TW201420915A - Buffer - Google Patents

Abstract

A buffer D includes a cylinder 1; a piston 2 slidably inserted into the cylinder 1 and partitioned into an extension side chamber R1 and a pressure side chamber R2 filled with fluid; a rod part 3 movably inserted into the cylinder 1 and connected to the piston 2; an oil tank R arranged in the rod part 3 and communicated with the pressure side chamber R2. Since the above buffer D arranges the oil tank R inside the rod part 3, it is not necessary to arrange the oil tank R at outer periphery of the cylinder 1. In addition, since the oil tank R is arranged parallel to the extension side chamber R1 and the pressure side chamber R2, the length of a stroke is not sacrificed, so as to easily ensure the length of the stroke.

Description

buffer

The invention relates to a buffer.

In general, the damper is a rod that is provided with a cylinder, is slidably inserted into the cylinder, and is divided into a piston that is filled with hydraulic oil in the extension side chamber and the pressure side chamber, and a rod that is connected to the piston at one end, and vibrates the vibration-damping object. Control it.

In general, as compared with a double-rod type damper having a lever member on both sides of the piston, it is easier to ensure the length of the stroke only by the single-rod type damper having the rod member on one side of the piston. Therefore, in the case where it is not possible to ensure a large mounting space, a single-rod type buffer is often used.

In such a single-rod type damper, when the piston moves in the axial direction relative to the cylinder, the rod enters and exits the cylinder. According to the volume of the rod that enters and exits the inside of the cylinder, the total volume of the expansion chamber and the pressure chamber in the cylinder may change, resulting in excessive or insufficient oil in the cylinder.

Therefore, the configuration of the damper is a double cylinder type or a single cylinder type configuration. The double-tube type buffer is, for example, an annular oil tank filled with gas and hydraulic oil between the cylinder and the outer cylinder covering the cylinder, and the excess or insufficient liquid is discharged or supplied by the oil tank to achieve compensation. effect. The single-cylinder type of damper is, for example, a free piston provided in the cylinder to form a plenum beside the pressure side chamber, and the expansion and compression of the extremely flexible gas volume allows the rod to extend in and out of the cylinder. The total volume change of the side chamber and the pressure side chamber is absorbed. As a structure of the damper, in the case of a single-tube type structure, in order to secure the length of the stroke and output a large damping force, Do not allow high pressure inside the chamber. Since the single cylinder type has such a limitation, the structure of the damper tends to be a double cylinder type. As the buffer of the double cylinder type, for example, there is a buffer disclosed in JP2011-174501A.

A double-type buffer like this, it is easy to ensure the length of the stroke, in the compression stroke It also exerts a large damping force. However, since the outer circumference of the cylinder is covered by a cylinder called a casing, a fuel tank is formed between the cylinder and the cylinder, so that the outer diameter of the damper becomes large.

In particular, in the case where the vibration-damping object is an extremely heavy object such as a building, From the viewpoint of strength, the rod diameter has to be thick. As soon as the rod diameter becomes larger, the amount of oil exchanged between the fuel tank and the cylinder becomes larger, and the cylinder diameter becomes thicker. Moreover, the volume of space provided between the outer casing and the cylinder also has to be increased, so that the outer casing diameter becomes large. As a result, the outer diameter of the damper becomes extremely large, the weight is increased, and the cost is also increased.

The present invention is directed to providing a buffer that is small, lightweight, and inexpensive.

A buffer according to a certain aspect of the present invention includes: a cylinder; a piston slidably inserted into the cylinder and dividing the cylinder into an extension side chamber and a pressure side chamber; the rod member is movably inserted into the cylinder and is coupled to the piston The fuel tank is disposed in the rod to compensate for volume change in the cylinder accompanying expansion and contraction; the oil tank is in communication with the pressure side chamber.

