Bidirectional rotating damper

Abstract

To provide a bidirectional rotating damper capable of reducing wear by suppressing the occurrence of excessive force in a contact portions between a rotating member and a stopper wall of a housing.SOLUTION: The bidirectional rotating damper includes vanes 25A, 25B movably provided on blade parts 23A, 23B for sliding integrally with the blade parts 23A, 23B, and a recessed groove 28 provided in the housing 12 at an internal peripheral face 12a in a fluid chamber 13. The vanes 25A, 25B includes a first slide face 26A provided on the first direction side for moving to a rotating member 14 in contact with the internal peripheral face in the fluid chamber 13 at rotation to a first direction, and a second slide surface 26B provided on the second direction side for moving to the rotating member 14 in contact with the internal peripheral face 12a in the fluid chamber 13 at rotation to a second direction.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a two-way rotary damper that applies braking force in both directions during opening and closing, for example, when opening and closing a lid, door, etc.

Background Art

[0002] Conventionally, for example, when opening and closing a lid, door, etc., a two-way rotary damper that applies braking force in both directions during opening and closing is known from Patent Document 1 and the like.

[0003] FIG. 9 is a schematic cross-sectional view showing an example of a conventional rotary damper 100 known from Patent Document 1. The rotary damper 100 includes a housing 101 having a fluid chamber 102 filled with and sealed with fluid, a base 103a housed in the fluid chamber 102, and a shaft portion (not shown) protruding outside the fluid chamber 102. It is composed of a rotary member 103 that is rotatable relative to the housing 101, a stopper wall 104 provided on the housing 101 to limit the rotation angle of the rotary member 103 in the fluid chamber 102, and blades 103b provided on the base 103a of the rotary member 103 for generating torque in cooperation with the stopper wall 104 when the rotary member 103 rotates relatively. Further, the rotary damper 100 has one partition wall 105 and the fluid chamber 102 is also a single chamber. The fluid chamber 102 is partitioned into two chambers, a first fluid chamber 102A and a second fluid chamber 102B, by the blades 103b. As the rotary member 103 rotates, the fluid moves to the first fluid chamber 102A side and the second fluid chamber 102B side, thereby providing braking force in both directions.

[0004] Furthermore, as shown in Figure 9(a), when the rotating member 103 of the rotary damper 100 is rotated counterclockwise and the first fluid chamber 102A enters the high torque range, the pressure P pushes the rotating member 103 in the direction 180 degrees opposite to the high torque range (in the direction of arrow 106A in the figure). Conversely, as shown in Figure 9(b), when the rotating member 103 is rotated clockwise and the second fluid chamber 102B enters the high torque range, the pressure P pushes the rotating member 103 in the direction 180 degrees opposite to the high torque range (in the direction of arrow 106B in the figure). In other words, depending on the direction of rotation, the rotating member 103 moves (shifts) in the direction of arrow 106A or arrow 106B. [Prior art documents] [Patent Documents]

[0005] [Patent Document 1] Japanese Patent Publication No. 2002-295561 [Overview of the Initiative] [Problems that the invention aims to solve]

[0006] As described above, the rotary damper 100 shown in Figure 9, known from Patent Document 1, etc., has a single partition wall and a single fluid chamber 102. Therefore, as shown in Figure 9(a), when the rotating member 103 is rotated counterclockwise and the first fluid chamber 102A enters the high torque range, the pressure pushes the rotating member 103 in the direction opposite to the high torque range (direction of arrow 106A in the figure) and causes it to move. Conversely, as shown in Figure 9(b), when the rotating member 103 is rotated clockwise and the second fluid chamber 102B enters the high torque range, the pressure pushes the rotating member 103 in the direction opposite to the high torque range (direction of arrow 106B in the figure), causing the rotating member 103 to move (shift), which is a problem. As a result of this action, the rotating member 103 rotates eccentrically, causing the outer diameter portion of the rotating member 103 and the partition wall 105 of the housing 101 to come into strong contact at the portion indicated by reference numeral 107 in Figures 9(a) and (b). This excessive force leads to wear on the portion indicated by reference numeral 107, which is a problem.

[0007] Therefore, a technical challenge arises in providing a bidirectional rotation damper that can reduce wear by suppressing the generation of excessive force at the contact point between the rotating member and the stopper wall of the housing. The present invention aims to solve this challenge. [Means for solving the problem]

[0008] The present invention has been proposed to achieve the above objective, and the invention described in claim 1 is a bidirectional rotation damper having a housing having a fluid chamber filled with fluid, a rotating member having a vane portion located in the fluid chamber and rotatable relative to the housing, a stopper wall provided in the housing for limiting the rotation angle of the rotating member in the fluid chamber, and a torque generating means for generating torque in cooperation with the stopper wall when the rotating member rotates relative to the housing, wherein the torque generating means comprises a vane movably provided on the vane portion and sliding integrally with the vane portion, and provided on the inner circumferential wall of the fluid chamber in the housing , formed with a width smaller than the axial length of the vane The vane is provided with a recessed groove, and when the rotating member rotates in the first direction, the fluid chamber Excluding the aforementioned groove A first sliding surface provided on the first direction side that slides in contact with the inner circumferential wall, and the fluid chamber when the rotating member rotates in the second direction Excluding the aforementioned groove The present invention provides a bidirectional rotation damper comprising a second sliding surface provided on the second direction side that slides in contact with the inner circumferential wall.

[0009] In this configuration, when the rotating member rotates in the first direction, the fluid filling the first direction side of the fluid chamber flows through the groove to the second direction side of the fluid chamber. When the first sliding surface rotates beyond the groove, it enters a high torque range, and braking force is applied. Conversely, when the rotating member rotates in the second direction, the fluid filling the second direction side of the fluid chamber flows through the groove to the first direction side of the fluid chamber. When the second sliding surface rotates beyond the groove, it enters a high torque range, and braking force is applied. Therefore, in this configuration, even when the rotating member rotates and enters a high torque range, the pressure is pushed back in the direction of rotation opposite to that of the rotating member. This causes strong contact between the outer diameter of the rotating member and the stopper wall of the housing, preventing wear on the outer diameter of the rotating member and the stopper wall of the housing caused by excessive force due to contact.

