JP5185209B2 - Reverse input cutoff clutch - Google Patents

Description

  The present invention relates to a reverse input cutoff clutch in which the rotational driving force from the input side is transmitted to the output side, and the rotational force from the output side is not transmitted to the input side.

  There has already been proposed a reverse input cutoff clutch in which a bidirectional driving force from the input side which is the driving side is transmitted to the output side which is the driven side, and a rotational force from the output side is not transmitted to the input side. For example, as an example of a reverse input cutoff clutch in which bidirectional driving force from the input side is transmitted to the output side and external force from the output side is not transmitted to the input side, when rotational force is applied to the output member, the input member is There has been proposed a reverse input cutoff clutch that has a mechanism to be locked, the output member cannot be rotated by the locking mechanism, and the rotational force from the output side is not transmitted to the input side (see Patent Documents 1 and 2).

  When a rotational force is applied to the output member, these reverse input shut-off clutches are locked by a rolling member such as a roller or a ball positioned between the output member and the housing that bites into the output member and the housing. Thus, the output member cannot be rotated. The reverse input cutoff clutch of this structure applies a pressing force (pressurization) in the rotation direction to each roller member by each spring piece of the spring member in order to improve responsiveness and operate reliably. In general, the spring body cannot be made very large from the viewpoints of reduction in size and weight of the reverse input cutoff clutch and cost, and usually has a necessary number of thin spring pieces.

  In the case of such a reverse input cut-off clutch using a spring body, it has a structure that does not enclose the lubricant, or if the viscosity is low even if the lubricant is encapsulated, the adhesive force is weak, so it works reliably without any trouble To do. However, when a lubricant such as grease with a relatively high viscosity is enclosed, the large adhesive force of the lubricant acts in the opposite direction to the direction of elasticity of the spring member, so an external force is applied to the output member. It takes time until the rolling member bites in. That is, the responsiveness of the input / output shut-off operation is deteriorated, and particularly when the rotational driving force applied to the input member is reversed, it does not operate smoothly, resulting in problems such as impact sound and vibration. In addition, this impedes the operation of the load coupled to the output member, or imposes a burden on the drive mechanism coupled to the input member.

Japanese Patent Laid-Open No. 2007-239981 JP 2008-101715 A

  The problem to be solved by the present invention is that, in a reverse input shut-off clutch in which a lubricant such as grease having a relatively high adhesive force due to its high viscosity is enclosed, the spring body becomes a rolling member by the adhesive force of the lubricant. Since the applied pressure is reduced, the biting operation of the rolling member is delayed particularly when the rotational driving force of the input member is reversed.

  In the present invention, an input member and an output member, and a rolling member and a spring body, which are engaged with each other, are housed in a housing, and are positioned between the input member and the output member. When an external force is applied, the rolling member is an input / output shut-off clutch that cuts between the output member and the housing and shuts off the input / output, and applies a pressing force (pressurization) in the direction of the central axis of the input member and the output member. By providing an annular spring member applied to the moving member at least between the side wall portion of the housing and the rolling member, or between the lid portion and the rolling member that closes the housing, the biting operation of the rolling member is delayed. Provided is a reverse input cutoff clutch that does not cause

  According to the present invention, a thin spring body can apply a desired amount of pressing force to the rolling member. Therefore, even if a lubricant with high adhesive strength is sealed in a desired housing, the input is particularly effective. It is possible to provide a small and economical reverse input shut-off clutch that operates smoothly even when the rotational driving force applied to the member is reversed, and does not generate impact sound or vibration. Furthermore, since the input member and the output member are not firmly coupled to each other, the input member and the output member can be handled separately, and can be easily incorporated into or removed from the housing.

It is drawing which shows the external appearance of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing which shows the housing of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing which shows the input member of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing which shows the input member of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing which shows a part of input member of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing which shows the output member of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing which shows the output member of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing for demonstrating the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing for demonstrating the spring member used for the reverse input interruption | blocking clutch which concerns on Embodiment 1 of this invention. It is drawing for demonstrating the structure of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of invention. It is drawing for demonstrating operation | movement of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of invention. It is drawing for demonstrating operation | movement of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of invention. It is drawing for demonstrating operation | movement of the reverse input interruption | blocking clutch which concerns on Embodiment 1 of invention.

  The reverse input cutoff clutch according to the present invention includes an annular spring member that applies a pressing force (pressure) in the same direction as the central axis of the input member and the output member to the rolling member, and at least the side wall portion of the housing and the rolling member. Or between the lid that closes the housing and the rolling member, even if a relatively high-viscosity lubricant is enclosed in the housing, it is not affected by the adhesive force of the lubricant. It is characterized in that it operates smoothly even when the rotational driving force applied to the input member is reversed.

[Embodiment 1]
The reverse input cutoff clutch according to the first embodiment of the present invention will be described with reference to FIGS.
This reverse input cutoff clutch is mainly shown in a housing 1 as shown in FIGS. 1 and 2, an input member 3 as shown in FIGS. 3 to 5, etc., FIG. 6, FIG. Such an output member 5, a roller member or a ball member (hereinafter collectively referred to as a rolling member 7) shown in FIG. 8, FIG. 10 to FIG. 13 and the like, and a spring exemplified in FIG. It consists of member 9.