A‧‧‧ space

D‧‧‧buffer

D1‧‧‧ buffer

L‧‧‧ liquid room

L1‧‧‧ liquid room

P‧‧‧Pressure room

P1‧‧‧Pressure room

R‧‧‧ fuel tank

R1‧‧‧Extension room

R2‧‧‧ pressure side room

R3‧‧‧ fuel tank

1‧‧‧ cylinder

2‧‧‧Piston

2a‧‧‧ pathway

2b‧‧‧ pathway

3‧‧‧ rods

3a‧‧‧ Hollow

3b‧‧‧ bottom

4‧‧‧ rod guides

5‧‧‧ cover

6‧‧‧Attenuation factor

7‧‧‧Attenuation factor

8‧‧‧Free piston

9‧‧‧pressure side attenuation path

10‧‧‧Inhalation pathway

11‧‧‧Attenuation factor

12‧‧‧ check valve

13‧‧‧Spring components

15‧‧‧ rods

16‧‧‧ Pipe fittings

17‧‧‧ Space

18‧‧‧Parts

18a‧‧‧through hole

19‧‧‧Package components

20‧‧‧Measurement attenuation path

21‧‧‧Inhalation path

22‧‧‧Attenuation factor

23‧‧‧ check valve

24‧‧‧Free piston

25‧‧‧Spring components

Fig. 1 is a longitudinal sectional view showing a damper according to a first embodiment of the present invention.

Fig. 2 is a longitudinal sectional view showing a damper according to a second embodiment of the present invention.

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

<First embodiment>

The configuration of the buffer D according to the first embodiment of the present invention will be described with reference to Fig. 1 . As shown in FIG. 1, the damper D of the first embodiment includes a cylinder 1, and is slidably inserted into the cylinder 1, and the cylinder 1 is divided into pistons 2 for respectively filling the liquid side chamber R1 and the pressure side chamber R2. The rod 3 that is slidably inserted into the cylinder 1, the rod 3 coupled to the piston 2, and the single rod type damper of the tank R provided in the rod 3 are slidably inserted.

The liquid filled in the extension side chamber R1, the pressure side chamber R2, and the oil tank R is hydraulic In addition to the oil, for example, water, an aqueous solution, a liquid called an electromagnetic viscous fluid, or an electrically viscous fluid may be used. Further, in the tank R, a gas is filled in addition to the liquid. Further, the gas filled in the tank R may be an inert gas such as nitrogen.

Hereinafter, each part of the buffer D will be described in detail. As shown in Fig. 1, the rod member 3 is supported so that the rotatable annular rod guide 4 is mounted at the left end of the cylinder 1 in Fig. 1. Further, the cover 5 that locks the cylinder end is mounted on the right side of the cylinder 1 in Fig. 1.

The piston 2 is slidably inserted into the cylinder 1. The piston 2 divides the inside of the cylinder 1 into the extension side chamber R1 through which the rod member 3 is inserted and the pressure side chamber R2 on the piston side. The piston 2 is provided with passages 2a, 2b that communicate the extension side chamber R1 and the pressure side chamber R2. The damping force generating elements 6 and 7 are provided on the way of the passages 2a and 2b. The damping force generating element 6 allows only the flow of the liquid from the extension side chamber R1 to the pressure side chamber R2, and applies a resistance to the flow of the liquid passing through the passage 2a to cause a predetermined pressure loss. The damping force generating element 7 allows only the flow of the liquid from the pressure side chamber R2 to the extension side chamber R1, and applies a resistance to the flow of the liquid passing through the passage 2b to cause a predetermined pressure loss. In the damping force generating elements 6 and 7, for example, a valve called a poppet valve or a leaf valve may be called an orifice. Blocking throttle valve.

The rod 3 is provided with a hollow portion 3a rotatably supported by a rod guide 4 provided at the left end of the cylinder 1 in Fig. 1. Further, the rod 3 is inserted into the cylinder 1 at the right end in Fig. 1, and the piston 2 is coupled to the right end. The piston 2 has an annular shape and is fixed to the outer periphery of the right end of the rod member 3 in Fig. 1. Further, the free piston 8 is slidably inserted into the hollow portion 3a of the rod 3. The free piston 8 is movable in the axial direction with respect to the rod 3. Further, the free piston 8 divides the hollow portion 3a of the rod member 3 into a liquid chamber L filled with liquid and a pressurizing chamber P through which the liquid chamber L is pressurized by the free piston 8.