[0010] The invention described in claim 2 provides a bidirectional rotation damper in which, in the configuration described in claim 1, two stopper walls are provided on the inner circumferential surface of the housing, forming two fluid chambers, a first fluid chamber and a second fluid chamber, that face each other with the rotating member in between.

[0011] This configuration forms two fluid chambers, a first fluid chamber and a second fluid chamber, directly opposite each other with the rotating member in between. This balances the pressing force in each fluid chamber, preventing the rotating member from moving horizontally (slipping). This further prevents wear on the outer diameter of the rotating member and the stopper wall of the housing. Specifically, when the rotating member rotates in the first direction, the fluid that was filled in the first direction side of the first fluid chamber flows through one groove to the fluid chamber on the second direction side. When the first sliding surface rotates beyond one groove, it enters a high torque range, and a braking force is applied. At this time, the fluid that was filled in the first direction side of the second fluid chamber, which is directly opposite the first fluid chamber with the rotating member as the center, also enters a high torque range beyond the other groove, and a braking force is applied simultaneously with the first fluid chamber. Conversely, when the rotating member rotates in the second direction, the fluid that was filled on the second direction side of the first fluid chamber flows through one groove into the fluid chamber on the first direction side, and when the second sliding surface rotates beyond one groove, it enters a high torque range and a braking force is applied. The fluid that was filled on the second direction side of the second fluid chamber also enters a high torque range beyond the other groove, and a braking force is applied simultaneously with the first fluid chamber. Therefore, in this configuration, even when the rotating member rotates and enters a high torque range, the pressure is balanced directly around the rotating member, the rotating member rotates without eccentricity, and a condition in which the rotating member moves horizontally (shifts) can be prevented.

[0012] The invention described in claim 3 provides a bidirectional rotation damper, wherein, in the configuration described in claim 1, the rotating member further comprises a base portion housed in the fluid chamber and a shaft portion protruding outside the fluid chamber, the rotating member is supported by a first bearing on the base side and by a second bearing on the shaft portion side, the housing has an opening on one end side that is closed by a cap and a bearing projection on the other closed end side that supports the first bearing, the first bearing has an air vent hole that penetrates from the rotating member side to the bearing projection side, and the cap supports the rotating member via the second bearing.

[0013] In this configuration, the rotating member is supported at its base by a first bearing and at its shaft by a second bearing, with the housing and rotating member positioned coaxially. This allows the rotating member to rotate smoothly relative to the housing without eccentricity, preventing wear on the rotating member, housing, and cap. Furthermore, the first bearing is provided with an air vent hole, facilitating the press-fitting of the first bearing into the rotating member and maintaining the accuracy of the bidirectional rotation damper.

[0014] The invention described in claim 4 provides a bidirectional rotation damper, wherein, in the configuration described in claim 3, a relief groove is provided on the bearing projection, extending from the tip of the bearing projection toward the other end of the housing body.

[0015] With this configuration, a relief groove is provided on the bearing protrusion, extending from the tip of the bearing protrusion toward the other end of the housing body. Therefore, when assembling the bidirectional rotation damper, the fluid that accumulates between the first bearing and the bearing protrusion can be guided through the relief groove toward the other end of the housing body, and further circulated to the outside of the rotating member and returned to the fluid chamber side.

[0016] The invention described in claim 5 provides a bidirectional rotation damper in which the first sliding surface and the second sliding surface of the vane are formed substantially symmetrically, in the configuration described in any one of claims 1 to 4.

[0017] With this configuration, the braking force when the rotating member is rotated in the first direction and the braking force when it is rotated in the second direction can be set to be approximately the same.

[0018] The invention described in claim 6 provides a bidirectional rotation damper in which, in the configuration described in any one of claims 1 to 5, the vane is provided so as to be able to swing in the first direction and the second direction with the tip of the blade portion as a pivot point.

[0019] This configuration allows the vanes to be pivotably fitted and connected to the tips of the blade portions of the rotating member.

[0020] The invention according to claim 7 provides a bi-directional rotary damper in which, in the configuration according to any one of claims 1 to 5, a through-hole penetrating vertically is formed between the first sliding surface and the second sliding surface of the vane, and the vane is formed slidable in the first direction and the second direction with respect to the blade portion. When the vane is slid in the first direction, the fluid filled on the first direction side is discharged to the second direction side through the through-hole, and when the vane is slid in the second direction, the fluid filled on the second direction side is discharged to the first direction side through the through-hole.

[0021] According to this configuration, the cross-sectional shape of the connection groove of the vane connected to the blade portion of the rotating member is formed in a substantially rectangular shape, and the connection groove of the vane can be loosely fitted and connected to the blade portion of the rotating member so as to be slidable in the circumferential direction. Further, a fluid flow path can be formed by using the gap and the through-hole formed by sliding in the circumferential direction.

[0023] Claim 8 The invention according to claim provides a bi-directional rotary damper in which, in the configuration according to claim 1, the first sliding surface and the second sliding surface are provided separately from each other.

Effect of the Invention

[0024] According to the present invention, even when the rotating member rotates and enters the high torque region, the pressure is pushed back in the rotational direction opposite to the rotation of the rotating member, and the rotating member is not pressed against the 180-degree facing surface in the high torque region. Therefore, it is possible to prevent the state where the rotating member moves (shifts) in the horizontal direction. As a result, the outer diameter portion of the rotating member and the stopper wall of the housing come into strong contact, and it is possible to prevent wear and the like of the outer diameter portion of the rotating member and the stopper wall of the housing due to excessive force caused by the contact, and the life of each member can be extended.

