JP3977065B2 - Clutch unit - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a clutch unit for transmitting input torque of an input side member to another member.
[0002]
[Prior art]
In general, in a clutch unit using an engagement element such as a roller or a ball, the input is performed by engaging or disengaging the engagement element such as a roller or a ball in a gap formed between the input side member and the output side member. It is configured to control transmission / cutoff of torque.
[0003]
[Problems to be solved by the invention]
As an actual mechanism of the clutch unit, by repeatedly rotating an operation member such as an operation lever, the input side member is intermittently rotated to transmit the input torque to the output side member. In some cases, the rotation amount for each operation is accumulated in a superimposed manner.
[0004]
In this clutch unit, each time the operating lever is operated once, it is necessary to return the operating lever to the neutral position by appropriate returning means while restricting the follow-up rotation of the output side member.
[0005]
As this returning means, one utilizing an elastic force of a spring can be considered. In this case, a large elastic force is required for the spring to reliably return the operating lever to the neutral position, but the necessary spring constant is secured under conditions such as a limited spring installation space. Therefore, there is a possibility that the return to the neutral position of the operation lever or the input side member may be insufficient.
[0006]
Therefore, an object of the present invention is to provide a clutch unit that can reliably return the operation member and the input side member to the neutral position even under a condition where the installation space of the spring is limited.
[0007]
[Means for Solving the Problems]
In order to achieve the above object, in the present invention, an input side member to which torque is input, a rotating member to which torque is output, a stationary side member to which rotation is constrained, and a rotating member using input torque from the input side member A clutch unit that accumulates the amount of rotation for each rotational operation of the input side member via the torque transmission unit by repeated rotation from the neutral position of the input side member. , As a torque transmission part, it is arranged in the gap between the input side member and the rotating member, and when the torque is input, it engages in the gap and transmits the input torque to the rotating member, and when the input torque is released, the engagement in the gap is released. With an engaging element, A first elastic member is arranged between the input side member and the stationary side member to accumulate an elastic force with the input torque and to return the input side member to the neutral position when the input torque is released with the accumulated elastic force. And the second elastic member is disposed between the retainer for holding the engagement element and the stationary member, and the elastic force is accumulated in the first and second elastic members when the input torque is applied, and the input torque Release the engagement of the engaging element into the gap by the elastic force of both elastic members It was decided.
[0008]
By using the engagement element as the torque transmission part, it is possible to provide a clutch unit that is structurally simple and low in cost, and has high operational stability and reliability. When the input torque is applied, elastic force is accumulated in the first and second elastic members, and when the input torque is released, the engagement of the engaging element into the gap can be released by the elastic force of both elastic members. An elastic force acts directly on the input side member from the first elastic member when the torque is released, and this elastic force is independent of the mechanism for locking / unlocking between the input side member and the rotating member. Therefore, a sufficient return force can be applied to the input side member, thereby making it possible to reliably return the input side member to the neutral position.
[0009]
If the first elastic member is formed of an end ring-shaped leaf spring, the structure can be simplified and the space can be saved as compared with the case where another elastic member such as a coil spring is used. In this case, by engaging one end of the first elastic member with the input side member and the other end with the stationary side member, the first elastic member is elastically deformed with the rotation of the input side member, and the elastic force On the other hand, when the torque is released, the accumulated elastic force is directly transmitted to the input side member, so that the input side member can be reliably returned to the neutral position.
[0011]
If the first and second elastic members are formed of end-plate-shaped leaf springs, one of the elastic members can be arranged on the inner diameter side of the other elastic member, and the above functions can be achieved with a compact structure. Obtainable.
[0012]
Of the elastic member on the inner diameter side, it is preferable to form a relief portion for avoiding the interference in a portion that interferes with the elastic member on the outer diameter side due to elastic deformation at the time of torque input. Interference between the elastic member on the inner diameter side and the elastic member on the outer diameter side should be avoided for functional stability. By forming such a relief portion, both members can be formed without enlarging the radial gap between the elastic members. Interference can be avoided.
[0013]
If both ends of the outer diameter side elastic member are extended to the outer diameter side and both ends of the inner diameter side elastic member are extended to the inner diameter side, interference between each end portion of both elastic members and the other elastic member can be avoided. Therefore, it is possible to increase the diameter of the elastic member on the inner diameter side to the same extent as the elastic member on the outer diameter side, and a sufficient elastic force can be ensured for the elastic member on the inner diameter side.
[0014]
One end of the first elastic member is engaged with the input side member, the other end is engaged with the stationary side member, one end of the second elastic member is engaged with the cage, and the other end is engaged with the stationary side member. For example, when torque is input, the elastic force is accumulated in both elastic members by rotation of the input side member and the cage, while when the torque is released, the outer ring is returned to the neutral position mainly by the elastic force of the first elastic member. It becomes possible to return the cage and the engagement element to the neutral position by the elastic force of the elastic member.