The liquid chamber L communicates with the suction passage 10 through the pressure side attenuating passage 9 provided at the right end of the rod member 3 in Fig. 1 to the pressure side chamber R2. In the middle of the pressure side attenuation passage 9, a flow of only the liquid from the pressure side chamber R2 to the liquid chamber L is provided, and a resistance to the flow of the liquid passing through the pressure side attenuation passage 9 is applied to cause a predetermined pressure loss. Element 11 occurs. In the middle of the other suction passage 10, a check valve 12 that allows only the flow of the liquid from the liquid chamber L to the pressure side chamber R2 is provided.

Among the pressurizing chambers P, between the bottom portion 3b of the left end of the rod member 3 and the free piston 8 in the hollow portion 3a of the rod member 3, the spring member 13 as a biasing means is mounted in a compressed state. Since the force to be extended by the spring member 13 acts on the liquid chamber L through the free piston 8, the liquid chamber L is pressurized. Further, the pressure side chamber R2 and the extension side chamber R1 are also pressurized by the liquid chamber L. Further, in the pressurizing chamber P, instead of the spring member 13, the gas may be sealed as a biasing means, and the pressurizing chamber P may function as a gas spring. As described above, by pressing the expansion side chamber R1 and the pressure side chamber R2 in the cylinder 1 by the biasing means of the pressurizing chamber P, the rigidity of the appearance of the liquid can be improved. Therefore, the damping force of the damper D can be copedibly improved, and generation of bubbles in the cylinder 1 can be prevented.

Next, the action of the buffer D will be described.

With the damper D extended, the piston 2 moves to the left in FIG. The extension side chamber R1 is compressed, and the pressure side chamber R2 on the opposite side is enlarged. Therefore, the liquid moves from the extension side chamber R1 to the pressure side chamber R2 through the passage 2a. Moreover, since the damper D is of a single rod type, once the rod 3 is extended, the rod 3 is withdrawn from the cylinder 1, and the volume corresponding to the volume of the rod 3 that has been withdrawn is pushed by the liquid chamber L of the tank R through the suction passage 10. Side chamber R2 is supplied. At this elongation stroke, since the liquid passes through the damping force generating element 6, a pressure difference is generated between the extension side chamber R1 and the pressure side chamber R2. Therefore, the damper D can exert a damping force for balancing the above-described pressure difference in a direction in which the piston 2 is prevented from moving to the left in FIG.

Conversely, in the case of buffer D compression, the piston 2 moves to the right in FIG. The pressure side chamber R2 is compressed to expand the opposite side extension chamber R1. Therefore, the liquid moves from the pressure side chamber R2 to the extension side chamber R1 through the passage 2b. Further, since the damper D is of a single rod type, the rod member 3 intrudes into the cylinder 1 once compressed, which corresponds to the discharge of the liquid of the rod member 3 in the cylinder 1 by the pressure side chamber R2 to the liquid chamber L of the tank R. The pressure side attenuation passage 9 is discharged to the liquid chamber L. At the time of this contraction stroke, the pressure in the pressure side chamber R2 rises due to the passage of the liquid through the damping force generating element 11 located on the pressure side damping passage 9. Then, the liquid passes through the damping force generating element 6 from the pressure side chamber R2 to the extension side chamber R1, and a pressure difference is generated in the pressure side chamber R2 and the extension side chamber R1. Therefore, the damper D can exert a damping force for balancing the above-described pressure difference in a direction in which the piston 2 is prevented from moving to the right in FIG.

As described above, the tank R supplies the liquid to the cylinder 1 when the damper D expands or contracts. Absorbed from the cylinder 1 to compensate for volume changes in the cylinder 1. Further, similarly to the conventional damper, the damper D can exert a damping force that hinders the movement of the piston 2 during expansion and contraction.