Brief Description of the Drawings

[0025] [Figure 1]The double-direction rotary damper of the first embodiment according to the embodiment of the present invention is shown. (a) is a front view thereof, (b) is a sectional view taken along line A-A of (a), and (c) is a sectional view taken along line B-B of (b). [Figure 2] It is an exploded perspective view of the double-direction rotary damper of the first embodiment described above. [Figure 3] The vane in the double-direction rotary damper of the first embodiment described above is shown. (a) is an external perspective view seen from the outer peripheral side, (b) is an external perspective view seen from the inner peripheral side, (c) is a plan view seen from the outer peripheral side, (d) is a plan view seen from the inner peripheral side, (e) is a side view seen from the direction of arrow X in (a), (f) is a side view seen from the direction of arrow Y in (a), (g) is a sectional view taken along line C-C of (e), and (h) is a sectional view taken along line D-D of (f). [Figure 4] It is an operation explanatory view of the double-direction rotary damper in the first embodiment described above. [Figure 5] The double-direction rotary damper of the second embodiment according to the embodiment of the present invention is shown. (a) is a front view thereof, (b) is a sectional view taken along line E-E of (a), and (c) is a sectional view taken along line F-F of (b). [Figure 6] It is an exploded perspective view of the double-direction rotary damper of the second embodiment described above. [Figure 7] The vane in the double-direction rotary damper of the second embodiment described above is shown. (a) is an external perspective view seen from the outer peripheral side, (b) is an external perspective view seen from the inner peripheral side, (c) is a plan view seen from the outer peripheral side, (d) is a plan view seen from the inner peripheral side, (e) is a side view seen from the direction of arrow X in (a), (f) is a side view seen from the direction of arrow Y in (a), (g) is a sectional view taken along line G-G of (e), and (h) is a sectional view taken along line H-H of (f). [Figure 8] It is an operation explanatory view of the double-direction rotary damper in the second embodiment described above. [Figure 9] It is a schematic sectional view showing an example of a conventional double-direction rotary damper. (a) is a view for explaining the action when the rotating member is rotated from the neutral position to the counterclockwise direction end, and (b) is a view for explaining the action when the rotating member is rotated from the neutral position to the clockwise direction end.

Mode for Carrying Out the Invention

[0026] The present invention aims to provide a bidirectional rotation damper capable of reducing wear by suppressing the generation of excessive force at the contact portion between the rotating member and the stopper wall of the housing. The present invention provides a bidirectional rotation damper comprising: a housing having a fluid chamber filled with fluid; a rotating member having a vane portion located in the fluid chamber and rotatable relative to the housing; a stopper wall provided in the housing that limits the rotation angle of the rotating member within the fluid chamber; and a torque generating means that generates torque in cooperation with the stopper wall when the rotating member rotates relative to the housing. The torque generating means comprises a vane movably provided on the vane portion and sliding integrally with the vane portion; and a groove provided in the inner circumferential wall of the fluid chamber in the housing. The vane comprises a first sliding surface provided on the first direction side that slides in contact with the inner circumferential wall of the fluid chamber when the rotating member rotates in the first direction; and a second sliding surface provided on the second direction side that slides in contact with the inner circumferential wall of the fluid chamber when the rotating member rotates in the second direction. [Examples]

[0027] Hereinafter, an embodiment of the present invention will be described in detail with reference to the accompanying drawings. In the following embodiments, when referring to the number, numerical values, quantities, ranges, etc., of the components, unless specifically indicated or clearly limited in principle to a particular number, the number is not limited to that particular number, and may be greater than or less than that number.

[0028] Furthermore, when referring to the shape, positional relationship, etc. of constituent elements, unless otherwise explicitly stated or it is clearly considered not to be so in principle, this includes things that are substantially similar or alike to those shapes, etc.

[0029] Furthermore, drawings may exaggerate features by enlarging characteristic parts to make them easier to understand, and the dimensional ratios of components may not be the same as in reality. Also, in cross-sectional drawings, hatching of some components may be omitted to make the cross-sectional structure of the components easier to understand.

[0030] Furthermore, in the following description, expressions indicating directions such as up and down or left and right are not absolute. They are appropriate when each part of the bidirectional rotation damper of the present invention is depicted in the orientation shown, but should be interpreted in accordance with the change in orientation if that orientation changes. Also, the same reference numerals are used for the same elements throughout the description of the embodiments.

[0031] Figures 1 and 2 show a bidirectional rotation damper 10A of the first embodiment according to the present invention, where (a) in Figure 1 is a front view thereof, (b) is a cross-sectional view along line AA in (a), and (c) is a cross-sectional view along line BB in (b), and Figure 2 is an exploded perspective view of the bidirectional rotation damper 10A. In the following description, the left side in the left-right direction of Figure 1(b) will be described as the front in the front-rear direction of the bidirectional rotation damper 10A, and the right side will be described as the rear.

[0032] In Figures 1 and 2, the bidirectional rotating damper 10A has a structure in which the base portion 14A of the rotating member 14 is incorporated into a fluid chamber 13 of a housing 12 that is filled and sealed with a fluid 11 such as highly viscous silicone oil, and the shaft portion 14B of the rotating member 14 protrudes to the outside of the fluid chamber 13.

[0033] The housing 12 is made of die-cast metal, and one end 12A of the housing 12 (hereinafter referred to as the "closed end 12A") is closed and forms one side wall of the fluid chamber 13. A bearing projection 15 is formed in the center of the closed end 12A on the fluid chamber 13 side. The other end 12B of the housing 12 (hereinafter referred to as the "open end 12B") is open and is closed in a sealed state by fitting and fixing an annular die-cast end cap 18 to a resin annular pressure partition plate 16 that forms the other side wall of the fluid chamber 13, via rubber O-rings 17A and 17B which are sealing members. The fitting and fixing of the end cap 18 to the open end 12B is performed by screw connection between a male thread formed on the outer circumference of the end cap 18 and a female thread formed on the inner circumference of the opening of the open end 12B.

[0034] The rotating member 14 is supported on the bearing projection 15 of the housing 12 via a first bearing 20, which consists of a bush inserted into a recess 19 provided at one end of the base 14A, and on the end cap 18 via a second bearing 21, which consists of a bush that penetrates the central part of the pressure bulkhead plate 16 and the end cap 18 and is interposed between the end cap 18 and the shaft portion 14B. The rotating member 14 is thus supported on the housing 12 by the first bearing 20 and the second bearing 21, allowing it to rotate relative to the housing 12.

[0035] The fluid chamber 13 of the housing 12 is provided with two stopper walls 22 that protrude from the inner circumferential surface 12a of the housing 12 toward the center, thereby dividing the fluid chamber 13 into a first fluid chamber 13A and a second fluid chamber 13B. The two stopper walls 22 are positioned so as to be approximately 180 degrees apart from each other in the circumferential direction, and the protrusions of each stopper wall 22 extend to a position where they are approximately in contact with the outer circumferential surface of the base 14A. Therefore, the first fluid chamber 13A and the second fluid chamber 13B are positioned so as to be approximately 180 degrees apart from each other in the circumferential direction.

