JP2018132131A - Rotary damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary damper which enables reduction of the number of component and can be manufactured at low costs.SOLUTION: A rotary damper of the invention includes a valve (18), and the valve (18) includes a valve body (25). The valve body (25) is characterized by a structure including: a linear part (37) which is inserted into a hole (27) through which oil passes; and an elastic part (38) which has elasticity and deforms when the linear part (37) is moved into the hole (27) by a pressure difference of the oil. Since the valve body (25) has the linear part (37) and the elastic part (38), a flow rate of the oil passing through the hole (27) can be controlled with one component.SELECTED DRAWING: Figure 9

Description

  The present invention relates to a rotary damper.

  2. Description of the Related Art Conventionally, a rotary damper having a valve, which includes a valve body that is inserted into a hole through which oil passes, and a spring that deforms when the valve body enters the hole due to a difference in oil pressure is known. (For example, refer to Japanese Patent No. 4625451).

  However, the conventional rotary damper requires two parts, that is, a valve body and a spring in order to control the flow rate of the oil passing through the hole.

Japanese Patent No. 4625451

  The problem to be solved by the present invention is to provide a rotary damper that can be manufactured at a low cost by reducing the number of parts.

  In order to solve the above-described problems, the present invention includes a valve, the valve includes a valve body, the valve body having a linear portion inserted into a hole through which oil passes, and having elasticity, the wire The rotary damper is provided with an elastic portion that deforms when the shape portion enters the hole due to a pressure difference of oil.

  According to the present invention, since the valve body has the linear portion and the elastic portion, the flow rate of the oil passing through the hole can be controlled by one component. Therefore, it is possible to provide a rotary damper that can be manufactured at low cost.

FIG. 3 is a cross-sectional view illustrating a cross section of the rotary damper according to the first embodiment. 1 is a cross-sectional view illustrating a vertical cross section of a rotary damper according to Embodiment 1. FIG. It is a top view of the 1st and 2nd vane. It is sectional drawing which shows the longitudinal cross-section of the 1st and 2nd vane. It is a bottom view of the 1st and 2nd vane. 2 is a plan view of first and second valve bodies employed in Example 1. FIG. It is a front view of the 1st and 2nd valve body employ | adopted in Example 1. FIG. It is a bottom view of the 1st and 2nd valve body employ | adopted in Example 1. FIG. 2 is a cross-sectional view showing a longitudinal section of a first valve employed in Example 1. FIG. FIG. 6 is a cross-sectional view for explaining the operation of the rotary damper according to the first embodiment. FIG. 6 is a cross-sectional view for explaining the operation of the rotary damper according to the first embodiment. FIG. 6 is a cross-sectional view for explaining the operation of the rotary damper according to the first embodiment. It is sectional drawing which shows the longitudinal cross-section of the valve | bulb employ | adopted in Example 2. FIG. 6 is a plan view of a valve body employed in Example 2. FIG. 6 is a front view of a valve body employed in Example 2. FIG. 6 is a bottom view of a valve body employed in Example 2. FIG. FIG. 10 is a cross-sectional view for explaining the operation of the rotary damper according to the second embodiment. FIG. 10 is a cross-sectional view for explaining the operation of the rotary damper according to the second embodiment. FIG. 10 is a cross-sectional view for explaining the operation of the rotary damper according to the second embodiment.

  Hereinafter, although embodiments of the present invention will be described in more detail based on examples of the present invention, the technical scope of the present invention is not limited to the contents of the following description.

  Example 1 is an embodiment of the present invention. As shown in FIGS. 1 and 2, the rotary damper according to the first embodiment includes a cylinder (10), a first oil chamber (11), a second oil chamber (12), and a first partition wall (13). , Second partition wall (14), oil, first vane (15), second vane (16), shaft (17), first valve (18), second valve (19) and cap ( 20).

