JP5862583B2 - Booster mechanism, pressurizing device and press-fitting device provided with the same - Google Patents

Description

  The present invention relates to a force-increasing mechanism that amplifies a load applied to an operation lever by moving the movable member as the operation lever rotates, and outputs the same from the movable member, and a pressurizing device and a press-fitting device including the same .

  Conventionally, as a positioning and assembling device for press-fitting assembly parts to an assembly target, a device having a mounting portion, an assembling slide portion, a positioning slide portion, an operation portion, a toggle mechanism, a connecting link mechanism, and a mount is known. (For example, refer to Patent Document 1). The toggle mechanism of this positioning and assembling device converts the input load applied to the operation part into a lock load and transmits it to the assembly slide part, and the connection link mechanism receives the operation of the operation part and receives the positioning slide part. To raise. As a result, the operation unit is operated by one stroke to raise the positioning slide part via the connecting link mechanism, and after positioning the assembly target with respect to the mounting part, the assembly slide part is lowered via the toggle mechanism. The assembly parts can be press-fitted into the assembly target.

JP 2010-194643 A

  According to the conventional positioning and assembling apparatus, the load required for press-fitting can be easily created by converting the input load to the operation unit into the lock load by the toggle mechanism. However, in order to further increase the output load due to the toggle mechanism, the dimensions of the operation part and the link constituting the toggle mechanism must be increased, and the entire apparatus becomes very large.

  Therefore, the main object of the present invention is to provide a compact force-increasing mechanism that can convert an input load into a larger output load, and a pressurizing device and a press-fitting device including the same.

  In order to achieve the above-mentioned main object, the force-increasing mechanism according to the present invention, the pressurizing device provided with the same, and the press-fitting device employ the following means.

The boosting mechanism according to the present invention is:
A movable member movable along a predetermined direction;
An operation lever that is rotatably connected to the movable member via a support shaft, and has a follower disposed at a distance from the support shaft;
A cam member having a cam surface for guiding the follower so that the movable member moves along the predetermined direction as the operating lever rotates in one direction around the support shaft;
The cam surface is formed so that a ratio of a moving amount of the movable member in the predetermined direction to a rotating amount of the operating lever becomes smaller as the operating lever rotates in the one direction. .

  In this force-increasing mechanism, an input load is applied to the operating lever, that is, the power point, and the operating lever rotates in one direction around the support shaft. The movable member moves along a predetermined direction together with the supporting shaft. As the operation lever rotates in one direction, the ratio of the movement amount of the movable member in the predetermined direction to the rotation amount of the operation lever decreases. As a result, as the operating lever rotates in one direction, the amplification factor (the amount of rotation of the operating lever / the amount of movement of the movable member) with respect to the input load applied to the operating lever increases. It is possible to convert the input load into a larger output load and output it from the movable member via the support shaft. In this boosting mechanism, the total moving amount of the movable member in a predetermined direction is reduced, so that a larger output load can be obtained even if the total length of the operation lever is shortened. can do.

  The cam surface includes the position of the support shaft at the start of rotation when the operation lever rotates by a predetermined angle, and the end of rotation when the operation lever rotates by the predetermined angle. The distance from the position of the driven node may be greater than or equal to the distance between the support shaft and the driven node, and may be formed so as to decrease as the operating lever rotates in the one direction. Accordingly, it is possible to obtain a cam surface that reduces the ratio of the moving amount of the movable member in the predetermined direction to the rotating amount of the operating lever as the operating lever rotates in one direction.

  Further, the cam member may have a lock surface that is continuous with the cam surface, and the movement of the movable member may be locked when the driven node reaches the lock surface. Thereby, it is possible to maintain a state in which a larger output load is output from the movable member.

  Further, the lock surface is formed between the support shaft centered on the support shaft and the follower node when the operation lever is further rotated in the one direction after the follower node reaches the lock surface. The follower node may be formed to move along an arcuate track having a radius as the interval. This makes it possible to obtain a lock surface that can favorably lock the movement of the movable member.

  Further, the operating lever may have a second driven node spaced from both the support shaft and the driven node, and the cam member guides the second driven node. You may have a 2nd cam surface. As a result, even if the driven load is guided by the cam surface and the input load is converted into the output load and cannot be output from the movable member, the second driven node is guided by the second cam surface. Since the input load can be favorably converted to the output load and output from the movable member, the input load applied to the operation lever can be converted to a larger output load while amplifying the input load better.

  The second cam surface may be formed on the cam member so as to be positioned downstream of the cam surface in the moving direction of the movable member as the operation lever rotates in the one direction. Good. As a result, the second follower is guided by the second cam surface after the amount of rotation of the operation lever in one direction reaches a predetermined amount, and the input load is obtained by guiding the follower by the cam surface. It becomes possible to convert the input load into the output load satisfactorily by guiding the second follower node with the second cam surface after it cannot be converted into the output load.

  Furthermore, the cam surface is continuous with the auxiliary cam surface and the auxiliary cam surface, and the ratio of the movement amount of the movable member in the predetermined direction with respect to the rotation amount of the operation lever is smaller than that of the auxiliary cam surface. The main cam surface may be included.

  The force increasing mechanism may further include a rotation driving device that rotates the operation lever around the support shaft. That is, by rotating the operation lever around the support shaft in one direction and / or the opposite direction by the rotation drive device, the operation lever is rotated in one direction to apply the input load to the force point. It is possible to automate at least one of the adding operation and the operation of rotating the operation lever in the direction opposite to the one direction and returning it to the original direction.

  Furthermore, the operation lever may be fixed to the support shaft, and the rotation driving device may rotate the support shaft.

  A pressurizing apparatus according to the present invention is a pressurizing apparatus including any one of the above-described boosting mechanisms, and includes a pressurizing member that moves along the predetermined direction together with the movable member and presses an object to be pressurized. And The force-increasing mechanism included in this pressurizing device converts the input load applied to the operation lever into a larger output load as described above and outputs it from the movable member, and can easily downsize the entire mechanism. . Therefore, in this pressurizing apparatus, it is possible to easily and satisfactorily perform the pressurizing process by reducing the input load to be applied to the operation lever while reducing the size of the entire apparatus.

  The pressurization target may be a return spring that urges the piston of the friction engagement element, and the pressurization device may include a case in which the piston and the return spring are assembled with the return spring and the pressurizing member. You may further provide the positioning part for positioning so that a pressure member may oppose. Thereby, the return spring of the friction engagement element can be easily compressed and assembled to the case.

  Furthermore, the return spring may be disposed between a plate member that is prevented from coming off by a snap ring that can be engaged with a mounting groove formed in the case, and the piston, and the cam member includes the operation lever. A linear motion guide surface that guides the driven node so as to restrict the rotation of the support shaft around the support shaft, and the cam surface includes an auxiliary cam surface that is continuous with the linear motion guide surface, and the auxiliary And a main cam surface that is continuous with the cam surface and has a smaller ratio of the amount of movement of the movable member in the predetermined direction to the amount of rotation of the operation lever than the auxiliary cam surface. The case may be assembled with the plate member so as to come into contact with the return spring, and the snap ring is movable along the predetermined direction. A snap ring supporting portion that supports the movable member, and a push member that moves along the predetermined direction together with the movable member to push the snap ring into the case on the positioning portion. While being guided by the linear motion guide surface, the pressure member moves along the predetermined direction together with the movable member until it abuts on the plate member, and while the driven node is guided by the auxiliary cam surface. The pushing member pushes the snap ring into the case, and the pressure member compresses the return spring via the plate member and the pushing member while the follower is guided by the main cam surface. The snap ring that is pushed by may fit into the mounting groove.