  First, the housing 1 will be described with reference to FIGS. 1 and 2. FIG. 1 is a view showing an example of the basic appearance of the reverse input cutoff clutch of the present invention. 2A shows a view of the housing 1 viewed from the left side, and FIG. 2B shows a cross section of the housing. The housing 1 includes a housing member 11 and a lid portion 12 that closes the housing member 11. The housing member 11 includes a cylindrical portion 14 having a cylindrical inner wall surface 13 and a side wall portion 15 that functions as a bottom portion that closes one end of the cylindrical portion 14. The side wall portion 15 has a through hole 16 at the center and a short cylindrical lead-out portion 17 surrounding the through hole 16. As shown in FIG. 10, the lead-out portion 17 is provided with an oil-impregnated metal obtained by soaking a sintered metal with oil as required, or a rotation promoting member 20 such as a small ball bearing or roller bearing. The housing 1 is made of various metal materials or engineering plastic materials, and the material is not particularly limited.

  Although the basic structure of the housing 1 has been described above, the housing member 11 may have a double structure (not shown). As will be described later, as shown in FIG. 12, since the rolling member 7 has an operation of biting between the cylindrical inner wall surface 13 of the cylindrical portion 14 and the output member 5, the first member made of a material having a high friction resistance is used. One housing member and a second housing member covering the housing member may be included. Further, in order to make the frictional force between the cylindrical inner wall surface 13 of the cylindrical portion 14 and the rolling member 7 uniform, one or more narrow annular grooves may be provided on the cylindrical inner wall surface 13. Further, the shape of the housing 1 can be arbitrarily changed according to the requirements of the equipment to be attached.

  Next, the input member 3 will be described with reference to FIGS. FIG. 3 is a perspective view of the input member 3. 4A is a front view of the input member, FIG. 4B is a cross-sectional view of the input member, and FIG. 4C is a back view of the input member. FIG. 5 is an enlarged view showing a part of the input member 3. The input member 3 is inserted into the through hole 16 of the side wall 15 of the housing member 11 in the housing 1 and has a cylindrical input shaft portion 31 having a diameter slightly smaller than the diameter of the through hole, and one end of the input shaft portion 31. And an input engaging portion 32 that is formed integrally with the input shaft portion 31. The input engaging portion 32 includes a regular pentagonal input common portion 33 that spreads outward in the radial direction with the tip of the input shaft portion 31 as a central portion, and five input engaging pieces 34, 35, 36, 37, and 38. Become. The input engagement pieces 34 to 38 extend from the corners of the regular pentagonal input common portion 33 at equal intervals through the center of the input shaft portion 31 in the direction of the central axis Z1 extending in the axial direction. And extends outward (radial direction) with respect to the central axis Z1.

  Further, the input engagement pieces 34, 35, 36, 37, 38 are respectively an arcuate outer wall surface A (such as FIG. 3), an arcuate inner wall surface B (such as FIG. 4), an arcuate outer wall surface A, and an arcuate outer wall. It has a concave outer wall surface C between the wall surface A. The diameter of a virtual circle connecting the five arcuate inner wall surfaces B is determined by the size of five output engagement pieces of the output member 5 described later, and the arcuate inner wall surface B does not contact the five output engagement pieces. The size is such that a predetermined interval exists. Therefore, the five arcuate inner wall surfaces B of the input engagement pieces 34 to 38 shown in FIG. 3 form a space suitable for receiving an output engagement portion 52 of the output portion 5 described later.

  The five input engagement pieces 34 to 38 have the same shape and the same size, and the gaps between the adjacent input engagement pieces and the input engagement pieces are almost the same. Therefore, in the following description, the input engagement piece 34 will be described as a representative, but the same applies to the other input engagement pieces 35 to 38. As shown in FIG. 5, as an example, the input engagement piece 34 includes inclined contact surfaces 34G having a predetermined angle with respect to the rotation direction of the input member 3 on both the left and right side wall surfaces, and the inclined contact surface 34G is a broken line. When pressed against the rolling member 7 shown, a pressing force having a vector directed inward, that is, toward the center point O of the rolling member 7 is applied. The concave outer wall surface C reduces the contact area between the cylindrical inner wall surface 13 of the housing member 11 and the input engagement piece 34, and forms a lubricant reservoir in which a lubricant such as grease is accommodated.

