JP2518657B2 - Rotary damper - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION <Field of Industrial Application> The present invention relates to a rotary damper for braking the rotational force of a rotating body.

<Prior Art> Conventionally, for example, an opening / closing lid of a mechanical device, a door, or the like is one that performs a desired function by reciprocally rotating a rotating body within a certain angle range.

Of the above-mentioned opening / closing lids, especially when the upper and lower opening / closing lids are closed by free fall, between opening and closing,
Since the distance from the axis of rotation of the lid to the center of gravity of the lid increases, the rotational force of the lid increases, which causes a large impact when the lid is closed. Therefore, in order to absorb this impact, a mechanism in which the rotational force of the lid is braked by a rotary damper provided on the rotary shaft is generally adopted.

As shown in FIG. 4, the rotary damper described above accommodates a plurality of vanes (blades) 2 or discs in a casing 1, forms a rotary shaft 3 integrally with the vanes 2, and further, the casing 1 The working oil 4 is filled in the inside, and the vane 2 is rotated by transmitting an external rotational force such as the opening / closing lid to the rotating shaft 3, and the vane 2 agitates the working oil 4 in the casing 1. The structure is such that the braking force is generated by the viscous resistance of the working oil 4 when it is carried out.

<Problems to be Solved by the Invention> The rotary damper configured as described above applies a braking force of a constant torque value to the rotating body, and the torque value depends on the position of the lid like the above-mentioned upper and lower lids. In the case where fluctuates, the effect as a rotary damper cannot be exhibited. That is, when a rotary damper set to the torque value when the lid is closed is used and the lid is allowed to fall freely, the torque value at this time is smaller than the torque value when the lid is closed. If you use a rotary damper that is stopped halfway and has a torque value that is smaller than the torque value when the lid is closed, the rotational force when the lid is closed cannot be braked and the impact There was a problem that occurs.

In order to solve the above problems, the present invention is to provide a rotary damper capable of braking the rotational force of a rotating body such that the torque value varies depending on the rotation angle.

<Means for Solving Problems> In order to solve the above problems, a rotary damper according to the present invention includes a plurality of fluid chambers divided by a fixed partition member and a movable partition member, and the fluid chambers mutually. A conduction chamber for conduction, a through hole for conduction between the fluid chamber and the conduction chamber, a transmission member for transmitting an external rotational force to the movable partition member, and each of the fluid chamber and the conduction chamber. A non-compressible working fluid to be filled, a through hole is formed in the movable partition member, and a valve rod that allows the working fluid to flow only in one direction is inserted into the through hole. is there.

In the above structure, a groove is formed on one of the surfaces of the movable partition member and the transmission member that face each other and a projection is formed on the other surface, so that the rotational force can be transmitted by fitting the groove and the projection. It is preferable to configure.

<Operation> In the rotary damper, the working fluid is filled in the fluid chamber and the conducting chamber, and the chambers are electrically connected by the through holes, and the movable partition member is fitted with the valve rod that allows the working fluid to flow only in one direction. Has been inserted. Therefore, when the external rotational force is transmitted to the movable partition member via the transmission member, and the movable partition member rotates in the direction that blocks the flow of the working fluid by the valve rod, the fluid is provided in the fluid chamber on the downstream side in the rotation direction. A certain working fluid is removed through the through hole to the conduction chamber, and the resistance generated when the working fluid passes through the through hole acts as a braking force against an external rotational force.

When the movable partition member is rotated in the direction in which the working fluid is circulated by the valve rod, the working fluid in the fluid chamber on the downstream side in the rotational direction is moved from the through hole formed in the movable partition member to the fluid chamber on the upstream side in the rotational direction. Distribute to. Therefore, even if the movable partition member rotates, almost no braking force is generated.

<Embodiment> An embodiment of the rotary damper to which the above means is applied will be described below with reference to FIGS. 1 to 3.

In the figure, A is a rotary damper. First, the schematic configuration of the rotary damper A will be described. A storage portion 11 formed at a predetermined position inside a main body case 10 formed in a cylindrical shape has a shaft portion 21 for receiving a rotational force from a rotating body (not shown). A flange 22 of the passive shaft 20 and a rotary vane 30 provided with a vane 31 projecting from each other are fitted and inserted into each other, and the shaft portion 21 projects outside the main body case 10. An end plate 40 provided with a fixed vane 42 is inserted and fixed from the rear end open portion of the main body case 10, that is, the opposite side of the shaft portion 21, and a bearing 50 is further inserted from the front end open portion, that is, the shaft portion 21 side. It is fixed.