  In the pressure device configured in this way, simply by applying an input load to rotate the operation lever, the snap ring is mounted in the mounting groove of the case while compressing the return spring, and both can be easily attached to the case. And it can be assembled quickly. Then, according to the cam surface including the auxiliary cam surface and the main cam surface that reduces the ratio of the moving amount of the movable member in the predetermined direction with respect to the rotation amount of the operation lever as compared with the auxiliary cam surface, the follower node assists. It is guided by the cam surface and reduces the input load to be applied to the operating lever when the pushing member pushes the snap ring into the case, and relatively small input load while the follower is guided by the main cam surface. Thus, the snap ring can be fitted into the mounting groove while the return spring is easily compressed. Further, in this pressurizing device, since the total movement amount of the movable member in the predetermined direction by the main cam surface is made as small as possible, a larger output load can be obtained even if the total length of the operation lever is shortened. Even if a linear motion guide surface or an auxiliary cam surface is provided on the member to ensure a stroke in a predetermined direction of the pressurizing member or the pushing member, an increase in the size of the entire apparatus can be suppressed.

  The pressurizing member may be formed in a cylindrical shape, the pushing member may be disposed inside the pressurizing member, and the snap ring support portion may be an inner peripheral surface of the pressurizing member. It may be. Thus, by using the pressure member also as the snap ring support portion, the entire pressure device can be made more compact.

  Further, the pressing device moves along the predetermined direction together with the movable member, and is movable from the pushing member side toward the inner peripheral surface of the pressing member so as to contact the snap ring. A contact member may be provided. As a result, when the snap ring is considered to be mounted in the mounting groove, the contact member is moved toward the inner peripheral surface of the pressure member to check whether the snap ring is normally mounted in the mounting groove. In addition, when the snap ring is not normally mounted in the mounting groove, the snap ring can be pressed by the contact member and fitted into the mounting groove.

  The press-fitting device according to the present invention includes a pressurizing member that moves along the predetermined direction together with the movable member to press-fit a press-fitting target into the press-fitted portion. The force-increasing mechanism included in this press-fitting device can convert the input load applied to the operation lever as described above into a larger output load and output it from the movable member. Therefore, according to the press-fitting device, it is possible to easily and satisfactorily perform the press-fitting process by reducing the input load to be applied to the operation lever while reducing the size of the entire device.

It is a schematic structure figure showing assembly device 1 as a pressurizing device concerning one embodiment of the present invention. 1 is a schematic configuration diagram illustrating a brake 100 to which an assembly apparatus 1 is applied. FIG. 6 is a schematic diagram showing the position of a support shaft 41 when the driven roller 45 rolls on the main cam surface 52. FIG. 6 is a schematic diagram showing the position of a support shaft 41 when the driven roller 45 rolls on the main cam surface 52. 4 is a schematic configuration diagram for explaining the operation of the assembling apparatus 1. FIG. 4 is a schematic configuration diagram for explaining the operation of the assembling apparatus 1. FIG. 4 is a schematic configuration diagram for explaining the operation of the assembling apparatus 1. FIG. 4 is a schematic configuration diagram for explaining the operation of the assembling apparatus 1. FIG. 4 is a schematic configuration diagram for explaining the operation of the assembling apparatus 1. FIG. 4 is a schematic configuration diagram for explaining the operation of the assembling apparatus 1. FIG. It is a schematic block diagram which shows the assembly apparatus 1B as a pressurization apparatus which concerns on other embodiment of this invention. It is an enlarged view which shows the principal part of the assembly apparatus 1B.

  Next, the form for implementing this invention is demonstrated, referring drawings.

  FIG. 1 is a schematic configuration diagram showing an assembling apparatus 1 according to an embodiment of the present invention. An assembling apparatus 1 shown in the figure is used for assembling a brake 100 for an automatic transmission as shown in FIG. First, the brake 100 to which the assembly apparatus 1 is applied will be described. As shown in FIG. 2, the brake 100 is fitted to a piston 102 slidably disposed in a transmission case 101 of an automatic transmission (not shown) or a spline formed on the outer peripheral surface of a brake hub (not shown). At least one friction plate (friction engagement plate with friction material attached to both surfaces, not shown), at least one mating plate (both surfaces) fitted to a spline formed on the inner peripheral surface of the transmission case 101 Is a so-called multi-plate brake including a friction engagement plate (not shown) formed smoothly.

  The piston 102 defines an engagement side oil chamber 103 together with the transmission case 101. An annular spring retainer 104 is fitted to the piston 102. Further, a backing plate (plate member) 105 is fitted to a spline formed on the inner peripheral surface of the transmission case 101 so as to face a friction plate arranged farthest from the piston 102. The backing plate 105 is mounted in a mounting groove 101 a formed on the inner peripheral surface of the transmission case 01 and is prevented from coming off by a snap ring (stopper) 106 positioned on the upper side in FIG.

  Between the spring retainer 104 and the backing plate 105, the above-described friction plate and the mating plate are arranged, and a plurality (four in this embodiment) of return springs 107 are arranged at equal intervals. In the present embodiment, the outer periphery of the mating plate fitted to the spline formed on the inner peripheral surface of the transmission case 101 has a plurality of teeth by cutting out a part of the plurality of teeth that engage with the groove of the spline. (For example, four teeth at equal intervals) are formed, and each return spring 107 is arranged in a groove of a spline corresponding to the tooth missing. In the brake 100 configured as described above, the backing plate is moved by the snap ring 106 mounted in the mounting groove 101a of the transmission case 101 by increasing the hydraulic pressure in the engagement side oil chamber 103 and moving the piston 102. A brake hub (not shown) can be fixed to the transmission case 101 by pressing the friction plate and the mating plate against the piston 105 by the piston 102.

  As shown in FIG. 1, the assembling apparatus 1 includes an assembly A including a piston 102, a spring retainer 104, a backing plate 105, a friction plate (not shown) and a mating plate, which are components of the transmission case 101 and the brake 100. Positioning portion 2 for positioning the shaft center so as to extend in the vertical direction, movable member 3 movable in the vertical direction (predetermined direction), and operating lever (lever member) rotatably connected to the movable member 3 ) 4 and the force-increasing mechanism 10 including the cam member 5 maintained in a stationary state, the pressing member 6 movable in the vertical direction together with the movable member 3 of the force-increasing mechanism 10, and the vertical together with the movable member 3 in the force-increasing mechanism 10. A pushing member 7 movable in the direction. In the assembly A, the piston 102, the spring retainer 104, the plurality of return springs 107, the friction plate, and the mating plate are assembled in the transmission case 101, and the backing plate 105 is disposed so as to come into contact with each return spring 107. And does not include the snap ring 106.