  Here, the diameter of the imaginary circle formed by the five arcuate outer wall surfaces A of the input engagement pieces 34 to 38 is cylindrical in the housing member 11 so that the input member 3 can stably rotate in the housing 1. It is preferable that the diameter is slightly smaller than the diameter of the cylindrical inner wall surface 13 of the portion 14. 3 and 4, the diameter of the virtual circle formed by the five arcuate outer wall surfaces A of the input engagement pieces 34 to 38 is larger than the outer diameter of the regular pentagonal input common portion 33. , May be the same or vice versa. For example, the input common portion 33 has a circular outer shape, and the diameter of the circle is substantially the same as the diameter of the virtual circle formed by the five arcuate outer wall surfaces A of the input engagement pieces 34 to 38, or from the diameter. May be larger. In this case, the outer diameter of the input common portion 33 is set so that the input member 3 rotates without any problem in the housing 1, and the maximum diameter of the input common portion 33 is the inner diameter of the cylindrical portion 14 of the housing member 11. It is smaller than the diameter of the wall surface 13. In addition, although demonstrated as the regular pentagonal input common part 33, it is of course possible to include other polygonal or circular shapes such as a regular hexagonal shape, and input engagement pieces that are located at regular intervals.

  Next, the output member 5 will be described with reference to FIGS. FIG. 6 is a perspective view of the output member 5. FIG. 7A is a view of the output member 5 seen from the side, and FIG. 7B is a view of the output member 5 seen from the front. As shown in FIGS. 6 and 7, the output member 5 includes an output shaft 51 having an outer diameter through which a through hole (not shown) of the lid 12 in the housing 1 shown in FIG. 1 is inserted, and the output shaft 51. An output engagement portion 52 is formed at one end integrally with the output shaft portion 51 or fixed by screwing or the like. A central axis Z2 extending in the axial direction through the central point of the output shaft portion 51 is coaxial with the above-described central axis Z1 of the input member 3. The output engagement part 52 has an output common part 53 at the tip of the output shaft part 51 and five output engagement pieces 54, 55, 56, 57, 58 extending from the output common part 53 at equal intervals in the radial direction. The output engaging pieces 54 to 58 extend in the direction of the central axis Z2 to have a predetermined thickness, and extend in the radial direction, that is, outward from the central axis Z2. The five output engagement pieces 54 to 58 have the same shape and the same size.

  The output engagement portion 52 is disposed in a space formed by the input engagement pieces 34 to 38. As shown in FIG. 8, the five output engagement pieces 54 to 58 are positioned at arbitrary intervals between the side surfaces of the adjacent input engagement pieces 34 to 38 in the housing member 11. The front end surface 54a (FIG. 7) of the output engagement piece 54 is gently curved or flat, and when the output member 5 rotates, the distance between the cylindrical inner wall surface 13 and the front end surface 54a decreases. Thus, the rolling member 7 bites in. The front end surface 54a supports the rolling member 7 indicated by a chain line in FIG. In a state where no rotational force is applied to the output member 5, the rolling member 7 is positioned substantially at the center of the front end surface 54 a, and a minute gap is formed between the rolling member 7 and the cylindrical inner wall surface 13 of the housing member 11. Exists. Therefore, the rolling member 7 is in a free state. However, when the output member 5 is slightly rotated to the left or right, the tip surface 54 a is inclined, so that the rolling member 7 is located between the cylindrical inner wall surface 13 of the housing member 11 and the tip surface 54 a of the output engagement piece 54. Bite into. The distal end surfaces of the other output engagement pieces 55, 56, 57, 58 are the same as the distal end surface 54 a of the output engagement piece 54. Further, contrary to FIG. 1, the output member 5 may be positioned on the bottom side of the housing 1 and the input member 3 may be positioned on the lid 12 side. In this embodiment, a roller member is used as the rolling member 7, but a ball may be used when the required torque is small.

  Next, a state in which the input member 3, the output member 5, and the rolling member 7 as described above are incorporated in the housing 1 will be described. FIG. 8 is a view as seen from the bottom side of the housing 1 and shows the cylindrical portion 14 in a state where the side wall portion 15 which is the bottom portion of the housing member 11 is removed. 8 is the bottom of the housing member 11, and the input shaft portion 31 is led out through the through hole 16 (FIG. 2) formed in the side wall portion 15 of the housing member 11 as shown in FIG. Next, the output engaging portion 52 of the output member 5 is inserted into the cylindrical portion 14 of the housing member 11, and the five output engaging pieces 54, 55, 56, 57, 58 of the output engaging portion 52 are input members. It is arranged so as to be positioned substantially in the middle between adjacent ones of the input engaging pieces 34, 35, 36, 37, 38 of the joint portion 32, and the respective front end surfaces (for example, 54a) of the five output engaging pieces 54-58. ) And the cylindrical inner wall surface 13 of the cylindrical portion 14 are respectively disposed. In FIG. 8, the spring member 9 is not shown.

  Next, the spring member 9 will be described with reference to FIGS. 9 and 10. Although not shown in the drawings, the conventional spring member applies a pressure in the rotation direction and a direction opposite to the rotation direction to each rolling member by each spring piece (for example, Patent Documents 1 and 2). In the present invention, the rolling centers of the rolling members 7 shown in FIG. 8, that is, the center axis Z1 of the input member 3 and the center axis Z3 of the output member 5 are coaxial. The direction is characterized in that the spring member 9 applies a pressing force to each rolling member 7. Such a spring member 9 can apply a pressing force of a desired magnitude to the rolling member 7 with a simple structure, and can be easily incorporated into the reverse input cutoff clutch, so that the cost is low.