The housing portion 11 of the main body case 10 is obtained by inserting the above-mentioned members.
, Fluid chambers B and C are formed by a fixed vane 42 which is a fixed partition member and a rotary vane 31 which is a movable partition member, and the capacities of the fluid chambers B and C are varied by the rotation of the rotary vane 31. Is configured. Further body case
A groove 12 is engraved on the outer peripheral portion of the outer peripheral portion 10 in the circumferential direction corresponding to the housing portion 11, and an outer cylinder 60 is fitted to cover the groove 12 and the groove 12 is formed. The outer cylinder 60 forms a conduction chamber D.

A plurality of orifices 13a, 13 described later are provided at predetermined positions in the circumferential direction of the main body case 10 between the fluid chamber B and the conduction chamber D.
b, 13c, 13d are provided to connect the fluid chamber B and the conduction chamber D. Similarly, a communication hole 14 is bored in the main body case 10 between the fluid chamber C and the conduction chamber D to connect the fluid chamber C and the conduction chamber D. In this way, the fluid chambers B and C and the conduction chamber D are configured to communicate with each other. The fluid chambers B and C and the conduction chamber D are filled with an incompressible working fluid E such as silicon oil to form a rotary damper A.

In the above structure, when a rotating body (not shown) receives a rotating force in the direction of arrow a, which is the counterclockwise direction in FIG. 3, this rotating force is transmitted to the rotating vane 30 via the passive shaft 20. . The vane 31 provided on the rotary vane 30 is rotated by the rotational force to try to remove the working fluid E in the fluid chamber B into the conduction chamber D by passing through the plurality of orifices 13a to 13d. A braking force with respect to the rotational force is generated.

 Next, the above-mentioned members will be described in detail.

A flange 16 having a plurality of mounting holes 15 is provided at the outer peripheral end of the main body case 10, and the rotary damper A is mounted and fixed to a frame of a machine device (not shown) through the mounting holes 15. It is configured.

A bearing housing 17 is formed at the tip of the inner surface of the main body case 10, and a groove 17a into which a retaining ring 51 for fixing the bearing 50 can be fitted is formed. Further, an end plate housing portion 18 is formed at the rear end portion of the inner surface of the main body case 10, and a screw portion 18a for fixing the end plate 40 is formed. Further, an outer cylinder fitting portion 19 is formed at a predetermined position on the outer circumference of the main body case 10.

The passive shaft 20 as a transmission member has a flange at one end of the shaft portion 21.
22 is integrally formed by molding or turning. A fitting groove 23 is formed on the surface of the flange 22 through the center thereof.

The tip of the shaft portion 21 is formed to have a width across flats, and a coupling, a gear, or the like is appropriately fixed to the tip, and the rotational force of the rotating body is transmitted through the coupling or the like. Further, by fitting a fitting protrusion 32 provided on a rotary vane 30 described later into the fitting groove 23, the rotational force can be transmitted to the rotary vane 30.

The passive shaft 20 is rotatably supported by inserting the shaft portion 21 into a bearing hole 54 formed in the bearing 50.

Next, the rotating vanes 30 are, as shown in FIG.
And a cylindrical portion 33 having a fitting protrusion 32 that fits into the fitting groove 23 of the passive shaft 20 that is continuously provided to the shaft, and a shaft portion that is provided continuously to the vane 31.
34 and 34 are integrally configured. The rotary vane 30 can be manufactured by a molding method using a molding die, precision casting, or a machining method such as machining. This processing method can selectively employ a material determined according to a setting condition such as a braking torque value required for the rotary damper A and a processing method corresponding to this material.

A communication hole 35 is formed at a predetermined position of the vane 31. A valve rod 36 is loosely fitted in the communication hole 35.
A head portion 37 having a diameter sufficiently larger than the diameter of the communication hole 35 is formed at one end of the 36, and a groove 39 for mounting a retaining ring 38 is formed at the other end. As shown in FIG. 3, the valve rod 36 is loosely fitted in the vane 31 so that the head portion 37 is located on the fluid chamber B side.

The distance from the head 31a of the vane 31 to the shaft center must be accurately finished. If this accuracy is insufficient, when the fitting vane 30 rotates in the direction of arrow a or b, Leakage of the working fluid E may occur between the portion 31a and the inner wall of the housing portion 11 of the main body case 10, and a sufficient braking force may not be exerted. According to experiments conducted by the present inventors, the gap between the head portion 31a of the vane 31 and the inner surface of the storage portion 11 is preferably about 20 μm. For example, when the gap becomes 50 μm, the planned braking force does not occur. It was

Next, as shown in FIG. 2, the end plate 40 is entirely formed in a cylindrical shape, and a bearing hole 41 is formed in the center thereof. The shaft portion 34 of the rotary vane 30 is inserted into the bearing hole 41. 42 is a fixed vane, and the axial length of the fixed vane 42 is the same as that of the rotary vane 31.
Is finished to the same size as the length of the
It is finished to the same size as the inner diameter of the storage unit 11 of 10.

