JP2016148440A - Fluid damper device, driving device, and apparatus with damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid damper device, a driving device, and an apparatus with a damper, capable of applying a load in any of rotation in a first direction and rotation in a second direction of a rotor shaft, and changing the load applied to the rotor shaft in the rotation in the second direction.SOLUTION: In a fluid damper device 10, a damper chamber 11 filled with a fluid 12, is formed between an inner peripheral wall 210 of a damper case 20 and a rotor shaft 40. A valve element 50 is supported on the rotor shaft 40, and the valve element 50 forms a gap G with the inner peripheral wall 210 when the rotor shaft 40 is rotated in a second direction B, and narrows the gap G when the rotor shaft 40 is rotated in a first direction A. An inner diameter of the inner peripheral wall 210 is various in the circumferential direction, and to the rotor shaft 40, the load corresponding to a size of the gap G is added from the fluid 12 in both of rotation in the first direction A and rotation in the second direction B.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a fluid damper device, a drive device including the fluid damper device, and a damper-equipped device including the drive device.

  In the fluid damper device in which a fluid is filled between the damper case and the rotor, a damper chamber is formed between the damper case and the cylindrical damper case in which the partitioning convex portion protrudes radially inward from the inner peripheral wall. A rotor shaft, and the damper chamber is filled with a fluid such as oil. A valve body is supported on the rotor shaft, and when the rotor shaft rotates in the first direction around the axis, the valve body is in a closed posture, so that a large load is applied to the rotor shaft. On the other hand, when the rotor shaft rotates in the second direction opposite to the first direction, the valve body is in the open posture, so that the fluid passes therethrough, so that only a small load is applied to the rotating shaft (Patent Document 1). reference). In such a fluid damper device, for example, a rotor shaft is connected to a toilet seat of a Western-style toilet, and the rotor shaft rotates in the first direction when the toilet seat changes from a standing posture (open posture) to a flat posture (closed posture). For this reason, it is possible to prevent the toilet seat from being tilted suddenly by its own weight due to the load applied to the rotor shaft.

JP 2010-151306 A

  For a fluid damper device, when the rotor shaft rotates in either the first direction or the second direction, a sufficient load is applied to the rotor shaft and the rotor shaft rotates in the second direction. There is a demand for switching the magnitude of the load applied to the rotor shaft according to the angular position of the rotor shaft.

  For example, when the toilet seat is driven in the opening direction by a driving device using a motor, the force to rotate the toilet seat in the closing direction due to the weight of the toilet seat changes depending on the posture of the toilet seat. The force to rotate the toilet seat in the closing direction is reduced. For this reason, since the rotational speed of the toilet seat increases, in order to mitigate the change in rotational speed when the toilet seat is driven in the opening direction, the posture of the toilet seat must be detected, and the motor must be controlled based on the detection result. I must. On the other hand, in a drive device using a motor, the rotor shaft of the fluid damper device is connected to the toilet seat, and the load applied to the rotor shaft in the fluid damper device is changed according to the posture of the toilet seat (angular position of the rotor shaft). If this is done, it is possible to alleviate changes in the rotational speed of the toilet seat only by driving the motor at a constant current, but such effects cannot be obtained with conventional fluid damper devices.

  In view of the above problems, the problem of the present invention is that a load can be applied both during rotation in the first direction and during rotation in the second direction of the rotor shaft, and during rotation in the second direction, An object of the present invention is to provide a fluid damper device capable of changing a load applied to a rotor shaft, a driving device including the fluid damper device, and a damper-equipped device including the driving device.

In order to solve the above problems, a fluid damper device according to the present invention includes a cylindrical damper case having an inner peripheral wall and a partition convex portion protruding radially inward from the inner peripheral wall, and an inner side of the damper case. A rotor shaft that is inserted and forms a damper chamber between the damper case, and a valve body that is supported by the rotor shaft and projects radially outward from the rotor shaft and in a first direction around the axis of the rotor shaft; The valve body is inclined in the first direction when the rotor shaft rotates in the second direction opposite to the first direction. A gap is formed between the body and the inner peripheral wall, and when the rotor shaft rotates in the first direction, the inner shaft is inclined in the second direction so that the gap is narrower than that in the second direction. Has different inner diameters in the circumferential direction. , The rotor shaft, at any time of the rotation of the rotating time and the second direction of the first direction, the load corresponding to the magnitude of the gap is equal to or applied from the fluid.

