JP2001355665A - Speed governor for rotating body - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a new speed governor capable of adjusting a relation between a rotation speed of a rotating body and a rotation resistance to be subjected on the rotating body according to a rotating position of the rotating body, and securing a large degree of freedom for setting a speed governing tuning of the rotating body. SOLUTION: A cam member 20 is provided in a movement transmission route transmitting a rotation movement of a rotating body to a damper main body 102. A rotation resistance subjected on the rotating body according to a rotating position of the rotating body, thereby, can be easily adjusted by changing a shape of a cam surface 46 of the cam member 20.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a speed governing device which suppresses the rotation of a rotating body at an excessive speed and realizes a smooth rotating operation of the rotating body. The present invention relates to a speed control device for a rotating body having a novel structure applied to a toilet seat and a lid, a lid of a trash can, furniture and the like.

[0002]

2. Description of the Related Art Heretofore, a rotating body has been assembled so as to be relatively rotatable with respect to a support so that the rotating body can be automatically rotated by urging means such as a coil spring or gravity. For example, there are a lid of a rice cooker, a toilet seat and a lid of a Western-style toilet, a lid of a trash box and furniture, and the like.
When such a rotating body is rotated at an excessive speed, a hitting sound is generated due to a collision between the rotating body and the support, and in a severe case, the rotating body or the support is damaged due to an impact at the time of the collision. May occur.

[0003] In order to cope with such a problem, various speed control devices have been proposed for suppressing the rotation speed of the rotating body and smoothly performing the rotating operation. For example, in Japanese Patent Publication No. 4-78290, the rotational movement of the rotating body is transmitted to the friction member via a gear, thereby utilizing the sliding resistance of the friction member to rotate the rotating body. It has been proposed to reduce this.

However, all of the prior arts described in the above publications or the like transmit the turning motion of the rotating body to the friction member at a fixed gear ratio. Regardless, only a rotation resistance force is exerted corresponding to the rotation speed alone. For this reason, for example, it has been difficult to adjust the turning resistance exerted according to the turning position of the turning body.

Specifically, for example, in an automatic lid-open rice cooker or the like, in the initial to middle stages of opening the lid, the rotating resistance force that acts even if the lid rotating speed is high is suppressed, while Tuning such as gradually increasing the turning resistance in the middle to final stages of the opening operation of the lid and decreasing the turning resistance again near the fully open position to reach the fully open position has been difficult.

[0006]

The present invention has been made in view of the above circumstances, and has as its object to solve the problem of the relationship between the rotational speed of a rotating body and the rotational resistance acting thereon. To adjust the speed of the rotating body in accordance with the rotating position of the rotating body, and to provide a novel structure of the rotating body speed governing device with a large degree of freedom in setting the tuning of the rotating body. And

[0007]

An embodiment of the present invention which has been made to solve such a problem will be described below. The components employed in each of the embodiments described below can be employed in any combination as possible. In addition, aspects or technical features of the present invention are not limited to those described below, but are described in the entire specification and drawings, or based on the invention ideas that can be understood by those skilled in the art from the descriptions. It should be understood that it is recognized on the basis of.

[0008] That is, the first aspect of the present invention is to provide a liquid crystal display device, which is mounted between a support and a rotary body which is mounted to be rotatable relative to the support about a rotation center axis. A speed control device for adjusting a rotation speed of a rotating body,
(A) a case member fixedly attached to one of the support and the rotating body; (b) a cam member rotatably supported around the one axis by the case member; and (c) a cam of the cam member. The slide member is slidably abutted on the surface, and is reciprocated in conjunction with the relative rotation operation of the support member and the rotation member, thereby applying a driving force to the cam member to rotate the cam member. A prime mover, and (d) a rotational resistor that exhibits a resistance substantially corresponding to the rotational speed;
A damper body supported by the support member and one of the rotating members together with the cam member; and (e) a damper body interposed between the cam member and the damper body to rotate the cam member. By transmitting the rotation resistance of the
A rotational force transmitting means for exerting rotational resistance by the damper body as a relative rotational resistance force between the support member and the rotational body via the cam member and the prime mover. Speeding device.

In the rotating body speed governing device having such a structure according to the present aspect, the use of the cam member allows a simple design change such that the shape of the cam surface of the cam member is changed so that the rotating body has a simple structure. It is possible to adjust the turning resistance force exerted according to the turning position with a large degree of freedom, thereby suppressing the turning of the rotating body at an excessive speed, and achieving a smooth turning operation of the rotating body. Can be realized.

[0010] Further, as the cam member employed in this embodiment, either a plate cam or a three-dimensional cam can be employed.
The plate cam may be one having a cam surface on the outer peripheral surface or one having a cam groove on a side surface (axial end surface).

Further, the prime mover is advantageously constituted by, for example, a pressing projection formed integrally with the rotating body and slidably in direct contact with the cam surface of the cam member. Further, for example, a reciprocating motion transmission member is disposed so as to be in contact with the cam surface of the cam member and linearly reciprocally displaceable. May be pressed in the axial direction by a pressing projection integrally formed so as to protrude outward in the direction perpendicular to the axis, and in this case, a driving body is constituted by the reciprocating power transmission and the pressing projection.

