JP2010166492A - Mechanism for adjusting actuation force, and mechanism for transmitting operation force - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a mechanism for adjusting actuation force allowing an operator to recognize the state of adjustment of actuation force and for preventing breakage even if strong operation force is applied, and to provide a mechanism for transmitting operation force. <P>SOLUTION: The mechanism for adjusting actuation force includes an actuation force-adjusting plate spring 25, and the mechanism for transmitting operation force which transmits operation force to the actuation force-adjusting plate spring 25 to adjust braking force. The mechanism for transmitting operation force includes: a worm 51 rotating by receiving operation force; a worm wheel 52 connected to the worm 51; a connection member 53 frictionally contacting the worm wheel 52 and rotating by receiving the rotation of the worm wheel 52; and a cam 27 integrally-rotatably connected to the connection member 53. The rotation of the cam 27 is restricted in a predetermined rotating range. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an operating force adjusting mechanism, and more particularly to an operating force adjusting mechanism suitable for a fader used for volume adjustment of an audio device such as a mixer or light amount adjustment in a theater or the like.

  2. Description of the Related Art Conventionally, an operating force adjustment mechanism that can finely adjust an operator's operation function characteristics has been proposed in a fader mounted on an acoustic device such as a mixer (see, for example, Patent Document 1). In this operating force adjusting mechanism, a slide member interlocked with a knob of a fader, a guide shaft that slides and guides the slide member in the axial direction, a spring means and a buffer means interposed between the slide member and the guide shaft The guide shaft is sandwiched between the spring means and the buffer means, and the magnitude of the clamping force to be sandwiched by the spring means can be arbitrarily adjusted from the outside by the operation of the adjusting screw.

Japanese Patent Laid-Open No. 2002-8907

  However, in the conventional operating force adjusting mechanism as described above, since the correspondence between the tightening degree of the adjusting screw and the operating force of the fader is unclear, it is difficult for the operator to recognize the adjusting degree of the operating force. It was. In addition, when a strong operating force is applied to the adjustment screw and tightened beyond the limit of the allowable rotation amount of the adjustment screw, there has been a problem that the screw thread and the screw hole are damaged.

  The present invention has been made in view of such a situation, and allows the operator to recognize the adjustment degree of the operating force and can also prevent the operating force adjusting mechanism and the operation even if a strong operating force is applied. An object is to provide a force transmission mechanism.

  The operating force adjusting mechanism of the present invention includes a braking unit that applies a braking force to the operating body, and an operating force transmission mechanism that transmits the operating force to the braking unit to adjust the braking force. A first rotating member that rotates in response to an operating force; and a first rotating member that frictionally contacts the first rotating member, rotates in response to the rotation of the first rotating member, and outputs an operating force to the braking portion. And the second rotating member is restricted in rotation within a predetermined rotation range.

  The operating force transmission mechanism of the present invention includes a first rotating member that rotates by receiving an operating force, and frictionally contacts the first rotating member, rotates by receiving the rotation of the first rotating member, and an operating body. And a second rotating member that outputs an operating force to a braking part that applies a braking force to the second rotating member, and the second rotating member is restricted in rotation within a predetermined rotation range. .

  According to this configuration, since the rotation of the second rotating member is restricted to a predetermined rotation range, for example, the upper limit of the rotation range is the maximum braking force of the braking unit, and the lower limit of the rotation range is the minimum braking force of the braking unit. By restricting the rotation of the second rotating member so as to correspond to the operating force, it is possible to clarify the correspondence between the operation amount applied to the operating force transmission mechanism and the operating force of the operating body. Thereby, the operator can recognize the adjustment degree of the operating force of the operating body. In addition, when the second rotating member is within a predetermined rotation range, the second rotating member rotates with the first rotating member to transmit the operating force, and the second rotating member is restricted from rotating. In the case where the first rotating member is idled, the transmission of the operating force is stopped. Therefore, even if a strong operating force is input to the operating force transmission mechanism, the operating force transmission mechanism is prevented from being damaged.

  In the operating force adjusting mechanism according to the present invention, the operating force transmission mechanism includes a friction member, and the first rotating member and the second rotating member are in frictional contact with each other via the friction material. It is characterized by.

