JP2008082462A - Rotary damper - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary damper wherein excessive force caused by expansion of viscous liquid is prevented from acting on a casing and the like, and braking characteristics are prevented from being changed by change in the viscosity of the viscous liquid. <P>SOLUTION: The rotary chamber includes an operation chamber 3 wherein viscous liquid is filled, a first chamber 7 which is in communication with the operation chamber 3, and is capable of accommodating increase in volume by expansion of the liquid, a second chamber 8 which is provided adjacent to the first chamber 7 with a movable member 9 provided in between, and allows outside-air to flow through, a spring member 10 provided in the second chamber 8 in order to move the movable member 9 in response to the volume of the viscous liquid held in the first chamber 7, a flow path 11 for causing a resistance in the viscous liquid when the viscous liquid passes through by being pushed by vanes 5, and a throttling part 9a. The throttling part 9a is provided in the flow path 11 so as to narrow the flow path 11 in the case when the volume of the first chamber 7 is expanded in accordance with movement of the movable member 9, while in the case when the volume is reduced, the throttling part 9a expands the flow path 11. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a rotary damper.

In Patent Document 1 below, a working chamber (2) filled with a viscous liquid, a vane (4) disposed in the working chamber and pressing the viscous liquid by a rotational motion, and communicated with the working chamber, the viscosity is shown. A first chamber (3a) capable of accommodating an increase in volume due to the expansion of the liquid, and a movable member (15) interposed between the first chamber and the first chamber (3a), which is adjacent to the first chamber and is capable of circulating outside air. Two chambers (3b), a spring member (16) which is provided in the second chamber and moves the movable member according to the amount of the viscous liquid accommodated in the first chamber, and the viscosity pressed by the vane A rotary damper is described that includes a flow path (6) that creates a resistance of a viscous liquid when the liquid passes through.
According to such a rotary damper, since the volume increase due to the expansion of the viscous liquid is accommodated in the first chamber (3a), an excessive force acts on the casing or the like when the viscous liquid expands due to an increase in temperature. Can be prevented.
However, since the rotary damper cannot change the size of the flow path (6) in response to the change in the viscosity of the viscous liquid, there is a problem that when the viscosity of the viscous liquid changes, the braking characteristics change accordingly. there were. That is, the viscosity of the viscous liquid changes with changes in the ambient temperature, and the viscosity of the viscous liquid increases at low temperatures, so the braking force increases. Was weak.
JP-A-6-117464

  The problem to be solved by the present invention is to prevent an excessive force from acting on the casing and other components due to the expansion of the viscous liquid as the temperature rises. It is to provide a rotary damper capable of suppressing changes in characteristics.

In order to solve the above problems, the present invention provides the following rotary damper.
A working chamber filled with a viscous liquid, a vane that is disposed in the working chamber and presses the viscous liquid by a rotational motion, communicates with the working chamber, and can accommodate a volume increase due to the expansion of the viscous liquid. A second chamber adjacent to the first chamber with a movable member interposed between the chamber and the first chamber, through which the outside air can circulate, and provided in the second chamber and accommodated in the first chamber. A rotary damper comprising: a spring member that moves the movable member in accordance with the amount of viscous liquid to be generated; and a flow path that generates resistance of the viscous liquid when the viscous liquid pressed by the vane passes. ,
When the volume of the first chamber is increased with the movement of the movable member, the size of the flow path is reduced and the movable member is moved with the movement of the movable member. A rotary damper characterized in that when the volume of the first chamber is reduced, a throttle portion is provided to increase the size of the flow path.

According to the present invention, when the viscous liquid expands due to an increase in temperature, the movable member receives the pressure of the viscous liquid flowing from the working chamber into the first chamber and moves to expand the volume of the first chamber. As a result, the volume increase of the viscous liquid is accommodated in the first chamber. At this time, since the viscosity of the viscous liquid decreases with an increase in temperature, the viscous liquid easily passes through the flow path. However, when the volume of the first chamber increases with the movement of the movable member, the size of the flow path is reduced by the action of the restricting portion that reduces the size of the flow path, and the viscous liquid passing through the flow path is reduced. Since the flow rate is reduced, it is possible to suppress the braking force from being weakened. On the other hand, when the temperature decreases, the volume of the viscous liquid decreases and the movable member moves under the pressure of the spring member to reduce the volume of the first chamber. At this time, since the viscosity of the viscous liquid increases as the temperature decreases, it becomes difficult for the viscous liquid to pass through the flow path. However, when the volume of the first chamber decreases with the movement of the movable member, the flow path becomes larger due to the action of the restricting portion that increases the size of the flow path, and the flow rate of the viscous liquid passing through the flow path increases. Therefore, it becomes possible to suppress the braking force from increasing.
Therefore, according to the present invention, it is possible to prevent an excessive force from acting on the casing and other components due to the expansion of the viscous liquid accompanying the temperature rise, and further, due to the viscosity change of the viscous liquid accompanying the temperature change. It is also possible to suppress changes in the braking characteristics. Moreover, since this invention is a structure which changes the magnitude | size of a flow path according to a motion of a movable member by providing a throttle part in a movable member, there exists an advantage that a structure can be simplified.