  The movable member 3 of the force-increasing mechanism 10 is formed in a plate shape, and is supported so as to be movable up and down in the vertical direction by a column 8 fixed to the installation location of the assembly apparatus 1 together with the positioning unit 2. Further, a counterweight 85 is connected to the movable member 3 via a cable body (chain or wire) 82 wound around a pulley 81 rotatably supported by a fixing member 80 fixed to the upper end of the column 8. ing. Furthermore, a support bracket 30 that rotatably supports the base end of the operation lever 4 is fixed to the upper surface of the movable member 3 in FIG.

  A support shaft 41 that is supported by the support bracket 30 and extends in the direction penetrating the paper surface of FIG. 1 is inserted into the base end of the operation lever 4, whereby the operation lever 4 is movable through the support shaft 41. 3 is supported rotatably. In addition, a grip portion 42 that is gripped by an operator when the brake 100 is assembled is provided at the free end of the operation lever 4. Further, a driven roller 45 as a driven node is attached to the operation lever 4 so as to be rotatable around an axis extending in parallel with the extending direction of the support shaft 41. In the present embodiment, the driven roller 45 is disposed, for example, at a distance G (interval between both axis centers) G from the support shaft 41 in a direction orthogonal to the extending direction of the operation lever 4.

  Further, the cam member 5 of the force-increasing mechanism 10 is formed in a plate shape, and is maintained stationary by fixing the upper end portion in FIG. 1 to the fixing member 80 (the column 8). Further, a linear motion guide surface 50 and a cam surface 55 for guiding the driven roller 45 are respectively formed on the side surfaces of the cam member 5, and the cam surface 55 is connected to the auxiliary cam surface 51 continuous with the linear motion guide surface 50. And a main cam surface 52 continuous to the auxiliary cam surface 51.

  The linear motion guide surface 50 is a flat surface extending vertically downward from the upper portion of the cam member 5 and guides the driven roller 45 so as to restrict the rotation of the operation lever 4 around the support shaft 41. That is, when the operation lever 4 is rotated around the support shaft 41 in the counterclockwise direction in FIG. 1 while the driven roller 45 is in contact with the upper end of the linear guide surface 50 in FIG. By rolling on the linear guide surface 50 and moving vertically downward, the rotation of the operation lever 4 in the counterclockwise direction in FIG. 1 is restricted, and the movable member 3 connected to the operation lever 4. Moves vertically downward by a distance corresponding to the height of the linear motion guide surface 50. In the assembling apparatus 1 of the present embodiment, the driven roller 45 contacts the upper end of the linear guide surface 50 when the operation lever 4 is rotated around the support shaft 41 in the clockwise direction in FIG. A stopper (not shown) for stopping the operation lever 4 at a stage is provided.

  As shown in FIG. 1, the auxiliary cam surface 51 constituting the cam surface 55 is inclined from the linear motion guide surface extending in the vertical direction by a relatively small angle α (for example, about 3 to 10 °) in the counterclockwise direction in the drawing. It is the flat surface formed so that. Further, the main cam surface 52 constituting the cam surface 55 is a curved surface extending from the lower end of the auxiliary cam surface 51 to the side (right side in FIG. 1), and the height of the main cam surface 52 in the vertical direction is It is determined to be much smaller than the height of the cam surface 51 in the vertical direction. As a result, when the operation lever 4 is rotated about the support shaft 41 in the counterclockwise direction in FIG. 1 while the driven roller 45 is in contact with the upper end of the auxiliary cam surface 51, the driven roller 45 is moved to the auxiliary cam surface 51. By rolling upward and moving in the extending direction (obliquely downward) of the auxiliary cam surface 51, the operation lever 4 is allowed to rotate counterclockwise in FIG. 1 and connected to the operation lever 4. The moved movable member 3 moves downward by a distance corresponding to the height of the auxiliary cam surface 51 in the vertical direction. Further, when the operation lever 4 is rotated around the support shaft 41 in the counterclockwise direction in FIG. 1 while the driven roller 45 is in contact with the starting end of the main cam surface 52, the driven roller 45 is placed on the main cam surface 52. 1 to allow the operation lever 4 to rotate counterclockwise in FIG. 1 and to be connected to the operation lever 4. The movable member 3 thus moved moves vertically downward by a distance corresponding to the height of the main cam surface 52.

  As described above, when a force, that is, an input load is applied to the gripping portion 42 as a power point and the operation lever 4 is rotated counterclockwise around the support shaft 41 in FIG. The member 5 rolls on the linear guide surface 50 and the cam surface 55 of the member 5, and accordingly, the movable member 3 moves vertically downward together with the support shaft 41 serving as an action point. Then, the cam surface 55 including the auxiliary cam surface 51 and the main cam surface 52 has a rotation amount of the operation lever 4, that is, the grip portion 42 as the operation lever 4 rotates counterclockwise (one direction) in FIG. The ratio of the movement amount in the vertical direction of the support shaft 41 and the movable member 3 to the rotation length around the support shaft 41 is formed to be small. Therefore, according to the force-increasing mechanism 10, as the operation lever 4 rotates counterclockwise in FIG. 1, the amplification factor for the input load applied to the operation lever 4 (the rotation amount of the operation lever 4 / the movement of the movable member). Therefore, the input load applied to the operation lever 4 can be converted into a larger output load and output from the movable member 3 via the support shaft 41.

  Next, the main cam surface 52 of the cam member 5 will be described. 3 and 4 are schematic views showing the position of the support shaft 41 when the driven roller 45 rolls on the main cam surface 52. 3 and 4, the main cam surface 52 is indicated by a thick line, and a relaxed curved surface is formed between the auxiliary cam surface 51 and the main cam surface 52. As shown in FIG. 3, the main cam surface 52 moves the support shaft 41, that is, the movable member 3 vertically downward when the operation lever 4 rotates by a predetermined angle (a constant angle) counterclockwise in FIG. 1. The amount ("da", "db", "dc", "dd" in FIG. 3) is formed so as to decrease as the operation lever 4 is rotated counterclockwise in FIG. That is, the ratio of the downward movement amount of the support shaft 41 and the movable member 3 to the rotation amount of the operation lever 4 corresponding to the predetermined angle (the rotation length of the grip portion 42 around the support shaft 41) R (“da / R "," db / R "," dc / R "," dd / R ") decreases as the operating lever rotates counterclockwise in FIG.