  The first and second oil chambers (11, 12) are formed in the cylinder (10) and are partitioned by the first and second partition walls (13, 14). The first and second partition walls (13, 14) are formed integrally with the cylinder (10). The oil is filled in the first and second oil chambers (11, 12). The first vane (15) is provided in the first oil chamber (11), and divides the first oil chamber (11) into a first chamber (21) and a second chamber (22). ing. The second vane (16) is provided in the second oil chamber (12), and divides the second oil chamber (12) into a third chamber (23) and a fourth chamber (24). ing. The first and second vanes (15, 16) are formed integrally with the shaft (17). The first valve (18) is provided on the first vane (15), and includes a first valve body (25), a first valve chamber (26), a first hole (27), a first flow. It has a channel (28), a second channel (29), and a first counterbore (30). The second valve (19) is provided on the second vane (16), and the second valve body (31), the second valve chamber (32), the second hole (33), and the third flow are provided. It has a channel (34), a fourth channel (35), and a second counterbore (36). The cap (20) is attached to the cylinder (10) and supports one end of the shaft (17). The other end of the shaft (17) is supported by the cylinder (10).

  The first valve (18) will be described in detail. The first valve chamber (26), the first hole (27), the first and second flow paths (28, 29), and the first counterbore (30) are as shown in FIGS. In addition, the first vane (15) is formed. The first valve chamber (26) and the first hole (27) are connected. The first valve chamber (26) has an inner diameter larger than the inner diameter of the first hole (27). The first flow path (28) is formed on the upper end surface of the first vane (15) in order to communicate the first valve chamber (26) and the second chamber (22). The second channel (29) is formed on the lower end surface of the first vane (15) in order to communicate the first hole (27) and the first chamber (21). The first counterbore (30) is formed on the upper end surface of the first vane (15). The first counterbore (30) has an inner diameter larger than the inner diameter of the first valve chamber (26).

  As shown in FIGS. 6 to 8, the first valve body (25) is one part made of a linear material. The first valve body (25) includes a first linear portion (37), a first elastic portion (38), and a first annular portion (39). The first elastic part (38) is a part formed in a coil shape and has elasticity. The first elastic portion (38) is a spring that is deformed by receiving a tensile load, and functions in the same manner as a tension coil spring. The first linear portion (37) is a linear portion extending perpendicularly from the first elastic portion (38), and exists on the central axis of the first elastic portion (38). The first annular portion (39) is a portion formed in an annular shape and exists at the upper end of the first elastic portion (38). The first annular portion (39) has an outer diameter larger than the outer diameter of the first elastic portion (38). The linear material is a material suitable for molding the first valve body (25) having the first linear portion (37) and the first elastic portion (38) as one component.

  As shown in FIG. 9, the first valve body (25) is accommodated in the first valve chamber (26). The first counterbore (30) has a depth that allows the first annular portion (39) to slide in the vertical direction. The bottom surface of the first counterbore (30) has a first annular portion (39). ) Can be supported. When the first valve body (25) is installed, the first annular portion (39) abuts the bottom surface of the first counterbore (30), and the first linear portion (37) is the first hole ( 27) is slightly inserted.

  In the prior art, first, the spring is put in the hole, and then the valve body is put in the valve chamber (see FIG. 2 of Japanese Patent No. 4625451). However, in the first embodiment, it is only necessary to put the first valve body (25) into the first valve chamber (26). Therefore, the process is halved compared to the prior art and the assembly is easy.

  The second valve (19) will be described in detail. The second valve chamber (32), the second hole (33), and the second counterbore hole (36) are formed in the second vane (16) as shown in FIGS. The first valve chamber (26), the first hole (27), and the first counterbore hole (30) have the same configuration. The third flow path (34) is formed on the upper end surface of the second vane (16) in order to communicate the second valve chamber (32) and the fourth chamber (24). The fourth channel (35) is formed on the lower end surface of the second vane (16) in order to communicate the second hole (33) and the third chamber (23). The second valve element (31) has the same configuration as the first valve element (25). The second valve element (31) is accommodated in the second valve chamber (32).

  The rotary damper according to the first embodiment operates as follows. That is, when the shaft (17) rotates in the clockwise direction in FIG. 1, the first and second vanes (15, 16) are inserted into the shafts (11, 12) in the first and second oil chambers (11, 12). By rotating in the same direction as 17), the oil in the second and fourth chambers (22, 24) is pressurized, and the oil in the first and third chambers (21, 23) is depressurized. Due to the pressure difference between the oil in the first chamber (21) and the oil in the second chamber (22), the first linear portion (37) enters the first hole (27). At the same time, due to the pressure difference between the oil in the third chamber (23) and the oil in the fourth chamber (24), the second linear portion (40) of the second valve body (31) is moved into the second hole ( Enter 33).