[0036] The stopper wall 22 has both the function of limiting the rotation angle of the rotating member 14 and the function of generating torque. On a part of the outer circumferential surface of the base portion 14A of the rotating member 14, a convex first vane portion 23A and a second vane portion 23B are provided along the axial direction of the rotating member 14, at positions that are approximately 180 degrees apart in the circumferential direction from each other. Furthermore, a first vane 25A and a second vane 25B, which constitute torque generating means that generate torque in cooperation with the stopper wall 22, are respectively attached to the tips of the first vane portion 23A and the second vane portion 23B so as to be able to swing in the circumferential direction of the rotating member 14.

[0037] The tip of the first vane portion 23A and the tip of the second vane portion 23B have a circular cross-section, and the connecting portion 24A between the first vane 25A and the second vane 25B has a C-shaped groove in cross-section. The connecting portion 24A is provided approximately in the center of the rotational direction of the first vane 25A and the second vane 25B, corresponding to the tip of the first vane portion 23A and the tip of the second vane portion 23B, respectively. The tip of the first wing portion 23A and the first vane 25A, and the tip of the second wing portion 23B and the second vane 25B are connected to the rotating member 14 so as to be able to swing (or rotate) in the circumferential direction by fitting the circular cross-sectional tips of the first wing portion 23A and the second wing portion 23B into the C-shaped connecting portion 24A. After connection, the first vane 25A and the second vane 25B are mounted so as to be able to swing back and forth in the circumferential direction of the rotating member 14, with the respective tips of the first wing portion 23A and the second wing portion 23B as pivot points. Furthermore, after mounting, when the rotating member 14 is rotated, the first vane 25A and the second vane 25B move along the inner circumferential surface 12a of the housing 12, which is integrated with the rotating member 14, in the same direction as the rotating member 14.

[0038] The first vane 25A and the second vane 25B have substantially the same structure. The first vane 25A and the second vane 25B are also shown as individual parts in Figure 3. Further explanation with reference to Figure 3 is provided, on the outer surface side of the housing 12 facing the inner circumferential surface 12a, and on both sides of the rotating member 14 in the direction of rotation, with the connecting portion 24A in between, the first sliding surface 26A and the second sliding surface 26B are provided in a substantially symmetrical manner. In addition, recesses 27 are formed in the front and rear portions of the first sliding surface 26A and the second sliding surface 26B, respectively, that are recessed inward from the first sliding surface 26A and the second sliding surface 26B. Then, as the rotating member 14 rotates in the first direction (clockwise), the first vane 25A and the second vane 25B rotate in the second direction (counterclockwise) with the tip of the first wing portion 23A and the tip of the second wing portion 23B as pivot points, respectively. As a result, the second slide surface 26B separates from the inner circumferential surface 12a of the housing 12, while the first slide surface 26A slides in the first direction while remaining in contact with the inner circumferential surface 12a of the housing 12. Conversely, when the rotating member 14 rotates in the second direction (counterclockwise), the first vane 25A and the second vane 25B rotate in the first direction (clockwise) with the tip of the first blade portion 23A and the tip of the second blade portion 23B as pivot points, respectively, so that the first sliding surface 26A moves away from the inner circumferential surface 12a of the housing 12, and the second sliding surface 26B slides in the second direction while remaining in contact with the inner circumferential surface 12a of the housing 12.

[0039] Furthermore, grooves 28 are provided on the inner circumferential surface 12a of the housing 12, which forms the fluid chamber 13, corresponding to the first fluid chamber 13A and the second fluid chamber 13B, respectively. The axial width of the grooves 28 is formed to be slightly smaller than the axial width of the first vane 25A and the second vane 25B, as shown in Figure 1(b). In addition, both ends of the grooves 28 in the circumferential direction extend to a position that slightly corresponds to the recess 27 when the first vane 25A and the second vane 25B are positioned as shown in Figure 4(a) and Figure 4(c), respectively, where their rotation is limited by the stopper wall 22, as described later, so that the fluid 11 in the high torque range can escape to the low torque range side through the grooves 28.

[0040] Furthermore, the first bearing 20 is provided with an air vent hole 29 that penetrates from the rotating member 14 side to the bearing projection 15 side, and a relief groove 30 is provided on the outer circumferential surface of the bearing projection 15, which is formed continuously from the tip of the bearing projection 15 toward the other end of the housing 12, that is, from the tip of the bearing projection 15 toward the inner surface of the closed end 12A. The air vent hole 29 facilitates the press-fitting of the first bearing 20 into the rotating member 14 by releasing air that has entered between the first bearing 20 and the rotating member 14, and also maintains the accuracy of the bidirectional rotation damper 10A. On the other hand, the relief groove 30 guides the fluid 11 that has entered and accumulated between the first bearing 20 and the bearing projection 15 toward the other end of the housing 12 (closed end 12A side) through the relief groove 30, and further circulates it toward the outside of the rotating member 14 and returns it to the fluid chamber 13 side.

[0041] Figure 4 is an operational diagram of the bidirectional rotating damper 10A. The operation of the bidirectional rotating damper 10A will be explained next using Figure 4.

[0042] In Figure 4(a), when the rotating member 14 rotates in the first direction (clockwise) indicated by arrow 51A, the pressure-receiving surfaces 31 of the first vane 25A and the second vane 25B are resisted by the viscous fluid 11 in the fluid chamber 13, and the first vane 25A and the second vane 25B rotate in the counterclockwise direction indicated by arrow 52A, with the tips of the first and second blade portions 23A and 23B respectively acting as pivot points, and the first sliding surface 26A comes into contact with the inner circumferential surfaces 12a of the first and second fluid chambers 13A and 23B, respectively. Since recesses 27 serving as fluid passages are formed in the first sliding surfaces 26A and 26B of the first vane 25A and the second vane 25B, the fluid 11 on the clockwise side in the first fluid chamber 13A and the second fluid chamber 13B flows counterclockwise through the grooves 28 and recesses 27, as shown by the dotted line 11A in Figure 4(a). As a result, the rotating member 14 and the housing 12 rotate relative to each other with low torque.