  Hereinafter, embodiments of the present invention will be described with reference to examples shown in the drawings.

  1 is a view showing an internal structure of a rotary damper according to a first embodiment of the present invention, FIG. 2 is a cross-sectional view taken along line AA in FIG. 1, FIG. 3 is a cross-sectional view taken along line BB in FIG. 1 is a cross-sectional view taken along the line CC in FIG. 1, and FIG. 5 is a cross-sectional view taken along the line AA in FIG. As shown in these drawings, the rotary damper according to this embodiment includes a casing 1, a shaft 2, a working chamber 3, a partition wall 4, a vane 5, a check valve mechanism 6, a first chamber 7, a second chamber 8, The movable member 9, the spring member 10, and the flow path 11 are included.

  The casing 1 includes a main body 1a having one end opened and the other end closed by a bottom wall 1c, and a lid 1b closing the opening of the main body 1a (see FIG. 2). The shaft 2 is provided so that one end side is supported by the lid 1b and the other end side is supported by the bottom wall 1c so that it can rotate in a space formed inside the casing 1 (see FIG. 2). The working chamber 3 is formed between the casing 1 and the shaft 2 and is partitioned by a partition wall 4 (see FIG. 1). The working chamber 3 is filled with a viscous liquid. The partition 4 is fixed to the casing 1 (see FIG. 4). The vane 5 is formed integrally with the shaft 2 and is disposed in the working chamber 3 (see FIG. 1). The working chamber 3 is partitioned into a pressure chamber 3a and a non-pressure chamber 3b by arranging the vanes 5 (see FIG. 1). The vane 5 includes a check valve mechanism 6. The check valve mechanism 6 includes a large hole portion 6a communicating with the pressure chamber 3a, a small hole portion 6b communicating with the large hole portion 6a and the non-pressure chamber 3b, and a valve body 6c provided in the large hole portion 6a. (See FIG. 3).

  The first chamber 7 and the second chamber 8 are formed in the partition wall 4 (see FIGS. 2 and 4). The first chamber 7 communicates with the working chamber 3 (non-pressure chamber 3b) (see FIGS. 1 and 4). The second chamber 8 is adjacent to the first chamber 7 with a movable member 9 interposed between the second chamber 8 and the first chamber 7 (see FIGS. 2 and 4). In the bottom of the partition wall 4, a hole 4 a that allows the second chamber 8 to communicate with the outside is formed in order to allow outside air to flow through the second chamber 8 (see FIGS. 2 and 4). The movable member 9 is configured to have a tapered throttle portion 9a (see FIGS. 2 and 4). O-rings 12 are disposed at both ends of the movable member 9 (see FIGS. 2 and 4). The spring member 10 is provided in the second chamber 8 (see FIGS. 2 and 4). The spring member 10 is a coil spring. The flow path 11 is opened to the inside of the partition wall 4 on the one surface side of the first flow path 11a formed around the throttle portion 9a and the partition wall 4 so that the first flow path 11a and the pressure chamber 3a communicate with each other. The second flow path 11b and the third flow path 11b that opens to the other surface side of the partition wall 4 and connects the first flow path 11a and the non-pressure chamber 3b (see FIGS. 4 and 5). The O-ring 12 provided at one end of the movable member 9 serves to prevent the viscous liquid from leaking from the first flow path 11 a to the first chamber 7, and the O-ring 12 provided at the other end of the movable member 9. Plays a role of preventing the viscous liquid from leaking from the first flow path 11 a to the second chamber 8.

  In the rotary damper configured as described above, when the shaft 2 rotates in the clockwise direction in FIG. 1, the vane 5 rotates accordingly and presses the viscous liquid in the pressure chamber 3 a. At this time, as shown in FIG. 3, the check valve mechanism 6 is configured so that the viscous liquid is adjacent to the pressure chamber 3 a with the vane 5 interposed between the valve body 6 c and the opening of the small hole portion 6 b. The flow into the chamber 3b is prevented. The viscous liquid pressed by the vane 5 passes through the flow path 11 and flows into the non-pressure chamber 3b adjacent to the pressure chamber 3a with the partition wall 4 interposed therebetween. When the viscous liquid passes through the first flow path 11a, resistance of the viscous liquid occurs. This resistance generates a braking force that slows the rotation of the shaft 2.