The damper body may be an oil damper, a governor damper, or the like. The rotary resistor may be an oil damper blade or a governor damper friction sliding member.

Further, the rotational force transmitting means employs an integral connecting shaft structure for directly connecting the cam member and the damper main body, and adopts a gear structure or the like to change the rotational speed of the cam member to change the rotational speed of the cam member. It is also possible to communicate to.

According to a second aspect of the present invention, there is provided a speed control device for a rotating body having a structure according to the first aspect, wherein the cam member has an axially inclined surface at one end face of a rotation center shaft. A cam having a cam surface extending in the circumferential direction, and a rotation center axis of the cam member is disposed at right angles to a rotation center axis of the rotating body. In the rotating body speed governing device having such a structure according to the present aspect, by adopting a three-dimensional cam, particularly a slope cam as the cam member, the rotation amount of the cam can be set to be larger than that of the plate cam. In addition to this, it becomes easier to adjust the turning resistance exerted according to the turning position of the turning body.

According to a third aspect of the present invention, there is provided a speed control device for a rotating body having a structure according to the first or second aspect, wherein the rotational resistor includes a centrifugal force accompanying rotation around a central axis. A governor type that has a sliding member that spreads in a direction, and that the sliding member slides on an inner peripheral surface of a sliding contact cylinder body that is spaced apart on the outer peripheral side of the center shaft to obtain a rotation resistance force. The damper main body is constituted by a damper. In the governing device for the rotating body having the structure according to this aspect, the damper body is constituted by the governor-type damper, so that the oil scent and oil leakage when the damper body is constituted by the oil-type damper. Do not have to worry. Therefore, it is particularly suitably used for a lid of a rice cooker and the like.

According to a fourth aspect of the present invention, there is provided a speed control device for a rotating body having a structure according to the first to third aspects, wherein the rotational movement of the cam member is increased to increase the damper body. The torque transmission means is configured to include a speed increasing mechanism for transmitting the torque to the rotation resistor. In the rotating body speed governing device having such a structure according to the present aspect, the use of the speed increasing mechanism makes it possible to give a sufficient speed to the rotating resistor, and accordingly, provide a sufficient rotating resistance. It is possible to gain strength. Note that, as the speed increasing mechanism, a planetary gear mechanism, another gear pair, a belt wheel, or the like may be employed.

According to a fifth aspect of the present invention, there is provided a speed control device for a rotating body having a structure according to the fourth aspect, wherein the cam member and the damper main body are arranged on the same central axis. At least one planetary gear mechanism is arranged on the same central axis between the cam member and the damper main body, and the speed increasing mechanism is constituted by the planetary gear mechanism. In the rotational body speed governing device having the structure according to this aspect, the cam member, the planetary gear mechanism, and the damper main body are arranged on the same central axis, so that the size of the device in the direction perpendicular to the axis is made compact. It is possible to do.
Also, by adopting the planetary gear mechanism, a large speed increase ratio can be obtained with a compact mechanism.
In addition, a larger speed increase ratio can be easily set by arranging a plurality of planetary gear mechanisms in the axial direction, so that the required rotation resistance can be easily obtained.

According to a sixth aspect of the present invention, there is provided a speed control device for a rotating body having a structure according to the first to fifth aspects, wherein a returning force for returning the cam member to an initial rotational position is provided. Is provided so that the cam member can be reciprocally rotated by a predetermined angle around the central axis in accordance with the relative reciprocating operation of the support and the rotating body. And In the rotating body speed governing device having the structure according to this aspect, the rotation stroke amount of the cam member can be set in a wide range of one rotation or less, and the tuning flexibility can be further improved. .

According to a seventh aspect of the present invention, there is provided a speed control device for a rotating body having a structure according to the first to sixth aspects, wherein a rotational force transmission path between the cam member and the damper body is provided. And a one-way clutch means for transmitting a rotational force of the cam member in only one direction to the damper body. In the rotational body speed governing device having the structure according to this aspect, the operation of returning the cam member to the initial rotational position can be performed smoothly and promptly. As the one-way clutch means, for example, a ratchet mechanism using a free joint, a one-way friction clutch using a coil spring, or the like is suitably adopted.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, in order to clarify the present invention more specifically, embodiments of the present invention will be described in detail with reference to the drawings.

First, a governing device 10 according to a first embodiment of the present invention will be described with reference to FIGS. FIG.
2 shows a state in which the push rod 12 is at the initial position, and FIG.
FIG. 3 is an explanatory view of the assembly and disassembly of the speed control device 10. This speed governing device 10 includes a cam member 20 and first and second planets as a speed increasing mechanism in an internal space formed by upper and lower case members 14 and 16 of a hollow structure as a case member and a cover 18. The gear mechanisms 22 and 24 and a sliding member 26 as a rotation resistor are incorporated by being superimposed on the same central axis by a gear pin 28, and the push rod 12 projects to one side in the axial direction to be displaced in the axial direction. Assembled as possible. Then, by rotating operation of a rotating body (not shown),
When a pressing projection (not shown) formed integrally with the rotating body pushes the push rod 12 in the axial direction, the cam member 20 is displaced.
Is rotated on the central axis, and the rotation is performed by the sliding member 26 via the first and second planetary gear mechanisms 22 and 24.
, The rotation resistance of the sliding member 26 is exerted. The upper and lower case members 14, 16 are fixedly attached to a support (not shown). Further, in the present embodiment, a driving body is formed by a pressing protrusion (not shown) and the push rod 12. In the following description, the vertical direction in FIG. 1 is simply referred to as the vertical direction.