  As an example, the spring member 9 includes an annular or polygonal first and second annular plates 91 and 92 and an annular or polygonal annular elastic member 93 sandwiched therebetween. The first and second annular plates 91 and 92 are made of a material having a relatively high wear resistance, for example, a washer made of a metal material. The annular elastic member 93 is formed of a wave spring, which is a kind of leaf spring, or a ring made of a rubber material. The first and second annular plates 91 and 92 include a central hole 94 that is somewhat larger than the outer diameter of the input shaft portion 31 or the output shaft portion 51. The annular elastic member 93 also has a central hole that is approximately the same as or larger than the central hole 94. Further, the first and second annular plates 91 and 92 and the annular elastic member 93 have outer diameters that fit in the cylindrical inner wall surface 13 of the housing member 11. In order for the first and second annular plates 91 and 92 and the annular elastic member 93 to operate stably in the housing member 11, their maximum outer diameter is at least the cylindrical inside of the cylindrical portion 14 in the housing member 11. It is preferably somewhat smaller than the wall surface 13.

  Although not shown, the spring member 9 includes an annular part or a polygonal part having a hole through which the input shaft part 31 or the output shaft part 51 is inserted, and a spring piece extending outward with respect to the central axis Z3. You may comprise only the plate-shaped spring body of a sheet. In this case, a relatively thick metal plate rich in elasticity is punched out by a press or the like to form a spring body that becomes the spring member 9, and the tip of each spring piece of the spring body is oriented in the direction of the central axis Z3. It can be bent to make a spring piece with a large spring force. As many spring pieces as the number of rolling elements 7 are provided in the annular part or the polygonal part. Referring to FIG. 8, each spring piece has a width that is approximately the same as or slightly smaller than the rotational width of the output engagement pieces 54, 55, 56, 57, 58. A pressing force is applied to each rolling member 7 in the direction of the central axis Z3 shown in FIG. In the configuration according to the present invention, even a sufficiently thin spring member can easily apply a significantly greater pressing force to the rolling member 7 than in the prior art.

  Therefore, in the spring member having such a configuration, even if the side surface of the rolling member 7 is retracted without protruding from the side surface of the input engagement pieces 34 to 38 in FIG. The desired pressing force can be applied to the side surface of the rolling member 7 even if it is approximately the same as the side surface of the rolling member. In addition, the said side surface points out the surface of each member located in the direction of the central axis line Z3 shown in FIG. This spring body is useful even when the rolling member 7 is made of a ball. The spring member 9 may be a wave-type spring. In this case, the protruding portion of the wave is structured to press the side surface of each rolling member 7. Moreover, you may fix such a spring member 9 to the side surface of the input engagement pieces 34-38 or the side surfaces of the output engagement pieces 54-58 as needed. In this case, after fixing the spring body, the spring body also serves to prevent the input member 3, the output member 5, and the rolling member 7 from falling apart.

  FIG. 10A shows a partial cross section of the reverse input cutoff clutch according to the present invention and a partial cross section related to the output engagement piece 54. As shown in FIG. 10A, the spring member 9 is disposed between the side wall portion 15 of the housing member 11 and one side surface of each rolling member 7, and is opposite to the spring member 9, that is, the lid portion 12. An annular metal plate 100 such as a washer is disposed between the other side surfaces of each rolling member 7. Therefore, the spring member 9 gives a pressing force in the direction of the central axes Z1 and Z2 of the input shaft portion 31 and the output shaft portion 51 to one side surface of each rolling member 7 so that the other side surface of each rolling member 7 is annular. The metal member 100 is pressed.

  Alternatively, as shown in FIG. 10B, which is a cross-sectional view of a part of the reverse input cutoff clutch according to the present invention, the spring member 9 is disposed between the lid portion 12 and the other side surface of each rolling member 7. The annular metal member 100 may be disposed on the opposite side of the spring member 9, that is, between the side wall portion 15 of the housing member 11 and one side surface of each rolling member 7. In this case, the spring member 9 applies a pressing force in the direction of the central axes Z1 and Z2 of the input shaft portion 31 and the output shaft portion 51 to the other side surface of each rolling member 7, and Are pressed against the annular metal plate 100. The annular metal plate 100 has a hole having an inner diameter somewhat larger than the diameter of the input shaft portion 31 or the output shaft portion 51 and has a circular or polygonal outer shape that can be accommodated in the cylindrical inner wall surface 13 of the housing member 11. . 10A and 10B, the annular metal plate 100 may be replaced with the spring member 9, or may be omitted.

  As shown in FIG. 10A, when the spring member 9 is disposed between the side wall portion 15 of the housing member 11 and one side wall of each rolling member 7, the first and second annular plates are provided. 91 and 92 and the center hole 94 of the annular elastic member 93 are inserted through the output shaft portion 51, and the input shaft portion 31 is inserted through the hole of the annular metal plate 100. On the other hand, as shown in FIG. 10B, when the spring member 9 is disposed between the lid portion 12 and the other side wall of each rolling member 7, the input shaft portion 31 is inserted through the central hole 94. Then, the output shaft portion 51 is inserted through the hole of the annular metal plate 100.