  On the other hand, when the shaft 2 is rotated in the counterclockwise direction in FIG. 1, the vane 5 is rotated accordingly and presses the viscous liquid in the non-pressure chamber 3b. At this time, in the check valve mechanism 6, as shown in FIG. 8, when the valve body 6 c opens the opening of the small hole portion 6 b, the viscous liquid is adjacent to the non-pressure chamber 3 b with the vane 5 interposed therebetween. It is allowed to flow into the pressure chamber 3a. When the viscous liquid passes through the small hole portion 6b and the large hole portion 6a, no resistance of the viscous liquid is generated, so that no braking force is generated.

  When the viscous liquid expands due to an increase in temperature, the increased volume of the viscous liquid flows into the first chamber 7 communicating with the working chamber 3 (non-pressure chamber 3b). The movable member 9 moves while compressing the spring member 10 by receiving the pressure of the viscous liquid flowing into the first chamber 7 from the non-pressure chamber 3b, and expands the volume of the first chamber 7 (see FIG. 6). . As a result, the volume increase of the viscous liquid is accommodated in the first chamber 7. At this time, the volume of the second chamber 8 is reduced, and the gas inside the second chamber 8 is discharged to the outside through the hole 4a.

  When the movable member 9 moves in the direction of expanding the volume of the first chamber 7, the tapered portion 9a formed in a tapered shape moves downward in FIG. 6 in the first flow path 11a. The size of the flow path 11 becomes smaller due to the relative positional relationship of the throttle portion 9a with respect to the second flow path 11b and the third flow path 11c at this time (see FIG. 6). Therefore, even if the viscosity of the viscous liquid decreases with an increase in temperature, the flow rate of the viscous liquid passing through the flow path 11 can be reduced, and as a result, the braking force can be prevented from becoming weak.

  When the temperature decreases, the volume of the viscous liquid decreases and the movable member 9 moves under the pressure of the spring member 10 to reduce the volume of the first chamber 7 (see FIG. 7). At this time, the volume of the second chamber 8 is enlarged, and outside air flows into the inside of the second chamber 8 through the hole 4a.

  When the movable member 9 moves in the direction of reducing the volume of the first chamber 7, the tapered portion 9a formed in a tapered shape moves upward in FIG. 7 within the first flow path 11a. The size of the flow path 11 increases due to the relative positional relationship of the throttle portion 9a with respect to the second flow path 11b and the third flow path 11c at this time (see FIG. 7). Therefore, even if the viscosity of the viscous liquid increases due to a decrease in temperature, the flow rate of the viscous liquid passing through the flow path 11 can be increased, and as a result, it is possible to suppress an increase in braking force.

  According to the rotary damper according to the present embodiment, as described above, it is possible to prevent an excessive force from acting on the casing 1 and other components due to the expansion of the viscous liquid accompanying the temperature rise, and to change the viscosity of the viscous liquid. Therefore, it is possible to suppress the change of the braking characteristic. Further, since the movable member 9 is provided with the narrowed portion 9a, the size of the flow path 11 is changed in accordance with the movement of the movable member 9, so that there is an advantage that the structure can be simplified.

  9 is a view showing the internal structure of the rotary damper according to the second embodiment of the present invention, FIG. 10 is a cross-sectional view taken along the line AA in FIG. 9, FIG. 11 is a cross-sectional view taken along the line BB in FIG. 10 is a cross-sectional view taken along line AA in FIG. 10, and FIG. 13 is a cross-sectional view taken along line BB in FIG. As shown in these drawings, the rotary damper according to this embodiment includes a casing 1, a shaft 2, a working chamber 3, a partition wall 4, a vane 5, a check valve mechanism 6, a first chamber 7, a second chamber 8, The movable member 9, the spring member 10, and the flow path 11 are included.

