FIGS. 10 and 11, in the modified example of the inner clutch 2, the groove depth of the axial direction supply groove 17 is deeper than the groove depth of the radial direction supply groove 16. In this case, the axial ends of the inner clutch 2 (here, the axial ends of the clutch key storage recess 11, specifically, the shaft-side partition member 6 and the universal joint-side partition member 7), which are likely to wear due to contact, , more lubricating fluid can be supplied than the radial supply groove 16.

However, the groove depth of the supply grooves may be such that the radial supply grooves 16 are deeper than the axial supply grooves 17 . In this case, more lubricating fluid can be supplied in the circumferential direction around the central axis O1. Furthermore, when there are a plurality of radial supply grooves 16, the groove depth may be changed between the plurality of radial supply grooves 16. Similarly, when there are a plurality of axial supply grooves 17, the groove depth may be changed between the plurality of axial supply grooves 17.

Although the one-way clutch according to one embodiment of the present invention has been described above, the present invention is not limited to the above embodiment, and can be variously modified within the scope of the claims. Can be done.

For example, in the present disclosure, the inner clutch side supply groove 15 is formed on each of the two circumferential side surfaces 13 of the clutch key storage recess 11. However, the inner clutch side supply groove 15 can be formed only in either one of the two circumferential side surfaces 13. For example, the inner clutch side supply groove 15 may be formed only on the circumferential side surface 13 located at a position facing the tip 4a of the clutch key 4.

Further, in the present disclosure, the radial supply groove 16 is parallel to the axial direction, for example, as shown in FIG. 5, but may be inclined with respect to the axial direction. The axial supply groove 17 is also parallel to the axial direction, for example, as shown in FIG. 5, but may be inclined with respect to the axial direction. Also, in the present disclosure, the plurality of radial supply grooves 16 are parallel to each other, but can be inclined to each other. This also applies to the case where there are a plurality of axial supply grooves 17.

Examples of the lubricating fluid include semi-solid or semi-fluid lubricants such as grease, and lubricating fluids such as lubricating oil.

1: One-way clutch, 2: Inner clutch, 2s: Spline groove, 2h: Through hole, 21: Large diameter portion, 22: Medium diameter portion, 22a: First medium diameter portion, 22b: Second medium diameter portion, 23: Small diameter portion, 3: Outer clutch, 3a: Notch, 3b: Axial end of outer clutch, 4: Clutch key, 4a: Tip of clutch key, 4b: Rear end of clutch key, 4c: Step surface of clutch key , 4e: Axial end of clutch key, 5: Elastic member, 6: Shaft side partition member, 7: Universal joint side partition member, 8: Annular seal member, 11: Clutch key accommodating recess, 12: Clutch key accommodating recess. Bottom surface, 13: Circumferential side surface of clutch key storage recess, 14: Circumferential outer edge surface of clutch key storage recess, 15: Inner clutch side supply groove, 16: Radial supply groove, 17: Axial supply groove, 30: Outer Clutch side supply groove, 31: Spiral supply groove, 32: Annular supply groove, 33: Lubricating fluid introduction part, 100: Yoke unit, 101: Yoke, B: Ball, C: Set cover, M1, M2: Welding part , R1: Backup ring, R2: L-shaped ring, R3: Stopper ring

Claims (8)

A one-way clutch comprising: an inner clutch, an outer clutch, a clutch key accommodated in a clutch key accommodating recess provided in the inner clutch, and an elastic member accommodated in the clutch key accommodating recess together with the clutch key. There it is,
When the clutch key sinks into the clutch key accommodating recess against the biasing force of the elastic member, the lubricating fluid accommodated in the clutch key accommodating recess is transferred between the inner clutch and the clutch key accommodating recess. A one-way clutch with a supply groove on the inner clutch side for supply between the outer clutch and the inner clutch. The one-way clutch according to claim 1, wherein the inner clutch side supply groove is formed by a radial supply groove and an axial supply groove intersecting the radial supply groove. The one-way clutch according to claim 2, wherein the radial supply groove and the axial supply groove have equal groove depths. The one-way clutch according to claim 2, wherein the radial supply groove and the axial supply groove have different groove depths. 5. The outer clutch according to claim 1, wherein an outer clutch side supply groove is formed in the outer clutch for supplying the lubricating fluid between the inner clutch and the outer clutch. One-way clutch. The one-way clutch according to claim 5, wherein the outer clutch-side supply groove includes a spiral supply groove extending spirally in the axial direction. 7. The one-way clutch according to claim 6, wherein an axial end of the spiral supply groove is discontinuous with an axial end of the outer clutch. The one-way clutch according to claim 7, further comprising at least one annular seal member for suppressing leakage of the lubricating fluid supplied between the inner clutch and the outer clutch.

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