[0015]
The clutch unit having the above-described configurations, an output side member to which torque is output, and the rotary member and the output side member of the clutch unit are arranged to output the input torque of the input side member through the rotary member. In combination with a reverse input torque blocking mechanism that transmits to the side member and blocks transmission of the reverse input torque from the output side member to the rotating member, the output side member is intermittently rotated by repeated rotation of the input side member, It is possible to provide a rotary drive device that blocks the return input torque from the output side member to the input side. In this apparatus, for example, in an apparatus that adjusts the position of a required part by transmitting an input torque generated by a rotation operation of the operation member to the output side mechanism, the position of the output side mechanism is not changed when the operation member is not operated. It is suitable for applications that require a function to hold
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment of a clutch unit according to the present invention will be described with reference to the drawings.
[0017]
As shown in FIGS. 1 (a) and 1 (b), the clutch unit of this embodiment includes an outer ring 1 as an input side member, an inner ring 2 as a rotating member, and an engagement element as a torque transmission unit, such as a plurality of rollers. 3, a cage 4 that holds the roller 3, and two types of elastic members 5 </ b> A and 5 </ b> B.
[0018]
The outer ring 1 includes a first thin member 1A and a second thin member 1B. In the present embodiment, the end inner periphery 1Be of the second thin member 1B is disposed on the outer periphery of the first thin member 1A, more specifically, on the outer periphery of the inner diameter flange portion 1Ac, and the end faces 1Ag of both members 1A, 1B, 1Bg is on the same plane in the radial direction. Although both the thin members 1A and 1B can be manufactured by pressing a steel plate, for example, the second thin member 1B can be formed of a molded product such as a resin.
[0019]
The first thin member 1A includes a drum portion 1Ab in which a plurality of cam surfaces 1Aa are formed on the inner periphery at equal intervals in the circumferential direction, an inner diameter flange portion 1Ac extending from the one end portion of the drum portion 1Ab to the inner diameter side, An outer-diameter flange portion 1Ad extending from the other end of the drum portion 1Ab to the outer-diameter side.
[0020]
Each cam surface 1Aa has a deep central portion in the circumferential direction and is shallow in an inclined manner from the central portion toward both sides in the circumferential direction. The inner diameter flange portion 1Ac serves to prevent the retainer 4 from coming off in one axial direction and to maintain the coaxiality of the outer ring 1 with respect to the inner ring 2.
[0021]
The outer diameter flange portion 1Ad is formed with a plurality of (six in the illustrated example) fitting grooves 1Ae used for coupling with the second thin member 1B, and the drum portion along the axial direction from the outer diameter end. One or a plurality of stopper claws 1Af extending to the opposite side to 1Ab are formed. This stopper claw 1Af is in one side of the first thin member 1A (on the right side in FIG. 1 (a)) and engages with a stopper (not shown) of a stationary side member whose rotation is restricted in the rotational direction. The rotation of the outer ring 1 is restricted to a predetermined range.
[0022]
The entire first thin member 1A or the cam surface 1Aa is subjected to heat treatment (surface hardening treatment) such as carburizing quenching tempering, carbonitriding quenching tempering, induction quenching tempering, and submerged quenching tempering.
[0023]
The second thin member 1B is formed with a plurality of (six in the illustrated example) fitting claws 1Ba extending from the outer diameter end to the first thin member 1A side along the axial direction. As shown in FIGS. 1 (a) and 1 (b), the joint claw 1Ba is fitted into the fitting groove 1Ae of the first thin member 1A and press-fitted or swaged to fix the relative rotation and shaft of the thin members 1A and 1B. Directional relative movement is restricted. Under this state, the fitting claw 1Ba engages with the concavo-convex portion of the operating lever 6 as an operating member mounted on the outer periphery thereof, so that the relative rotation of the operating lever 6 with respect to the outer ring 1 is performed. Being regulated. Accordingly, by rotating the operation lever 6, the first thin member 1 </ b> A and the second thin member 1 </ b> B rotate integrally, whereby the input torque from the operation lever 6 is input to the outer ring 1.
[0024]
The illustrated inner ring 2 has a cylindrical shape and includes a circumferential surface 2a that forms a wedge gap between the outer ring 1 and the cam surface 1Aa of the outer ring 1 (first thin member 1A).
[0025]
As shown in FIG. 2, the cage 4 has a cylindrical shape, and includes a plurality of (for example, ten) window-shaped pockets 4a for accommodating the rollers 3, and a pair of notch portions 4b spaced apart in the circumferential direction. Engaging portions 5B1 and 5B2 of a second elastic member 5B, which will be described later, are inserted into both cutout portions 4b (see FIG. 3). Although the material of the cage 4 is not particularly limited, in this embodiment, the cage 4 is an injection-molded product of a synthetic resin material, for example, a synthetic resin material in which 25% by weight of glass fiber is blended with polyamide 66 (PA66).
[0026]
As shown in FIGS. 1B and 3, the elastic members 5A and 5B are each formed of an end ring-shaped leaf spring formed by rolling a strip plate material (for example, made of metal such as stainless steel). be able to. One elastic member 5B is disposed on the inner diameter side of the other elastic member 5A.