  The first elastic portion (38) is deformed when the first linear portion (37) enters the first hole (27). More specifically, when the first linear portion (37) enters the first hole (27), the first elastic portion (38) is deformed by receiving a tensile load. Similarly, the second elastic portion (41) of the second valve body (31) is also deformed when the second linear portion (40) enters the second hole (33).

  Due to the deformation of the first elastic part (38), a restoring force is generated in the first elastic part (38). Since this force becomes a resistance that prevents the first linear portion (37) from entering, the depth at which the first linear portion (37) enters the first hole (27) depends on the shaft (17 ) Becomes deeper as the force to rotate) increases. That is, when the force for rotating the shaft (17) is small, the oil pressure difference is small, so that the first linear portion (37) enters the first hole (27) as shown in FIG. When the depth of rotation becomes shallow and the force to rotate the shaft (17) is large, the oil pressure difference is large, so that the first linear portion (37) is in the first hole as shown in FIG. The depth to enter (27) becomes deeper. Similarly, the depth at which the second linear portion (40) enters the second hole (33) also increases as the force for rotating the shaft (17) increases.

  The greater the depth at which the first linear portion (37) enters the first hole (27), the more difficult it is for the oil to pass through the first hole (27). Therefore, the flow rate per unit time of the oil passing through the first hole (27) decreases as the depth at which the first linear portion (37) enters the first hole (27) becomes deeper. Similarly, the flow rate per unit time of the oil passing through the second hole (33) decreases as the depth at which the second linear portion (40) enters the second hole (33) becomes deeper. Accordingly, when the force for rotating the shaft (17) is small, the resistance of the oil received by the first and second vanes (15, 16) is small, and when the force for rotating the shaft (17) is large, The resistance of the oil received by the first and second vanes (15, 16) is increased. As a result, the rotational speed of the shaft (17) is substantially constant, that is, substantially the same speed even if the force for rotating the shaft (17) changes.

  On the other hand, when the shaft (17) rotates counterclockwise in FIG. 1, the first and second vanes (15, 16) are in the first and second oil chambers (11, 12). By rotating in the same direction as (17), the oil in the first and third chambers (21, 23) is pressurized, and the oil in the second and fourth chambers (22, 24) is depressurized. As shown in FIG. 12, due to the pressure difference between the oil in the first chamber (21) and the oil in the second chamber (22), the first annular portion (39) becomes the first counterbore (30). The first linear portion (37) escapes from the first hole (27). At the same time, due to the pressure difference between the oil in the third chamber (23) and the oil in the fourth chamber (24), the second annular portion (42) of the second valve body (31) is moved into the second counterbore ( It slides away from the bottom surface of 36), and the second linear portion (40) escapes from the second hole (33). At this time, since the oil passes through the fully opened first and second holes (27, 33), the resistance of the oil received by the first and second vanes (15, 16) becomes very small.

  As described above, in the rotary damper according to the first embodiment, the valve bodies (first and second valve bodies (25, 31)) are linear portions (first and second linear portions (37, 40)). ) And elastic parts (first and second elastic parts (38, 41)), the flow rate of oil passing through the holes (first and second holes (27, 33)) with one component is controlled. can do. Further, since it is a single component, there is an advantage that the flow rate can be easily adjusted and the variation in the flow rate is less than that of the combination of two conventional components.

  Example 2 is another embodiment of the present invention. As shown in FIG. 13, the valve (43) employed in Example 2 has a valve body (44), a valve chamber (45), a hole (46), and two flow paths (47, 48). It is configured. As shown in FIGS. 14 to 16, the valve body (44) is one part made of a linear material, and has a linear part (49) and an elastic part (50). The elastic part (50) is a part formed in a coil shape and has elasticity. The elastic portion (50) is a spring that is deformed by receiving a compression load, and functions in the same manner as a compression coil spring. The linear portion (49) is a linear portion extending from the elastic portion (50), and exists on the central axis of the elastic portion (50).