  In the present invention, the valve element supported by the rotor shaft protrudes radially outward from the rotor shaft and in a first direction around the axis of the rotor shaft. For this reason, when the rotor shaft rotates in the second direction opposite to the first direction, the valve body tilts in the first direction to form a gap between the valve body and the inner peripheral wall, and the rotor shaft is When rotating in the first direction, the valve body tilts in the second direction and narrows the gap as compared with the rotation in the second direction. During such rotation, a load corresponding to the size of the gap is applied to the rotor shaft from the fluid during both rotation in the first direction and rotation in the second direction. Here, since the inner peripheral walls have different inner diameters in the circumferential direction, the size of the gap changes depending on the angular position of the rotor shaft when the rotor shaft rotates in the second direction, so that the rotor shaft receives from the fluid. The magnitude of the load can be changed.

  In the present invention, it is possible to employ a configuration in which the inner diameter of the inner peripheral wall monotonously decreases in the second direction in the range of movement angles of the valve body when the rotor shaft rotates.

  In the present invention, it is possible to adopt a configuration in which the inner diameter of the inner peripheral wall is switched in two or more stages in the circumferential direction in the range of movement angle of the valve body when the rotor shaft rotates.

  In this invention, you may employ | adopt the structure which the internal diameter of the said internal peripheral wall is changing continuously in the circumferential direction in the movement angle range of the said valve body when the said rotor shaft rotates.

  In the present invention, when the rotor shaft rotates in the first direction, it is preferable that the valve body is in contact with the inner peripheral wall at least at an angular position where the gap is the narrowest.

  The fluid damper device to which the present invention is applied can be used in a drive device, and in such a drive device, a configuration in which a rotation drive unit using a motor as a drive source is provided on the rotor shaft can be adopted. .

  In the present invention, it is preferable that constant current drive or constant voltage drive is performed in the motor regardless of the angular position of the rotor shaft during the period of driving the rotor shaft. According to this configuration, even when the motor is driven at a constant current, the change in the rotational speed of the rotor shaft can be mitigated.

The drive device to which the present invention is applied can be used in a damper-equipped device, and in the damper-equipped device, a movable member that switches between a flat posture and a standing posture as the rotor shaft rotates is connected to the rotor shaft. The movable member switches from the standing posture to the flat posture when the rotor shaft rotates in the first direction, and from the flat posture when the rotor shaft rotates in the second direction. A configuration that switches to the standing posture can be employed. According to such a configuration, when the movable member starts to rise from the flat posture when the rotor shaft rotates in the second direction, a large load due to the dead weight of the movable member is applied to the rotor shaft, whereas when the movable member approaches the standing posture, In the fluid damper device, a load applied from the fluid to the rotor shaft increases. Therefore, the change in speed when the rotor shaft rotates in the second direction and the movable member rotates from the flat posture to the standing posture can be mitigated.

  In the present invention, the movable member is, for example, a toilet seat of a Western-style toilet.

  In the present invention, the valve element supported by the rotor shaft protrudes radially outward from the rotor shaft and in a first direction around the axis of the rotor shaft. For this reason, when the rotor shaft rotates in the second direction opposite to the first direction, the valve body tilts in the first direction to form a gap between the valve body and the inner peripheral wall, and the rotor shaft is When rotating in the first direction, the valve body tilts in the second direction and narrows the gap as compared with the rotation in the second direction. During such rotation, a load corresponding to the size of the gap is applied to the rotor shaft from the fluid during both rotation in the first direction and rotation in the second direction. Here, since the inner peripheral walls have different inner diameters in the circumferential direction, the size of the gap changes depending on the angular position of the rotor shaft when the rotor shaft rotates in the second direction, so that the rotor shaft receives from the fluid. The magnitude of the load can be changed.

It is explanatory drawing of the western style toilet unit using the drive device provided with the fluid damper apparatus to which this invention is applied. It is a perspective view of the drive device to which the present invention is applied. It is sectional drawing of the fluid damper apparatus to which this invention is applied. It is explanatory drawing of the rotor axis | shaft of the fluid damper apparatus to which this invention is applied. It is explanatory drawing which shows the internal structure of the damper chamber of the fluid damper apparatus to which this invention is applied. It is explanatory drawing of the internal diameter of the internal peripheral wall of the 1st cylindrical part of the fluid damper apparatus to which this invention is applied. In the fluid damper device to which this invention is applied, it is explanatory drawing of the clearance gap between a valve body and an inner peripheral wall when a rotor shaft rotates to a 2nd direction. It is explanatory drawing which shows typically the relationship between the attitude | position (angular position of a rotor shaft) of the toilet seat and the magnitude | size of load, etc. in the fluid damper apparatus to which this invention is applied. It is explanatory drawing of the modification 1 of the internal diameter of the internal peripheral wall of the 1st cylindrical part of the fluid damper apparatus to which this invention is applied. It is explanatory drawing of the modification 2 of the internal diameter of the internal peripheral wall of the 1st cylindrical part of the fluid damper apparatus to which this invention is applied.