[0027]
As shown in FIG. 3, engaging portions 5A1, 5A2 bent to the outer diameter side are formed at both ends of the first elastic member 5A on the outer diameter side. One of the engaging portions 5A1 and 5A2 engages with the outer ring 1 and the other engages with the stationary member (not shown) when the input torque is applied and released. Specifically, the locking portion 1a is formed on the outer ring 1 as shown, the locking portion 7a is formed on the stationary member 7, and the locking portion when the outer ring 1 is in the neutral state as shown in the drawing. The phases of 1a and 7a in the circumferential direction are matched, and both engaging portions 5A1 and 5A2 are elastically brought into contact with both sides of the engaging portions 1a and 7a in the circumferential direction. As a result, even when the outer ring 1 rotates in either forward or reverse direction, one engaging portion engages with the outer ring 1 and the other engaging portion engages with the stationary member 7. Thus, the circumferential distance between the engaging portions 5A1 and 5A2 can be expanded and the elastic force can be accumulated in the first elastic member 5A. When the rotational force (input torque) acting on the outer ring 1 is released, the outer ring 1 returns to the neutral state by the elastic force of the first elastic member 5A.
[0028]
Engagement portions 5B1 and 5B2 bent toward the inner diameter side are formed at both ends of the second inner diameter side elastic member 5B. The engaging portions 5B1 and 5B2 are arranged with a phase shift in the circumferential direction with respect to the engaging portions 5A1 and 5A2 of the first elastic member 5A (for example, having a phase difference of about 90 °). desirable. Both the engaging portions 5B1 and 5B2 are inserted into the notch portions 4b of the retainer 4, respectively. When the cage 4 is in a neutral state, the engaging portions 5B1 and 5B2 are elastically engaged with the side surfaces 4b1 and 4b2 (side surfaces facing in the circumferential direction) of the notch portion 4b, respectively, and are stationary. The engaging portions 7b formed on the member are elastically engaged with each other. From this state, when the cage 4 rotates in either the forward or reverse direction, one engaging portion of the second elastic member 5B is engaged with the cage 4, and the other engaging portion is engaged with the stationary member 7. Accordingly, the circumferential distance between the engaging portions 5B1 and 5B2 is expanded with the rotation of the cage 4, and an elastic force is accumulated in the second elastic member 5B. When the rotational force acting on the cage 4 is released, the cage 4 receives a restoring force by the elastic force of the second elastic member 5 and returns to the neutral state.
[0029]
When the engaging portions 5B1 and 5B2 of the second elastic member 5B are pushed and spread, the deformation amount of the elastic member 5B increases in the vicinity of the engaging portions 5B1 and 5B2, so that this deforming portion becomes the first on the outer diameter side. May interfere with the elastic member 5A. In order to avoid this, as shown in FIG. 3, in the second elastic member 5B, in the vicinity of the engaging portions 5B1 and 5B2, for example, a linear shape that draws a chord with respect to an arc as shown in the figure. It is desirable to form the escape portion 5B3.
[0030]
With the above assembly, as shown in FIG. 4, the outer ring 1 and the cage 4 are connected to the stationary member 7 via the elastic members 5A and 5B, respectively.
[0031]
Next, the operation of the clutch unit of this embodiment will be described with reference to FIGS. 4 to 6, the first and second elastic members 5 </ b> A and 5 </ b> B and the stationary member 7 are schematically illustrated and conceptually illustrated. Further, the operation lever 6 is not shown. In the drawing, the second elastic member 5B is drawn larger than the first elastic member 5A, but this is for the convenience of drawing and is not related to the spring characteristics such as the strength of the elastic force.
[0032]
FIG. 4 shows a neutral state of the clutch unit. In this neutral state, the roller 3 is positioned at the center of the cam surface 1Aa, and is separated from the wedge gaps in both the forward and reverse directions formed between the cam surface 1Aa and the circumferential surface 2a. The diameter of the roller 3 is set to be slightly smaller than the radial distance between the central portion of the cam surface 1Aa and the circumferential surface 2a, and between the roller 3 and the central portion of the cam surface 1Aa and the circumferential surface 2a. Has a radial gap.
[0033]
FIG. 5 shows a state in which the operating lever 6 is rotated and input torque is input to the outer ring 1. For example, in the figure, when an input torque in the counterclockwise direction is input to the outer ring 1, the cam surface 1Aa moves relative to the roller 3 in the counterclockwise direction as the outer ring 1 rotates, so that the roller 3 Engage (bite) the wedge gap. Since the retainer 4 tries to stop together with the stationary side member 7 by the second elastic member 5B, the outer ring 1 can be relatively moved. Thereby, since the outer ring 1 and the inner ring 2 are locked, the input torque from the outer ring 1 is transmitted to the inner ring 2 through the roller 3, and the outer ring 1, the roller 3, the cage 4, and the inner ring 2 are integrated. It rotates counterclockwise. The maximum amount of this rotation is regulated by the contact between the stopper portion of the stationary member 7 and the stopper claw 1Af of the outer ring 1. Then, as described above, the elastic members 5A and 5B are bent as the outer ring 1 and the retainer 4 are rotated, and elastic forces corresponding to the amount of the bending are accumulated.