More specifically, the case member has a cylindrical upper case member 14 superposed on the same central axis on the opening side of the lower case member 16 having a bottom and a cylindrical shape. An annular plate-shaped cover 18 is formed on the upper opening 14 by being overlapped on the same central axis. Thereby, such a case member has a hollow cylindrical shape in which both sides in the axial direction are covered, and a through hole 30 is formed in the center of the cover 18 forming the upper bottom wall portion, while At the center of the bottom wall, a circular rod-shaped gear pin 28 is fixedly provided upright.
An annular step 32 extending radially inward is formed integrally with the lower opening of the upper case member 14, and extends downward from the inner peripheral edge of the annular step 83 in the axial direction to form a lower part. A small-diameter cylindrical portion 34 fitted into the opening of the case member 14 and an annular support portion 36 that extends radially inward from the distal end opening of the small-diameter cylindrical portion 34 are integrally formed. Furthermore, on the inner peripheral surface of the small-diameter cylindrical portion 34 of the upper case member 14,
The internal gear teeth are formed and the lower case member 16 is formed.
The internal gear teeth are also formed on the inner peripheral surface near the opening of the gear.

A gear pin 28 erected on the lower bottom wall of the case member is fixedly disposed extending on the center axis in the hollow interior of the case member. It reaches the inside of the through hole 30 of the cover 18.
Then, the push rod 1 is moved to the upper end of the gear pin 28.
2 are assembled. The push rod 12 has a circular rod shape, and has a through hole 38 formed on the center axis thereof. And protrudes outward in the axial direction. Further, a pair of rod-shaped cam contact portions 40, 40 projecting radially outward from both sides of the central axis are fixedly provided at the lower end in the axial direction of the push rod 12,
The cam contact portions 40, 40 contact the inner surface of the cover 18 to prevent the push rod 12 from coming out of the through hole 30. In short, push rod 1
2 is disposed so as to protrude axially outward from the case member through the through-hole 30, and is movable in the axial direction by being guided by the gear pin 28.

The inner peripheral surface of the upper case member 14
A pair of guide grooves 42, 42 extending in the axial direction are formed in portions facing each other in one radial direction. Then, the projecting tips of a pair of cam contact portions 40, 40 projecting from the push rod 12 are inserted into these guide grooves 42, 42 to guide the inside of the guide grooves 42, 42 in the axial direction. It is supposed to be. As a result, the rotation of the push rod 12 about the central axis with respect to the case member is prevented, and only the relative displacement in the axial direction is allowed.

A cam member 20 is disposed inside the case member below the push rod 12. The cam member 20 has a bottomed cylindrical cam portion 44 opened upward in the axial direction, and the axial height of the cylindrical wall portion of the cam portion 44 is changed in the circumferential direction. An inclined cam 48 having a cam surface 46 which is inclined in the axial direction and extends in the circumferential direction is provided on the distal end surface in the axial direction with a predetermined length in the circumferential direction. In the present embodiment, two inclined cams 48, 48 each extending over substantially a half circumference in the circumferential direction.
Are formed. That is, in the cam portion 44, two inclined cams 48 are formed by the cylindrical wall portion.

Further, a small-diameter circular protrusion 50 projecting downward in the axial direction is formed integrally with the bottom wall portion of the cam member 20, and an insertion hole 5 is formed on the center axis of the circular protrusion 50.
2 are penetrated. In addition, the cam member 20 is rotatably inserted into and assembled with the gear pin 28 projecting from the case member in the insertion hole 52. The push rod 12 is inserted into the cam portion 44 of the cam member 20 from an axially upper opening, and a pair of cam contact portions 40, 40 protruding from the push rod 12 are connected to the cam portion 44.
The cam surfaces 46, 46 of the slant cams 48, 48 are abutted against the cam surfaces 46, 46 so that they can slide on the cam surfaces 46, 46.

Further, below the cam member 20 in the axial direction,
A first planetary gear member 54 is provided. The first planetary gear member 54 has upper and lower disks 56, 58 which are disposed to face each other at an axial distance from each other, and the upper and lower disks 56, 58 A plurality of wires (in this embodiment, 3
The first planetary gear 6 is fixed to each other by the
2 is rotatably mounted. The upper disk 56 and the lower disk 58 have a center hole 6 extending through the center axis.
4 and an insertion hole 66 are formed. Further, the lower disk 58
Is formed integrally with the inner peripheral edge of the insertion hole 66, that is, on the peripheral edge of the insertion hole 66.