Here, the main cam surface 52 in the present embodiment reduces the ratio of the downward movement amount of the support shaft 41 to the rotation amount of the operation lever 4 as the operation lever 4 rotates in one direction. The distances d ₀₁ , d ₁₂ , d ₂₃ and d ₃₄ in FIG. 4 are formed so as to satisfy the relationship d ₀₁ > d ₁₂ > d ₂₃ > d ₃₄ = interval G. However, “d ₀₁ ” refers to the position of the axis of the support shaft 41 when the driven roller 45 comes into contact with the main cam surface 52 (time t = t0) and from the time when the driven roller 45 comes into contact with the main cam surface 52. This is the distance from the position of the axis of the driven roller 45 when the operation lever 4 is rotated by, for example, an angle γ (time t = t1). “D ₁₂ ” is a driven roller when the operating lever 4 is rotated by an angle γ from the position of the axis of the support shaft 41 at time t = t1 and the position at time t = t1 (time t = t2). It is a distance between the positions of 45 axial centers. Furthermore, “d ₂₃ ” is a driven roller at the time when the operating lever 4 is rotated by an angle γ from the position of the shaft 41 at the time t = t2 and the position at the time t = t2 (time t = t3). It is a distance between the positions of 45 axial centers. “D ₃₄ ” is a driven roller when the operating lever 4 is rotated by an angle γ from the position of the axis of the support shaft 41 at time t = t3 and the position at time t = t3 (time t = t4). It is a distance between the positions of 45 axial centers. Thus, the main cam surface 52 satisfying the relationship d ₀₁ > d ₁₂ > d ₂₃ > d ₃₄ = interval G is at the start of rotation when the operation lever 4 is rotated by the angle γ (time t0, t1, t2). Alternatively, the position (axial center) of the support shaft 41 at t3) and the position (axial center) of the driven roller 45 at the end of rotation (time t1, t2, t3 or t4) when the operation lever 4 is rotated by the angle γ. The distance between the support shaft 41 and the driven roller 45 is set to be equal to or greater than the distance G, and the distance is reduced as the operation lever 4 rotates counterclockwise in FIG. In FIG. 4, for ease of explanation, the case where the rotation angle γ of the operation lever 4 is a relatively large value is described as an example. However, when designing the actual main cam surface 52, It is preferable that the angle γ be a smaller value (for example, about 5 °).

  The main cam surface 52 has a position (axial center) of the support shaft 41 at the start of rotation when the operation lever 4 is rotated by an angle γ, and at the end of rotation when the operation lever 4 is rotated by an angle γ. At the point where the distance G between the support shaft 41 and the driven roller 45 coincides with the distance G between the driven roller 45 and the driven roller 45 at the time t = t4. The cam member 5 is continuous with the end of the cam surface 55, that is, the main cam surface 52 as described above, and includes a lock surface 57 including a curved surface portion having a curvature substantially matching the radius of the driven roller 45, and a lock surface 57. It has a facing surface 59 that is continuous and faces the main cam surface 52. The opposing surface 59 extends along the main cam surface 52 at a distance slightly longer than the diameter of the driven roller 45 as shown in the figure.

The lock surface 57 is centered on the support shaft 41 when the operation lever 4 is further rotated counterclockwise in FIG. 1 after the driven roller 45 reaches the lock surface 57 (the end of the main cam surface 52). After the driven roller 45 is moved along an extremely short arc-shaped track whose radius is the distance G, the driven roller 45 is formed so as to contact the curved surface portion. That is, the distance between the axis of the support shaft 41 and the axis of the driven roller 45 at time t = t4 is d _44, and the axis of the support shaft 41 at the time when the driven roller 45 contacts the curved surface (time t = t5). When the distance between the center and the axis of the driven roller 45 is d ₄₅ , d ₄₄ = d ₄₅ = interval G. As a result, even if the driven roller 45 reaches the position at time t = t4, the operation lever 4 further rotates counterclockwise in FIG. 1, and even if the driven roller 45 rolls on the lock surface 57, the support shaft 41. Can be kept at the position at time t = t4, that is, the movement of the support shaft 41 and the movable member 3 can be locked. Then, when the driven roller 45 comes into contact with the curved surface portion, the rotation of the operation lever 4 is locked.

  On the other hand, the pressing member 6 movable in the vertical direction together with the movable member 3 of the force-increasing mechanism 10 is formed in a substantially cylindrical shape, and includes a plurality of pressing portions 60 extending in the axial direction of the pressing member 6. Have. The plurality of pressing portions 60 are annular (comb-like) at intervals so that they can be inserted (engaged) into the groove portions of the splines formed on the inner peripheral surface of the transmission case 101 constituting the assembly A. Arranged. Further, the inner peripheral surface 61 of the pressurizing member 6 (the plurality of pressing portions 60) has substantially the same radius of curvature as the inner peripheral surface of the transmission case 101 (the spline tooth portion), and the snap ring 106 is arranged in the vertical direction. It functions as a snap ring support that can be movably supported. The pressing member 6 is connected to the movable member 3 of the force-increasing mechanism 10 via the expansion / contraction support mechanism 65 so that each pressing portion 60 extends in the vertical direction (predetermined direction).

  The expansion / contraction support mechanism 65 supports the pressing member 6 so as to be movable in the vertical direction with respect to the movable member 3 and allows the movable member 3 and the pressing member 6 to move integrally in the vertical direction. That is, the telescopic support mechanism 65 of the present embodiment is in a state where the pressing member 6 is lowered from the movable member 3 most when the tip of each pressing portion 60 (the lower end in FIG. 1) is not supported from below (FIG. 1). The pressure member 6 moves vertically upward with respect to the movable member 3 (becomes stationary with respect to the positioning portion 2) when the tip of each pressing portion 60 is supported from below. Is acceptable. In addition, when the pressing member 6 moves upward in FIG. 1 by a predetermined distance with respect to the movable member 3, the expansion / contraction support mechanism 65 is pressed vertically downward by the movable member 3 and the movable member 3. Allow to move together.

  Further, the pushing member 7 is formed so as to be able to contact the snap ring 106 supported by the inner peripheral surface 61 of the pressing member 6, and is fixed to the movable member 3 of the force-increasing mechanism 10. That is, the pushing member 7 always moves together with the movable member 3 when the movable member 3 moves in the vertical direction. Further, the pushing member 7 supports the plurality of contact members 70 so as to be movable in the left-right direction, that is, the horizontal direction in FIG. 1, and supports each contact member 70 with respect to the inner peripheral surface of the pressure member 6 on the outer peripheral side. A drive device (not shown) that can be moved closer to and away from each other is supported. As shown in FIG. 1, when the pressure member 6 is maintained in the state where it is lowered most from the movable member 3, a constant interval is formed between the upper end of the pressure member 6 and the lower end of the pushing member 7. Is done.

  Next, a procedure for assembling the brake 100 using the assembly device 1 described above, specifically, a procedure for mounting the snap ring 106 in the mounting groove 101a of the transmission case 101 while compressing the plurality of return springs 107 of the assembly A. Will be described.

  When assembling the brake 100 by the assembling apparatus 1, the operation lever 4 is rotated around the support shaft 41 in the clockwise direction in FIG. 1 so that the driven roller 45 abuts the upper end of the linear guide surface 50, and the above-described operation is performed. The assembly A is positioned (fixed) on the positioning portion 2 such that the axis of the piston 102 extends in the vertical direction. Further, the snap ring 106 is supported on the upper end portion in FIG. 1 of the inner peripheral surface 61 of the pressure member 6 that functions as a snap ring support portion. Next, the grip portion 42 is manually operated so that the operation lever 4 rotates counterclockwise in FIG. As a result, the driven roller 45 rolls on the linear guide surface 50 and moves vertically downward, and the rotation of the operation lever 4 in the counterclockwise direction in the figure is restricted, as shown in FIG. The movable member 3 connected to the operation lever 4 via the support shaft 41 moves vertically downward by a distance corresponding to the height of the linear guide surface 50.