[0034]
FIG. 6 shows a state when the operation lever 6 (outer ring 1) is opened. In this case, the elastic force in the clockwise direction acts on the outer ring 1 by the elastic force accumulated in the first elastic member 5A, and the outer ring 1 rotates in the clockwise direction to return to the neutral position shown in FIG. At the same time, the rotational force in the clockwise direction acts on the cage 4 by the elastic force accumulated in the second elastic member 5B, and the roller 3 is pushed by the cage 4 and returns to the neutral position together with the cage 4. At this time, since the roller 3 presses the cam surface 1Aa, the outer ring 1 returns to the neutral position not only by the elastic force of the first elastic member 5A but also by the elastic force f from the second elastic member 5B. On the other hand, the inner ring 2 maintains the rotation position given by the rotation operation of FIG. Therefore, when the rotation operation of the operation lever 6 is repeatedly performed, the rotation amount for each rotation operation is accumulated in the inner ring 2 in a superimposed manner. From the above, this clutch unit is suitable for an application in which, for example, the input torque generated by the turning operation of the operation lever 6 is transmitted to the output side mechanism and the position of the required part is adjusted.
[0035]
4 to 6, the same operation as described above is performed when the clockwise input torque is input to the outer ring 1 (the direction of the operation is reversed). Alternatively, the input torque can be input from the inner ring side. In this case, a cam surface is provided on the outer periphery of the inner ring and a circumferential surface is provided on the inner periphery of the outer ring.
[0036]
By the way, when the input torque is released as described above, the elastic force in the returning direction acts on the outer ring 1 not only from the first elastic member 5A but also from the second elastic member 5B. Therefore, in principle, the return operation of the outer ring 1 can be performed only with the elastic force from the second elastic member 5B. That is, in FIG. 3, even if the first elastic member 5A and the engaging portions 1a and 7a engaged therewith are omitted, it is considered that the outer ring 1 can be returned to the neutral position.
[0037]
However, with this structure, the return force of the outer ring 1 when the input torque is released may be insufficient, and the outer ring 1 may not return to the neutral position completely. That is, in order to increase the restoring force of the outer ring 1, it is ideal that the elastic force F of the elastic member 5B acts only on the path of the cage 4 → the roller 3 → the outer ring 1 as shown in FIG. However, according to the study by the present inventors, it has been found that in practice, most of the elastic force F is lost due to the friction loss μF ′ between the inner ring 2 and the roller 3. Specifically, the force of μ × F / tan 2α is lost, and only the force F (1−μ × F / tan 2α) acts as a return force on the outer ring 1 (μ is the inner ring 2 and the roller 3). The coefficient of friction, α is the Strat angle). In a normal clutch unit, the value of α is about 4 °. Therefore, assuming that μ is 0.1, the effective return force is about 30% of the elastic force F, and there is a concern that the return force is insufficient. In order to secure a sufficient restoring force, it is sufficient to increase the elastic force F of the elastic member 5B. However, it is difficult to expand the installation space of the elastic member 5B, and it is necessary to consider the allowable stress of the elastic member 5B. For this reason, simply increasing the size or thickness of the elastic member 5B is not sufficient as a measure for insufficient restoring force.
[0038]
On the other hand, the structure which arrange | positions the 1st elastic member 5A between the outer ring | wheel 1 and the stationary side member 7 as mentioned above, and returns the outer ring | wheel 1 directly with the elastic force of this elastic member 5A, ie, an elastic member, The outer ring 1 has a structure separated into a first elastic member 5A dedicated to returning the outer ring 1 and a second elastic member 5B dedicated to switching the locked / unlocked state between the outer ring 1 and the inner ring 2. 1 can be reliably performed, and the operation stability of the clutch unit can be improved.
[0039]
In order to confirm the above effects, the outer ring of the clutch unit (present invention) shown in FIG. 4 and the clutch unit (comparative product) shown in FIG. A return force of 1 was measured. In the conventional product, 44.1 to 53.9 [× 10 when opened at 25 ° ^-2 N · m] (the unit is the same hereinafter), the return force is 24.5 to 29.4 at standby, whereas the product of the present invention is 117.6 to 127.4 at 25 ° open, standby It was clarified that a restoring force of 58.8 to 69.6 was obtained in some cases, and in any case, an outer ring restoring force about twice as large as that of the comparative product could be obtained.
[0040]
The clutch unit can be incorporated in a power transmission unit of various devices. In the following description, an embodiment of a rotary drive device using the clutch unit will be described as an example.
[0041]
As shown in FIG. 8, the rotary drive device includes an outer ring 1 as an input side member, an output shaft 12 as an output side member, an inner ring 13 as a rotating member, an outer ring 14 as a stationary side member, and an input. The first clutch part 15 provided on the side and the second clutch part 16 as a reverse input blocking mechanism provided on the output side are configured as main elements.
[0042]
The outer ring 1 as an input side member is comprised by the 1st thin member 1A and the 2nd thin member 1B similarly to the outer ring of the clutch unit shown in FIG. An operation lever 23 is coupled to the outer ring 1 (see FIG. 14), and input torque in the forward direction or the reverse direction is input from the operation lever 23 to the outer ring 1. In this embodiment, an axial preload is applied to the outer ring 1 by interposing an elastic body 29 made of a wave spring or a disc spring between the washer 28 and the end face 1Ag of the first thin member 1A. A configuration is added.