  According to this configuration, the first rotating member and the second rotating member can be brought into frictional contact with a simple configuration.

  According to the present invention, in the operating force adjusting mechanism, the operating force transmission mechanism includes a worm that is rotated about an axis orthogonal to a rotation axis of the first rotating member by a tool. The rotating member is a worm wheel that rotates by engaging with the worm.

  According to this configuration, the operating force of the operating body can be adjusted by rotating the worm around an axis orthogonal to the rotation axis of the first rotating member by the tool.

  According to the present invention, in the operating force adjustment mechanism, the second rotating member is in frictional contact with the first rotating member, and the input member to which an operating force is input from the first rotating member and the predetermined member The output member is configured to be separable in the direction of the rotation axis, and an engagement portion that engages with the output member is formed on the input member. The output member is formed with an engaged portion that engages with the engaging portion so as to rotate integrally with the input member, and the engaging portion is engageable with the tool.

  According to this configuration, it is possible to change the operation direction of the tool by separating the input member and the output member of the second rotating member. That is, when the input member and the output member of the second rotating member are engaged, the working body is rotated by rotating the worm around an axis orthogonal to the rotating shaft of the first rotating member by a tool. Can be adjusted. On the other hand, when the input member and the output member of the second rotating member are separated, the operating force of the operating body can be adjusted by rotating the output member around the axis with a tool.

  According to the present invention, in the operating force adjusting mechanism, the braking portion includes a leaf spring, and the second rotating member is provided with a cam for adjusting a pressing force of the leaf spring.

  According to this structure, the braking force with respect to the operating body by a leaf | plate spring can be adjusted with rotation of the cam formed in the 2nd rotation member.

  ADVANTAGE OF THE INVENTION According to this invention, while making an operator recognize the adjustment condition of an operating force, even if a strong operating force is applied, damage can be prevented.

It is a figure which shows embodiment of the operating force adjustment mechanism which concerns on this invention, and is an external appearance perspective view of a fader. It is a figure which shows embodiment of the operating force adjustment mechanism which concerns on this invention, and is an external appearance perspective view of an operating force adjustment mechanism. It is a figure which shows embodiment of the operating force adjustment mechanism which concerns on this invention, and is the perspective view which isolate | separated the slide member from the operating force adjustment mechanism. It is a figure which shows embodiment of the operating force adjustment mechanism which concerns on this invention, and is an exploded perspective view of an operating force transmission mechanism. It is a figure which shows embodiment of the operating force adjustment mechanism which concerns on this invention, and is the transition diagram which demonstrated typically an example of the transmission structure of operating force. It is a figure which shows embodiment of the operating force adjustment mechanism which concerns on this invention, and is the figure which demonstrated the operating force adjustment by an operating force adjustment mechanism typically.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. In addition, prior to developing this technology, the applicant of the present patent application controls the rotation of the cam within a predetermined rotation range in an operating force adjustment mechanism that adjusts the braking force of the leaf spring by rotating the cam with a tool. A configuration has been devised to clarify the correspondence between the cam operation amount and the braking force of the leaf spring. The present invention is improved from the viewpoint of durability when a strong operating force is applied to the operating force adjusting mechanism. That is, the present invention absorbs the reaction force due to rotation restriction by interposing a member connected by frictional contact between the input side and the output side with respect to the structure that directly transmits the operating force to the rotation restricted one. It is what I did. This improvement can prevent the cam from being damaged even when a strong operating force is applied in a state where the cam is restricted in rotation.

  In the following, a case will be described in which the operating force adjustment mechanism according to the present embodiment is applied to a fader used for volume adjustment of an audio device such as a mixer or light amount adjustment in a theater or the like. However, the application target of the operating force adjustment mechanism according to the present embodiment is not limited to this and can be changed as appropriate.

  With reference to FIG. 1, a fader to which an operating force adjusting mechanism according to an embodiment of the present invention is applied will be described. FIG. 1 is an external perspective view of a fader to which an operating force adjusting mechanism according to an embodiment of the present invention is applied.