  Thus, when the movable member 3 moves vertically downward, the pressure member 6 moves vertically downward together with the movable member 3 while being maintained in the state of being most lowered from the movable member 3 by the telescopic support mechanism 65. Each is inserted into a groove portion of a spline of the transmission case 101 constituting the assembly A. The pushing member 7 also moves vertically downward together with the movable member 3. In the present embodiment, when the driven roller 45 reaches the lower end of the linear guide surface 50 or in the vicinity thereof, the lower end of each pressing portion 60 of the pressing member 6 is a view of the backing plate 105 constituting the assembly A. The specifications of each element, the vertical length of the linear motion guide surface 50, and the like are determined so as to abut the upper surface of 5 and the like. It should be noted that while the driven roller 45 rolls on the linear guide surface 50, the force to be applied to the grip portion 42 of the operation lever 4 in order to lower the movable member 3, the pressure member 6, the pushing member 7 and the like integrally. That is, the input load is determined by the force corresponding to the sum of the weight of the counterweight 85 and the resistance of the rope 82, the movable member 3, the pressure member 6 that descends integrally with the movable member 3, the telescopic support mechanism 65, and the push-in. What is necessary is just to be larger than the force obtained by subtracting the force corresponding to the weight of the member 7 or the like.

  When the driven roller 45 reaches the cam surface 55 and rolls on the auxiliary cam surface 51 as the operating lever 4 is manually operated so as to rotate counterclockwise in FIG. Due to the auxiliary cam surface 51 being inclined from the vertical direction by a relatively small angle α in the counterclockwise direction in the figure, the operation lever 4 is rotated counterclockwise in the figure as shown in FIG. Move. When the driven roller 45 rolls on the auxiliary cam surface 51 in this way, the tip of each pressing portion 60 is supported by the backing plate 105 of the assembly A from below, so that the telescopic support mechanism 65 The pressing member 6 moves basically vertically with respect to the movable member 3 due to the function, so that the pressing member 7 moves together with the movable member 3 vertically downward. . Thus, the pushing member 7 that moves together with the movable member 3 contacts the snap ring 106 supported by the inner peripheral surface 61 of the pressure member 6, and the snap ring 106 is brought into contact with the inner peripheral surface 61 of the pressure member 6. Along the vertical downward direction, that is, into the transmission case 101 of the assembly A.

  Here, when the pressing member 6 is stationary with respect to the positioning portion 2, in order to lower the movable member 3, the pushing member 7, and the like, the pressing member 6 that is stationary with respect to the positioning portion 2, etc. It is necessary to increase the force applied to the movable member 3 and the like by the weight. Based on this, in this embodiment, the cam member 5 of the force-increasing mechanism 10 is provided with the auxiliary cam surface 51 that is inclined from the vertical direction by a relatively small angle α in the counterclockwise direction in the drawing as described above. Thus, while the driven roller 45 rolls on the auxiliary cam surface 51, the rotation amount of the operation lever 4, that is, the rotation length around the support shaft 41 of the grip portion 42 is the vertical direction of the support shaft 41, that is, the movable member 3. Therefore, the input load applied to the grip portion 42 of the operation lever 4 can be amplified and output to the movable member 3. As a result, the driven roller 45 is guided by the auxiliary cam surface 51 and the input load to be applied to the operation lever 4 (gripping portion 42) when the pushing member 7 pushes the snap ring 106 into the transmission case 101 is reduced. That is, the input load to be applied to the operation lever 4 (gripping part 42) is substantially constant between the time when the driven roller 45 rolls on the linear guide surface 50 and the time when the driven roller 45 rolls on the auxiliary cam surface 51 ( The same).

  In the present embodiment, as the operating lever 4 is manually operated so that the operating lever 4 rotates counterclockwise in FIG. 1 and the like, the driven roller 45 has the auxiliary cam surface 51 and the main cam surface 52 of the cam surface 55. When the pressure member 6 is pressed downward by the movable member 3 again by the function of the expansion / contraction support mechanism 65, the movable member 3 moves integrally with the movable member 3. When the driven roller 45 reaches the vicinity of the boundary between the auxiliary cam surface 51 and the main cam surface 52 of the cam surface 55, the snap ring 106 supported by the inner peripheral surface 61 of the pressure member 6 is moved together with the movable member 3. The moving push member 7 reaches the vicinity of the backing plate 105 of the assembly A.

  Furthermore, when the driven roller 45 rolls on the main cam surface 52 of the cam surface 55 as the operating lever 4 is manually operated so as to rotate counterclockwise in FIG. 7, the amount of movement of the support shaft 41, that is, the movable member 3, vertically downward when rotating counterclockwise by a predetermined angle γ decreases as the operating lever 4 is rotated counterclockwise in the figure. Become. That is, the position (axial center) of the support shaft 41 at the start of rotation when the operation lever 4 rotates by the angle γ, and the driven roller 45 at the end of rotation when the operation lever 4 rotates by the angle γ. The distance to the position (axial center) is equal to or greater than the distance G between the support shaft 41 and the driven roller 45, and decreases as the operation lever 4 rotates counterclockwise in FIG.

  Thus, according to the force-increasing mechanism 10 including the movable member 3, the operation lever 4, the support shaft 41, the cam member 5, and the like, the operation lever 4 is moved in FIG. 7 while the driven roller 45 is guided by the main cam surface 52. As it is rotated counterclockwise, the amplification factor (the amount of rotation of the operation lever 4 / the amount of movement of the movable member 3) with respect to the input load applied to the operation lever 4 increases. The input load thus obtained can be converted into a larger output load and output from the movable member 3 to the pressing member 6 and the pushing member 7 via the support shaft 41. As a result, while the driven roller 45 is guided by the main cam surface 52, as shown in FIGS. 8 and 9, a plurality of return springs 107 that are difficult to compress by simple manual work are connected to the movable member 3. While being compressed by the respective pressing portions 60 of the pressed member 6, the snap ring 106 can be pushed by the push member 7 connected to the movable member 3 and can be fitted into the mounting groove 101 a of the transmission case 101.

  When the gripping portion 42 is manually operated so that the operation lever 4 rotates counterclockwise in FIG. 1 and the like, when the driven roller 45 reaches the lock surface 57, the operation lever 4 further moves counterclockwise in the figure. Even if it rotates in the direction, the movement of the support shaft 41 and the movable member 3 is locked, and the rotation of the operation lever 4 is locked when the driven roller 45 comes into contact with the curved surface portion of the lock surface 57. Accordingly, it is possible to maintain a state in which a larger output load is output from the movable member 3, that is, the pressing member 6 and the pushing member 7, and to suppress the return of the operation lever 4. In the assembling apparatus 1 of the present embodiment, when the movement of the support shaft 41 and the movable member 3 and the rotation of the operation lever 4 are locked, that is, when the snap ring 106 is considered to be mounted in the mounting groove 101a of the transmission case 101. Thus, each contact member 70 supported by the pushing member 7 by a driving device (not shown) is moved toward the inner peripheral surface 61 of the pressure member 6 as shown in FIG. Thereby, by checking whether each contact member 70 moves smoothly, it is inspected whether the snap ring 106 is normally attached to the attachment groove 101a, and the snap ring 106 is inserted into the attachment groove 101a. When not normally mounted, the snap ring 106 can be pressed by each contact member 70 and fitted into the mounting groove 101a.