  With reference to the drawings, a fluid damper device according to an embodiment of the present invention, a drive device including the fluid damper device, and a damper-equipped device including the drive device will be described. Moreover, in the following description, it demonstrates centering on the case where the apparatus with a damper is a western style toilet. In the following description, the direction in which the rotor shaft 40 extends is defined as the axis L direction, and in the axis L direction, the side opposite to the side where the rotor shaft 40 protrudes from the damper case 20 is defined as one side L1. The side where the shaft 40 protrudes from the damper case 20 will be described as the other side L2.

(Overall configuration of device with damper and fluid damper device 10)
FIG. 1 is an explanatory diagram of a Western-style toilet unit 100 using a drive device 1 including a fluid damper device 10 to which the present invention is applied. FIG. 2 is a perspective view of the drive device 1 to which the present invention is applied. FIGS. 2A and 2B are a perspective view of the drive device 1 as viewed from the other side L2 in the axis L direction, and the drive device. It is the disassembled perspective view seen from the other side L2 of the axis line L direction.

A Western toilet unit 100 shown in FIG. 1 includes a Western toilet 2 (equipment with a damper) and a water tank 3. The western toilet 2 includes a toilet body 4, a toilet seat 5 (movable member), a toilet lid 6, a unit cover 7, and the like. A drive device 1 to be described later is built in the unit cover 7 as a toilet seat and a toilet lid, and the toilet seat 5 and the toilet lid 6 are respectively connected to the toilet body 4 via the drive device 1. Here, the drive device 1 connected to the toilet seat 5 and the drive device 1 connected to the toilet lid 6 can be of the same configuration, but in the following description, the drive connected to the toilet seat 5 The apparatus 1 will be mainly described.

  As shown in FIG. 2, the drive device 1 includes a rotation drive unit 8 that uses a motor 80 as a drive source on one side L1 and a rotor shaft 40 that is rotationally driven by the rotation drive unit 8. Reference numeral 40 denotes the fluid damper device 10. The drive device 1 has a drive unit case 99 that covers the rotation drive unit 8, and the fluid damper device 10 has a damper case 20 that covers the rotor shaft 40. In the fluid damper device 10, the third shaft portion 43 of the rotor shaft 40 protrudes from the damper case 20 to the other side L2, and the third shaft portion 43 is connected to the toilet seat 5 shown in FIG. The third shaft portion 43 has a flat surface 431 facing each other, and the flat surface 431 prevents the toilet seat 5 from being idle around the third shaft portion 43. In the present embodiment, the motor 80 is a motor that can rotate in both directions, such as a DC motor with a brush, and is a type of motor whose rotational speed changes with a load.

(Configuration of the rotation drive unit 8)
The rotation drive unit 8 includes a motor 80 and a speed reduction wheel train 90 that transmits the rotation of the motor 80 to the rotor shaft 40. The speed reduction wheel train 90 includes the first car 91, the second car 92, and the third car. A car 93, a fourth car 94, and a fifth car 95 are provided. The first wheel & pinion 91 has a large-diameter gear 911 that meshes with the motor pinion 85 and a small-diameter gear 912. The second wheel & pinion 92 has a large-diameter gear 921 that meshes with the small-diameter gear 912 and a small-diameter gear 922. The third wheel & pinion 93 has a large-diameter gear 931 that meshes with the small-diameter gear 922 and a small-diameter gear 932. The fourth wheel & pinion 94 has a large-diameter gear 941 that meshes with the small-diameter gear 932 and a small-diameter gear 942. The fifth wheel & pinion 95 is attached to the end of the rotor shaft 40 on one side L1 and meshes with the small-diameter gear 942.

(Configuration of fluid damper device 10)
FIG. 3 is a cross-sectional view of a fluid damper device 10 to which the present invention is applied, and FIGS. 3A and 3B are cross-sectional views of the fluid damper device 10 cut along a plane orthogonal to the axis L. 3 is a cross-sectional view of the fluid damper device 10 cut along a plane along the axis L. FIG. FIG. 4 is an explanatory view of the rotor shaft 40 of the fluid damper device 10 to which the present invention is applied. FIGS. 4A and 4B are perspective views in a state where the valve body 50 is supported by the rotor shaft 40. FIG. 2 is a perspective view of the state in which the valve body 50 is removed from the rotor shaft 40.