[0043]
FIG. 9 shows the output shaft 12 as an output side member. The output shaft 12 includes a journal portion 12a on one end side, a large diameter portion 12b on the center side, and a connecting portion 12c on the other end side. The journal portion 12a is inserted into a radial bearing surface 13a1 of an inner ring (13: see FIG. 10) described later. A plurality of (for example, eight) cam surfaces 12b1 are formed at equal intervals in the circumferential direction on the outer periphery of the large diameter portion 12b. Each cam surface 12b1 is formed in a flat surface shape that forms a chord with respect to a circle centered on the axis of the output shaft 12. Further, a plurality of (for example, eight) pin holes 12b3 in the axial direction are formed at predetermined intervals in the one end side portion of the large diameter portion 12b. The pins 13b1 of the inner ring 13 are inserted into these pin holes 12b3. An annular recess 12b4 is formed in the other end portion of the large diameter portion 12b. A friction member (19: see FIG. 13) to be described later is press-fitted into the annular recess 12b4, and an inner peripheral wall 12b5 of the annular recess 12b4 is inserted into a radial bearing surface 17e2 of a fixed side plate (17: see FIG. 12) to be described later. Become a journal surface. The connecting portion 12c is formed with a tooth mold 12c1 for connecting another rotating member.
[0044]
The output shaft 12 is formed by forging from a steel material such as case-hardened steel, carbon steel for machine structural use, bearing steel, and the like, and is subjected to appropriate heat treatment such as carburizing and tempering, carbonitriding and tempering, induction quenching and tempering, and quenching and tempering. Is given. In this embodiment, case-hardened steel (for example, chromium molybdenum steel SCM420) is used as a steel material for forming the output shaft 12, and carburizing and tempering is performed as a heat treatment to adjust the surface hardness of the surface layer portion to 57 to 62HRC. is doing. The output shaft 12 may be a steel cut product.
[0045]
FIG. 10 shows the inner ring 13 as a rotating member. The inner ring 13 includes a cylindrical portion 13a, a flange portion 13b extending from one end of the cylindrical portion 13a to the outer diameter side, and a plurality of (for example, eight) extending from the outer diameter end of the flange portion 13b to one side in the axial direction. The main part is composed of the column part 13c. The cylindrical portion 13 a is extrapolated to the journal portion 12 a of the output shaft 12 and is inserted into the outer ring 1. A radial bearing surface 13a1 that supports the journal portion 12a of the output shaft 12 in the radial direction is formed on the inner periphery of the other end portion of the cylindrical portion 13a, and on the outer periphery of the other end portion of the cylindrical portion 13a, A circumferential surface 13a2 is formed between the outer ring 1 and the cam surface 1Aa to form a wedge gap in both forward and reverse rotation directions. A plurality of (for example, eight) pins 13b1 projecting to one side in the axial direction are formed on the flange portion 13b at predetermined intervals in the circumferential direction. These pins 13b1 are inserted into the pin holes 12b3 of the output shaft 12, respectively. Further, pockets 13c1 that open toward one side in the axial direction are formed between the column portions 13c adjacent to each other in the circumferential direction, and a roller 30 of a second clutch portion (16: see FIG. 15) described later is formed in these pockets 13c1. The leaf spring 31 is accommodated. Since the roller 30 and the leaf spring 31 can be incorporated into the pocket 13c1 from the opening in the axial direction of the pocket 13c1, the assembling work is easy.
[0046]
The inner ring 13 is formed by forging from a steel material such as case hardened steel, machine structural carbon steel, bearing steel, and the like, and subjected to appropriate heat treatment such as carburizing quenching tempering, carbonitriding tempering quenching, induction quenching tempering, and submerged quenching tempering. Applied. In this embodiment, case-hardened steel (for example, chromium molybdenum steel SCM420) is used as the steel material forming the inner ring 13, and carburization quenching and tempering is performed as a heat treatment to adjust the surface hardness of the surface layer portion to 57 to 62HRC. ing. Note that the inner ring 13 can be a steel cut product or a press-formed product of a steel plate (for example, a cold rolled steel plate).
[0047]
FIG. 11 shows the outer ring 14 as a stationary side member. The outer ring 14 protrudes toward the outer diameter side from a flange portion 14a extending toward the radially inner side, a cylindrical portion 14c extending from the outer diameter end of the flange portion 14a to one side in the axial direction, and one end of the cylindrical portion 14c. The main part is composed of the flange 14d. A plurality of (for example, two) stopper portions 14a1 protruding to the other side in the axial direction are arranged and formed at predetermined intervals in the circumferential direction on the flange portion 14a. These stopper portions 14a1 engage with the stopper claws 1Af (see FIG. 1A) of the outer ring 1 in the rotation direction to restrict the rotation range of the outer ring 1. Further, the flange portion 14a is formed with a pair of locking portions 14a2 protruding to the other side in the axial direction, and a second elastic force of the first clutch portion 15 is formed on the outer circumferential surface of the pair of locking portions 14a2. The engaging portions 5B1 and 5B2 of the member 5B are locked (see FIG. 3). Further, a locking portion 14a4 is formed in the vicinity of the outer periphery of the flange portion 14a, and the engaging portions 5A1, 5A2 of the first elastic member 5A of the first clutch portion 15 are formed on both sides in the circumferential direction of the locking portion 14a4. Are respectively locked.
