JP4136570B2 - Damper device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention obtains a resistance force against an external force in one rotation direction by using hydraulic oil, exhibits a buffering action by the resistance force, that is, a braking force, and in a reverse rotation direction. On the other hand, the present invention relates to an improvement of a damper mechanism that can be used for various applications that require as little resistance as possible.
[0002]
[Prior art]
In recent years, hot water cleaning apparatuses have become widely used because they are clean and hygienic. To open and close the toilet lid, toilet seat, and the like of this hot water cleaning device, and hit the toilet, an attempt is made to suppress the impact by using a damper device together with a rotating shaft in some hot water cleaning devices.
Conventionally, there has been constituted as shown in FIG. 13 for this type of damper device. The configuration will be described below with reference to the drawings. As shown in FIG. 13 , the damper device 100 is composed of a cylinder 102, a rotary shaft 103, a check valve 104, and the like. The cylinder 102 has a partition wall 102a on its inner wall, and the rotary shaft 103 penetrates inside. Oil is filled in the chamber 105 divided into two by the rotating shaft 103 and the partition wall 102a. The rotating shaft 103 has a wing 106 protruding radially, and the check valve 104 and the wing 106 divide the chamber 105 into a pressurizing chamber 105a and a depressurizing chamber 105b. The wing portion 106 has a communication passage 107 that allows the pressurization chamber 105 a and the decompression chamber 105 b to communicate. The check valve 104 has an outer surface that is in contact with the inner peripheral surface of the cylinder 102, and an inner surface that surrounds the wing portion 106. In addition, a control port 108 is provided on the decompression chamber 105b side, and the pressurization chamber 105a and the decompression chamber 105b are communicated together with the communication passage 107 of the blade portion 106. In FIG. 14, 109 denotes an O-ring, and 110 denotes a cap for sealing the tip of the cylinder 102. Then, the rotating shaft 103 rotates to change the mutual position between the wing portion 106 and the check valve 104, and the check valve 104 controls the amount of oil flowing from the pressurizing chamber 105a to the decompression chamber 105b to rotate the rotation speed. It suppresses.
As shown in FIG. 14 , the damper device 100 is fixed to the cleaning device main body 112 installed on the toilet, and the toilet seat 113 and the toilet lid 114 are coupled to each other via the rotation shaft 103 of each damper device 100. . Then, when the user opens the toilet seat 113 or the toilet lid 114 and lifts it upward or closes it, if the user pulls the toilet seat 113 or the toilet lid 114 lightly toward the front, the damper device 100 will suddenly It closes while suppressing the rotational speed. (For example, refer to Patent Document 1.)
[0003]
[Patent Document 1]
JP-A-5-296267 [0004]
[Problems to be solved by the invention]
However, because there is a gap in the axial direction between the cylinder and the rotating shaft due to production variations, the fluid speed cannot be controlled because oil passes through this gap, and the slow closing time varies and the closing operation is stable. I did not.
In order to solve such a problem, for example, there is a mechanism provided with an adjustment mechanism that eliminates a gap by pressing a rotating shaft against a cylinder against variations in the axial direction.
However, in this method, if the number of times of opening and closing is increased, the contact portion is worn and the frictional force is reduced, so that the slow closing time becomes considerably shorter than the initial time, and there is a possibility that the slow closing operation is finally stopped.
Furthermore, since the wings push viscous fluid during the closing operation, a large internal pressure is generated in the oil chamber, and the valve body tries to block the flow of viscous fluid while being pressed by the cylinder inner wall and the wing outer wall. If the valve body is worn out and repeated opening and closing over a long period of time, the initial stable soft closing operation may not be maintained.