Then, the first planetary gear member 54
Is rotatably extrapolated to the gear pin 28,
The outer peripheral edges of the upper disk 56 and the lower disk 58 are formed by the annular step portions 32 of the upper case member 14 constituting the case member.
By being slidably superimposed on the respective upper surfaces of the annular support portion 36 and the annular support portion 36, they are positioned and arranged in the axial direction. Thereby, each planetary gear 62 of the first planetary gear member 54 is accommodated and arranged in the small-diameter cylindrical portion 34 of the upper case member 14, and the gear internal teeth engraved on the inner peripheral surface of the small-diameter cylindrical portion 34. The first planetary gear mechanism 22 is thus configured. The cylindrical portion 68 of the lower disk 58 is inserted into the annular support portion 36 of the upper case member 14 and extends into the lower case member 16.

A circular projection 50 of the cam member 20 is slidably superimposed on the upper surface of the upper disk 56 in the axial direction of the first planetary gear member 54, and is supported in the axial direction. Further, a cylindrical portion 70 protruding upward in the axial direction is integrally formed on the upper disk 56, and the cylindrical portion 70 is arranged radially outward with respect to the circular protrusion 50 of the cam member 20. And the cylindrical portion 70
The lower surface in the axial direction of the cam portion 44 of the cam member 20 is slidably overlapped with the upper end surface in the axial direction of the cam member 20.

A one-way clutch spring 72 is accommodated in a cylindrical space formed between the circular projection 50 of the cam member 20 and the radially opposed surface of the cylindrical portion 70 of the first planetary gear member 54. The lower end of the spring 72 in the axial direction is locked and fixed to a locking portion 74 protruding from the inner peripheral surface of the cylindrical portion 70. The one-way clutch spring 72 is formed of a coil spring made of metal or the like, and is wound around and provided in contact with the outer peripheral surface of the circular protrusion 50, whereby the direction in which the spring 72 is tightened is provided. First planetary gear member 5
The one-way clutch means for preventing the relative rotation of the cam member 20 from the cam member 20 while preventing the relative rotation of the first planetary gear member 54 and the cam member 20 in a direction in which the spring 72 is loosened while friction between the spring 72 and the like is prevented. Have been.

The cylindrical portion 7 of the first planetary gear member 54
A cam return spring 76 is externally disposed on the outer peripheral surface of the zero. This cam return spring 76
Is formed by a coil spring made of metal or the like, the upper end of which is locked and fixed to a locking portion 78 protruding from the outer peripheral surface of the cam portion 44 of the cam member 20, while the lower end portion is The upper case member 14 is locked and fixed to a locking projection 80 protruding from an inner peripheral surface of the upper case member 14. Thereby, when the cam member 20 is rotated around the central axis with respect to the case member, the elastic force in the direction of returning to the initial rotation position is applied to the cam member 20 based on the elastic energy stored in the spring 76. Has been affected.

Further, a second planetary gear member 82 is arranged below the first planetary gear member 54 in the axial direction.
Like the first planetary gear member 54, the second planetary gear member 82 includes upper and lower disks 84 and 86 that are axially separated from each other and are opposed to each other. The lower disks 84 and 86 are fixed to each other by a plurality of (three in the present embodiment) gear pins 88 provided so as to extend between the opposing surfaces around the central axis. A second planetary gear 90 is rotatably mounted on each of the gear pins 88. The upper circular plate 84 and the lower circular plate 86 are formed with a center hole 92 and an insertion hole 94 extending through the center axis. Further, a cylindrical tubular portion 96 protruding axially downward is formed integrally with the inner peripheral edge of the lower disk 86, that is, the peripheral edge of the insertion hole 94.

Then, the second planetary gear member 82
Is rotatably extrapolated to the gear pin 28,
An outer peripheral edge of the upper disc 84 is formed in an annular step 9 formed in an opening of the lower case member 16 constituting the case member.
8 slidably supported and positioned in the axial direction. Thereby, each planetary gear 90 of the second planetary gear member 82 is disposed in the opening of the lower case member 16, and the gear internal teeth carved on the inner peripheral surface of the lower case member 16 are opposed. And the second planetary gear mechanism 2
4 are configured.

The upper circular plate 84 of the second planetary gear member 82 is integrally formed with a thick cylindrical boss 100 projecting upward on the center axis.
8 so as to be rotatable and externally inserted into the cylindrical portion 68 of the lower disk 58 formed on the first planetary gear member 54 and extended into the first planetary gear member 54. Is arranged. The protruding tip of the boss 100 is
The pinion has gear teeth on the outer peripheral surface, and the pinion is meshed with the planetary gear 62 of the first planetary gear member 54. In short, the sun gear in the first planetary gear mechanism 22 is constituted by the pinion of the boss 100. As a result, the rotational motion of the first planetary gear member 54 about the central axis is accelerated by the first planetary gear mechanism 22 and the second planetary gear member 82
Is transmitted as a rotational motion about the central axis.