  10 (A) and 10 (B) show only a part, but the input engagement pieces 34 to 38 of the input member 3 shown in FIG. 3 and the like and the output members of the output member 5 shown in FIG. 6 and the like. The housing 1 is filled with a relatively high-viscosity lubricant 110 so that an appropriate space shown in FIG. The main purpose of the lubricant 110 is to reduce both friction and noise generated when a rotational driving force is applied to the input member 3 and each member is operating in the housing 1. As will be described later, the force with which the spring member 9 presses each rolling member 7 is such that the operation (movement) of each rolling member 7 is not adversely affected by the adhesive force of the lubricant 110 having a relatively high viscosity. Act on. Therefore, the pressing force that the spring member 9 applies to each rolling member 7, that is, the spring force of the spring member 9 must be at least larger than the adhesive force of the lubricant 110.

[Basic operation when the high-viscosity lubricant 110 is not filled]
First, the basic operation of the reverse input cutoff clutch will be described with reference to FIGS. 11 to 13, it is assumed that the lubricant 110 is not filled in the housing 1. For example, when a rotational driving force in the counterclockwise direction (left direction) is applied to the input member 3 to rotate in the counterclockwise direction, the input engagement pieces 34 and 38 move to the left in FIG. The surface Xa is pressed against the right side surface Ya of the output engagement piece 54 and the rolling member 7 and pushed to the left. At this time, the rolling member 7 is pushed by the inclined contact surface 34G of the input engagement piece 34 and is positioned substantially at the center of the front end surface 54a of the output engagement piece 54, so that the rolling member 7 and the housing member 11 are in the cylindrical shape. There is a minute gap between the wall surface 13. Therefore, as described above, the rolling member 7 does not bite between the tip end surface 54 a of the output engagement piece 54 and the cylindrical inner wall surface 13 of the cylindrical portion 14 of the housing member 11. That is, it is not locked. The same applies to the other rolling members 7. Accordingly, the input engagement pieces 34 to 38 rotate counterclockwise so as to press the output engagement pieces 54 to 58 and the rolling member 7, and the output member 5 and the rolling member 7 are housed together with the input member 3. 1 can freely rotate counterclockwise. The same is true for clockwise rotation. In this way, the rotational driving force applied to the input member 3 is transmitted to the output member 5.

  Next, as shown in FIG. 12, assuming that the rotational force in the counterclockwise direction is applied only to the output member 5 from the state in which the rotational force is not applied to the input member 3 and the output member 5, the output engagement piece 54. Moves to the left of the drawing. At this time, the rolling member 7 does not substantially move or only slightly moves. Accordingly, as the output engagement piece 54 moves to the left in FIG. 12, the rolling member 7 comes to be positioned on the right side of the distal end surface 54a of the output engagement piece 54 in the drawing. The gap between the right end side of the distal end surface 54a and the cylindrical inner wall surface 13 of the housing member 11 is narrowed.

  That is, the gap between the end side of the front end surface 54 a of the output engagement piece 54 and the cylindrical inner wall surface 13 of the housing member 11 is closer to the end of the rolling member 7 than the center of the front end surface 54 a of the output engagement piece 54. Since the rolling member 7 tends to become narrower than the diameter, the rolling member 7 bites between the front end surface 54a of the output engagement piece 54 and the cylindrical inner wall surface 13 of the housing member 11, and the left end surface Yb of the output engagement piece 54 is input. Before contacting the right end surface Xb of the engagement piece 38, the locked state is reached. The same applies to the other output engagement pieces 55 to 58. Therefore, the output member 5 can no longer rotate, and the left end surface Yb of the output engagement pieces 54 to 58 of the output member 5 does not contact the right end surface Xb of the input engagement pieces 34 to 38. The applied rotational force is not transmitted to the input member 3. This is exactly the same when the output member 5 rotates clockwise.

  Next, the operation will be described on the assumption that the reverse input cutoff clutch is incorporated in a device (not shown). For example, a clockwise rotational force (rightward) is applied to the output member 5 although the magnitude of the load varies depending on a downward load (hereinafter referred to as a load) caused by a part of an apparatus or an article (not shown). Shall. In this state, when the rotational driving force applied to the input member 3 is removed, the input member 3 stops. However, since the clockwise rotational force is applied to the output member 5, the rolling member 7 immediately enters the locked state as described above unless the high-viscosity lubricant 110 is filled. That is, when the input member 3 stops rotating, the output member 5 also stops immediately, and a part of the device or an article (not shown) is held at that position.

  Thereafter, when a rotational driving force in the counterclockwise direction (leftward direction) larger than the load is applied to the input member 3, the input engagement pieces 34 to 38 of the input member 3 output as described with reference to FIG. Each of the output engagement pieces 54 to 58 of the member 5 is pushed counterclockwise. Therefore, while releasing the locked state, the input member 3 rotates the output member 5 counterclockwise against the load. In this case, a part of the device (not shown) or the article moves upward. That is, according to the rotational speed of the input member 3, a part of the device (not shown) or the article is raised.