[0005]
[Means for solving the problem, operation and effect]
In order to solve the above problems, in the present invention, a cylindrical cylinder having a partition wall that bisects the interior in the axial direction, a columnar rotation shaft that is rotatably inserted into the cylinder, By rotating the rotation shaft relative to the cylinder, the inner peripheral wall surface of the cylinder can be slid, and the wing portion on the outer periphery of the rotation shaft projects in the radial direction, and this wing portion rotates the inside of the cylinder. a chamber which is divided in the axial direction of the shaft, opposite which are provided between the oil to be filled into the chamber, a rotating body fixed to the rotating non ability to the rotary shaft, and the rotating body and the wings Ri Do and a check valve device unit, since it is configured the rotating shaft and the rotating body is moved in the axial direction, respectively the damper device by the pressing force of the oil in the check valve device portion, between the rotating body and the rotating shaft The valve body of the check valve device provided in the Kicking pressing the rotary shaft and the rotary member on the end wall side of the cylinder pressure, it is possible to aggregate the gap in the axial direction between the rotary shaft and the cylinder caused by the "Production variations" in the gap of the rotating body with all the rotating shaft.
As a result, the slow closing time is not changed by the gap in the axial direction between the rotating shaft and the cylinder due to “production variation”, and a stable slow closing operation can be obtained.
Therefore, a mechanism for adjusting the gap in the axial direction between the rotating shaft and the cylinder is not necessary, and the cost can be reduced.
In addition, compared to the case where the valve element is placed between the rotating shaft and the cylinder, sliding friction does not occur, so performance degradation due to wear of the valve element hardly occurs. realizable.
An O-ring is fitted between the outer peripheral wall of the rotating body and the inner peripheral wall surface of the cylinder, and oil is supplied from the O-ring side to the outer peripheral wall of the rotating body near the groove of the rotating body without passing through the check valve device. When a bypass groove for escaping to another chamber is formed, the O-ring is deformed by crushing the O-ring through the bypass groove when a force greater than the self-weight torque of the seat cover or the like is received, and the O-ring groove When the viscous fluid flows in from the bypass path, the damper device can be prevented from being destroyed by the impact force.
Further, when an air bleeding groove is formed above the partition wall on the inner periphery of the cylinder, air can be discharged to the outside through the air bleeding groove when the viscous fluid is sealed in the damper chamber.
[0006]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings. First, the first embodiment will be described with reference to FIGS. FIG. 1 is an exploded perspective view of a damper device 1 according to a first embodiment of the present invention, FIG. 2 is a sectional view, FIG. 3 is a plan view for explaining damper chambers A and B, and FIG. FIG. 5 is a partially enlarged cross-sectional view when the communication path 52a is opened by the check valve 40, and FIG. 6 is a rotating body for explaining the groove 52 and the communication path 52a. 50 is a partially enlarged perspective view of 50. FIG.
First, the components of the damper device 1 will be described with reference to FIG. The damper device 1 includes a cylinder 20, an O-ring 29, a rotating shaft 30, a valve body 40 of a check valve device section, a rotating body 50, an O-ring 59, a lid 60, and a permanent magnet 70. The permanent magnet 70 is for detecting the rotational position of the rotary shaft 30 by a Hall IC provided in the vicinity of the damper device 1, and is omitted when it is not necessary to detect the rotational position.
The cylinder 20 is formed in a cylindrical shape with a bottom, and a pivot hole 21 for rotatably supporting the output shaft 31 of the rotary shaft 30 is provided at the bottom. Further, a partition wall 22 is formed on the bottom side of the cylinder inner wall, and a female screw portion 23 is formed at the open end.
The rotating shaft 30 is formed in a substantially columnar shape, the output shaft 31 is formed at the tip, the wing portion 35 projecting in the radial direction is formed on the outer periphery of the intermediate portion, and the connecting shaft 34 is formed at the rear end. The output shaft 31 is formed with a hinge hole 32 for fixing a hinge pin such as a toilet seat or a toilet lid so that the hinge pin cannot rotate. Further, a groove 33 for accommodating a part of the check valve body 40 is formed at the rear end of the wing portion 35. Further, an O-ring groove 36 for accommodating the O-ring 29 is provided on the outer periphery of the output shaft 31.