Further, below the second planetary gear member 82, a damper member 102 is provided. The damper member 102 includes a disk-shaped support plate 104, and upper and lower bosses 106 and 108 of each circular shape projecting vertically in the axial direction are formed integrally with a central portion of the support plate 104. Have been. The support plate 104 and the upper and lower bosses 106 and 108 are formed with through holes 110 extending through the center axis.
At 0, the gear pin 28 is rotatably extrapolated and assembled. In addition, the axial end surface of the lower boss portion 108 is overlapped with the protruding end surface of the gear pin support portion 112 projecting from the center of the bottom wall of the lower case member 16 and is positioned and supported in the axial direction. ing.

In the support plate 104, support pins 114, 114 protruding downward in the axial direction are fixed at a plurality of positions (two positions in the present embodiment) on the periphery. The sliding member 26 is externally attached to the pin 114. The sliding member 26 has a substantially crescent-shaped or arc-shaped block shape as a whole, and is externally inserted into the support pin 114 through a hole 116 provided at one end in the circumferential direction. As a result, it is assembled so as to be rotatable around the support pin 114. Then, when the support plate 104 is rotated around the central axis, the respective sliding members 26 spread radially outward around the support pins 114 by centrifugal force. Note that the outer peripheral surface of the sliding member 26 is a sliding contact surface curved in the circumferential direction, and is slidably contacted with the inner peripheral surface of the lower case member 16 when the sliding member 26 spreads radially outward due to centrifugal force. It has become.

Further, the upper boss 10 of the support plate 104
6 is inserted into a cylindrical portion 96 formed on the lower disk 86 of the second planetary gear member 82, and is disposed to extend into the second planetary gear member 82. The upper boss 10
6 is a pinion having gear teeth on the outer peripheral surface, and the pinion is used as a second planetary gear member 8.
2 are meshed with the respective planetary gears 90. In short, the pinion of the upper boss portion 106 constitutes a sun gear in the second planetary gear mechanism 24. As a result, the rotational motion of the second planetary gear member 82 about the central axis is increased by the second planetary gear mechanism 24, and the rotational motion of the second planetary gear member 82 about the central axis is moved relative to the damper member 102 (support plate 104). Is transmitted as.

Next, the speed governing device 1 having the above-described structure will be described.
The operation at 0 will be described with reference to FIGS.
FIG. 1 shows a state in which the push bar 12 is in the protruding position, while FIG. 3 shows a state in which the push bar 12 is in the push position.

In the governing device 10, in the initial state where no external force is applied to the push rod 12, the cam member 20 elastically positioned by the coil spring 72 as shown in FIG. The cam contact portions 40, 40 of the push rod 12 are brought into contact with and supported near the upper ends of the cam surfaces 46, 46 in the axial direction.
Is held at a position protruding outward in the axial direction.

When the push rod 12 is pushed downward in the axial direction from the initial state shown in FIG. 1, the cam contact portion 40 displaced in a non-rotatable manner by the guide grooves 42 of the case member. As a result, the cam surface 46 of the cam member 20 is slid, and the cam member 20 is driven to rotate about the central axis. At this time, the one-way clutch spring 72 is in a state in which the circular protrusion 50 is tightened, and the rotational power of the cam member 20 is transmitted to the first planetary gear member 54. Also, a cam return spring 76 is provided.
Is elastically deformed in the winding direction (direction for reducing the diameter), and stores a return force for returning the cam member 20 to the initial rotation position as described above.

As a result, the first planetary gear member 54 is
The cam member 20 is rotated substantially integrally in the same direction. Further, when the first planetary gear member 54 is rotated, the rotational motion of the first planetary gear member 54 is increased by the driving force transmitting action of the first planetary gear mechanism 22 as described above, and the second planetary gear member 54 is rotated. The second planetary gear member 82 is transmitted to the planetary gear member 82 so that the first planetary gear member 5
The rotation speed is increased in the same direction as that of the rotation direction No. 4. In the present embodiment, the first planetary gear member 54
The rate of increase in rotation speed between the second planetary gear member 82 and the second planetary gear member 82 is approximately 4 to 5 times.

Further, when the second planetary gear member 82 is rotated, the rotational motion of the second planetary gear member 82 is increased by the driving force transmitting action of the second planetary gear mechanism 24 as described above. The power is transmitted to the damper member 102, and the speed of the support plate 104 of the damper member 102 is increased in the same direction as the second planetary gear member 82, and the support plate 104 is driven to rotate. In the present embodiment, the second planetary gear member 8
The rate of increase in the rotational speed between the damper member 2 and the damper member 102 is approximately 4 to 5 times.

When the damper member 102 is rotated, the sliding members 26, 26 on the damper member 102 are rotated.
Are spread by centrifugal force and slid against the inner peripheral surface of the lower case member 16, thereby exerting a rotational resistance.

Thereafter, when the pushing force exerted on the push rod 12 is removed, the cam member 20 is displaced by the restoring force stored in the cam return spring 76 when the push rod 12 is pushed as described above. Is rotated in the opposite direction to that at the time, so that the cam contact portion 40 is
6 and is pushed up in the axial direction to automatically return to the initial projecting position. In this operating state, the one-way clutch spring 72 tightening the circular projection 50 is expanded and loosened, so that the rotational power of the cam member 20 is not transmitted to the first planetary gear member 54. ing. That is, the first and second planetary gear members 54 and 82 and the damper member 102 hardly rotate, and therefore, the sliding contact resistance of the sliding member 26 and the first and second planetary gear members The cam members 20 are smoothly returned to the initial position without the rotation resistance of the cam members 20 being exerted by the rotational resistances 54 and 82.