[0043] Furthermore, as the rotation of the rotating member 14 progresses, the first sliding surface 26A reaches the end of the groove 28 provided on the inner circumferential surface 12a of the housing 12, and as shown in Figure 4(b), the first sliding surface 26A comes into contact with the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively. Up to the state shown in Figure 4(b), the fluid 11 in the clockwise direction within the first fluid chamber 13A and the second fluid chamber 13B is in a low torque range, flowing counterclockwise through the groove 28 and recess 27, allowing the rotating member 14 and the housing 12 to rotate relative to each other with low torque. However, when the first sliding surface 26A contacts the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively, beyond the portion where the groove 28 is provided, the fluid 11 flows little by little in the counterclockwise direction through the gap between the inner circumferential surface 12a of the housing 12 and the first vane 25A and the second vane 25B, and through the gap between the first blade portion 23A and the second blade portion 23B and the first vane 25A and the second vane 25B. As a result, the rotating member 14 and the housing 12 enter a high torque range and rotate slowly relative to each other. This slow relative rotation continues until the first vane 25A and the second vane 25B collide with the stopper wall 22 and their rotation is restricted. Figure 4(c) shows the state in this high torque range.

[0044] The above describes the operation when the rotating member 14 is rotated in the first direction (clockwise) indicated by arrow 51A. Next, we will explain the operation when the rotating member 14 is rotated from the state where it is stopped at the first direction end shown in Figure 4(c) to the second direction (counterclockwise) end.

[0045] In Figure 4(d), when the rotating member 14 rotates in the second direction (counterclockwise) indicated by arrow 51B, the pressure-receiving surfaces 31 of the first vane 25A and the second vane 25B are resisted by the fluid 11, and the first vane 25A and the second vane 25B rotate in the clockwise direction indicated by arrow 52B, with the tips of the first blade portion 23A and the second blade portion 23B as pivot points, respectively, and the second sliding surface 26B comes into contact with the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively. Since recesses 27 serving as fluid passages are formed in the first sliding surface 26A and the second sliding surface 26B of the first vane 25A and the second vane 25B, the fluid 11 on the counterclockwise side in the first fluid chamber 13A and the second fluid chamber 13B flows clockwise through the groove 28 and the recesses 27. As a result, the rotating member 14 and the housing 12 rotate relative to each other with low torque.

[0046] Furthermore, as the rotation of the rotating member 14 progresses, the first sliding surface 26A reaches the end of the groove 28 provided on the inner circumferential surface 12a of the housing 12, and as shown in Figure 4(e), the second sliding surface 26B comes into contact with the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively. Up to the state shown in Figure 4(e), the fluid 11 in the counterclockwise direction within the first fluid chamber 13A and the second fluid chamber 13B is in a low torque range, flowing clockwise through the groove 28 and the recess 27, allowing the rotating member 14 and the housing 12 to rotate relative to each other with low torque. However, when the second sliding surface 26B comes into contact with the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively, beyond the portion where the groove 28 is provided, the fluid 11 flows little by little clockwise through the gap between the inner circumferential surface 12a of the housing 12 and the first vane 25A and the second vane 25B, and through the gap between the first blade portion 23A and the second blade portion 23B and the first vane 25A and the second vane 25B. As a result, the rotating member 14 and the housing 12 enter a high torque range and rotate slowly relative to each other. This slow relative rotation continues until the first vane 25A and the second vane 25B collide with the stopper wall 22 and their rotation is restricted. Figure 4(f) shows the state in this high torque range.

[0047] Therefore, in the bidirectional rotating damper 10A shown in the first embodiment, regardless of whether it rotates in the first direction (clockwise) or the second direction (counterclockwise), it can rotate smoothly with low torque before reaching the end, and as it approaches the end, it can rotate slowly with high torque. Thus, when this bidirectional rotating damper 10A is applied to the opening and closing mechanism of the lid door, braking force can be applied in both directions during opening and closing, so that it can close slowly at the closing end, preventing accidents such as finger pinching.

[0048] Furthermore, when the rotating member 14 rotates in the first direction, the fluid 11 that was filled on the first direction side of the fluid chamber 13 flows through the recess 27 and groove 28 to the fluid chamber 13 on the second direction side, and when the first sliding surface 26A rotates beyond the groove 28, it enters a high torque range and a braking force is applied. Conversely, when the rotating member 14 rotates in the second direction, the fluid 11 that was filled on the second direction side of the fluid chamber 13 flows through the recess 27 and groove 28 to the fluid chamber 13 on the first direction side, and when the second sliding surface 26B rotates beyond the groove 28, it enters a high torque range and a braking force is applied. Therefore, in this configuration, even when the rotating member 14 rotates and enters a high torque range, the pressure is balanced directly in front of the rotating member 14, the rotating member 14 rotates without eccentricity, and it is possible to prevent the rotating member 14 from moving horizontally (shifting). This prevents the base 14A of the rotating member 14 and the stopper wall 22 of the housing 12 from coming into strong contact. In other words, wear caused by strong contact between the base 14A of the rotating member 14 and the stopper wall 22 of the housing 12 can be prevented.

[0049] Figures 5 and 6 show a bidirectional rotation damper 10B of a second embodiment according to the present invention. Figure 5(a) is a front view thereof, (b) is a cross-sectional view along the EE line of (a), and (c) is a cross-sectional view along the FF line of (b). Figure 6 is an exploded perspective view of the bidirectional rotation damper 10B. In the following description, the left side in the left-right direction of Figure 5(b) will be described as the front in the front-rear direction of the bidirectional rotation damper, and the right side will be described as the rear. Furthermore, the bidirectional rotation damper 10B of the second embodiment shown in Figures 5 and 6 is a modified version of the structure of the first vane portion 23A and second vane portion 23B and the first vane 25A and second vane 25B of the base portion 14A of the bidirectional rotation damper 10A of the first embodiment shown in Figures 1 to 4. The other structures are substantially the same, and it performs the same function. Therefore, the same reference numerals are used for the same components as in the bidirectional rotation damper 10A of the first embodiment shown in Figures 1 to 4, and some explanations are omitted.

[0050] In Figures 5 and 6, the bidirectional rotating damper 10B has a structure in which the base portion 14A of the rotating member 14 is incorporated into a fluid chamber 13 of a housing 12 that is filled and sealed with a fluid 11 such as highly viscous silicone oil, and the shaft portion 14B of the rotating member 14 protrudes to the outside of the fluid chamber 13.