According to the first embodiment described above, the following effects are obtained.

Since the buffer D is provided with the oil tank R in the rod 3, there is no cylinder 1 It is necessary to set the fuel tank outside. Further, in the damper D, the oil tank R is arranged side by side with respect to the extension side chamber R1 and the pressure side chamber R2. Therefore, unlike the single cylinder in which the gas chamber is arranged in series with respect to the extension side chamber and the pressure side chamber The type of buffer will sacrifice the length of the stroke, making it easier to ensure the length of the stroke.

Therefore, according to the damper D, the outer diameter is not increased, and the weight of the damper is also light. The weight is sufficient, and there is no problem of high cost, so it is small, light, and inexpensive.

Further, the damper D is provided with a tank R, and is disposed between the tank R and the pressure side chamber R2. The pressure side attenuation path 9. Therefore, a large damping force can be exerted during the compression stroke, and the damping of the vibration-damping object of a large weight is not insufficient, and the vibration can be sufficiently oscillated.

Moreover, in the buffer D, the oil tank R is divided into the pressurized chamber P and the liquid chamber L, It is necessary to fill the liquid chamber L with a gas, and it is possible to fill only the liquid in the liquid chamber L. Therefore, since no liquid level is generated in the liquid chamber L, even if the entire shock absorber D vibrates, the gas in the liquid chamber L is not mixed into the liquid, and the damper D can exhibit a stable damping force. Further, the separation of the pressurizing chamber P from the liquid chamber L can be performed by, for example, a bladder, a bellows or the like in addition to the free piston 8.

<Second embodiment>

Next, a buffer D1 according to a second embodiment of the present invention will be described with reference to Fig. 2 . The same components as those in the first embodiment are denoted by the same reference numerals and will not be described.

The damper D1 of the second embodiment has a tubular shape in the rod member 15 with respect to the structure of the damper D of the first embodiment, and includes a tube member 16 that forms the oil tank R3 together with the rod member 15, and the support tube member 16 and the lid body. The points between the partition members 18 forming the space 17 between the five are different.

In the damper D1, the rod member 15 is cylindrical, and the anti-cylinder side end at the left end in Fig. 2 is closed by the packing member 19. The piston 2 is coupled to the outer circumference of the right end of the rod member 15 in Fig. 1.

The partition member 18 is attached to the inner circumference of the right end of the cylinder 1 in FIG. The pressure side chamber R2 is formed between the two by the partition member 18 and the piston 2. The partition member 18 is in the same position as the cylinder 1 The space 17 is partitioned between the lids 5 that are closed at the right end in FIG. 1, and includes a pressure attenuation passage 20 and a suction passage 21. The pressure side attenuation passage 20 connects the pressure side chamber R2 and the space 17, and the damping force generating element 22 is provided in the middle. The damping force generating element 22 allows only the flow of the liquid from the pressure side chamber R2 to the space 17, and applies a resistance to the flow of the liquid passing through the pressure side attenuation passage 20 to cause a predetermined pressure loss. The suction passage 21 in the other direction communicates the pressure side chamber R2 and the space 17, and a check valve 23 that allows only the flow of the liquid from the space 17 to the pressure side chamber R2 is provided in the middle.

The pipe member 16 is coupled to the pressure side chamber side of the partition member 18, penetrates the pressure side chamber R2, and is inserted into the rod member 15. The closed space A formed by the pipe member 16 and the rod member 15 becomes the oil tank R3. Further, in the second embodiment, the outer circumference of the pipe member 16 is slid on the inner circumference of the rod member 15, and the space A and the pressure side chamber R2 are prevented from communicating without any resistance. Instead, a sealing member is provided between the rod member 15 and the tube member 16 to prevent the space A from communicating with the pressure side chamber R2. In the above case, by using the sealing member, there is an advantage that high precision is not required for the processing and assembly of the rod member 15 and the tube member 16.