  As shown in FIGS. 2 and 3, the fluid damper device 10 includes a rotor shaft 40 extending in the direction of the axis L, and a circle that rotatably supports the vicinity of the end portion on one side L1 of the rotor shaft 40 around the axis L. A plate-like first bearing member 61, a second bearing member 66 that supports the vicinity of the end of the other side L <b> 2 of the rotor shaft 40 so as to be rotatable around the axis L, and a damper case 20 disposed around the rotor shaft 40. And have.

  The damper case 20 has a first cylindrical portion 21 that surrounds the rotor shaft 40 and a second cylindrical portion 22 that surrounds the first cylindrical portion 21 on the outside in the radial direction. , Projecting from the first cylindrical portion 21 to the one side L1. The first cylindrical portion 21 and the second cylindrical portion 22 are connected via an annular first end plate portion 23 on the other side L2. Further, on the inner side of the first cylindrical portion 21, an annular second end plate portion 24 projecting radially inward from the first cylindrical portion 21 is provided in the vicinity of the end portion on the one side L <b> 1. The rotor shaft 40 is disposed so as to penetrate the central hole 240 of the plate portion 24. Inside the first cylindrical portion 21, a step portion 27 is formed at the end of the other side L <b> 2, and the cylindrical portion 661 of the second bearing member 66 is held using the step portion 27.

An assist spring 70 composed of a coil spring is disposed between the first cylindrical portion 21 and the second cylindrical portion 22. One end (not shown) of the assist spring 70 is held by the damper case 20, and the other end (not shown) is held by the fifth gear 95. The assist spring 70 exerts an urging force in a direction to erect the toilet seat 5 in a state where the toilet seat 5 is flattened.

  As shown in FIGS. 2, 3, and 4, the rotor shaft 40 has a first shaft portion 41 having a round bar shape at a substantially central portion in the direction of the axis L. An end portion adjacent to the first shaft portion 41 on the one side L1 is a second shaft portion 42 in which a flat surface 421 is formed at a position facing each other. A fifth wheel & pinion 95 is fixed to the second shaft portion 42.

  In the rotor shaft 40, the end portion adjacent to the first shaft portion 41 on the other side L2 is a third shaft portion 43 in which a flat surface 431 is formed at a position facing each other. A large diameter portion 44 having a larger diameter than the first shaft portion 41 is formed between the first shaft portion 41 and the third shaft portion 43, and the large diameter portion 44 is a cylinder of the second bearing member 66. It is located inside the portion 661. A circumferential groove 441 is formed in the large diameter portion 44, and an O-ring 451 is attached to the circumferential groove 441.

  The first shaft portion 41 protrudes from the second end plate portion 24 to the one side L1. In the first shaft portion 41, a first bearing member 61 is disposed at a location adjacent to the first cylindrical portion 21 on one side L 1, and between the first bearing member 61 and the second end plate portion 24. The O-ring 452 is attached.

  In this way, the damper chamber 11 is partitioned between the inner peripheral wall 210 of the first cylindrical portion 21 and the outer peripheral surface 410 of the first shaft portion 41 of the rotor shaft 40 inside the first cylindrical portion 21. The damper chamber 11 is filled with a fluid 12 such as oil.

(Configuration of damper chamber 11)
FIG. 5 is an explanatory view showing the internal configuration of the damper chamber 11 of the fluid damper device 10 to which the present invention is applied, and FIGS. 5A and 5B each show the toilet seat 5 in a prone posture as an upright posture. An explanatory view showing a state in the damper chamber 11 when the rotor shaft 40 is driven in the second direction B (opening direction), and the rotor in the first direction A (closing direction) in which the toilet seat 5 in the standing posture is in a flat posture. It is explanatory drawing which shows the mode in the damper chamber 11 when the axis | shaft 40 is driven.

  As shown in FIGS. 3 and 5, the damper chamber 11 has a plate-like partition projection 26 protruding radially inward from the inner peripheral wall 210 of the first cylindrical portion 21 of the damper case 20. The front end portion 261 of the convex portion 26 is in contact with the outer peripheral surface 410 of the first shaft portion 41 of the rotor shaft 40. In this embodiment, the partitioning convex portions 26 are provided at two locations that are separated by 180 ° around the axis L. The partition convex portion 26 extends in the damper chamber 11 over the entire axis L direction, and the damper chamber 11 is partitioned into two chambers.