Next, a specific example in the case where the governing device 10 having the above-described structure is adopted as a rotating speed adjusting means of the lid of a rice cooker will be described.

FIG. 4 shows a rice cooker main body 1 as a support.
18 shows a state in which the lid 120 of the rice cooker as a rotating body assembled so as to be relatively rotatable around the rotation center axis with respect to 18 is closed. In this state, the push bar 12 of the governing device 10 is located at the initial position as shown in FIG. 1 and is projected outward from the case member in the axial direction. The lid 120 is formed integrally with the lid 120 at a position facing the lid 120 with respect to the rotation center axis so as to push the push rod 12 in.

FIG. 5 shows the rice cooker body 118 with the lid 120 closed. In this state, the push rod 12 of the governing device 10 is located at the pushing position as shown in FIG. That is, the lid 12
When 0 is displaced from the closed state to the open state, the pushing section 122 is pushed into the pushing position from the initial position by the contact of the pushing section 122 with the pushing rod 12, as described above. The speed control device 10 is operated in a resistance manner. When the lid 120 is displaced from the opened state to the closed state, the pushing force applied to the pushing rod 12 by the pushing part 122 is released, and the pushing rod 12 is moved from the pushing position to the initial position. After being returned, the governor 1
0 is set to return operation.

Here, in the governing device 10 structured as described above, when the cover 120 is opened,
As the push rod 12 is pushed in the axial direction, the sliding member 2
6 and 26 are slid on the inner peripheral surface of the lower case member 16, thereby exhibiting an effective rotation resistance. Therefore, the opening speed of the lid 120 is suppressed, and the opening speed of the lid 120 is suppressed. A simple lid opening operation can be realized.

Further, in such a governing device 10,
The rotational speed of the damper member 102 with respect to the pushing operation speed of the push rod 12, and thus the lower case member 1 of the sliding members 26, 26
6 with respect to the cam surface 4 of the cam member 20.
6 can be adjusted easily and with a large degree of freedom by adjusting the shape of the cam surface 46. In particular, by changing the inclination angle of the cam surface 46 in the circumferential direction, the pushing position of the push rod 12, that is, For example, it can be set so that the exerted rotational resistance varies depending on the opening angle of the lid 120.

Therefore, the operating resistance exerted when the lid 120 is opened can be easily adjusted with an extremely large degree of freedom, and the intended opening operation can be easily realized. It becomes possible.

Also, in the speed governing device 10 of the present embodiment, the first and second planetary gear mechanisms 22 and 24 are employed, so that the cam member 20 and the damper member 102 are separated.
On the power transmission path to the motor, the speed-up mechanism could be made compact, and as a result, the sliding damper mechanism, which was easier to manufacture and cheaper than the oil-type damper,
It is possible to obtain an effective operation resistance.

FIG. 6 shows a speed control device 124 according to a second embodiment of the present invention. In the following description, the up-down direction refers to the up-down direction in FIG. 6 in principle, and members and parts having the same structure as the first embodiment are described in the first embodiment. The same reference numerals are given in the drawings to omit detailed description thereof.

The speed control device 124 of this embodiment is different from the speed control device of the first embodiment in that the spring (72) for the one-way clutch and the second planetary gear mechanism (24) (both
(See FIG. 1) is not adopted. That is, since the one-way clutch spring (72) in the first embodiment (see FIG. 1) is not employed, the circular projection 50 of the cam member 20 is attached to the cylindrical portion 70 of the first planetary gear member 54. It is interpolated and fixedly attached by bonding or the like.

Since the second planetary gear mechanism (24) (see FIG. 1) in the first embodiment is not employed, the lower case member 16 has an annular step (98).
(See FIG. 1) is not formed. In short, the lower case member 16 has a cylindrical shape with a lower bottom than the first embodiment, and has an additional dimension enough to accommodate the damper member 102. In this embodiment, the sliding member 2 is also formed by the inner peripheral surface near the bottom wall of the lower case member 16.
6 is formed with a sliding contact surface on which it is slid.

The damper member 102 is connected to the support plate 10.
4, the upper boss portion 106 is inserted into the cylindrical portion 68 of the lower disk 58 of the first planetary gear member 54 and extends into the first planetary gear member 54 and is disposed. The pinion formed in the portion 106 is used for the first planetary gear member 5.
4 is meshed with each planetary gear 62. In short, in the present embodiment, the upper boss 10 of the damper member 102
The sun gear in the first planetary gear mechanism 22 is constituted by the pinion 6. As a result, the rotational motion of the first planetary gear member 54 about the central axis is increased by the first planetary gear mechanism 22 and the rotational motion of the first planetary gear member 54 about the central axis is moved relative to the damper member 102 (support plate 104). Is transmitted as.