  Thus, when the compression of the plurality of return springs 107 and the mounting of the snap ring 106 to the mounting groove 101a are completed, the operation roller 4 is moved by the stopper (not shown) until the driven roller 45 reaches the upper end of the linear guide surface 50. The operation lever 4 is rotated in the opposite direction until the movement is stopped. Then, the assembly A in which the mounting of the snap ring 106 to the mounting groove 101a is completed is removed from the positioning unit 2 and is transported to the construction site for the next process.

  As described above, in the force increasing mechanism 10 included in the assembling apparatus 1 as a pressurizing apparatus that compresses the plurality of return springs 107 of the assembly A, an input load is applied to the grip portion 42 of the operating lever 4, that is, the force point. As the operation lever 4 rotates in one direction around the support shaft 41 (counterclockwise in FIG. 1 and the like), the driven roller 45 as a fulcrum is a cam surface 55, that is, an auxiliary cam surface 51 and a main cam surface 52. The movable member 3 moves along a predetermined direction, that is, the vertical direction together with the support shaft 41 serving as a point of action. As the operation lever 4 rotates in one direction, the amount of movement of the movable member 3 in a predetermined direction (vertical direction) with respect to the rotation amount of the operation lever 4, that is, the rotation length around the support shaft 41 of the grip portion 42. The ratio becomes smaller. As a result, as the operation lever 4 rotates in one direction, the amplification factor (the amount of rotation of the operation lever 4 / the amount of movement of the movable member 3) with respect to the input load applied to the operation lever 4 increases. An input load applied to the lever 4 can be converted into a larger output load and output from the movable member 3 via the support shaft 41. In the force-increasing mechanism 10, even if the total length of the movable member 3 in the predetermined direction while the driven roller 45 is guided by the main cam surface 52 is reduced, the operation lever 4 can be further shortened. Since a large output load can be obtained, the entire mechanism can be easily made compact.

  Further, the entire cam surface 55 including the auxiliary cam surface 51 and the main cam surface 52 that makes the ratio of the amount of movement of the movable member 3 in the predetermined direction with respect to the rotation amount of the operation lever 4 smaller than that of the auxiliary cam surface 51, and The main cam surface 52 includes a position of the support shaft 41 at the start of rotation when the operation lever 4 rotates by a predetermined angle, and a driven roller at the end of rotation when the operation lever 4 rotates by a predetermined angle. The distance from the position 45 is set to be equal to or greater than the interval G between the support shaft 41 and the driven roller 45, and is made smaller as the operation lever 4 rotates in one direction. As a result, it is possible to obtain the cam surface 55 and the main cam surface 52 that reduce the ratio of the moving amount of the movable member 3 in the predetermined direction to the rotating amount of the operating lever 4 as the operating lever 4 rotates in one direction. Become.

  Further, the cam member 5 has a lock surface 57 that is continuous with the cam surface 55, that is, the main cam surface 52. In the assembling apparatus 1, when the driven roller 45 reaches the lock surface 57, the support shaft 41 and the movable member are provided. The movement of 3 is locked. As a result, it is possible to maintain a state in which a larger output load is output from the movable member 3, that is, the pressing member 6 and the pushing member 7. In the above embodiment, the lock surface 57 and the support shaft 41 centered on the support shaft 41 when the operation lever 4 is further rotated in one direction after the driven roller 45 reaches the lock surface 57. The driven roller 45 is formed to move along an arcuate path having a radius G from the driven roller 45. Thereby, it becomes possible to obtain the lock surface 57 that can favorably lock the movement of the movable member 3.

  As described above, the force-increasing mechanism 10 included in the assembling apparatus 1 as the pressurizing apparatus can convert the input load applied to the operation lever 4 into a larger output load and output it from the movable member 3 to the pressurizing member 6. In addition, the entire mechanism can be easily made compact. Therefore, in the assembling apparatus 1, it is possible to easily and satisfactorily perform the pressurizing process of the return spring 107 to be pressurized by reducing the input load to be applied to the operation lever 4 while downsizing the entire apparatus. . In addition, the assembling apparatus 1 includes the positioning portion 2 for positioning the transmission case 101 in which the piston 102 and the return spring 107 are assembled, that is, the assembly A so that the return spring 107 and the pressing member 6 face each other. The return spring 107 of the assembly A (brake 100) can be easily compressed and assembled to the transmission case 101.

  Furthermore, in the above-described embodiment, the cam member 5 has the linear motion guide surface 50 that guides the driven roller 45 so as to restrict the rotation of the operation lever 4 around the support shaft 41. An auxiliary cam surface 51 that is continuous with the moving guide surface 50, and an amount of movement in a predetermined direction (vertical direction) of the movable member 3 relative to the rotation amount of the operation lever 4 is continuous with the auxiliary cam surface 51 and compared with the auxiliary cam surface 51. And a main cam surface 52 for reducing the ratio. Further, the assembling apparatus 1 moves along the predetermined direction (vertical direction) together with the movable member 3 so that the snap ring 106 supported by the inner peripheral surface 61 (snap ring support portion) of the pressure member 6 is positioned on the positioning portion 2. The push-in member 7 to be pushed into the transmission case 101 is included. While the driven roller 45 is guided by the linear guide surface 50, the pressure member 6 moves along the predetermined direction (vertical direction) together with the movable member 3 until it abuts against the backing plate 105 of the assembly A, While the driven roller 45 is guided by the auxiliary cam surface 51, the pushing member 7 pushes the snap ring 106 into the transmission case 101, and while the driven roller 45 is guided by the main cam surface 52, the pressing member 6 is backing. The return spring 107 is compressed via the plate 105, and the snap ring 106 pushed by the pushing member 7 is fitted into the mounting groove 101a.

  As a result, in the assembling apparatus 1, the snap ring 106 is mounted in the mounting groove 101 a of the transmission case 101 while compressing the return spring 107 only by applying an input load so as to rotate to the operation lever 4. 101 can be assembled easily and quickly. The cam includes an auxiliary cam surface 51 and a main cam surface 52 that makes the ratio of the moving amount of the movable member 3 in the predetermined direction (vertical direction) to the rotating amount of the operation lever 4 smaller than that of the auxiliary cam surface 51. According to the surface 55, the driven roller 45 is guided by the auxiliary cam surface 51, and the input load to be applied to the operation lever 4 when the pushing member 7 pushes the snap ring 106 into the transmission case 101 is reduced, and the driven member 45 is driven. While the roller 45 is guided by the main cam surface 52, the snap ring 106 can be fitted into the mounting groove 101a while the return spring 107 is easily compressed with a relatively small input load. Furthermore, in the assembling apparatus 1, even if the total length of the operation lever 4 is shortened by reducing the total amount of movement of the movable member 3 in the predetermined direction (vertical direction) by the main cam surface 52, a larger output load can be obtained. be able to. Accordingly, even if the linear motion guide surface 50 and the auxiliary cam surface 51 are provided on the cam member 5 to ensure the stroke in the predetermined direction (vertical direction) of the pressing member 6 and the pushing member 7, the enlargement of the entire apparatus is suppressed. be able to.