[0051] The housing 12 is made of die-cast metal, and one end 12A of the housing 12 (hereinafter referred to as the "closed end 12A") is closed and forms one side wall of the fluid chamber 13. A bearing projection 15 is formed in the center of the closed end 12A on the fluid chamber 13 side. The other end 12B of the housing 12 (hereinafter referred to as the "open end 12B") is open and is closed in a sealed state by fitting and fixing an annular die-cast end cap 18 to a resin annular pressure partition plate 16 that forms the other side wall of the fluid chamber 13, via rubber O-rings 17A and 17B which are sealing members. The fitting and fixing of the end cap 18 to the open end 12B is performed by screw connection between a male thread formed on the outer circumference of the end cap 18 and a female thread formed on the inner circumference of the opening of the open end 12B.

[0052] The rotating member 14 is supported on the bearing projection 15 of the housing 12 via a first bearing 20, which consists of a bush inserted into a recess 19 provided at one end of the base 14A, and on the end cap 18 via a second bearing 21, which consists of a bush that penetrates the central part of the pressure bulkhead plate 16 and the end cap 18 and is interposed between the end cap 18 and the shaft portion 14B. The rotating member 14 is thus supported on the housing 12 by the first bearing 20 and the second bearing 21, allowing it to rotate relative to the housing 12.

[0053] The fluid chamber 13 of the housing 12 is divided into a first fluid chamber 13A and a second fluid chamber 13B by two stopper walls 22 that protrude from the inner circumferential surface 12a of the housing 12 toward the center. The two stopper walls 22 are positioned approximately 180 degrees apart from each other in the circumferential direction, and the protrusions of each stopper wall 22 extend to a position where they are approximately in contact with the outer circumferential surface of the base 14A. Therefore, the first fluid chamber 13A and the second fluid chamber 13B are positioned approximately 180 degrees apart from each other in the circumferential direction.

[0054] The stopper wall 22 has both the function of limiting the rotation angle of the rotating member 14 and the function of generating torque. On a part of the outer circumferential surface of the base portion 14A of the rotating member 14, a convex first vane portion 23C and a second vane portion 23D are provided along the axial direction of the rotating member 14, at positions where they are displaced approximately 180 degrees relative to each other in the circumferential direction. Furthermore, a first vane 25C and a second vane 25D, which constitute torque generating means that generate torque in cooperation with the stopper wall 22, are respectively mounted on the tips of the first vane portion 23C and the second vane portion 23D so as to be slidable by an amount limited in the circumferential direction of the rotating member 14.

[0055] The tips of the first vane portion 23C and the second vane portion 23D have a rectangular cross-section, and the connecting portion 24B between the first vane 25C and the second vane 25D has a rectangular groove. The connecting portion 24B is provided approximately in the center of the rotational direction of the first vane 25C and the second vane 25D, corresponding to the tips of the first vane portion 23C and the second vane portion 23D, respectively. The tips of the first vane portion 23C and the first vane 25C, and the tips of the second vane portion 23D and the second vane 25D are loosely fitted into the connecting portion 24B, which has a rectangular groove, so that the respective rectangular tips of the first vane portion 23C and the second vane portion 23D can slide, and are connected so that they can slide by an amount limited to the circumferential direction of the rotating member 14. In other words, the circumferential groove width of the connecting portion 24B is formed to be larger than the circumferential width of the respective tips of the first vane portion 23C and the second vane portion 23D, and the first vane 25C and the second vane 25D can slide circumferentially relative to the first vane portion 23C and the second vane portion 23D, respectively, by the difference between the groove width and the circumferential width of the tips. In addition, the tips of the first vane portion 23C and the tips of the second vane portion 23D are each provided with a notch 33 that is removed from the tip surface toward the base portion 14A. The notch 33 functions as a flow path for the fluid 11.

[0056] The first vane 25C and the second vane 25D have substantially the same structure. The first vane 25C and the second vane 25D are also shown as individual parts in Figure 7. Further explanation with reference to Figure 7 is provided, on the outer surface side of the housing 12 facing the inner circumferential surface 12a, and on both sides of the rotating member 14 in the direction of rotation, with the connecting portion 24B in between, the first sliding surface 26C and the second sliding surface 26D are provided in substantially symmetrical configuration. In addition, recesses 27 are formed in the front and rear portions of the first sliding surface 26C and the second sliding surface 26D, respectively, that are recessed inward from the first sliding surface 26C and the second sliding surface 26D. Furthermore, a through hole 32 that functions as a fluid passage for the fluid 11 is provided in the vicinity of the center of the recess 27, extending through to the connecting portion 24B.

[0057] Then, when the rotating member 14 rotates in the first direction (clockwise), the first vane 25C and the second vane 25D slide in the second direction (counterclockwise) relative to the tip of the first blade portion 23C and the tip of the second blade portion 23D, causing a gap to form between the side surfaces of the tips of the tips of the first blade portion 23C and the second blade portion 23D on the second direction side and the inner surfaces of the first vane 25C and the second vane 25D on the second direction side, forming a passage through which the fluid 11 flows in the second direction (counterclockwise) through the gap between the recess 27, the through hole 32, the notch 33 and the base portion 14A. Conversely, when the rotating member 14 rotates in the second direction (counterclockwise), the first vane 25C and the second vane 25D slide in the first direction (clockwise) relative to the tip of the first blade portion 23C and the tip of the second blade portion 23D, causing a gap to form between the side surfaces of the tips of the first blade portion 23C and the second blade portion 23D on their respective first-direction sides and the inner surfaces of the first vane 25C and the second vane 25D on their respective first-direction sides, thereby forming a passage through which the fluid 11 flows to the first direction side through the gap between the recess 27, the through hole 32, the notch 33, and the base portion 14A.

[0058] Furthermore, grooves 28 are provided on the inner circumferential surface 12a of the housing 12, which forms the fluid chamber 13, corresponding to the first fluid chamber 13A and the second fluid chamber 13B, respectively. The axial width of the grooves 28 is formed to be slightly smaller than the axial width of the first vane 25C and the second vane 25D, as shown in Figure 5(b). In addition, both ends of the grooves 28 in the circumferential direction extend to a position that slightly corresponds to the recess 27 when the first vane 25C and the second vane 25D are positioned as shown in Figure 8(a) and Figure 8(c), which will be described later, where their rotation is limited by the stopper wall 22, respectively, so that the fluid 11 in the high torque range can escape to the low torque range side through the grooves 28.