  As shown in FIGS. 3, 4, and 5, the valve body supporting convex portions 46 are formed on the outer peripheral surface 410 of the first shaft portion 41 of the rotor shaft 40 at two locations that are separated by 180 ° around the axis L. The valve body 50 is supported on each of the two valve body support convex portions 46. Each of the two valve body supporting convex portions 46 extends from the large diameter portion 44 to a position close to the second end plate portion 24 in the axis L direction.

The radially outer portion of the valve body supporting convex portion 46 has a first convex portion 461 projecting radially outward and a diameter adjacent to the first convex portion 461 in the first direction A around the axis L. A second convex portion 462 that protrudes outward in the direction is formed, and a groove 460 is formed between the first convex portion 461 and the second convex portion 462. The groove 460 has an arc shape whose inner peripheral surface is curved over an angular range exceeding about 180 °, and the valve body 50 is supported by the groove 460. The first convex portion 461 is wider in the circumferential direction than the second convex portion 462, and the tip side of the first convex portion 461 sticks out in the first direction A. In addition, the distal end portion of the first convex portion 461 is located radially outside the distal end portion of the second convex portion 462. Further, the valve body supporting convex portion 46 has a circumferential width that is narrower on the radially inner side than on the radially outer side.

  The valve body 50 includes a base 51 having a substantially circular cross section that extends in the axial direction parallel to the axis L, and a tip 52 that protrudes radially outward from the base 51 in the first direction A. The base 51 is supported so as to be rotatable about an axis parallel to the axis L in a groove 460 between the first convex 461 and the second convex 462, and the tip 52 is diameter-adjusted by the second convex 462. It inclines in the 1st direction A so that it may cover from the direction outer side. In addition, the radially outer portion of the tip portion 52 is located on the radially outer side from the first convex portion 461 and the second convex portion 462.

(basic action)
In the fluid damper device 10 of the present embodiment, when the toilet seat 5 in the flat posture is driven in a direction (opening direction) in which the toilet seat 5 is in the standing posture, the rotor shaft 40 is moved around the axis L as shown in FIG. It rotates in the second direction B opposite to the first direction A. For this reason, the front-end | tip part 52 of the valve body 50 receives the fluid pressure from the fluid 12, inclines in the 1st direction A centering on the base 51, and the front-end | tip part 52 moves toward the 2nd convex part 462 side. As a result, a gap G is formed between the radially outer portion of the distal end portion 52 and the inner peripheral wall 210 of the first cylindrical portion 21 of the damper case 20. Therefore, in the valve body 50 and the valve body supporting convex portion 46, the movement of the fluid in the first direction A is restricted by the gap G, so that a load (drag) is applied to the rotor shaft 40. However, the gap G when the rotor shaft 40 rotates around the axis L in the second direction B is wider than the gap G when the rotor shaft 40 rotates around the axis L in the first direction A, as will be described later. Therefore, the load (drag) when the rotor shaft 40 rotates about the axis L in the second direction B is smaller than the load (drag) when the rotor shaft 40 rotates about the axis L in the first direction A.

  Next, as illustrated in FIG. 5B, when the toilet seat 5 in the standing posture is driven in a direction (closed direction) in which the toilet seat 5 is in a flat posture, the rotor shaft 40 rotates in the first direction A around the axis L. . For this reason, the front-end | tip part 52 of the valve body 50 receives the fluid pressure from the fluid 12, inclines in the 2nd direction B centering on the base 51, and the front-end | tip part 52 moves toward the 1st convex part 461 side. As a result, the radially outer portion of the tip portion 52 moves radially outward, so that the gap G between the radially outer portion of the tip portion 52 and the inner peripheral wall 210 of the first cylindrical portion 21 of the damper case 20 is The rotor shaft 40 becomes narrower than the gap G when the rotor shaft 40 rotates around the axis L in the second direction B. In this embodiment, when the rotor shaft 40 rotates around the axis L in the first direction A, the radially outer portion of the tip 52 is the inner peripheral wall 210 of the first cylindrical portion 21 of the damper case 20 over the entire angular range. And the gap G becomes zero. Accordingly, the movement of the fluid 12 in the second direction B is prevented between the valve body 50 and the inner peripheral wall 210, and as a result, the rotor shaft 40 rotates about the axis L in the second direction B. A load (drag) greater than the load (drag) is applied. Even in such a case, a slight gap is left between the end portion of the valve body 50 and the second end plate portion 24 on the one side L1 from the valve body 50. Therefore, the movement of the fluid in the second direction B is slightly allowed on the one side L1 from the valve body 50. Therefore, the rotor shaft 40 is allowed to rotate in the first direction A at a low speed although a large load is applied.