  Then, the rotational driving force applied to the input member 3 at a certain position, for example, the upper limit position is reversed, and a clockwise rotational driving force that is the same direction as the rotational force applied to the output member 5 is applied. . When the rotational driving force applied to the input member 3 reverses, the input member 3 temporarily stops even momentarily, but the output member 5 tries to rotate in the clockwise direction, so that the rolling member as shown in FIG. 7 is immediately locked, and the output member 5 is once stopped. However, when the input member 3 starts rotating in the clockwise direction, the right side surface Xb of the input engaging pieces 34 to 38 of the input member starting to rotate becomes the output engaging piece 54 of the output member 5 as shown in FIG. While pushing the left side surface Yb of .about.58 and the right inclined contact surface (for example, 38G) of each output engaging piece located next to it presses the rolling member 7 in the clockwise direction, the locked state is released immediately after the reversal. Is done. Therefore, the input member 3 and the output member 5 rotate together in the clockwise direction in the positional relationship shown in FIG. 11, and a part of an apparatus (not shown) or an article coupled to the output member 5 is rotated by the input member 3. It will descend according to the speed. That is, even if the spring force is weak, if the lubricant 110 having a relatively high viscosity is not filled in the housing 1, the output member 5 is locked and locked immediately after the rotation of the input member 3 is reversed. Since the release is performed, a part of the device (not shown) or the article coupled to the output member 5 performs a stable operation without any problem. However, in this case, since the lubricant 110 does not exist, noise is generated when the input member 3 rotates, and wear increases.

[Operation when the high-viscosity lubricant 110 is filled and the spring force is weak]
However, if the pressing force applied to the rolling member 7 is weak because the spring force is weak as in the prior art and the lubricant 110 having a relatively high viscosity is filled in the housing 1, the input member 3 A problem arises when the rotational driving force applied to is reversed from the direction opposite to the rotation direction of the output member 5 in the same direction. Therefore, this point will be described in detail next. In general, a lubricant having a high viscosity naturally has a higher adhesive force than a lubricant having a low viscosity. In this embodiment, since the lubricant 110 having a relatively high viscosity is used as the lubricant, the adhesive force thereof is relatively large. For example, referring to FIG. 11, the lubricant 110, which is not shown in detail in the drawing, adheres to the surface of each member in the housing 1. It is mainly the lubrication adhering between the tip surfaces (for example, 54a) of the output engagement pieces 54 to 58 and the rolling member 7 that affects the locking operation of the rolling member 7 when the rotational driving force is reversed. The lubricant 110 is adhered between the rolling contact member 7 and the inclined contact surfaces (for example, 34G) of the input engagement pieces 34 to 38 of the input member 3.

  In FIG. 11, when the input member 3 that has been rotated counterclockwise is reversed in the clockwise direction, the input member 3 and the output member 5 start to rotate clockwise from the positional relationship shown in FIG. At this time, if the pressing force (pressurizing force) applied to the rolling member 7 is smaller than the adhesive force of the lubricant 110 because the spring force is weak as in the conventional case, the lubrication mainly adhering to the two locations described above. Due to the adhesive force of the agent 110, the rolling member 7 does not stay at the position when the rotational driving force is reversed, and the left inclined contact surface (for example, 34G) of the input engagement pieces 34-38 and the output engagement pieces 54-58. In the state shown in FIG. 11, the input engagement pieces 34 to 38 and the output engagement pieces 54 to 58 are moved in the clockwise direction while being adhered to the distal end surface (for example, 54a). That is, for a short period, the rolling member 7 does not bite between the front end surfaces (for example, 54a) of the output engagement pieces 54 to 58 and the cylindrical inner wall surface 13 of the housing member 11, that is, without being locked. It moves in a free state. In this state, the output member 5 rotates in the clockwise direction according to the rotational speed of the input member 3, and accordingly, a part of an unillustrated device or article coupled to the output member 5 is lowered for a short time. .

  Thereafter, the rolling member is caused by contact resistance between the rolling member 7 and the cylindrical inner wall surface 13 of the housing member 11, a weak spring force, a difference in the speed between the input member 3 and the output member 5 in the clockwise direction, or the like. 7 moves away from the inclined contact surface (for example, 34G) on the left side of the input engagement pieces 34 to 38, and each rolling member 7 is moved to the tip end surface (for example, the output engagement pieces 54 to 58) by the clockwise rotation of the output member 5. 54a) and the cylindrical inner wall surface 13 of the housing member 11 are bitten into a locked state (FIG. 12). At this time, the output member 5 stops for a moment. For example, after the rotational driving force of the input member 3 is reversed in the clockwise direction, the input member 3, the output member 5, and the rolling member 7 are brought into a locked state before and after approximately one rotation. When in the locked state, naturally, the output member 5 stops, and a part or an article (not shown) connected to the output member 5 also stops.