[0059] Furthermore, the first bearing 20 is provided with an air vent hole 29 that penetrates from the rotating member 14 side to the bearing projection 15 side, and a relief groove 30 is provided on the outer circumferential surface of the bearing projection 15, which is formed continuously from the tip of the bearing projection 15 toward the other end of the housing 12, that is, from the tip of the bearing projection 15 toward the inner surface of the closed end 12A. The air vent hole 29 facilitates the press-fitting of the first bearing 20 into the rotating member 14 by releasing air that has entered between the first bearing 20 and the rotating member 14, and also helps maintain the accuracy of the bidirectional rotation damper 10B. On the other hand, the relief groove 30 guides the fluid 11 that has entered and accumulated between the first bearing 20 and the bearing projection 15 toward the other end of the housing 12 (closed end 12A side) through the relief groove 30, and further circulates it toward the outside of the rotating member 14 and returns it to the fluid chamber 13 side.

[0060] Figure 8 is a diagram illustrating the operation of the bidirectional rotation damper 10B. The operation of the bidirectional rotation damper 10B will be explained below using Figure 8.

[0061] In Figure 8(a), when the rotating member 14 rotates in the first direction (clockwise) indicated by the arrow 51A, the pressure-receiving surfaces 31 of the first vane 25C and the second vane 25D are resisted by the viscous fluid 11 in the fluid chamber 13, causing the first vane 25C and the second vane 25D to slide in the second direction (counterclockwise) relative to the tips of the first and second blade portions 23C and 23D, respectively. This creates a gap between the side surfaces of the tips of the first and second blade portions 23C and 23D on their respective second-direction sides and the inner surfaces of the first and second vanes 25C and 25D on their respective second-direction sides, allowing the fluid 11 to move between the recess 27, the through hole 32, the notch 33 and the base 14A. Furthermore, since recesses 27 serving as fluid passages are formed in the first sliding surfaces 26C and 26D of the first vane 25C and the second vane 25D, the fluid 11 on the clockwise side of the first fluid chamber 13A and the second fluid chamber 13B enters the recesses 27 from the grooves 28, as shown by the dotted line 11A in Figure 8(a), and then flows to the second direction (counterclockwise) through the gap between the through hole 32, the notch 33, and the base 14A. As a result, the rotating member 14 and the housing 12 rotate relative to each other with low torque.

[0062] Furthermore, as the rotation of the rotating member 14 progresses, the first sliding surface 26C reaches the end of the groove 28 provided on the inner circumferential surface 12a of the housing 12, and as shown in Figure 8(b), the first sliding surface 26C comes into contact with the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively. Up to the state shown in Figure 8(b), the fluid 11 on the clockwise side of the first fluid chamber 13A and the second fluid chamber 13B is in a low torque range, flowing counterclockwise through the groove 28 and the recess 27, allowing the rotating member 14 and the housing 12 to rotate relative to each other with low torque. However, when the first sliding surface 26C contacts the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively, beyond the portion where the groove 28 is provided, the fluid 11 flows little by little in the counterclockwise direction through the gap between the inner circumferential surface 12a of the housing 12 and the first vane 25C and the second vane 25D, and through the gap between the first blade portion 23C and the second blade portion 23D and the first vane 25A and the second vane 25B, as well as through the notch 33 and the through hole 32. As a result, the rotating member 14 and the housing 12 enter a high torque range and rotate slowly relative to each other. This slow relative rotation continues until the first vane 25C and the second vane 25D collide with the stopper wall 22 and the rotation is restricted. Figure 8(c) shows the state in the high torque range.

[0063] The above describes the operation when the rotating member 14 is rotated in the first direction (clockwise) indicated by arrow 51A. Next, we will explain the operation when the rotating member 14 is rotated from the state where it is stopped at the first direction end shown in Figure 8(c) to the second direction end (counterclockwise).

[0064] In Figure 8(d), when the rotating member 14 rotates in the second direction (counterclockwise) indicated by arrow 51B, the pressure-receiving surfaces 31 of the first vane 25C and the second vane 25D are resisted by the viscous fluid 11 in the fluid chamber 13. The first vane 25C and the second vane 25D slide in the first direction (clockwise) relative to the tips of the first blade portion 23C and the second blade portion 23D, respectively. This creates a gap between the side surfaces of the tips of the first blade portion 23C and the second blade portion 23D on the second direction side and the inner surfaces of the first vane 25C and the second vane 25D on the first direction side, allowing the fluid 11 to pass through between the recess 27, the through hole 32, the notch 33 and the base portion 14A. Furthermore, since recesses 27 serving as fluid passages are formed in the first sliding surfaces 26C and 26D of the first vane 25C and the second vane 25D, the fluid 11 on the clockwise side in the first fluid chamber 13A and the second fluid chamber 13B enters the recesses 27 from the grooves 28, as shown by the dotted line 11A in Figure 8(d), and then flows in the first direction (clockwise) through the gap between the through hole 32, the notch 33, and the base 14A. As a result, the rotating member 14 and the housing 12 rotate relative to each other with low torque.

[0065] Furthermore, as the rotation of the rotating member 14 progresses, the second sliding surface 26D reaches the end of the groove 28 provided on the inner circumferential surface 12a of the housing 12, and as shown in Figure 8(e), the second sliding surface 26D comes into contact with the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively. Up to the state shown in Figure 8(e), the fluid 11 in the counterclockwise direction within the first fluid chamber 13A and the second fluid chamber 13B is in a low torque range, flowing clockwise through the groove 28 and the recess 27, allowing the rotating member 14 and the housing 12 to rotate relative to each other with low torque. However, when the second sliding surface 26D comes into contact with the inner circumferential surfaces 12a of the first fluid chamber 13A and the second fluid chamber 13B, respectively, beyond the portion where the groove 28 is provided, the fluid 11 flows little by little clockwise through the gap between the inner circumferential surface 12a of the housing 12 and the first vane 25C and the second vane 25D, and through the gap between the first blade portion 23C and the second blade portion 23D and the first vane 25C and the second vane 25D, as well as through the notch 33 and the through hole 32. As a result, the rotating member 14 and the housing 12 enter a high torque range and rotate slowly relative to each other. This slow relative rotation continues until the first vane 25C and the second vane 25D collide with the stopper wall 22 and their rotation is restricted. Figure 8(f) shows the state in the high torque range.