(Configuration of inner peripheral wall 210)
6 is an explanatory diagram of the inner diameter of the inner peripheral wall 210 of the first cylindrical portion 21 of the fluid damper device 10 to which the present invention is applied. In FIG. 6, the change in the inner peripheral wall 210 in the circumferential direction is exaggerated. It is shown. FIG. 7 is an explanatory view of the gap G between the valve body 50 and the inner peripheral wall 210 when the rotor shaft 40 rotates in the second direction B in the fluid damper device 10 to which the present invention is applied. (B) is explanatory drawing when rotation starts the toilet seat 5 which is in a prone posture toward a standing posture, and explanatory drawing when it has finished reaching a standing posture. FIG. 8 is an explanatory view schematically showing the relationship between the posture of the toilet seat 5 (angular position of the rotor shaft 40) and the magnitude of the load in the fluid damper device 10 to which the present invention is applied, and FIG. (B), (c), (d), and (e) are explanatory views showing the relationship between the posture of the toilet seat 5 and the rotational force caused by the gravity applied to the toilet seat 5, and the relationship between the angular position and the inner diameter of the inner peripheral wall 210. Explanatory diagram showing the relationship, explanatory diagram showing the relationship between the angular position of the rotor shaft 40 and the load applied from the fluid 12 to the rotor shaft 40, the relationship between the posture of the toilet seat 5 and the rotational speed when the toilet seat 5 is driven in the opening direction FIG. 5 is an explanatory diagram illustrating the relationship between the posture of the toilet seat 5 and the rotational speed when the toilet seat 5 is driven in the closing direction.

As shown in FIG. 6, in the fluid damper device 10 of the present embodiment, the inner diameter of the inner peripheral wall 210 of the first cylindrical portion 21 is different in the circumferential direction. In the present embodiment, the inner diameter of the inner peripheral wall 210 monotonously decreases in the second direction B in the range of movement angles of the valve body 50 when the rotor shaft 40 rotates. Further, the inner diameter of the inner peripheral wall 210 is switched in two steps in the circumferential direction in the range of the movement angle of the valve body 50 when the rotor shaft 40 rotates. In this embodiment, when the angle position where the valve body 50 is located when the toilet seat 5 is in the flat posture is 0 °, and the angle position where the valve body 50 is located when the toilet seat 5 is in the standing posture is 90 °, The movable range of the toilet seat 5 (movement angle range of the valve body 50) is set to about 110 °. Here, the inner peripheral wall 210 has a radius r1 in an angle range θ1 of about 70 ° to about 110 °, and a radius r2 in an angle range θ2 of 0 ° to about 45 °, and the radii r1 and r2 have the following relationship: r1 <r2
It has become. Further, the inner peripheral wall 210 continuously changes from the radius r2 to the radius r1 in an angle range of about 45 ° to about 70 °.

  Accordingly, the gap G between the valve body 50 and the inner peripheral wall 210 when the rotor shaft 40 starts to rotate in the second direction B and starts to rotate the toilet seat 5 in the flat posture toward the standing posture (FIG. 7A). Therefore, the gap G (see FIG. 7B) between the valve body 50 and the inner peripheral wall 210 when the toilet seat 5 has reached the standing posture is narrowed. Therefore, as will be described below with reference to FIG. 8, in the fluid damper device 10 and the drive device 1 of the present embodiment, when the toilet seat 5 is driven from the flat posture to the standing posture, the change in the moving speed of the toilet seat 5 is changed. Can be relaxed.

  First, as shown in FIG. 8A, the relationship between the posture (angle) of the toilet seat 5 and the rotational force caused by the gravity applied to the toilet seat 5, when the toilet seat 5 is in the flat posture, the rotation caused by gravity. The force is the largest, and the rotational force due to the gravity of the toilet seat 5 becomes smaller as it shifts to the standing posture.

  Therefore, as shown by the solid line V1b in FIG. 8D, when the motor 80 is driven at a constant current, the rotational speed of the toilet seat 5 (rotor shaft 40) is 0 ° when the load from the fluid damper device 10 is not taken into consideration. It becomes faster until it shifts to 90 °.