  The casing 1 includes a main body 1a having one end opened and the other end closed by a bottom wall 1c, and a lid 1b closing the opening of the main body 1a (see FIG. 10). The shaft 2 is provided such that one end side is supported by the lid 1b and the other end side is supported by the main body 1a so that the shaft 2 can rotate in a space formed inside the casing 1 (see FIGS. 9 and 10). ). The shaft 2 has a first hole 2a that opens at one end, a second hole 2b that opens at the other end and has a larger inner diameter than the first hole 2a, and the first hole 2a and the second hole 2b. And a third hole 2c having an inner diameter that is larger than the first hole 2a and smaller than the second hole 2b (see FIG. 10). The first hole portion 2a and the third hole portion 2c, and the second hole portion 2b and the third hole portion 2c communicate with each other. The shaft 2 further includes a partition member 2d (see FIGS. 9 and 10). The partition member 2d is provided in the second hole 2b, and includes a wall 2e that divides the second hole 2b into two chambers. The flow path 11 consists of a hole penetrating the center of the wall part 2e (refer FIG. 9 thru | or FIG. 10). The working chamber 3 is formed between the casing 1 and the shaft 2 and is partitioned by a partition wall 4 (see FIG. 9). The working chamber 3 is filled with a viscous liquid. The partition wall 4 is formed by recessing a part of the peripheral wall of the main body 1a (see FIG. 9). The vane 5 is formed integrally with the shaft 2 and is disposed in the working chamber 3 (see FIG. 9). The working chamber 3 is divided into a pressure chamber 3a and a non-pressure chamber 3b by arranging the vanes 5 (see FIG. 9). The check valve mechanism 6 is in contact with one surface of the wall portion 2e and a valve hole 6d formed so as to penetrate the wall portion 2e around the flow path 11 formed in the wall portion 2e of the partition member 2d. Thus, it is configured to have an annular valve body 6c that closes the valve hole 6d (see FIGS. 9 to 11).

  The first chamber 7 and the second chamber 8 are formed on the shaft 2 (see FIGS. 10 and 11). The first chamber 7 communicates with the working chamber 3 (non-pressure chamber 3b) (see FIGS. 11 and 12). The 1st channel | path 13 which connects the 1st chamber 7 and the non-pressure chamber 3b is formed so that the surrounding wall of the axis | shaft 2 and the surrounding wall of the partition member 2d may be penetrated. The second chamber 8 is adjacent to the first chamber 7 with a movable member 9 interposed between the second chamber 8 and the first chamber 7 (see FIGS. 10 and 11). The first hole 2a formed in the shaft 2 plays a role of communicating the second chamber 8 with the outside in order to allow the outside air to flow through the second chamber 8 (see FIGS. 10 and 11). The third chamber 15 adjacent to the first chamber 7 across the wall 2e communicates with the working chamber 3 (pressure chamber 3a) (see FIGS. 11 and 13). The 2nd channel | path 14 which connects the 3rd chamber 15 and the pressure chamber 3a is formed so that the surrounding wall of the axis | shaft 2 and the surrounding wall of the partition member 2d may be penetrated. The movable member 9 is configured to have a tapered throttle portion 9a in a rod-like portion protruding from the main body portion (see FIGS. 9 to 12). An O-ring 12 is disposed on the movable member 9 (see FIG. 10). The spring member 10 is provided in the second chamber 8 (see FIGS. 10 and 11). The spring member 10 is a coil spring. The O-ring 12 provided on the movable member 9 serves to prevent the viscous liquid from leaking from the first chamber 7 to the second chamber 8.

  In the rotary damper configured as described above, when the shaft 2 rotates in the clockwise direction in FIG. 9, the vane 5 rotates accordingly and presses the viscous liquid in the pressure chamber 3 a. At this time, as shown in FIG. 11, the check valve mechanism 6 causes the viscous liquid to flow from the pressure chamber 3a to the non-pressure chamber 3b through the valve hole 6d when the valve body 6c closes the opening of the valve hole 6d. To stop doing. Thereby, the viscous liquid pressed by the vane 5 passes only through the flow path 11 and flows into the non-pressure chamber 3b from the pressure chamber 3a. When such viscous liquid passes through the flow path 11, resistance of the viscous liquid occurs. This resistance generates a braking force that slows the rotation of the shaft 2.

  On the other hand, when the shaft 2 rotates in the counterclockwise direction in FIG. 9, the vane 5 rotates accordingly and presses the viscous liquid in the non-pressure chamber 3b. At this time, as shown in FIG. 16, in the check valve mechanism 6, the valve body 6c opens the opening of the valve hole 6d so that the viscous liquid passes through the valve hole 6d and is pressurized from the non-pressure chamber 3b. It is allowed to flow into the chamber 3a. When the viscous liquid passes through the valve hole 6d, no resistance of the viscous liquid is generated, so that no braking force is generated.