The rotating body 50 is formed in a substantially cylindrical shape having a slightly smaller diameter than the cylinder 20, and has a hinge hole 51 similar to the connecting shaft 34 and a groove 52 for accommodating a part of the check valve body 40 at the front end. An O-ring groove 53 for accommodating the O-ring 59 is formed on the outer periphery. In addition, an insertion hole 54 for inserting the permanent magnet 70 is provided on the outer periphery of the rear end. Further, a bypass groove 55 that connects the front end surface of the rotating body 50 and the O-ring groove 53 is provided. The lid 60 is formed in a bottomed cylindrical shape, and a male screw portion 61 is formed on the outer periphery in order to be screwed into the cylinder 20. The lid 60 keeps the rotating body 50 in contact with the rotating shaft 30 and prevents these members from coming off the cylinder 20. Further, a plurality of gripping holes 62 for gripping with a dedicated assembly jig are formed on the rear end surface.
[0007]
Next, the structure of the damper apparatus 1 is demonstrated using FIG.2 and FIG.3. Oil is filled in the damper chambers A and B which are divided into two by the partition wall 22 around the rotary shaft 30 sealed by the O-ring 29 and the O-ring 59 inside the damper device 1. The check valve body 40 disposed on the end face of the wing portion 35, and the wing portion 35 and the rotating body 50 that are in contact with each other face the chamber A (B) into the pressurizing chamber A1 (B1) and the decompression chamber A2 (B2). It is further divided into two. Further, the groove 52 has a communication passage 52a that allows the pressurizing chamber A1 and the decompression chamber A2 to communicate with each other, and the check valve 40 is slidably provided within the groove 33 and the groove 52 of the blade portion 35 and the rotating body 50. Yes. As shown in FIGS. 4 to 6, in order to define the operating range of the valve body 40, the groove 33 has a cross-sectional shape in which the end is substantially the same diameter as the valve body 40 and the middle portion is connected by a straight line, and is substantially the same as the valve body 40. Form the same length. One end of the communication path 52 a provided in the groove 52 is provided in a position facing the groove 33, and the other end is provided in a portion protruding from the position facing the groove 33.
Here, the braking force by the damper mechanism is applied by the relative rotational movement of the rotating shaft 30 with respect to the cylinder 20, but now when the rotating shaft 30 is rotated in the direction of arrow R in FIG. The device portion 40 constituted by the check valve body 40 and the grooves 33 and 52, which will be described later, is in a closed state, whereby the damper is turned on and a braking force based on oil is exhibited. (See Figure 4)
That is, in the state of the damper ON, the wing portion 35 on the rotary shaft 30 and extending on one diameter line thereof rotates in the direction of arrow R in FIG. Since the oil in the pressurizing chambers A1 and B1 is pressurized, the check valve 40 is pressed by the oil and the check valve 40 moves in the direction opposite to the rotating direction of the rotary shaft 30 and is recessed in the groove 52. 52a is closed. At this time, the pressing force received from the oil by the check valve 40 is disassembled by the grooves 33 and 52 and presses the rotating shaft 30 and the rotating body 50 in the axial direction. Thereby, the clearance gap between the rotating shaft 30 and the bottom part of the cylinder 20 is eliminated. Accordingly, the oil moves to the decompression chambers A2 and B2 through a slight gap between the blade portion 35 and the cylinder 20, or to the decompression chambers B2 and A2 through a slight gap between the partition wall 22 and the rotating shaft 30, respectively.
Further, if the rotary shaft 30 is rotated in the direction opposite to the arrow R direction, the damper is turned off. When the damper is OFF, the check valve 40 opens the communication passage 52a, so that the oil smoothly moves from the decompression chambers A2 and B2 to the pressurization chambers A1 and B2 via the communication passage 52a. (See Figure 5)
[0008]
Next a second embodiment will be described with reference to FIGS. 7 through 12. In the second embodiment, a groove 24 is formed on the bottom surface of the cylinder 20 in addition to the first embodiment. The configuration and operation of the groove 24 will be described in detail with reference to the drawings. 7 is a sectional view of the damper device 1 according to the second embodiment, FIG. 8 is a plan view for explaining the damper chambers A and B and the groove 24, and FIG. 9 is a simplified sectional view taken along the line CC in FIG. FIG. 10 is a side view showing the state of the toilet seat, FIG. 11 is a graph showing the angular velocity with respect to the angle when the toilet seat on which the damper device 1 of the second embodiment is mounted, and FIG. 12 is the air vent groove 25. It is a perspective view of the cylinder 20 for demonstrating these.