[0066] Therefore, even with the bidirectional rotation damper 10B shown as the second embodiment, regardless of whether it rotates in the first direction (clockwise) or the second direction (counterclockwise), it can rotate smoothly with low torque before reaching the end, and as it approaches the end, it can rotate slowly with high torque. Thus, when this bidirectional rotation damper 10B is applied to the opening and closing mechanism of the lid door, braking force can be applied in both directions during opening and closing, so that it can close slowly at the closing end, preventing accidents such as finger pinching.

[0067] Furthermore, when the rotating member 14 rotates in the first direction, the fluid 11 that was filled on the first direction side of the fluid chamber 13 flows through the recess 27 and groove 28 to the fluid chamber 13 on the second direction side, and when the first sliding surface 26C rotates beyond the groove 28, it enters a high torque range and a braking force is applied. Conversely, when the rotating member 14 rotates in the second direction, the fluid 11 that was filled on the second direction side of the fluid chamber 13 flows through the recess 27 and groove 28 to the fluid chamber 13 on the first direction side, and when the second sliding surface 26D rotates beyond the groove 28, it enters a high torque range and a braking force is applied. Therefore, in this configuration, even when the rotating member 14 rotates and enters a high torque range, the pressure is balanced directly around the rotating member 14, the rotating member 14 rotates without eccentricity, and it is possible to prevent the rotating member 14 from moving horizontally (shifting). This prevents the base 14A of the rotating member 14 and the stopper wall 22 of the housing 12 from coming into strong contact. In other words, wear caused by strong contact between the base 14A of the rotating member 14 and the stopper wall 22 of the housing 12 can be prevented.

[0068] In each embodiment, the positions of the high-torque region and the low-torque region with respect to the rotation angle of the rotating member 14 can be changed by adjusting the relative positions of the grooves 28 and recesses 27, etc.

[0069] Furthermore, the present invention can be modified in various ways as long as it does not depart from the spirit of the invention, and it goes without saying that the present invention extends to such modified forms. [Explanation of Symbols]

[0070] 10A: Bidirectional rotation damper 10B: Bidirectional Rotation Damper 11:Fluid 11A: Fluid flow 12: Housing 12A: Closed end 12B: Open end 12a: Inner surface 13:Fluid chamber 13A: 1st fluid chamber 13B: 2nd fluid chamber 14: Rotating member 14A: Base 14B:Shaft part 15: Bearing protrusion 16: Pressure bulkhead plate 17A: O-ring 17B: O-ring 18: End cap 19: Recess 20: First bearing 21: Second bearing 22: Stopper Wall 23A: First wing section 23B: Second wing section 23C: First wing section 23D: Second wing section 24A: Connection part 24B:Connection part 25A: First vane 25B: Second Bane 25C: First Bane 25D: Second vane 26A: First slide surface 26B: Second slide surface 26C: First slide surface 26D: Second slide surface 27: Recess 28: Groove 29: Air vent hole 30: Relief groove 31: Pressure-receiving surface 32: Through hole 33: Notch 51A: Arrow 51B: Arrow 52A: Arrow 52B: Arrow 100: Rotating damper 101: Housing 102:Fluid chamber 102A: 1st fluid chamber 102B: 2nd fluid chamber 103: Rotating member 103a: Base 103b: Feather 104: Stopper Wall 105: Bulkhead 106A: Arrow 106B: Arrow P: Pressure X: Arrow Y: Arrow

Claims

1. A housing having a fluid chamber filled with fluid, A rotating member having a blade portion located in the fluid chamber and being rotatable relative to the housing, A stopper wall provided in the housing limits the rotation angle of the rotating member within the fluid chamber, A bidirectional rotation damper having a torque generating means that generates torque in cooperation with the stopper wall when the rotating member rotates relative to the other, The torque generating means comprises a vane that is movably provided on the blade portion and slides integrally with the blade portion, and a groove provided on the inner circumferential wall of the fluid chamber in the housing and formed with a width smaller than the axial length of the vane. The vane comprises a first sliding surface provided on the first direction side that slides in contact with the inner circumferential wall of the fluid chamber excluding the groove when the rotating member rotates in the first direction, and a second sliding surface provided on the second direction side that slides in contact with the inner circumferential wall of the fluid chamber excluding the groove when the rotating member rotates in the second direction. A bidirectional rotation damper characterized by the following features.

2. The stopper walls are provided in pairs on the inner circumferential surface of the housing, forming two fluid chambers, a first fluid chamber and a second fluid chamber, that face each other across the rotating member. The bidirectional rotation damper according to feature 1.

3. The rotating member further comprises a base portion housed within the fluid chamber and a shaft portion protruding outside the fluid chamber. The rotating member is supported at its base by a first bearing and at its shaft by a second bearing. The housing has an opening on one end that is closed with a cap, and on the other closed end, it has a bearing projection that supports the first bearing. The first bearing has an air vent hole that penetrates from the rotating member side to the bearing protrusion side, The cap supports the rotating member via the second bearing. The bidirectional rotation damper according to feature 1.

4. The bidirectional rotation damper according to claim 3, characterized in that a relief groove is provided on the bearing protrusion, extending from the tip of the bearing protrusion toward the other end of the housing.

5. The bidirectional rotation damper according to any one of claims 1 to 4, characterized in that the first sliding surface and the second sliding surface of the vane are formed substantially symmetrically.

6. The bidirectional rotation damper according to any one of claims 1 to 5, characterized in that the vane is provided so as to be able to swing in a first direction and a second direction with the tip of the blade portion as a pivot point.

7. The bidirectional rotation damper according to any one of claims 1 to 5, characterized in that the vane has a through hole formed between the first slide surface and the second slide surface that penetrates vertically, and is formed to be slidable in a first direction and a second direction relative to the blade portion, and when slid toward the first direction, the fluid filled toward the first direction side is released toward the second direction side through the through hole, and when slid toward the second direction side, the fluid filled toward the second direction side is released toward the first direction side through the through hole.

8. The bidirectional rotation damper according to claim 1, characterized in that the first sliding surface and the second sliding surface are provided separately from each other.

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