  Here, in the fluid damper device 10, the inner diameter of the inner peripheral wall 210 becomes smaller in the middle of the transition from 0 ° to 90 ° as shown in FIG. As indicated by the solid line Db, the load applied from the fluid 12 to the rotor shaft 40 increases in the fluid damper device 10 while the toilet seat 5 is in the standing posture from the flat posture. Therefore, even when the motor 80 is driven at a constant current, when the load from the fluid damper device 10 is taken into consideration, the rotational speed of the toilet seat 5 (rotor shaft 40) is 0 as shown by the solid line V2b in FIG. Changes in the rotational speed of the toilet seat 5 (rotational speed of the rotor shaft 40) can be reduced during the period from 0 ° to 90 °.

When the toilet seat 5 changes from the standing posture to the flat posture, the radially outer portion of the distal end portion 52 of the valve body 50 comes into contact with the inner peripheral wall 210 of the first cylindrical portion 21 of the damper case 20 and the gap G is 0. Therefore, as shown by the solid line Da in FIG. 8C, the load applied from the fluid 12 to the rotor shaft 40 is constant. Therefore, when the motor 80 is driven at a constant current and the toilet seat 5 is driven from the standing posture to the flat posture, the speed when the load from the fluid damper device 10 is not taken into consideration is shown by a solid line V1a in FIG. As shown by the solid line V2a in FIG. 8E, the speed when the load from the fluid damper device 10 is taken into consideration, as shown by the solid line V2a, the rotational speed of the toilet seat 5 (the rotational speed of the rotor shaft 40). ) Will be slower overall.

(Main effects of this form)
As described above, in the fluid damper device 10 and the drive device 1 of the present embodiment, the valve body 50 supported by the rotor shaft 40 is the first outside the rotor shaft 40 in the radial direction and around the axis L line of the rotor shaft 40. Projects in direction A. For this reason, when the rotor shaft 40 rotates in the second direction B opposite to the first direction A, the valve body 50 is inclined in the first direction A and the gap G is formed between the valve body 50 and the inner peripheral wall 210. When the rotor shaft 40 rotates in the first direction A, the valve body 50 tilts in the second direction B and narrows the gap G when rotating in the second direction B. During the rotation, a load corresponding to the size of the gap G is applied to the rotor shaft 40 from the fluid 12 during both the rotation in the first direction A and the rotation in the second direction B. Here, since the inner peripheral wall 210 has different inner diameters in the circumferential direction, the size of the gap G changes when the rotor shaft 40 rotates in the second direction B, so that the rotor shaft 40 receives from the fluid 12. The magnitude of the load changes.

  For this reason, when the toilet seat 5 (movable member) that switches between the prone posture and the standing posture with the rotation of the rotor shaft 40 is connected to the rotor shaft 40, the rotor shaft 40 rotates in the second direction B and When 5 rises from the flat posture, a large load due to the weight of the toilet seat 5 is applied to the rotor shaft 40, while when approaching the standing posture, the load applied from the fluid 12 to the rotor shaft 40 in the fluid damper device 10 increases. Accordingly, it is possible to mitigate a change in speed when the rotor shaft 40 rotates in the second direction B and the toilet seat 5 rotates from the flat posture to the standing posture. Therefore, when the rotor shaft 40 is driven in the second direction B, the rotor shaft 40 can be detected without adopting a complicated circuit configuration in which the angular position of the rotor shaft 40 is detected and the magnitude of the drive current for the motor 80 is switched. The change in the rotational speed of 40 can be mitigated. Therefore, it is possible to avoid a situation in which the toilet seat 5 rotates rapidly as it approaches the standing posture.

(Modification of inner peripheral wall 210)
FIG. 9 is an explanatory diagram of a first modification of the inner diameter of the inner peripheral wall 210 of the first cylindrical portion 21 of the fluid damper device 10 to which the present invention is applied. FIG. 10 is an explanatory diagram of a second modification of the inner diameter of the inner peripheral wall 210 of the first cylindrical portion 21 of the fluid damper device 10 to which the present invention is applied. 9 and 10, the change in the circumferential direction of the inner diameter of the inner peripheral wall 210 is exaggerated.

In the embodiment described above, the inner diameter of the inner peripheral wall 210 of the first cylindrical portion 21 has been switched to two stages. However, as shown in FIG. 9, the inner diameter of the inner peripheral wall 210 of the first cylindrical section 21 has two or more stages. You may employ | adopt the structure switched. For example, the inner diameter of the inner peripheral wall 210 of the first cylindrical portion 21 is switched in three stages. More specifically, in the angle range θ1, the radius of the inner peripheral wall 210 of the first cylindrical portion 21 is r1, and in the angle range θ2, the radius of the inner peripheral wall 210 of the first cylindrical portion 21 is r2. At θ3, the radius of the inner peripheral wall 210 of the first cylindrical portion 21 is r3. Here, the radii r1, r2, and r3 have the following relationship: r1 <r3 <r2
have.