As shown in FIG. 9, the groove 24 forms a groove having a substantially constant depth in the range of 40 ° (quick start region) from the base of the partition wall 22 on the decompression chamber A2 side, and the range of 40 to 90 ° (variation) The region 24 is formed so as to be gradually shallow, and the groove 24 is not formed in the range of 90 to 120 ° (slow end region).
Thus, the oil in the pressurizing chambers A1 and B1 between the wing portion 35 and the partition wall 22 is pressurized and pressed by the oil until the check seat 40 is rotated until the toilet seat exceeds the position where the toilet seat is self-supporting. The shaft 30 moves in a direction opposite to the direction of rotation of the shaft 30 and closes the communication path 52a. However, since the groove 24 is formed at a substantially constant depth in this quick start region, the decompression chambers A2, B2 and the pressurization chamber A1, Since it communicates with B1, the oil moves to the decompression chambers B2 and A2 via the groove 24, respectively. Therefore, in this quick region, the state is the same as the state of damper OFF.
In the region where the toilet seat falls over its own position (position where it cannot fall by its own weight) and falls due to its own weight, the groove 24 is formed gradually shallower, so that the pressurizing chambers A1, B1 through the groove 24 to the decompression chambers A2, B2 The amount of oil that moves to gradually decreases, and the damper is gradually turned on. Since the groove 24 is not formed in the region where the toilet seat is just closed, the damper is in an ON state, and as described above, the oil passes through a slight gap between the outer periphery of the wing 35 and the inner periphery of the cylinder 20. Then, they move to the decompression chambers A2 and B2 or to the decompression chambers B2 and A2 through a slight gap between the inner periphery of the partition wall 22 and the outer periphery of the rotary shaft 30, respectively.
As a result, the toilet seat moves to a state immediately before closing relatively quickly, and then the toilet seat comes into contact with and closes to the upper surface of the toilet bowl at a moderate speed.
[0009]
In this embodiment, the quick start area is set to 40 ° from the open end, but this is set according to the toilet seat's self-supporting angle. If the hinge position and the center of gravity position of the toilet seat are changed, the quick start area is changed accordingly. There must be.
Further, although the slow end region is set to 30 ° from the closed end, this also needs to be changed in accordance with the change of the hinge position, the gravity center position and the own weight of the toilet seat. This is because if the vehicle is not sufficiently decelerated in the slow end region and the angular velocity is less than or equal to a predetermined value, it collides with the upper surface of the toilet and makes a loud sound.
[0010]
It will now be described with reference to FIG. 6 bypass channel 55. The bypass groove 55 is provided so as to bypass the wing part 35 as shown (the same bypass groove 55 is also provided on the opposite wing part 35 side not shown). With such a configuration, when an impact force (a force greater than the weight of the toilet seat or toilet lid on the rotating shaft) is applied, the internal pressure of the pressurizing chamber A1 (B1) increases, and the viscous fluid is bypassed for shock buffering. By crushing the O-ring through the groove 55, the O-ring is deformed, the flow path of the O-ring groove is expanded and the viscous fluid easily flows, and the viscous fluid flows from the pressurizing chamber A1 (B1) to the O-ring. By passing through the groove and flowing into the decompression chamber A2 (B2), an increase in the internal pressure of the pressurization chamber A1 (B1) due to the impact force can be suppressed, and therefore, the impact damage of the damper device 1 can be prevented. .
[0011]
Next, the air release groove 25 will be described with reference to FIG. 12. The air vent groove 25 is provided with a smooth curvature above the partition wall 22 as shown. With such a configuration, when the viscous fluid is sealed in the damper chamber, the rotary shaft 30 is assembled to the cylinder 20 to inject the viscous fluid, and then the viscous fluid is sealed in the rotating body 50 with an O-ring 59 for sealing sealing. At this time, the air accumulated in the damper chamber is discharged to the outside through the gap between the O-ring 59 of the rotating body 50 and the air vent groove 25. Therefore, the damper chamber is made of viscous fluid. Fully filled.