  As shown in FIG. 1, a fader 1 according to the present embodiment includes a case 2 whose front surface is opened, and a cover 3 that is attached to the opening of the case 2 and forms an accommodating portion. Are combined to form a rectangular parallelepiped box. The fader 1 is attached with a small case 4 which is adjacent to the case 2 and opened on one side so that the opening portion faces the case 2. An operating force adjusting mechanism 6, which will be described later, is installed in the small case 4. The components of the operation direction changing unit 7 constituting a part are accommodated.

  A notch 2a is formed on the upper wall of the case 2 so as to extend in the longitudinal direction, and is combined with the cover 3 to form a slit. Two side walls located in the longitudinal direction of the case 2 are formed with two notches 2b and 2c spaced apart in the vertical direction in the figure, and the first shaft 11 is horizontally mounted horizontally on the notch 2b located on the upper side. The second shaft 12 is horizontally mounted in the notch 2c located on the lower side. A slide member 13 is supported on the first shaft 11 and the second shaft 12, and the slide member 13 is slidably accommodated in the accommodating portion along the first shaft 11 and the second shaft 12. .

  A lever member 14 is provided on the slide member 13 so as to protrude upward. The lever member 14 is exposed to the outside through a slit formed by the case 2 and the cover 3. An operation knob (not shown) is attached to the exposed portion of the lever member 14, and the slide member 13 is operated in the sliding direction by this operation knob. The slide member 13 incorporates a part of the operating force adjustment mechanism 6 for adjusting the operating force of the fader 1.

  Further, the slide member 13 is provided with a magnetic detection member 15 having a magnetoresistive effect element 17 (GMR element) at a substantially central portion. The side walls along the slide direction of the slide member 13 of the case 2 and the cover 3 are respectively provided with inner surfaces. A thin plate-like magnet 18 (a magnet attached to the cover 3 is not shown) is attached. Further, the magnet 18 attached to the case 2 and the magnet attached to the cover 3 have outer shapes in which opposing surfaces are magnetized to have different polarities and are inclined in opposite directions along the sliding direction. . Therefore, a magnetic field is formed in the storage portion so that the direction of the magnetic field acting on the magnetoresistive effect element 17 is rotationally displaced depending on the position of the slide member 13.

  The magnetoresistive effect element 17 is configured such that the electric resistance value changes according to the direction of the magnetic field that acts. Therefore, the position of the slide member 13 can be detected from the output signal based on the electric resistance value of the magnetoresistive effect element 17. In addition, the magnetoresistive effect element 17 is connected to the substrate 22 via the FPC 21 (flexible printed circuit board), and an output signal is output to the substrate 22.

  With reference to FIGS. 2 to 4, the operating force adjusting mechanism according to the embodiment of the present invention will be described. FIG. 2 is an external perspective view of the operating force adjusting mechanism according to the embodiment of the present invention. FIG. 3 is a perspective view in which the slide member is separated from the operating force adjusting mechanism according to the embodiment of the present invention. FIG. 4 is an exploded perspective view of the operating force transmission mechanism according to the embodiment of the present invention.

  As shown in FIGS. 2 and 3, the operating force adjusting mechanism 6 includes a slide member 13 and a first shaft 11, an operating force adjusting leaf spring 25 attached to the side surface of the slide member 13 on the cover 3 side, and an operating force adjusting mechanism 6. A brake plate 26 that is pressed against the first shaft 11 by being pressed by the power adjustment plate spring 25 and a cam 27 that adjusts the pressing force of the operating force adjustment plate spring 25 against the brake plate 26 are provided. The cam 27 is connected to the components of the operation direction changing unit 7 accommodated in the small case 4 to transmit the operation force.

  An insertion passage 31 through which the first shaft 11 is inserted is formed in the upper part of the slide member 13 so as to extend in the slide direction, and the cover 3 side of the intermediate portion excluding both end portions in the slide direction is opened. A cam accommodating portion 32 for accommodating the cam 27 is formed below the insertion passage 31 of the slide member 13, and constitutes a recess that opens on the cover 3 side. The cam housing portion 32 is formed with a presser portion 33 that supports the cam 27 from the cover side. The presser portion 33 prevents the cam 27 from falling off.