  However, on the other hand, the input member 3 is driven to rotate in the clockwise direction regardless of the locked state. Therefore, the right side surface Xb of the input engagement pieces 34 to 38 is connected to the output member 5 as shown in FIG. While pushing the left side surface Yb of the joining pieces 54-58, the inclined contact surface (for example, 38G) on the right side of each adjacent output engagement piece pushes the rolling member 7 in the clockwise direction. As a result, the locked state is released and each rolling member 7 becomes free, so that the output member 5 moves normally clockwise by the clockwise rotational driving force of the input member 3, and a part or article of equipment (not shown) The downward direction descends at a speed according to the rotational speed of the input member 3. The problem here is that when the rotational driving force of the input member 3 is reversed, the rolling member 7 is not instantaneously locked. This is the same when rotation of the input member 3 is started in the same direction as the rotation direction of the output member 5 from the state where the input member 3 is stopped.

  That is, there is a delay time from when the rotational driving force of the input member 3 is reversed until the normal operation is performed, and the output member 5 is locked and temporarily stopped while the input member 3 is moving clockwise. Immediately thereafter, the locked state is released and the output member 5 rotates, so that the operation of the output member 5 immediately after the rotational driving force of the input member 3 is reversed becomes unstable. Although this operation instability is a short period of time, after a part of an unillustrated device or article is lowered downward, it causes an undesired operation of temporarily stopping due to the locked state of the rolling member 7. Sometimes it generates impact sound (impact sound) and vibration.

[Operation when the high-viscosity lubricant 110 is filled and the spring force is large]
The present invention can solve such problems. As described in detail with reference to FIG. 10, the spring member 9 has a predetermined large pressing force (given in the direction of the central axis Z3 (FIG. 9), that is, the direction of the input shaft portion 31 and the output shaft portion 51 (FIG. 1). Pressure) is applied to each rolling member 7, so that when the rotational driving force of the input member 3 is reversed clockwise, the input member 3 is reversed without being affected by the adhesive force of the lubricant 110. The rolling member 7 is kept at the position of time. Referring to FIG. 11, even if the rotational driving force of the input member 3 is reversed in the clockwise direction at the illustrated position and the input engagement pieces 34 to 38 of the input member 3 are moved in the clockwise direction, the spring member 9 is not pushed. Each rolling member 7 remains in the position shown in FIG. 11, that is, the position when the input member 3 is reversed without being affected by the adhesive force of the lubricant 110 due to the pressure. That is, the pressing force (pressure) in the direction of the central axis Z3 (FIG. 9) that the spring member 9 applies to the rolling member 7 is superior to the adhesive force in the rotating direction of the rolling member 7 due to the viscosity of the lubricant 110. .

  Therefore, as in the normal operation of the input / output shut-off clutch described above, the output of the output member 5 is output by the rotational force applied to the output member 5 almost simultaneously with the rotation driving force of the input member 3 being reversed clockwise. Since the engagement pieces 54 to 58 move in the clockwise direction, the rolling member 7 bites between the distal end surfaces (for example, 54 a) of the output engagement pieces 54 to 58 and the cylindrical inner wall surface 13 of the housing member 11 by the movement. Then, the locked state is established (FIG. 12). At substantially the same time, the right side surface Xb of the input engagement pieces 34 to 38 of the input member starting to rotate by the rotational driving force is changed to the left side surface Yb of the output engagement pieces 54 to 58 of the output member 5 as shown in FIG. And the right inclined contact surface (for example, 38G) of each adjacent output engagement piece pushes the rolling member 7 in the clockwise direction, so that the locked state is immediately released. Accordingly, at almost the same time as the rotational driving force of the input member 3 is reversed in the clockwise direction, the output member 5 is both locked and unlocked in a very short time. It descends smoothly in the direction and does not generate impact sound or vibration. This operation is the same when rotation is started in the same direction as the rotation direction of the output member 5 from the state where the input member 3 is stopped.

  In the first embodiment described above, the input engagement piece of the input member 3 and the output engagement piece of the output member 5 have been described as five, but only one output engagement piece may be used. The input member 3 has two input engagement pieces that form one space that fits into one output engagement piece, and is formed by the cylindrical inner wall surface 13 of the housing and the input member 3. One output engagement piece, one rolling member, and a spring member that gives an elastic force to the rolling member may be provided in the space. That is, when a rotational driving force is applied from the output member to the input member, one rolling member may bite into one output engagement piece and the cylindrical inner wall surface 13 of the housing. Further, two to four output engagement pieces, or six or more output engagement pieces may be arranged at equal intervals. Even when the rolling member 7 is a ball, it operates in the same manner as described above.

  In addition, the inclination of the inclined contact surface (for example, 38G) on the right side of each output engagement piece may be opposite to that shown in the figure, and the inclination angle is not particularly limited. Note that, even when the input / output shut-off clutch is not filled with a lubricant, or when it is filled with a low-viscosity lubricant, it operates in the same manner as described above. Therefore, the present invention performs reverse input without filling with a lubricant. It is also useful for a shut-off clutch or a reverse input shut-off clutch filled with a low viscosity lubricant.