  Moreover, in the said embodiment, the pressurization member 6 is formed in a cylinder shape, the pushing member 7 is arrange | positioned inside the pressurization member 6, and the internal peripheral surface 61 of the pressurization member 6 is used as a snap ring support part. Function. In this way, by using the pressing member 6 also as the snap ring support portion, the entire assembly apparatus 1 can be made more compact. Furthermore, the assembling apparatus 1 moves along a predetermined direction (vertical direction) together with the movable member 3, and moves from the pushing member 7 side toward the inner peripheral surface 61 of the pressing member 6 so as to contact the snap ring 106. A possible abutment member 70 is included. Accordingly, when the snap ring 106 is considered to be mounted in the mounting groove 101a, the snap ring 106 is normally mounted in the mounting groove 101a by moving the contact member 70 toward the inner peripheral surface of the pressure member 6. When the snap ring 106 is not normally mounted in the mounting groove 101a, the snap ring 106 can be pressed by the contact member 70 and fitted into the mounting groove 101a. .

  FIG. 11 is a schematic configuration diagram showing an assembling apparatus 1B as a pressurizing apparatus according to another embodiment of the present invention. Note that, among the components of the assembly apparatus 1B, the same elements as those of the above-described assembly apparatus 1 are denoted by the same reference numerals, and redundant description is omitted.

  The force-increasing mechanism 10B of the assembling apparatus 1B shown in FIG. 11 includes a rotation driving device 35 that rotates the operation lever 4B around the support shaft 41. In the force-increasing mechanism 10 </ b> B of FIG. 11, the rotation driving device 35 is fixed to the movable member 3 and can move integrally with the movable member 3. Further, the base end of the operation lever 4B is fixed to the support shaft 41, and as can be seen from FIGS. 11 and 12, the rotation drive device 35 rotates the support shaft 41 around the axis in the counterclockwise direction in FIG. Direction) and clockwise can be rotated 180 °. As the rotational drive device 35, for example, a device including a fluid rotary actuator and a gear mechanism (not shown) is employed, but a device including a motor and a gear mechanism may be employed. Furthermore, in addition to the driven roller 45 as the first driven node, the second driven roller 46 as the second driven node extends in parallel with the extending direction of the support shaft 41 in the operation lever 4B of the force-increasing mechanism 10B. It is mounted so that it can rotate around its axis. As shown in FIGS. 11 and 12, the second driven roller 46 is disposed at a predetermined interval (interval between both axis centers) in the extending direction (longitudinal direction) of the operation lever 4 </ b> B from the driven roller 45. And at a distance from the support shaft 41.

  As shown in FIGS. 11 and 12, the cam member 5B of the force-increasing mechanism 10B is a second member that guides the second driven roller 46 in addition to the cam surface 55 including the auxiliary cam surface 51 and the main cam surface 52. It has a cam surface 56 and a second facing surface 58 that faces the second cam surface 56. The second cam surface 56 and the second opposing surface 58 rotate the support shaft 41 in the counterclockwise direction in FIG. 11 relative to the cam surface 55, that is, the auxiliary cam surface 51 and the main cam surface 52, that is, the operation lever 4B in FIG. It is formed so as to be located on the downstream side in the moving direction of the movable member 3 accompanying the rotation in the clockwise direction (one direction), that is, on the lower side in FIG. The position and shape of the second cam surface 56 are based on the locus of the second driven roller 46 (one point on the outer peripheral surface) when the driven roller 45 as the first driven node rolls on the main cam surface 52. Can be easily determined. The second facing surface 58 is formed so as to extend along the second cam surface 56 at a slightly longer interval than the diameter of the second driven roller 46 and substantially coincides with the radius of the driven roller 45. It continues to the second cam surface 56 via a curved surface portion of curvature. Furthermore, in the cam member 5B of the force-increasing mechanism 10B, as shown in FIGS. 11 and 12, the linear guide surface 50 in the cam member 5 described above is omitted. This eliminates the need to move the operation lever 4B downward (vertically below) in FIG. 11 without rotating it, and eliminates the need for a drive device that moves the operation lever 4B in the vertical direction in FIG.

  In the force-increasing mechanism 10B of the assembling apparatus 1B configured as described above, the operation lever 4B is turned around the support shaft 41 by rotating the support shaft 41 counterclockwise in FIG. By rotating in the clockwise direction, an input load can be applied to the grip portion 42 as a force point. Further, in the force-increasing mechanism 10B, the rotation driving device 35 rotates the support shaft 41 counterclockwise in FIG. 11 to operate after the compression of the plurality of return springs 107 and the mounting of the snap ring 106 to the mounting groove 101a are completed. The lever 4B can be rotated around the support shaft 41 in the clockwise direction in FIG. Thereby, in the assembling apparatus 1B, it is possible to automate both the operation of applying an input load to the operation lever 4B and the operation of returning the operation lever 4B.

  Further, in the force increasing mechanism 10B of the assembling apparatus 1B, as shown in FIG. 12, the rotation amount from the initial position of the support shaft 41, that is, the rotation amount in the counterclockwise direction in FIG. The second driven roller 46 as the second driven node is moved by the second cam surface 56 from the stage where the driven roller 45 rolls on the main cam surface 52 and approaches the lock surface 57 to some extent. I will be guided. As a result, the driven roller 45 that rolls on the main cam surface 52 approaches the lock surface 57, so that the driven load 45 is guided by the main cam surface 52, so that the input load from the rotary drive device 35 is improved. Even if the output load cannot be converted and output from the movable member 3, the second driven roller 46 is guided by the second cam surface 56 so that the input load can be converted into the output load and output from the movable member 3. It becomes possible. Therefore, in the force-increasing mechanism 10B, it is possible to convert the input load applied to the support shaft 41, that is, the operation lever 4B into a larger output load while amplifying the input load better. In addition, since the booster mechanism 10B can efficiently obtain a larger output load, it is possible to reduce the burden on the rotary drive device 35 that applies an input load (rotational torque) to the support shaft 41, that is, the operation lever 4B. .

  In the force-increasing mechanism 10B of the assembling apparatus 1B, the operation lever 4B is rotated to apply an input load to the gripping portion 42 as a force point, and the operation lever 4B is rotated in the reverse direction to return to the original position. Both are automated, but only one of these two operations may be automated by a rotary drive. For example, in the assembling apparatus 1 shown in FIG. 1 and the like, after the compression of the plurality of return springs 107 by manual operation of the operation lever 4 and the mounting of the snap ring 106 in the mounting groove 101a are completed, The operation lever 4 may be rotated around the support shaft 41 in the clockwise direction in FIG. 1 until the driven roller 45 reaches the linear guide surface 50. In this case, the force-increasing mechanism 10 of the assembling apparatus 1 is configured to return the operation lever 4 to the initial position when the driven roller 45 rolls and rises on the linear guide surface 50 by the action of the counter weight 85. It is good to be done. Furthermore, two or more second driven rollers 46 as described above may be disposed on the operation lever 4B or the like, and two or more second cam surfaces 56 as described above may be formed on the cam member 5B or the like.