  A plate spring mounting portion 34 to which the operating force adjusting plate spring 25 is mounted is formed below the cam housing portion 32, and has convex portions 34b and 34c protruding from the support surface 34a toward the cover 3 and a positioning pin 34d. Configured. The operating force adjusting plate spring 25 is held by the convex portions 34b and 34c and positioned by the positioning pin 34d.

  The brake plate 26 is disposed so as to cover the opening of the intermediate portion of the insertion passage 31 and is in contact with the outer peripheral surface of the first shaft 11. The contact surface of the brake plate 26 with the first shaft 11 is formed to be complementary to the outer peripheral surface of the first shaft 11. Further, a peripheral surface portion 26 a that receives a pressing force from the operating force adjusting plate spring 25 is formed on the surface of the brake plate 26 on the cover 3 side so as to slightly protrude.

  The cam 27 is housed in the cam housing portion 32, and includes a rotating body 41 formed in a columnar shape, a substantially disk-shaped support portion 42 that is connected to one end surface of the rotating body 41 and supported by the pressing portion 33, and a support. It is comprised from the drive pin 43 which protruded from the end surface of the part 42, and was provided in the position eccentric with respect to the rotating shaft of the rotary body 41 (refer FIG. 4). Further, a hexagonal hole 41a is formed in the rotating body 41 from the other end surface side toward the inside on the rotating shaft, and the hexagonal portion 58 of the connecting member 53 of the operation direction changing unit 7 is inserted into the hexagonal hole 41a. .

  The support portion 42 protrudes radially outward from the outer peripheral surface to form a convex portion 42a, and the cam 27 is restricted in rotation within a predetermined rotation range by the convex portion 42a and the pressing portion 33 described above. That is, the holding portion 33 is formed with a semicircular inner peripheral surface 33a and a pair of restricting surfaces 33b and 33c that are continuous with the inner peripheral surface 33a in the vertical direction (see FIG. 3). The surface is in sliding contact with the inner peripheral surface 33a of the pressing portion 33, and the convex portion 42a is in contact with the pair of regulating surfaces 33b and 33c at a predetermined rotational position. As described above, the cam 27 is rotationally restricted to a rotation range of 180 degrees by the convex part 42 a of the support part 42 and the pair of restriction surfaces 33 b and 33 c of the pressing part 33. The drive pin 43 is provided at a position eccentric with respect to the rotation axis of the rotating body 41, and moves around in a semicircular arc shape according to the rotation of the rotating body 41.

  The operating force adjusting leaf spring 25 includes a flat portion 45 fixed to the leaf spring mounting portion 34, a contact piece 46 extending from the flat portion 45 toward the cam 27 and contacting the rotating body 41 of the cam 27, and a flat surface. And a pressing piece 47 that extends from the portion 45 toward the braking plate 26 and presses the peripheral surface portion 26 a of the braking plate 26. Further, the flat portion 45 is formed with notches 45a and 45b and positioning holes 45c. The operating force adjusting plate spring 25 is inserted into the plate spring mounting portion 34 by inserting the positioning pin 34d of the plate spring mounting portion 34 into the positioning hole 45c and engaging the notches 45a and 45b with the convex portions 34b and 34c. It is attached.

  The actuating force adjusting plate spring 25 is provided with a pulling piece 48 that is pulled perpendicularly to the pressing piece 47 and pulled by the drive pin 43 of the cam 27. The pulling piece 48 is formed with a rectangular hole 48a at the center, and the drive pin 43 is inserted through the hole 48a. Then, the rotating body 41 of the cam 27 is rotated, and the driving pin 43 provided at the knitting core position of the rotating body 41 moves around, so that the pulling piece 48 is pulled by the driving pin 43 and the operating force adjusting plate. The spring 25 is deformed, and the braking force on the braking plate 26 can be changed.

  As shown in FIG. 4, the operation direction conversion unit 7 converts the operation direction using a hexagon wrench and is connected to the hexagonal hole 41 a of the cam 27. That is, when the operation direction conversion unit 7 is not connected to the cam 27, the hexagon wrench is inserted into the hexagon hole 41a of the cam 27, so that the operation force is directly transmitted to the cam 27 by operating the hexagon wrench around the rotation axis. It becomes possible to do. On the other hand, by connecting the operation direction conversion unit 7 to the cam 27 instead of the hexagon wrench, the operation direction of the hexagon wrench can be rotated by 90 degrees.