In the governing device 124 having such a structure, the push rod 12 is pushed and displaced axially downward, and the cam abutment portions 40, 40 abut on the cam surfaces 46, 46 to cause the cam member to move. When the 20 is rotated, the first planetary gear member 54 is rotated integrally with the cam member 20. And, the planetary gear 62 of the first planetary gear member 54
When the damper member 102 having the pinion meshed with the first member is rotated at an increased speed, the sliding members 26 and 26 are spread radially outward as in the first embodiment, and the lower case member 16 is The sliding resistance is exerted by being slid on the inner peripheral surface.

When the pressing force exerted on the push rod 12 is released, the cam is returned by the restoring force stored in the cam return spring 76 when the push rod 12 is pushed and displaced, as in the first embodiment. As the member 20 is rotated in the direction opposite to the direction of the pushing displacement, the cam contact portions 40, 40 of the pushing rod 12 are pushed up in the axial direction outward by the cam surface 46, and the pushing rod 12 is moved to the initial position. Will be restored. At this time, together with the cam member 20, the first planetary gear member 54 and the damper member 102 are also rotated backward and returned to the initial positions. When the damper member 102 rotates in the reverse direction, the support pins 114 are provided in front of the respective sliding members 26 in the rotation direction.
The sliding resistance of the sliding member 26 to the lower cover member 16 is reduced.

In the speed governing device 124 of this embodiment having such a structure, a one-way clutch and a second planetary gear mechanism are not required as compared with the first speed governing device.
A reduction in the number of parts, simplification of the structure, downsizing, and the like can be advantageously achieved.

FIG. 7 shows a speed controller 126 according to a third embodiment of the present invention. In the following description, the vertical direction refers to the vertical direction in FIG. 7 in principle. In addition, members and parts having the same structure as in the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.

That is, in the governing device 126 of the present embodiment, a slope cam is not used and a plate cam 128 is used instead of the governing device of the first embodiment. There is a feature.

More specifically, the cam member 130 according to the present embodiment has a substantially elliptical or beveled-shaped plate cam 128, and its rotation center axis 132 is biased in the long axis direction. Further, the rotation center shaft 132 has a cylindrical shape, and is rotatably mounted on the upper end portion of the gear pin 28 so as to be externally attached thereto. Furthermore, the rotation center axis 1
32 is inserted into the cylindrical portion 70 of the first planetary gear member 54, and a coil spring 72 is provided on the outer peripheral surface, similarly to the circular projection (50) of the cam member (20) in the first embodiment. The one-way clutch is formed by being wound.

In the vicinity of the plate cam 128, a cam lever 134 as a prime mover is provided. The cam lever 134 has a curved plate-like lever shape, and is externally inserted into a support shaft (not shown) in a support hole 136 penetrating near one end thereof, and has a central axis parallel to the gear pin 28. It is supported so as to be rotatable around. The cam lever 134 is reciprocally rotated with the rotation of a rotating body (not shown).
Further, the projecting side tip of the cam lever 134 is
8, the plate cam 128 is driven to rotate in conjunction with the rotation operation of the cam lever 134.

Therefore, in the governing device 126 of this embodiment having such a structure, the cam lever 134 is
The plate cam 128 is rotationally driven by the cam lever 134 by being rotated in conjunction with a rotary body such as a rice cooker lid. Then, the rotational operation of the plate cam 128 is increased through the first and second planetary gear mechanisms 22 and 24 to increase the speed of the damper member 1 as in the first embodiment.
By transmitting the sliding force to the lower cover member 16, the operating resistance based on the sliding contact with the lower cover member 16 is exerted.

By changing and setting the shape of the outer peripheral surface 138 constituting the cam surface of the plate cam 128, the cam lever 134, and hence the plate cam 12 with respect to the amount of rotation of the rotating body, is changed.
By appropriately adjusting the amount of rotation of 8, the rotation resistance exerted can be easily adjusted.

Since the speed control device 126 employs a plate cam 128 having a flat plate shape, the axial dimension is smaller than that of the first embodiment in which the inclined cam (48) is employed. It becomes possible to make it small and compact. In particular, in the present embodiment, the plate cam 128
However, it is also used as a cover member that covers the upper opening of the case member, and the number of parts is further reduced.

Since the center axes of rotation of the plate cam 128 and the cam lever 134 for driving the plate cam 128 are parallel to each other, an arrangement different from that of the governing device 10 of the first embodiment is adopted. Therefore, the governing device 126 of the present embodiment and the governing device 10 of the first embodiment can be selectively used in accordance with the structure of the rotating body and the like, thereby disposing the governing device. The degree of freedom in setting the structure is improved, and the range of application can be expanded.

The embodiments of the present invention have been described in detail above, but these are merely examples.
By the specific description in the above embodiment,
It is not to be construed as limiting.

For example, in the first to third embodiments, the upper case member 14 and the lower case member 16 can be formed integrally.

Further, the damper body may be constituted by an oil damper instead of the sliding resistance type as illustrated. Further, when a large resistance force can be obtained as compared with the rotational speed as in an oil damper or the like, there is no need to provide a planetary gear mechanism as a speed increasing means, and the oil is provided below the cam member in the axial direction. An oil-type damper may be directly provided by a cam member to provide an oil-type damper. At that time, a spring for returning the cam and a one-way clutch are employed as necessary.