A through hole 44 for filling the working fluid E is formed at a predetermined position of the cylindrical portion 43, and after the working fluid E is filled through the through hole 44, the through hole 44 has a set screw 45 and Ball 45
It is configured to be sealed by a.

The end plate 40 is inserted into the end plate housing portion 18 formed at the rear end of the main body case 10, and further, a stop ring 46 having a screw carved on the outer periphery from the rear end is formed at the rear end of the main body case 10. It is fixed by being screwed into 18a.

Further, in order to fix the relative position between the end plate 40 and the orifice bored in the main body case 10, a knock pin 71, which will be described later, is driven into the hole 47 and engaged with each other to perform the positioning of each other.

Further, a groove 48 for fitting the O-ring 72a is formed in a predetermined position of the cylindrical portion 43, and when the O-ring 72a is housed in the end plate housing 18, the gap between the end plate 40 and the main body case 10 is set to the O The ring 72a is sealed by fitting.

Next, the bearing 50 is formed such that the outer diameter is equal to the inner diameter of the bearing housing portion 17 of the main body case 10, and a bearing hole 54 is formed in the center so that the shaft portion 21 of the passive shaft 20 can be rotatably fitted therein. It is configured. The bearing 50 is inserted in the shaft portion 21 from the tip of the main body case 10 and is housed in the bearing housing portion 17 of the main body case 10, and the retaining ring.
It is fixed by fitting the 51 into the groove 17a.

Grooves 52 and 53 for fitting the O-rings 72b and 72c are formed at predetermined positions on the inner and outer surfaces of the bearing 50. The grooves between the main body case 10 and the bearing 50 and the bearing 50 and the shaft portion are respectively formed. The structure is such that the working fluid E can be sealed so as not to leak from the gap with the gap 21.

Next, the outer cylinder 60 is fitted into the main body case 10 so that the inner diameter thereof is made equal to the outer diameter of the fitting portion 19 of the main body case 10.
The outer cylinder 60 is fixed to the body case 10 by a knock pin 71. As described above, the outer cylinder 60 forms the conduction chamber D by covering the groove 12 formed in the body case 10, and the O-rings 72d and 72e are provided on both sides of the groove 12.
Grooves 61 and 62 for fitting the
The working fluid E can be sealed so as not to leak.

Next, 71 is a knock pin, which is driven into the hole 47 formed in the end plate 40 by penetrating the outer cylinder 60 and the main body case 10, thereby determining the related position between the end plate 40 and the main body case 10. In addition, the outer cylinder 60 is fixed to the main body case 10. That is, the positions of the plurality of orifices bored in the main body case 10 and the position of the fixed vane 41 of the end plate 40 are important factors in determining the braking characteristics of the rotary damper A, and therefore the design of the rotary damper A is designed. The positional relationship between the fixed vane and the orifice 13d is determined in stages. From another point of view, by changing the relational position between the orifice of the main body case 10 and the fixed vane of the end plate 40, the rotary damper A having different braking characteristics can be formed by using the same component. It means that you can get it.

 Next, 72a, 72b, 72c, 72d and 72e are O-rings, respectively.

Next, generation of the braking force by the rotary damper A configured as described above will be described in detail.

When the rotating force of the rotating body (not shown) in the direction of arrow a shown in FIG. 3 is transmitted to the shaft portion 21 directly or through a transmission mechanism such as a gear, the rotation is performed through the fitting groove 23 of the passive shaft 20. The force is transmitted to the rotary vane 30, and the vane 31 rotates in the direction of arrow a. Due to the rotation of the vane 31, the working fluid E in the fluid chamber B is
Are removed to the conduction chamber D through the orifices 13a to 13d. At this time, a braking force against the rotational force is generated by the exclusion resistance when the working fluid E is removed from each orifice. As the vane 31 rotates, the orifice 13a is first closed by the head 31a of the vane 31, and the working fluid E is removed from the orifices 13b to 13d. Therefore, the number of passages through which the working fluid E is removed decreases, so that the amount of the working fluid E removed decreases, which increases the braking force with respect to the rotational force. When the vane 31 further rotates in the direction of arrow a, the orifice
13b is blocked by the head 31a of the vane 31, and the working fluid E
Are eliminated by the orifices 13c and 13d,
The braking force with respect to the rotational force further increases. When the head 13a of the vane 31 closes the orifice 13c by the rotation of the vane 31 in the direction of the arrow a, the working fluid E is removed only from the orifice 13d. It will be maximum.

Through the above operation, the through hole 35 provided in the vane 31 becomes the valve rod.
It is closed by the head portion 37 of 36, and the working fluid E is not removed from the through hole 35 to the fluid chamber C side. Further, the working fluid E removed to the conduction chamber D flows into the fluid chamber C through the conduction chamber D and the communication hole 14.