  When the viscous liquid expands due to an increase in temperature, the increased volume of the viscous liquid flows into the first chamber 7 communicating with the working chamber 3 (non-pressure chamber 3b). The movable member 9 moves while compressing the spring member 10 by receiving the pressure of the viscous liquid flowing into the first chamber 7 from the non-pressure chamber 3b, and expands the volume of the first chamber 7 (see FIG. 14). . As a result, the volume increase of the viscous liquid is accommodated in the first chamber 7. At this time, the volume of the second chamber 8 is reduced, and the gas inside the second chamber 8 is discharged to the outside through the first hole 2a.

  When the movable member 9 moves in a direction in which the volume of the first chamber 7 is enlarged, the throttle portion 9a formed in a tapered shape moves upward in FIG. The size of the flow path 11 becomes smaller due to the relative positional relationship of the throttle portion 9a with respect to the flow path 11 at this time (see FIG. 14). Therefore, even if the viscosity of the viscous liquid decreases with an increase in temperature, the flow rate of the viscous liquid passing through the flow path 11 can be reduced, and as a result, the braking force can be prevented from becoming weak.

  When the temperature decreases, the volume of the viscous liquid decreases and the movable member 9 moves under the pressure of the spring member 10 to reduce the volume of the first chamber 7 (see FIG. 15). At this time, the volume of the second chamber 8 is enlarged, and the outside air flows into the second chamber 8 through the first hole 2a.

  When the movable member 9 moves in the direction of reducing the volume of the first chamber 7, the tapered portion 9a formed in a tapered shape moves downward in FIG. The size of the flow path 11 increases due to the relative positional relationship of the throttle portion 9a with respect to the flow path 11 at this time (see FIG. 15). Therefore, even if the viscosity of the viscous liquid increases due to a decrease in temperature, the flow rate of the viscous liquid passing through the flow path 11 can be increased, and as a result, it is possible to suppress an increase in braking force.

  According to the rotary damper according to the present embodiment, as described above, it is possible to prevent an excessive force from acting on the casing 1 and other components due to the expansion of the viscous liquid accompanying the temperature rise, and to change the viscosity of the viscous liquid. Therefore, it is possible to suppress the change of the braking characteristic. Further, since the movable member 9 is provided with the narrowed portion 9a, the size of the flow path 11 is changed in accordance with the movement of the movable member 9, so that there is an advantage that the structure can be simplified.

It is a figure which shows the internal structure of the rotary damper which concerns on Example 1 of this invention. It is an AA section sectional view in FIG. It is a BB section sectional view in FIG. It is CC sectional view taken on the line in FIG. FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. It is a figure for demonstrating the motion of the movable member at the time of temperature rise. It is a figure for demonstrating the movement of the movable member at the time of temperature fall. It is a figure which shows the valve opening state of a non-return valve mechanism. It is a figure which shows the internal structure of the rotary damper which concerns on Example 2 of this invention. FIG. 10 is a cross-sectional view taken along line AA in FIG. 9. FIG. 10 is a cross-sectional view taken along the line BB in FIG. 9. It is AA section sectional drawing in FIG. It is BB part sectional drawing in FIG. It is a figure for demonstrating the motion of the movable member at the time of temperature rise. It is a figure for demonstrating the movement of the movable member at the time of temperature fall. It is a figure which shows the valve opening state of a non-return valve mechanism.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Casing 1a Main-body part 1b Cover 1c Bottom wall 2 Shaft 2a 1st hole 2b 2nd hole 2c 3rd hole 2d Partition member 2e Wall part 3 Working chamber 3a Pressure chamber 3b Non-pressure chamber 4 Partition 4a Hole 5 Vane 6 check valve mechanism 6a large hole portion 6b small hole portion 6c valve body 6d valve hole 7 first chamber 8 second chamber 9 movable member 9a throttle portion 10 spring member 11 flow channel 11a first flow channel 11b second flow channel 11c Third flow path 12 O-ring 13 First passage 14 Second passage 15 Third chamber

Claims (1)

A working chamber filled with a viscous liquid, a vane that is disposed in the working chamber and presses the viscous liquid by a rotational motion, communicates with the working chamber, and can accommodate a volume increase due to the expansion of the viscous liquid. A second chamber adjacent to the first chamber with a movable member interposed between the chamber and the first chamber, through which the outside air can circulate, and provided in the second chamber and accommodated in the first chamber. A rotary damper comprising: a spring member that moves the movable member in accordance with the amount of viscous liquid to be generated; and a flow path that generates resistance of the viscous liquid when the viscous liquid pressed by the vane passes. ,
When the volume of the first chamber is increased with the movement of the movable member, the size of the flow path is reduced and the movable member is moved with the movement of the movable member. A rotary damper characterized in that when the volume of the first chamber is reduced, a throttle portion is provided to increase the size of the flow path.

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