Further, as the one-way clutch means,
The present invention is not limited to the example structure employing the coil spring, and for example, a Kahn-type knock mechanism such as that employed in a knock-type ballpoint pen may be employed.

Further, by providing an urging means for urging the sliding member 26 inward in the radial direction, the sliding member 26 is always moved to the initial position when a large centrifugal force is not applied to the sliding member 26. It is also possible to make it located in.

The sliding member 26 may be superposed on the bottom wall surface of the lower case member 16 and supported in a sliding contact state.

Further, in the second embodiment, the circular projection 50 of the cam member 20 is fixed to the cylindrical portion 70 of the first planetary gear member 54 by bonding or the like, but these are integrally formed. It is also possible.

In addition, although not enumerated one by one, the present invention
Based on the knowledge of those skilled in the art, various changes, modifications, improvements, and the like can be made, and unless such embodiments depart from the spirit of the present invention.
Both are included in the scope of the present invention,
Needless to say.

[0075]

As is apparent from the above description, in the speed governing device having the structure according to the present invention, the use of the cam member allows the rotation resistance acting according to the rotation position of the rotating body. The force can be easily adjusted with a large degree of freedom in tuning, and the rotation of the rotating body at an excessive speed can be suppressed, and a smooth rotating operation of the rotating body can be realized.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing an initial state of a speed governor as a first embodiment of the present invention.

FIG. 2 is an exploded view of the governing device in FIG. 1;

FIG. 3 is a longitudinal sectional view showing a state after a pushing operation of a push rod in the governing device in FIG. 1;

FIG. 4 is a side view showing a rice cooker equipped with the speed control device in FIG. 1 in a lid closed state.

FIG. 5 is a side view showing the rice cooker shown in FIG. 4 in a lid open state.

FIG. 6 is an exploded explanatory view of a governing device according to a second embodiment of the present invention.

FIG. 7 is an exploded explanatory view of a governing device as a third embodiment of the present invention.

[Explanation of symbols]

 10, 124, 126 Governor 14 Upper case member 16 Lower case member 18 Cover 20, 130 Cam member 26 Sliding material 46, 138 Cam surface 118 Main body 120 Lid

Claims (7)

[Claims] 1. A rotation speed of a rotating body is adjusted by being assembled between a supporting body and a rotating body attached to the supporting body so as to be relatively rotatable around a rotation center axis. A speed controller, a case member fixedly attached to one of the support member and the rotating member, a cam member rotatably supported by the case member about one axis, and a cam surface of the cam member. A driving body which is slidably abutted and arranged to reciprocate with the relative rotation of the support and the rotating body, thereby exerting a driving force on the cam member to rotate the cam member. A damper body supported by one of the supporter and the rotating body together with the cam member; and a damper body supported by one of the rotating body and the cam member. Intervening Te,
By transmitting the rotational movement of the cam member to the rotational resistor of the damper main body, the rotational resistance of the damper main body is relatively reduced between the support and the rotating body via the cam member and the prime mover. A rotational force transmitting means for exerting a rotational resistance force as a rotational resistance force. 2. A cam member having a cam surface having a cam surface inclined in an axial direction and extending in a circumferential direction at one end surface of a rotation center shaft, and the rotation center shaft of the cam member is connected to the rotation center shaft. 2. The speed adjusting device for a rotating body according to claim 1, wherein the speed adjusting apparatus is disposed at right angles to a rotation center axis of the moving body. 3. A sliding contact cylinder having a sliding member which spreads due to centrifugal force accompanying rotation about a central axis as the rotation resistor, and wherein the sliding member is spaced apart on the outer peripheral side of the central axis. The speed governing device for a rotating body according to claim 1 or 2, wherein the damper main body is constituted by a governor-type damper configured to obtain a rotational resistance by sliding on an inner peripheral surface. 4. The rotational force transmitting means according to claim 1, further comprising a speed increasing mechanism for increasing the rotational movement of the cam member and transmitting the rotational movement to a rotation resistor of the damper body. A speed governing device for a rotating body according to claim 1. 5. The method according to claim 5, wherein the cam member and the damper main body are arranged on the same central axis, and at least one planetary gear mechanism is arranged on the same central axis between the cam member and the damper main body. The speed adjusting device for a rotating body according to claim 4, wherein the speed increasing mechanism is formed by a planetary gear mechanism. 6. An urging means for exerting a returning force on the cam member to return the cam member to an initial rotation position, wherein the cam member is moved in accordance with a relative reciprocating rotation operation of the support member and the rotating member. The speed control device for a rotating body according to any one of claims 1 to 5, wherein the member is reciprocally rotated about a central axis by a predetermined angle. 7. A one-way clutch means disposed on a rotational force transmission path between the cam member and the damper main body to transmit a rotational force of the cam member in only one direction to the damper main body. Item 7. A speed adjusting device for a rotating body according to any one of Items 1 to 6.