When the rotating body has a rotating force in the direction of the arrow b shown in FIG. 3, the rotating force is transmitted to the rotating vane 30 via the shaft portion 21 as described above. As a result, the vane 31 rotates in the direction of the arrow b, and at this time, the working fluid E is removed from the communication hole 14 into the conduction chamber D and, at the same time, removed from the communication hole 35 into the fluid chamber B. Since the communication hole 14 and the communication hole 35 are formed with a sufficiently large diameter, the braking force against the rotational force is hardly generated.

In the embodiment described above, the working fluid E can be used as long as it is an incompressible fluid. For example, if grease-like oil or the like is used, the viscous resistance of the oil and the oil can be passed through the orifice. The braking force can be obtained by utilizing the combined resistance of the exclusion resistances at the time of exclusion.

In the above-described embodiment, four orifices 13a to 13d are formed between the fluid chamber B and the conduction chamber D, but this is a design problem and is used to generate the planned braking force. It should be clear that it should be selectively designed in relation to the working fluid, and the present invention is not limited to this example.

In the above-described embodiment, the conduction chamber D is formed between the outer cylinder 60 and the main body case 10, but it may be formed in another portion. In short, the working fluid E is the fluid chamber B and the fluid chamber. It is sufficient if it can be distributed with C.

In the above-described embodiment, the passive shaft 20 and the rotary vane 30 are formed separately, but this is a problem in manufacturing technology.
Even if both are integrally formed, the object and effect of the present invention can be expected, and therefore both may be integrally formed.

In the above-described embodiment, the component for engraving the fitting groove of the O-ring is not limited to that of this embodiment, and the component for sealing the working fluid E is not limited to the O-ring. Can be used similarly.

In the above-described embodiment, the body case 10, the end plate 40, and the outer cylinder 60 are positioned and fixed with the knock pin 71.
This is not limited to the knock pin 71 of the present embodiment, other methods, for example, by engraving a key groove or the like on the end plate housing portion 18 of the main body case 10 and the end plate 40 and performing positioning by the key. Is also good.

<Effects of the Invention> As described in detail above, in the rotary damper according to the present invention, the braking force against the external rotational force is generated by the resistance generated when the working fluid is removed from the fluid chamber to the conduction chamber through the through hole. Since the diameter or the number of the through holes is selectively set, even if the external rotational force changes according to the fluctuation of the rotational position, the control corresponding to this rotational force is generated. It can generate power.

Further, when the rotation direction of the movable partition member is the direction in which the working fluid is circulated through the through hole formed in the member, the working fluid circulates through the through hole as the movable partition member is rotated, and almost no resistance occurs. Does not occur. Therefore, the braking force can be generated only in one direction with respect to the external rotational force.

Further, when the groove is formed in one of the movable partition member and the transmission member and the projection is formed in the other, it is not necessary to increase the processing accuracy of the transmission member, and the cost increase can be suppressed.

[Brief description of drawings]

FIG. 1 is a sectional view in the axial direction of the rotary damper of this embodiment, FIG.
FIG. 4 is an exploded perspective view of a main part, FIG. 3 is a circumferential sectional view of a rotary damper, and FIG. 4 is an explanatory view of a conventional rotary damper. A is a rotary damper, B and C are fluid chambers, D is a conduction chamber, E is a working fluid, 10 is a main body case, 11 is a housing portion, 12 is a groove, 13a, 13b,
13c and 13d are orifices, 14 is a communication hole, 16 is a flange, 17
Is a bearing housing portion, 18 is an end plate housing portion, 19 is an outer tube fitting portion, 20 is a passive shaft, 21 is a shaft portion, 22 is a flange, 23 is a fitting groove, 30 is a rotating vane, 31 is a vane, and 31a. Is a head part, 32 is a fitting protrusion, 35 is a communication hole, 36 is a valve rod, 40 is an end plate,
41 is a bearing hole, 42 is a fixed vane, 44 is a through hole, 45 is a set screw, 50 is a bearing, 51 is a retaining ring, 54 is a bearing hole, 60 is an outer cylinder, 71
Is a knock pin.

Claims (2)

(57) [Claims] 1. A plurality of fluid chambers divided by a fixed partition member and a movable partition member, a conduction chamber for electrically connecting the fluid chambers to each other, and a passage for electrically connecting the fluid chambers and the conduction chambers. A hole, a transmission member for transmitting an external rotational force to the movable partition member, and an incompressible working fluid filled in each of the fluid chambers and the conduction chamber, and the through hole is formed in the movable partition member. And a valve rod that allows the working fluid to flow only in one direction is inserted into the through hole. 2. A groove is formed on one of the surfaces of the movable partition member and the transmission member facing each other, and a projection is formed on the other surface, so that the rotational force can be transmitted by fitting the groove and the projection. Claim 1 characterized in that it is configured
The rotary damper described in the item.