  The operation direction conversion unit 7 includes a worm 51 in which a hexagonal hole 51 a is formed, a worm wheel 52 that converts the rotational axis direction of the worm 51 by 90 degrees, a connecting member that frictionally contacts the worm wheel 52 and that is connected to the cam 27. 53. The worm 51 is rotatably supported by the small case 4 with the vertical direction as a rotation axis, and the hexagonal hole 51a formed at the upper end is exposed through the opening 4a formed in the upper wall of the small case 4. (See FIG. 1). The worm wheel 52 has a sliding contact hole 52a formed inward from the connecting member 53 side, and an O-ring 54 is accommodated in the sliding contact hole 52a. The diameter of the sliding contact hole 52a is smaller than the outer diameter of the O-ring 54, and the O-ring 54 is held in the sliding contact hole 52a by elastic force.

  The connecting member 53 includes a cylindrical portion 56 inserted into the sliding contact hole 52a via the O-ring 54, and a flange portion 57 that is connected to the cylindrical portion 56 in the rotation axis direction and contacts the end surface of the worm wheel 52 on the connecting member 53 side. And a hexagonal portion 58 that is connected to the flange portion 57 in the rotation axis direction and engages with the hexagonal hole 41a of the cam 27. The outer diameter of the cylindrical portion 56 is formed larger than the inner diameter of the O-ring 54, and the cylindrical portion 56 is held by the O-ring 54 due to the elastic force of the O-ring 54. Therefore, the connecting member 53 is configured to rotate integrally with the worm wheel 52 by the frictional force of the O-ring 54. The hexagonal portion 58 is formed with a hexagonal outer peripheral surface in the same manner as the hexagonal wrench, and the tip end portion is inclined so as to be easily inserted into the hexagonal hole 41 a of the cam 27.

  Thus, the worm wheel 52 rotates integrally with the connecting member 53 by the frictional force of the O-ring 54, and the connecting member 53 is connected to the cam 27, so that the operating force output from the worm 51 is the worm wheel 52. , And transmitted to the cam 27 via the O-ring 54 and the connecting member 53. In the present embodiment, the operating force transmission mechanism described in the claims includes the worm 51, the worm wheel 52, the O-ring 54, the connecting member 53, and the cam 27.

  Next, with reference to FIG. 5, an example of a transmission structure for operating force will be described. FIG. 5 is a transition diagram schematically illustrating an example of a configuration for transmitting an operating force. 5 (a), (c), (e), and (g) are diagrams schematically explaining the operation force transmission configuration, and FIGS. 5 (b), (d), (f), and FIG. (H) is the figure which demonstrated typically the rotation control structure of the cam.

  FIG. 5A shows an initial state where no operating force is applied to the worm 51. At this time, as shown in FIG. 5B, the convex portion 42a of the cam 27 is at the lowest position, and the clockwise rotation of the cam 27 is restricted by the restriction surface 33c located on the lower side. As shown in FIG. 5C from this initial state, when the worm 51 rotates in the direction of the arrow, the worm wheel 52 rotates and the connecting member 53 and the cam 27 rotate with the worm wheel 52. At this time, as shown in FIG. 5 (d), the projection 42 a provided on the cam 27 also moves counterclockwise by the rotation of the connecting member 53.

  As shown in FIG. 5 (e), when the worm 51 further rotates in the direction of the arrow, as shown in FIG. 5 (f), the convex portion 42a of the cam 27 moves to the uppermost position, and the regulating surface 33b located on the upper side. Abut. At this time, since the convex portion 42 a of the cam 27 is in contact with the upper regulating surface 33 b, a frictional force F is generated between the worm wheel 52 and the connecting member 53 via the O-ring 54. Since the frictional force F increases the operating force load, the operator can recognize the allowable rotation range of the cam 27.