  Needless to say, the application target of the assembling apparatuses 1 and 1B is not limited to the multi-plate brake as described above, and may be a multi-plate clutch. Further, a plurality of cam members 5 and 5B may be provided for the integral movable member 3. Furthermore, the moving direction of the movable member 3 or the like is not limited to the vertical direction as in the above embodiment, and may be a horizontal direction or an oblique direction. Further, the force-increasing mechanisms 10 and 10B as described above may be applied to a press-fitting device including a pressurizing member that moves along a predetermined direction together with the movable member 3 and press-fits a press-fitting target into the press-fitted portion. In other words, the force-increasing mechanisms 10 and 10B can output from the movable member 3 by converting the input load applied to the operation levers 4 and 4B into a larger output load as described above. Therefore, according to the press-fitting device provided with such a force-increasing mechanism 10 or 10B, the press-fitting process can be easily and satisfactorily performed by reducing the input load to be applied to the operation levers 4 and 4B while reducing the size of the entire device. Is possible.

  The correspondence between the main elements of the above embodiment and the main elements of the invention described in the section for solving the problem is described in the section for the means for solving the problem by the embodiment. Since the embodiment for carrying out the invention is an embodiment for specifically explaining the invention, the elements of the invention described in the column of means for solving the problems are not limited. That is, the above embodiment is merely a specific form of the invention described in the section for solving the problem, and the interpretation of the invention described in the section for solving the problem is This should be done based on the description in the column.

  Although the embodiment of the present invention has been described above, the present invention is not limited to the above embodiment, and it goes without saying that various modifications can be made without departing from the scope of the present invention. .

  INDUSTRIAL APPLICABILITY The present invention can be used in a manufacturing mechanism of a force-increasing mechanism, a pressurizing device having the same, a press-fitting device, and the like.

  1, 1B assembly device, 2 positioning part, 3 movable member, 4, 4B operation lever, 5, 5B cam member, 6 pressurizing member, 7 pushing member, 8 strut, 10, 10B force increasing mechanism, 30 support bracket, 35 rotation Drive device, 41 support shaft, 42 gripping part, 45 driven roller, 46 second driven roller, 50 linear motion guide surface, 51 auxiliary cam surface, 52 main cam surface, 55 cam surface, 56 second cam surface, 57 lock surface , 58 second facing surface, 59 facing surface, 60 pressing portion, 61 inner peripheral surface, 65 telescopic support mechanism, 70 abutting member, 80 fixing member, 81 pulley, 82 cable body, 85 counterweight, 100 brake, 101 transmission Case, 101a Mounting groove, 102 Piston, 103 Engagement side oil chamber, 104 Spring retainer, 105 Backing plate, 1 6 snap ring, 107 return spring.

Claims (15)

A movable member movable along a predetermined direction;
An operation lever that is rotatably connected to the movable member via a support shaft, and has a follower disposed at a distance from the support shaft;
A cam member having a cam surface for guiding the follower so that the movable member moves along the predetermined direction as the operating lever rotates in one direction around the support shaft;
The cam surface is formed so that a ratio of a moving amount of the movable member in the predetermined direction to a rotating amount of the operating lever becomes smaller as the operating lever rotates in the one direction. Booster mechanism. The force-increasing mechanism according to claim 1,
The cam surface includes the position of the support shaft at the start of rotation when the operation lever rotates by a predetermined angle, and the follower node at the end of rotation when the operation lever rotates by the predetermined angle. A force-increasing mechanism characterized in that the distance to the position is equal to or greater than the distance between the support shaft and the driven node, and is made smaller as the operating lever rotates in the one direction. The force-increasing mechanism according to claim 1 or 2,
The cam member has a lock surface continuous with the cam surface, and the movement of the movable member is locked when the driven node reaches the lock surface. The force-increasing mechanism according to claim 3,
The lock surface is configured such that the distance between the support shaft and the follower node around the support shaft when the operation lever is further rotated in the one direction after the follower node reaches the lock surface. A force-increasing mechanism, wherein the follower node is formed to move along an arcuate track having a radius of. The force-increasing mechanism according to any one of claims 1 to 4,
The operating lever further includes a second driven node spaced from both the support shaft and the driven node,
The force-increasing mechanism, wherein the cam member further includes a second cam surface for guiding the second follower node. The force-increasing mechanism according to claim 5,
The second cam surface is formed on the cam member so as to be positioned downstream of the cam surface in the moving direction of the movable member as the operation lever rotates in the one direction. A booster mechanism. The force-increasing mechanism according to any one of claims 1 to 6,
The cam surface is continuous with the auxiliary cam surface, and the main cam further reduces the ratio of the amount of movement of the movable member in the predetermined direction to the amount of rotation of the operation lever as compared to the auxiliary cam surface. And a force-increasing mechanism characterized by including a surface. The force-increasing mechanism according to any one of claims 1 to 7,
A force-increasing mechanism, further comprising a rotation drive device that rotates the operation lever around the support shaft. The force-increasing mechanism according to claim 8,
The operation lever is fixed to the support shaft, and the rotation driving device rotates the support shaft. A pressurizing device including the force-increasing mechanism according to any one of claims 1 to 9,
A pressurizing apparatus comprising a pressurizing member that moves along the predetermined direction together with the movable member and presses an object to be pressurized. The pressurizing device according to claim 10,
The object to be pressurized is a return spring that biases the piston of the friction engagement element,
A pressurizing apparatus, further comprising: a positioning portion for positioning the case in which the piston and the return spring are assembled so that the return spring and the pressurizing member face each other. The pressurizing device according to claim 11, wherein
The return spring is disposed between the piston and the plate member that is prevented from coming off by a snap ring that can be engaged with a mounting groove formed in the case.
The cam member has a linear motion guide surface that guides the driven node so as to restrict the rotation of the operation lever around the support shaft.
The cam surface includes an auxiliary cam surface that is continuous with the linear motion guide surface, and an amount of movement of the movable member in the predetermined direction relative to the amount of rotation of the operation lever as compared with the auxiliary cam surface. Including a main cam surface that reduces the ratio of
The plate member is assembled to the case positioned in the positioning portion so as to contact the return spring,
A snap ring support portion that supports the snap ring movably along the predetermined direction, and a pushing member that moves along the predetermined direction together with the movable member and pushes the snap ring into the case on the positioning portion. The pressure member moves along the predetermined direction together with the movable member until the driven node is guided by the linear guide surface, and the driven node is moved along the predetermined direction. While being guided by the auxiliary cam surface, the pushing member pushes the snap ring into the case, and while the follower is guided by the main cam surface, the pressing member is moved through the plate member. A pressurization characterized by compressing a return spring and fitting the snap ring pushed by the pushing member into the mounting groove apparatus. The pressurizing device according to claim 12,
The pressurizing member is formed in a cylindrical shape, the pushing member is disposed inside the pressurizing member, and the snap ring support portion is an inner peripheral surface of the pressurizing member. Pressurizing device. The pressurizing apparatus according to claim 13,
A contact member that moves along the predetermined direction together with the movable member and that is movable from the pushing member side toward the inner peripheral surface of the pressure member so as to contact the snap ring is further provided. Pressurizing device. A press-fitting device including the force-increasing mechanism according to any one of claims 1 to 9,
A press-fitting device comprising a pressurizing member that moves along the predetermined direction together with the movable member and press-fits a press-fitting object into a press-fitted portion.

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