  The present invention can be applied to a mechanism for moving a tray of a paper discharge mechanism of a printer up and down, or various rotation mechanisms in which force may be applied from various devices on the output side to the input side.

DESCRIPTION OF SYMBOLS 1 ... Housing 11 ... Housing member 12 ... Cover part 13 ... Cylindrical inner wall surface 14 ... Cylindrical part of the housing member 11 15 ... Side wall part 16 of the housing member 11 ... Through hole 17 in side wall portion 15... Derived portion of side wall portion 15 3... Input member 31... Input shaft portion 32. Input engagement piece 34G: inclined contact surface of input engagement piece 34 38G: inclined contact surface of input engagement piece 38 A: arcuate outer wall surface of input engagement piece B: input engagement Arc-shaped inner wall surface of the piece C ... Concave outer wall surface of the input engagement piece 5 ... Output member 51 ... Output shaft portion 52 ... Output engagement portion 53 ... Output common portion 54-58 ..Output engagement piece 54a... Tip end surface of output engagement piece 54 7 Rolling member 9 Spring member 91 92... First and second annular plates 93... Ring elastic member 94... Hole of spring member 9 100... Metal plate 110 .. Lubricant Xa. Left end face of Xb ... Right end face of input engagement piece Ya ... Right end face of output engagement piece Yb ... Left end face of output engagement piece Z1 ... Center axis of input shaft Z2 ... Output Center axis of shaft 5 Z3... Center axis of spring member 9

Claims (2)

An input member, an output member, a rolling member, and a housing for housing these members;
The input member has an input shaft portion and an input engagement portion located at one end of the input shaft portion,
The input engagement portion extends at a constant interval in the radial direction with respect to a central axis extending in the axial direction through the center of the input shaft portion, and has a plurality of input engagements having a predetermined thickness in the direction of the central axis Have a piece,
The output member has an output shaft portion having the same center axis as the center axis, and an output engagement portion located on one end side of the output shaft portion,
The output engagement portion includes one or more output engagement pieces extending in a radial direction with respect to the central axis and having a predetermined thickness in the direction of the central axis.
The input engagement piece and the output engagement piece are engaged with each other in the housing,
The rolling member is provided between the cylindrical inner wall surface of the housing, the radial front end surface of the output engagement piece, and the input engagement piece.
When a rotational driving force is applied to the input member, the rotational engagement force is transmitted to the output member by the input engagement piece and the output engagement piece being directly engaged and rotating together, and When the external force is applied to the output member, the rolling member bites between the cylindrical inner wall surface of the housing and the tip end surface of the output engagement piece, so that the external force is not transmitted to the input member. A shut-off clutch,
An annular spring member that applies a pressing force in the direction of the central axis to the rolling member, at least between the side wall portion of the housing and the rolling member, or a lid portion that closes the housing and the rolling member In preparation,
The input member starts rotating in the same direction as the rotation direction of the output member caused by the external force from the state where the input member is rotated or stopped while an external force is applied to the output member from the outside. The spring member keeps the rolling member at a position just before the start of rotation of the output member, so that the rolling member has no time delay and the cylindrical inner wall surface of the housing member and the front end surface of the output member And the output member rotates together with the input member after the lock state is released immediately after the input member starts to rotate. Input cutoff clutch. An input member, an output member, a rolling member, and a housing for housing these members;
The input member has an input shaft portion and an input engagement portion located at one end of the input shaft portion,
The input engagement portion extends at a constant interval in the radial direction with respect to a central axis extending in the axial direction through the center of the input shaft portion, and has a plurality of input engagements having a predetermined thickness in the direction of the central axis Have a piece,
The output member has an output shaft portion having the same center axis as the center axis, and an output engagement portion located on one end side of the output shaft portion,
The output engagement portion includes one or more output engagement pieces extending in a radial direction with respect to the central axis and having a predetermined thickness in the direction of the central axis.
The input engagement piece and the output engagement piece are engaged with each other in the housing,
The rolling member is provided between the cylindrical inner wall surface of the housing, the radial front end surface of the output engagement piece, and the input engagement piece.
When a rotational driving force is applied to the input member, the rotational engagement force is transmitted to the output member by the input engagement piece and the output engagement piece being directly engaged and rotating together, and When the external force is applied to the output member, the rolling member bites between the cylindrical inner wall surface of the housing and the tip end surface of the output engagement piece, so that the external force is not transmitted to the input member. A shut-off clutch,
An annular spring member that applies a pressing force in the direction of the central axis to the rolling member, at least between the side wall portion of the housing and the rolling member, or a lid portion that closes the housing and the rolling member In preparation,
The housing member is filled with an appropriate amount of a relatively high-viscosity lubricant so that a space exists,
The reverse input cutoff clutch according to claim 1, wherein the pressing force applied by the spring member to the rolling member is larger than an operation of the rolling member that is not affected by an adhesive force of the lubricant .

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