  If the worm 51 is further rotated from this state as shown in FIG. 5G, the rotation of the cam 27 is restricted as shown in FIG. The worm wheel 52 idles against the connecting member 53 against the frictional force F between the connecting member 53 and the connecting member 53. Thus, when the worm 51 is operated with an operating force stronger than the frictional force F between the worm wheel 52 and the connecting member 53, transmission of the operating force from the worm 51 to the cam 27 is stopped. In the present embodiment, the transmission structure for operating force when the worm 51 is rotated in one direction has been described, but the same applies to the case where the worm 51 is rotated in the opposite direction.

  Next, with reference to FIG. 6, the operation force adjustment by the operation force adjustment mechanism according to the embodiment of the present invention will be described. FIG. 6 is a diagram schematically illustrating the operation force adjustment by the operation force adjustment mechanism according to the embodiment of the present invention, and (a) is an approach position where the drive pin of the cam approaches the operation force adjustment plate spring. (B) shows a state in which the drive pin of the cam is in a separated position separated from the approach position. In FIG. 6, the braking force by the braking plate 26 is represented by the size of the arrow.

  As shown in FIGS. 6A and 6B, the drive pin 43 is configured to be capable of circular movement between an approach position approaching the operating force adjusting leaf spring 25 and a separate position spaced from the approach position. . In this case, as shown in FIG. 5B, when the convex portion 42a of the cam 27 is in contact with the lower regulating surface 33c, the drive pin 43 moves to the approach position, and FIG. As shown, when the convex portion 42a of the cam 27 is in contact with the upper restriction surface 33b, the drive pin 43 moves to the separated position.

  As shown in FIG. 6A, when the drive pin 43 of the cam 27 is in the approach position, the traction piece 48 is not pulled by the drive pin 43. Accordingly, the braking plate 26 is not pressed by the pressing piece 47 connected to the traction piece 48, and therefore the braking force on the braking plate 26 is minimized.

  On the other hand, as shown in FIG. 6B, when the drive pin 43 of the cam 27 is in the separated position, the traction piece 48 is pulled by the drive pin 43 and pulled rightward as shown in FIG. Along with this, the pressing piece 47 connected to the traction piece 48 is also pulled out in the right direction shown in the figure to press the braking plate 26, and the braking force on the braking plate 26 is maximized.

  Thus, when the drive pin 43 of the cam 27 is in the approach position, the convex portion 42a of the cam 27 abuts on the lower regulating surface 33c, and when the drive pin 43 of the cam 27 is in the separated position, Since the 27 convex portions 42a are in contact with the upper regulating surface 33b, the operator can recognize the operating force of the fader 1. That is, when the convex portion 42a of the cam 27 comes into contact with the upper and lower restricting surfaces 33b and 33c, the load of the operating force is increased due to the frictional force between the worm wheel 52 and the connecting member 53. Can be recognized.

  As described above, according to the operating force adjustment mechanism 6 according to the present embodiment, the upper limit of the rotation range of the cam 27 is the maximum braking force of the braking plate 26, and the lower limit of the rotation range is the minimum braking force of the braking plate 26. Since they are associated with each other, it is possible to clarify the correspondence between the operation amount to be applied to the worm 51 and the operating force of the fader 1. This makes it possible for the operator to recognize the adjustment level of the operating force. Further, when the cam 27 is within a predetermined rotation range, the operating force is transmitted as the connecting member 53 rotates with the worm wheel 52, and when the cam 27 is restricted in rotation, the worm wheel 52 is rotated. The transmission of the operating force is stopped by idling. Therefore, even if a strong operating force is input to the worm 51, the cam 27 is prevented from being damaged.

  In the above-described embodiment, the operation direction conversion unit 7 is connected to the cam 27 and the cam 27 is rotated via the operation direction conversion unit 7. However, the operation direction conversion unit 7 is not provided. It is good. In this case, the cam 27 is configured to be separable into an input member formed with a hexagonal hole and an output member formed with a drive pin so that the input member and the output member are brought into frictional contact. In such a configuration, even if a strong operating force is input to the input member, the cam 27 can be prevented from being damaged.

  In the above-described embodiment, the connecting member 53 and the cam 27 are configured to be separable, but may be formed integrally. Even in this configuration, the worm wheel 52 and the connecting member 53 are in frictional contact, so that the operator can recognize the adjustment of the operating force of the fader 1 and a strong operating force can be applied. It becomes possible to prevent the cam 27 from being damaged.