[0048]
A circumferential surface 14c1 is formed on the inner periphery of the cylindrical portion 14c. The circumferential surface 14c1 forms a wedge clearance in both the forward and reverse rotation directions with the cam surface 12b1 of the output shaft 12. A plurality of (for example, six) notches 14d1 are formed in the collar portion 14d at predetermined intervals in the circumferential direction. The cutout portion 14d1 is compatible with a caulking portion 17c (see FIG. 12) of the fixed side plate 17 described later.
[0049]
The outer ring 14 is formed by forging from a steel material such as case-hardened steel, carbon steel for machine structure, bearing steel, etc., and subjected to appropriate heat treatment such as carburizing and tempering, carbonitriding and tempering, induction quenching and tempering, and submerged quenching and tempering. Applied. In this embodiment, case-hardened steel (for example, chromium molybdenum steel SCM420) is used as the steel material forming the outer ring 14, and carburization quenching and tempering is performed as a heat treatment to adjust the surface hardness of the surface layer portion to 57 to 62HRC. ing. The outer ring 14 can also be a cut-out product of a steel material or a press-formed product of a steel plate (for example, a cold rolled steel plate).
[0050]
FIG. 12 shows the fixed side plate 17 fixed to the outer ring 14. The fixed side plate 17 includes a flange portion 17a extending in the radial direction, a plurality of (for example, four) bracket portions 17b protruding from the outer diameter end of the flange portion 17a to the outer diameter side, and a shaft extending from the outer diameter end of the flange portion 17a. A plurality of (for example, six) caulking portions 17c protruding in one direction, a plurality of (for example, eight) engagement holes 17a1 formed in the flange portion 17a, and an axial direction from the inner diameter end of the flange portion 17a. The boss portion 17e protruding to one side is mainly configured. The four bracket portions 17b are formed at a predetermined interval in the circumferential direction, and a hollow pin-like caulking portion 17b1 is formed integrally (or separately) on each of them. The six crimping portions 17c are formed at predetermined intervals in the circumferential direction, and each includes a pair of claw portions 17c1 branched in a bifurcated shape. The fixed side plate 17 of the outer ring 14 is mounted by attaching the crimped portion 17c to the notch portion 14d1 of the outer ring 14 and crimping the pair of claw portions 17c1 in opposite directions in the circumferential direction to contact the flange portion 14d. Relative movement in the axial direction and relative movement in the rotational direction can be prevented. The caulking portion 17b1 is caulked and fixed in the mounting hole of the counterpart member.
[0051]
A radial bearing surface 17e2 is formed on the inner periphery of the boss portion 17e. The boss portion 17e is inserted into the annular recess 12b4 of the output shaft 12, and a friction member (19: see FIG. 13) described later is mounted between the outer periphery of the boss portion 17e and the outer peripheral wall of the annular recess 12b4. The engagement hole 17a1 engages with the convex portion 19a of the friction member 19 in the rotation direction to prevent relative rotation of the friction member (19) with respect to the fixed side plate 17. The radial bearing surface 17e2 of the boss portion 17e is extrapolated to the journal surface 12b5 of the annular recess 12b4, and supports the journal surface 12b5 in the radial direction.
[0052]
The fixed side plate 17 is formed by press working from a steel plate material such as a cold rolled steel plate, for example. In this embodiment, a cold rolled steel plate (for example, SPCE) is used as a steel plate material forming the fixed side plate 17. Further, heat treatment is not performed in consideration of workability and the like when the crimping portions 17c and 17b1 are crimped. It should be noted that the parts to be swaged, such as the swaged portions 17c and 17b1, may be subjected to carburizing treatment (or carbonitriding and nitriding treatment) to perform carburizing and tempering (or carbonitriding and tempering).
[0053]
FIG. 13 shows a friction member 19 as braking means. In this embodiment, the friction member 19 is ring-shaped, and a plurality of (for example, eight) convex portions 19a are formed on one end face thereof at a predetermined interval in the circumferential direction. The convex portion 19 a engages with the engagement hole 17 a 1 of the fixed side plate 17 in the rotation direction, and prevents the friction member 19 from rotating relative to the fixed side plate 17.
[0054]
The friction member 19 is formed of an elastic material such as rubber or synthetic resin, and is press-fitted into the outer peripheral wall of the annular recess 12b4 of the output shaft 12 with a tightening margin, for example. A braking force in the rotational direction (friction braking force) is applied to the output shaft 12 by the frictional force generated between the outer periphery of the friction member 19 and the outer peripheral wall of the annular recess 12b4. The magnitude of the braking force (braking torque) may be appropriately set in consideration of the magnitude of the reverse input torque input to the output shaft 12, but from the viewpoint of effectively preventing the reverse input torque reflux phenomenon. It is preferable to set it to the same magnitude as the assumed reverse input torque. When the friction member 19 is used as the braking means as in this embodiment, there is an advantage that the braking force can be set and changed by adjusting the tightening allowance of the friction member 19.
[0055]
Although the material of the friction member 19 is not particularly limited, in this embodiment, the friction member 19 is an injection molded product of a synthetic resin material, for example, a synthetic resin material in which 25% by weight of glass fiber is blended with polyacetal (POM).