  The valve body (44) is accommodated in the valve chamber (45) as shown in FIG. The valve chamber (45) has a depth that allows the elastic portion (50) to slide in the vertical direction, and the bottom surface of the valve chamber (45) can support the elastic portion (50). When the valve body (44) is installed, the elastic portion (50) contacts the bottom surface of the valve chamber (45), and the linear portion (49) is slightly inserted into the hole (46). In the second embodiment, similarly to the first embodiment, it is only necessary to put the valve body (44) into the valve chamber (45). Therefore, the process is halved compared to the prior art, and the assembly is easy.

  The elastic part (50) is deformed when the linear part (49) enters the hole (46) due to the oil pressure difference. More specifically, when the linear portion (49) enters the hole (46), the elastic portion (50) is deformed by receiving a compressive load. Due to the deformation of the elastic part (50), a restoring force is generated in the elastic part (50). Since this force becomes a resistance that prevents the linear portion (49) from entering, the depth at which the linear portion (49) enters the hole (46) increases as the force for rotating the shaft increases. That is, when the force for rotating the shaft is small, the oil pressure difference is small, and as shown in FIG. 17, the depth at which the linear portion (49) enters the hole (46) becomes shallow, and the shaft is When the rotating force is large, the oil pressure difference is large, and as shown in FIG. 18, the depth at which the linear portion (49) enters the hole (46) increases.

  The greater the depth at which the linear portion (49) enters the hole (46), the more difficult it is for the oil to pass through the hole (46), so the flow rate of oil per unit time passing through the hole (46) is The depth at which the shape portion (49) enters the hole (46) decreases as the depth increases. Therefore, when the force that rotates the shaft is small, the resistance of the oil that the vane receives is small, and when the force that rotates the shaft is large, the resistance of the oil that the vane receives increases. As a result, the rotational speed of the shaft is substantially constant, that is, substantially the same speed even if the force for rotating the shaft changes.

  When the shaft rotates in the reverse direction, as shown in FIG. 19, the elastic portion (50) slides away from the bottom surface of the valve chamber (45) due to the oil pressure difference, and the linear portion (49) Escape from hole (46). At this time, since the oil passes through the fully open hole (46), the resistance of the oil received by the vane becomes very small.

  As described above, in the rotary damper according to the second embodiment, since the valve body (44) has the linear portion (49) and the elastic portion (50), the flow rate of oil passing through the hole (46) with one component is as follows. Can be controlled. Further, since it is a single component, there is an advantage that the flow rate can be easily adjusted and the variation in the flow rate is less than that of the combination of two conventional components.

DESCRIPTION OF SYMBOLS 10 Cylinder 11 1st oil chamber 12 2nd oil chamber 13 1st partition 14 Second partition 15 1st vane 16 2nd vane 17 Shaft 18 1st valve 19 2nd valve 20 Cap 21 1st 1 chamber 22 2nd chamber 23 3rd chamber 24 4th chamber 25 1st valve body 26 1st valve chamber 27 1st hole 28 1st flow path 29 2nd flow path 30 1st Counterbore hole 31 Second valve element 32 Second valve chamber 33 Second hole 34 Third flow path 35 Fourth flow path 36 Second counterbore 37 First linear portion 38 First elasticity Part 39 First annular part 40 Second linear part 41 Second elastic part 42 Second annular part 43 Valve 44 Valve body 45 Valve chamber 46 Hole 47, 48 Channel 49 Linear part 50 Elastic part

Claims (4)

  The valve includes a valve body, the valve body has a linear portion inserted into a hole through which oil passes, and has elasticity, and the linear portion is brought into the hole by a pressure difference of oil. A rotary damper comprising: an elastic portion that deforms when entering.   The rotary damper according to claim 1, wherein the valve body is made of a linear material.   The rotary damper according to claim 1, wherein the elastic portion is a spring that is deformed by receiving a tensile load.   The rotary damper according to claim 1, wherein the elastic portion is a spring that is deformed by receiving a compressive load.

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