  A configuration in which the inner diameter of the inner peripheral wall 210 of the first cylindrical portion 21 is continuously switched may be employed. For example, as shown in FIG. 10, the inner diameter of the inner peripheral wall 210 of the first cylindrical portion 21 may continuously change to a radius r1, a radius r3, and a radius r2.

[Other embodiments]
In the above embodiment, when the rotor shaft 40 rotates in the first direction A around the axis L, the radially outer portion of the tip 52 contacts the inner peripheral wall 210 of the first cylindrical portion 21 of the damper case 20, Although the gap G was 0, the inner diameter of the inner peripheral wall 210 was only in a small angle range, the radially outer portion of the tip 52 contacted the inner peripheral wall 210 of the first cylindrical portion 21 of the damper case 20, and the other In the angle range, the gap G between the radially outer portion of the tip 52 and the inner peripheral wall 210 of the first cylindrical portion 21 of the damper case 20 may not be zero. In the above embodiment, the motor 80 is driven at a constant current regardless of the angular position of the rotor shaft 40 during the period during which the rotor shaft 40 is being driven. In the middle, a constant voltage driven configuration may be adopted regardless of the angular position of the rotor shaft 40.

DESCRIPTION OF SYMBOLS 1 ... Drive device, 2 ... Western style toilet, 4 ... Toilet body, 5 ... Toilet seat, 6 ... Toilet lid, 7 ... Unit cover, 8 ... Rotary drive part, 10 ... Fluid damper device, 11 ..Damper chamber, 12 ..Fluid, 20 ..Damper case, 21 ..First cylindrical portion, 22 ..Second cylindrical portion, 26 ..Convex convex portion, 40 ..Rotor shaft, 41. 1 shaft part, 46 .. convex part for supporting valve body, 50 .. valve body, 51 .. base part, 52 .. tip part, 70 .. assist spring, 80 .. motor, 90. ..Western-style toilet unit, 460 ..groove, 461 ..first convex portion, 462 ..second convex portion, A ..first direction, B .. second direction, G ..gap, L,.

Claims (9)

A cylindrical damper case having an inner peripheral wall and a partitioning convex portion protruding radially inward from the inner peripheral wall;
A rotor shaft inserted inside the damper case and constituting a damper chamber between the damper case;
A valve body supported by the rotor shaft and projecting radially outward from the rotor shaft and in a first direction around the axis of the rotor shaft;
Fluid filled in the damper chamber;
Have
When the rotor shaft rotates in the second direction opposite to the first direction, the valve body is inclined in the first direction to form a gap between the valve body and the inner peripheral wall, When the rotor shaft rotates in the first direction, it tilts in the second direction and narrows the gap from the time of rotation in the second direction,
The inner peripheral wall has a different inner diameter in the circumferential direction, and the rotor shaft has a load corresponding to the size of the gap both when rotating in the first direction and when rotating in the second direction. Is added from the fluid.   2. The fluid damper device according to claim 1, wherein an inner diameter of the inner peripheral wall monotonously decreases in the second direction in a range of movement angles of the valve body when the rotor shaft rotates.   3. The fluid damper device according to claim 2, wherein an inner diameter of the inner peripheral wall is switched in two or more stages in a circumferential direction in a range of movement angles of the valve body when the rotor shaft rotates.   3. The fluid damper device according to claim 2, wherein an inner diameter of the inner peripheral wall continuously changes in a circumferential direction in a range of movement angles of the valve body when the rotor shaft rotates.   5. The valve body according to claim 2, wherein when the rotor shaft rotates in the first direction, the valve body is in contact with the inner peripheral wall at least at an angular position where the gap is the narrowest. The fluid damper device described. A drive device comprising the fluid damper device according to any one of claims 2 to 5,
The rotor shaft is provided with a rotation drive unit having a motor as a drive source.   The driving apparatus according to claim 6, wherein the motor performs constant current driving or constant voltage driving regardless of an angular position of the rotor shaft during a period of driving the rotor shaft. A damper-equipped device comprising the drive device according to claim 6 or 7,
The rotor shaft is connected to a movable member that switches between a prone posture and a standing posture as the rotor shaft rotates.
The movable member switches from the standing posture to the flat posture when the rotor shaft rotates in the first direction, and changes from the flat posture to the standing posture when the rotor shaft rotates in the second direction. A damper-equipped device characterized by switching. The apparatus with a damper according to claim 8, wherein the movable member is a toilet seat of a Western-style toilet.

Images