[0056]
The configuration of the first clutch portion 15 is only that the inner ring 13 is a rotating member arranged on the outer peripheral side of the output shaft 12 as an output side member, as compared with the clutch unit shown in FIGS. Are different, and the other configurations are the same. Accordingly, the operation of the first clutch portion 15 is substantially the same as the explanation items based on FIGS. 1 to 6 described above, and the explanation thereof is omitted.
[0057]
FIG. 15 (AA cross-sectional view of FIG. 8) shows the second clutch portion 16. The second clutch portion 16 includes a circumferential surface 14c1 provided on the outer ring 14, a plurality of (for example, eight) cam surfaces 12b1 provided on the output shaft 12, and a space between each cam surface 12b1 and the circumferential surface 14c1. A pair of rollers 30 (for example, a total of 8 pairs) as an intervening member, an elastic member interposed between the pair of rollers 30, for example, a leaf spring 31 having an N-shaped cross section, a column portion 13c of the inner ring 13, and an inner ring 13 The pin 13b1 and the pin hole 12b3 of the output shaft 12 are configured as main elements. In this embodiment, the leaf spring 31 is made of stainless steel (for example, SUS301CPS-H) and subjected to tempering as a heat treatment.
[0058]
As shown in an enlarged view in FIG. 16, in the neutral position, the pair of rollers 30 are formed by wedge springs 31 in the forward and reverse rotational directions formed between the cam surface 12 b 1 and the circumferential surface 14 c 1, respectively. Pressed in the direction. At this time, a rotation direction gap δ1 exists between each column portion 13c of the inner ring 13 and each roller 30. Further, between the pin 13b1 of the inner ring 13 and the pin hole 12b3 of the output shaft 12, there are rotational direction gaps δ2 in both forward and reverse rotational directions. The rotation direction gap δ1 and the rotation direction gap δ2 have a relationship of δ1 <δ2. The size of the rotation direction gap δ1 is, for example, about 0 to 0.4 mm (0 to 1.5 ° about the axis of the second clutch portion 16), and the size of the rotation direction gap δ2 is, for example, 0.5 to It is about 0.8 mm (1.8 to 3.7 ° centering on the axis of the second clutch portion 16).
[0059]
In the state shown in the figure, for example, when a reverse input torque in the clockwise direction is input to the output shaft 12, the roller 30 in the counterclockwise direction (backward in the rotational direction) engages with the wedge clearance in that direction and outputs. The shaft 12 is locked clockwise with respect to the outer ring 14. When counterclockwise reverse input torque is input to the output shaft 12, the roller 30 in the clockwise direction (backward in the rotational direction) engages with the wedge clearance in that direction, and the output shaft 12 counteracts against the outer ring 14. Locked clockwise. Therefore, the reverse input torque from the output shaft 12 is locked in both forward and reverse rotation directions by the second clutch portion 16, and the reverse input torque to the first clutch portion 15 is interrupted.
[0060]
FIG. 17 shows an initial state in which the input torque (clockwise in the figure) from the outer ring 1 is input to the inner ring 13 via the first clutch portion 15 and the inner ring 13 starts to turn clockwise in the figure. ing. Since the rotation direction clearance is set to δ1 <δ2, first, the counterclockwise (backward in the rotation direction) column portion 13c of the inner ring 13 is engaged with the roller 30 in that direction (backward in the rotation direction). It is pressed clockwise (forward in the rotational direction) against the elastic force of the leaf spring 31. As a result, the counterclockwise (backward in the rotation direction) roller 30 is released from the wedge gap in that direction, and the output shaft 12 is unlocked. Therefore, the output shaft 12 can be rotated clockwise.
[0061]
When the inner ring 13 further rotates in the clockwise direction, the pin 13b1 of the inner ring 13 engages with the pin hole 12b3 of the output shaft 12 in the clockwise direction as shown in FIG. Thereby, the clockwise input torque from the inner ring 13 is transmitted to the output shaft 12 via the pin 13b1 and the pin hole 12b3, and the output shaft 12 rotates clockwise. When the counterclockwise input torque is input to the outer ring 1, the output shaft 12 rotates counterclockwise by the reverse operation. Therefore, the input torque in the forward and reverse rotational directions from the outer ring 1 is transmitted to the output shaft 12 via the first clutch portion 15, the inner ring 13, and the pin 13b1 and the pin hole 12b3 as torque transmitting means. Rotates in both forward and reverse rotation directions. When the input torque from the inner ring 13 is lost, the spring returns to the neutral position shown in FIG.
[0062]
As described above, the second clutch portion 16 transmits the input torque in the forward and reverse directions of the outer ring 1 to the output shaft 12 via the inner ring 13, while transmitting the reverse input torque from the output shaft 12 to the inner ring 13 and the outer ring 1. It functions as a reverse input torque shut-off mechanism that shuts off.