Further, since the air vent groove 25 is a small groove that is smoothly curved with respect to the inner surface of the cylinder 20, leakage of viscous fluid from the O-ring 59 does not occur.
[Brief description of the drawings]
FIG. 1 is an exploded perspective view of a damper device 1 of the present invention. FIG. 2 is a sectional view of a first embodiment of the damper device 1 of the present invention. FIG. 3 is a damper chamber of the first embodiment of the damper device 1 of the present invention. FIG. 4 is a partially enlarged cross-sectional view of the damper device 1 according to the first embodiment of the present invention when the communication passage 52a is blocked by the check valve 40 in the first embodiment of the present invention. FIG. 6 is a partially enlarged cross-sectional view of the first embodiment of the damper device 1 of the present invention when the communication passage 52a is opened by the check valve 40. FIG. 6 shows the groove 52 and the communication passage of the first embodiment of the damper device 1 of the present invention. Fig. 7 is a partial enlarged perspective view of a rotating body 50 for explaining 52a. Fig. 7 is a sectional view of a second embodiment of the damper device 1 of the present invention. Fig. 8 is a damper chamber of the damper device 1 of the second embodiment of the present invention. FIG. 9 is a plan view for explaining A and B and the groove 24. FIG. FIG. 10 is a side view showing a state of a toilet seat on which a damper device 1 according to a second embodiment of the present invention is mounted. FIG. 11 shows a damper device 1 according to the second embodiment of the present invention. FIG. 12 is a perspective view of a cylinder 20 for explaining an air vent groove 25. FIG . 13 is a cross-sectional view showing a conventional damper device. FIG. Fig . 14 is a longitudinal sectional view. Fig . 14 is a transverse sectional view . Fig . 14 is a perspective view of a main body of a sanitary washing device provided with a conventional damper device.
DESCRIPTION OF SYMBOLS 20 ... Cylinder, 22 ... Partition wall, 30 ... Rotating shaft, 33 ... Groove, 35 ... Blade part, 40 ... Valve body, 50 ... Rotating body, 52 ... Groove, 52a ... Communication path, A1 ... Pressurization chamber, A2 ... Decompression chamber, B1 ... pressurization chamber, B2 ... decompression chamber

Claims (5)

By a cylindrical cylinder having a partition wall that bisects the interior in the axial direction, a columnar rotation shaft that is rotatably inserted into the cylinder, and a relative rotation of the rotation shaft with respect to the cylinder A wing that is slidable on the inner peripheral wall surface of the cylinder and that protrudes in the radial direction on the outer periphery of the rotating shaft, a chamber in which the inside of the cylinder is partitioned in the axial direction of the rotating shaft by the wing, and oil filled in the chamber, Ri Do from a rotating body fixed to the rotating non ability to the rotary shaft, a check valve device portion provided between said rotary member and said wings, inverse the rotary shaft and the damper device Before moving the rotating body to each of the axial direction by the pressing force of the oil in the check valve device unit.   2. The damper according to claim 1, wherein the check valve device portion includes a groove provided at the rear end of the wing portion and / or the front end of the rotating body, and a valve body that can slide between the grooves. apparatus.   The damper device according to claim 2, wherein the valve body is formed in a columnar shape, and is arranged so that an axis of the columnar valve body faces a radial direction of the rotating shaft.   An O-ring is fitted between the outer peripheral wall of the rotating body and the inner peripheral wall surface of the cylinder, and oil is supplied to the outer peripheral wall of the rotating body near the groove of the rotating body from the O-ring side without passing through the check valve device. The damper device according to any one of claims 1 to 3, wherein a bypass groove is formed for escape.   The damper device according to any one of claims 1 to 4, wherein an air vent groove is formed above the partition wall on the inner periphery of the cylinder.

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