  In the above-described embodiment, the worm wheel 52 and the connecting member 53 are brought into frictional contact via the O-ring 54. However, the present invention is not limited to this configuration. Any configuration may be used as long as the worm wheel 52 and the connecting member 53 are in frictional contact with each other, and the worm wheel 52 and the connecting member 53 may be connected by the respective frictional forces without using the friction member. A member other than the O-ring may be used.

  In the above-described embodiment, the worm 51 is operated with a hexagon wrench. However, the present invention is not limited to this configuration. Any configuration may be used as long as the worm 51 is operated. For example, a hexagonal outer peripheral surface may be formed in the worm 51 in place of the hexagonal hole 51a, and the worm 51 may be operated by a monkey wrench. .

  In the embodiment described above, the pulling piece 48 is formed on the operating force adjusting plate spring 25 to adjust the operating force of the fader 1, but the present invention is not limited to this configuration. Any configuration may be used as long as the operation force of the fader 1 is adjusted.

  The embodiment disclosed this time is illustrative in all respects and is not limited to this embodiment. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims for patent.

  As described above, the present invention has an effect that the operator can recognize the adjustment degree of the operating force and can prevent damage even when a strong operating force is applied. It is useful for an operating force adjustment mechanism and an operating force transmission mechanism suitable for a fader used for adjusting the volume of the sound and adjusting the amount of light in a theater or the like.

DESCRIPTION OF SYMBOLS 1 Fader 6 Operating force adjustment mechanism 7 Operation direction conversion unit 13 Slide member (operating body)
25 Actuating force adjustment leaf spring (leaf spring, braking part)
26 Braking plate (braking part)
26a peripheral surface portion 27 cam (operation force transmission mechanism, second rotating member, output member)
33 Presser part 33a Inner peripheral surface 33b, 33c Restricting surface 41a Hexagon socket (engaged part)
42a Convex part 43 Drive pin 48 Traction piece 48a Hole part 51 Worm (operating force transmission mechanism)
51a Hexagon socket 52 Worm wheel (operating force transmission mechanism, first rotating member)
52a Sliding contact hole 53 Connecting member (operation force transmission mechanism, second rotating member, input member)
54 O-ring (operation force transmission mechanism, friction member)
56 Cylinder part 58 Hexagon part (engagement part)

Claims (6)

A braking unit for applying a braking force to the operating body;
An operating force transmission mechanism that transmits the operating force to the braking unit to adjust the braking force;
The operating force transmission mechanism is in frictional contact with the first rotating member that rotates in response to the operating force and the first rotating member, and rotates in response to the rotation of the first rotating member to the braking portion. A second rotating member that outputs an operating force;
The operating force adjusting mechanism, wherein the second rotating member is restricted in rotation within a predetermined rotation range. The operating force transmission mechanism has a friction member,
The operating force adjusting mechanism according to claim 1, wherein the first rotating member and the second rotating member are in frictional contact with each other via the friction material. The operating force transmission mechanism has a worm that is rotated around an axis orthogonal to the rotation axis of the first rotating member by a tool,
The operating force adjusting mechanism according to claim 1, wherein the first rotating member is a worm wheel that engages and rotates with the worm. The second rotating member frictionally contacts the first rotating member and the input member to which an operating force is input from the first rotating member, and the braking in a state where the rotation is restricted within the predetermined rotation range. It is configured to be separable in the direction of the rotation axis with the output member that outputs the operating force to the part,
The input member is formed with an engaging portion that engages with the output member, and the output member is formed with an engaged portion that engages with the engaging portion so as to rotate integrally with the input member.
The operating force adjusting mechanism according to claim 3, wherein the engaging portion is engageable with the tool. The braking part includes a leaf spring,
The operating force adjusting mechanism according to any one of claims 1 to 4, wherein the second rotating member is provided with a cam for adjusting a pressing force of the leaf spring. A first rotating member that rotates in response to an operating force and a braking unit that frictionally contacts the first rotating member, rotates in response to the rotation of the first rotating member, and applies a braking force to the operating body. A second rotating member that outputs an operating force to the second rotating member,
The operating force transmission mechanism, wherein the second rotation member is restricted in rotation within a predetermined rotation range.

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