[0063]
When the outer ring 1, the output shaft 12, the inner ring 13, the outer ring 14, the first clutch part 15, the second clutch part 16, the fixed side plate 17 and the friction member 19 are assembled in the manner shown in FIG. 8, the rotational drive of this embodiment The device is completed. For example, an operation lever 23 made of resin is coupled to the outer ring 1, and the output shaft 12 is connected to a rotation member of an output side mechanism (not shown). The fixed side plate 17 is swaged and fixed to a fixing member such as a casing (not shown) by a swaged portion 17b1. In this apparatus, for example, in an apparatus that adjusts the position of a required part by transmitting an input torque generated by a rotation operation of the operation member to the output side mechanism, the position of the output side mechanism is not changed when the operation member is not operated. It is suitable for applications that require a function to hold
[0064]
【The invention's effect】
Thus, according to the present invention, the first elastic member for returning the input side member to the neutral position is disposed between the input side member and the stationary side member, and the lock / The elastic force is directly applied to the input side member regardless of the unlock switching mechanism. Accordingly, it is possible to apply a large elastic force to the input side member, and when the input torque is released, the input side member can be surely returned to the neutral position, and includes the clutch unit and further. The operational stability of the rotary drive device can be improved.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view (a view) showing an overall configuration of a clutch unit according to the present invention, and a sectional view taken along line BB in FIG.
FIG. 2 is a perspective view showing a retainer of the clutch unit.
FIG. 3 is a front view schematically illustrating a mounting state of first and second elastic members.
FIG. 4 is a sectional view conceptually illustrating the operation of the clutch unit.
FIG. 5 is a cross-sectional view conceptually illustrating the operation of the clutch unit.
FIG. 6 is a sectional view conceptually illustrating the operation of the clutch unit.
FIG. 7 is a sectional view conceptually illustrating the operation of a comparative product.
FIG. 8 is a cross-sectional view of a rotary drive device including the clutch unit.
9A is a front view showing an output shaft of the rotary drive device, and FIG. 9B is a sectional view taken along line BB in FIG. 9A.
10A is a front view showing an inner ring (rotating member) of the rotation drive device, FIG. 10B is a sectional view taken along line BB in FIG. 10A, and FIG.
11A is a front view showing an outer ring (stationary side member) of the rotary drive device, and FIG. 11B is a sectional view taken along line BB in FIG.
FIGS. 12A and 12B are a front view and a cross-sectional view taken along line BB in FIG.
FIG. 13 is a front view (a) and a longitudinal sectional view (b) showing a friction member (braking means) of a rotary drive device.
14 is a cross-sectional view of the first clutch portion of the rotary drive device taken along the line 8B-B in FIG.
15 is a cross-sectional view of FIG. 8A-A showing a second clutch portion of the rotary drive device.
FIG. 16 is a partially enlarged front view showing the operation of the first clutch portion (neutral position).
FIG. 17 is a partially enlarged front view showing the operation of the first clutch portion (when unlocked).
FIG. 18 is a partially enlarged front view showing the operation of the first clutch portion (at the time of torque transmission).
[Explanation of symbols]
1 Outer ring (input side member)
1a Locking part
1A 1st thin member
1Aa Cam surface
1B Second thin member
2 Inner ring (rotating member)
2a Circumference surface
3 Roller (engagement element)
4 Cage
4b Notch
5A First elastic member
5A1 engagement part
5A2 engaging part
5B Second elastic member
5B1 engaging part
5B2 engaging part
5B3 escape section
6 Operation lever (operation member)
7 Static side member
7a Locking part
7b Locking part
12 Output shaft (output side member)
13 Inner ring (rotating member)
14 Outer ring (stationary member)
14a2 Locking part
14a4 Locking part
15 First clutch part (clutch unit)
16 Second clutch part (reverse input blocking mechanism)
23 Operation lever (operation member)

Claims (5)

An input side member to which torque is input, a rotating member to which torque is output, a stationary side member in which rotation is constrained, and a torque transmission unit that rotates the rotating member with input torque from the input side member, In the clutch unit that accumulates the rotation amount for each rotation operation of the input side member in the rotation member via the torque transmission unit by repeated rotation from the neutral position of the input side member.
As a torque transmission part, it is arranged in the gap between the input side member and the rotating member, and when the torque is input, it engages in the gap and transmits the input torque to the rotating member, and when the input torque is released, the engagement in the gap is released. A first engaging member that stores an elastic force with an input torque between the input side member and the stationary side member and that returns the input side member to a neutral position when the input torque is released with the accumulated elastic force. An elastic member is disposed , and a second elastic member is disposed between the cage that holds the engagement element and the stationary member, and elastic force is accumulated in the first and second elastic members when an input torque is applied. In addition , the clutch unit is configured to release the engagement of the engaging element into the gap by the elastic force of both elastic members when the input torque is released .   The clutch unit according to claim 1, wherein the first elastic member is formed of an end ring-shaped leaf spring. Clutch unit according to claim 1, wherein the first and second elastic members are formed with end-defined ring-shaped leaf spring. The clutch unit according to claim 1 or 3 , wherein a relief portion for avoiding the interference is formed in a portion of the inner diameter side elastic member that interferes with the outer diameter side elastic member due to elastic deformation at the time of torque input. Rotating a clutch unit according to either one of claims 1-4, and an output-side member torque is output, it is arranged between the rotating member and the output side member of the clutch unit, an input torque of the input-side member A rotation drive device comprising: a reverse input torque blocking mechanism that transmits a reverse input torque from an output side member to a rotation member through a member and blocks transmission of a reverse input torque from the output side member to the rotation member.

Images