The free piston 24 is slidably inserted into the inner circumference of the pipe member 16, and the inside of the oil tank R3 is divided into a liquid chamber L1 and a pressurizing chamber P1. Further, the liquid chamber L1 communicates with the space 17 through the through hole 18a provided in the partition member 18. Further, the space 17 communicates with the pressure side chamber R2 through the pressure side attenuation passage 20 and the suction passage 21. As a result, the liquid chamber L1 communicates with the pressure side chamber R2 through the space 17. In other words, the oil tank R3 communicates with the pressure side chamber R2 via the space 17. According to the above aspect, the damping force generating element 22 and the check valve 23 can be provided to the partition member 18 without difficulty. When the damping force generating element 22 and the check valve 23 can be provided in the lid body 5 or the pipe member 16, the pipe member 16 can be attached to the lid body 5 without providing the partition member 18. Moreover, since the free piston 24 is disposed on the side of the tube member 16, the free piston 24 does not form the axis of the rod member 15 and the tube member 16 when the damper D1 is compressed. The relative movement of the direction creates interference without hindering the relative movement.

Further, in the pressurizing chamber P1, between the package member 19 and the free piston 24, The spring member 25 as a biasing means is mounted in a compressed state. The force of the spring member 25 to be extended acts through the free piston 24 to the liquid chamber L1. Therefore, the liquid chamber L1 is pressurized, and the pressure side chamber R2 and the extension side chamber R1 are also pressurized. Further, in the pressurizing chamber P1, instead of the spring member 25, the gas is sealed as an elastic means, and the pressurizing chamber P1 can also function as a gas spring. The effect of pressurizing the inside of the cylinder 1 by the pressurizing chamber P1 is the same as the effect of pressurizing the buffer D by the pressurizing chamber P.

According to the second embodiment described above, the following effects are obtained.

The buffer D1 can interfere with the same as the buffer D at the time of expansion and contraction. The damping force of the movement of the plug 2. Since the damper D1 is provided with the oil tank R3 in the rod member 15 and the pipe member 16, it is not necessary to provide a fuel tank on the outer circumference of the cylinder 1. Further, in the damper D1, since the oil tank R3 is arranged side by side with respect to the extension side chamber R1 and the pressure side chamber R2, it is easier to sacrifice the length of the stroke unlike the single cylinder type buffer in which the gas chamber is arranged in series with the extension side chamber and the pressure side chamber. Make sure the length of the trip.

As described above, according to the damper D1, the outer diameter does not become large, and the weight of the damper The amount is also light weight, and there is no problem of high cost, so it is small, light, and inexpensive.

Moreover, according to the buffer D1, not only in the rod member 15, but also in the tube member 16 The volume of the tank R3 contributes. Therefore, when the rod 15 having a large diameter is used, even when the amount of exchange of the liquid in the tank R3 and the cylinder 1 becomes large during the expansion stroke, the volume shortage is not caused. Therefore, the effect of preventing the diameter of the damper D1 from being increased is higher, and the miniaturization of the damper D1 becomes more advantageous.

Moreover, the oil tank R3 is disposed in the buffer D1, and is in the oil tank 3 and the pressure side chamber R2. Since the pressure side attenuation passage 20 is provided between them, a large damping force can be exerted even during the compression stroke. Therefore, the vibration damping of the large-weight vibration-damping object is not insufficient, and the vibration can be sufficiently stabilized.

Although the embodiments of the present invention have been described above, the above embodiments are described. It is only a part of the application examples of the present invention, and the scope of the technology of the present invention is not limited to the specific configuration of the above embodiment.

D‧‧‧buffer

L‧‧‧ liquid room

P‧‧‧Pressure room

R‧‧‧ fuel tank

R1‧‧‧Extension room

R2‧‧‧ pressure side room

1‧‧‧ cylinder

2‧‧‧Piston

2a‧‧‧ pathway

2b‧‧‧ pathway

3‧‧‧ rods

3a‧‧‧ Hollow

3b‧‧‧ bottom

4‧‧‧ rod guides

5‧‧‧ cover

6‧‧‧Attenuation factor

7‧‧‧Attenuation factor

8‧‧‧Free piston

9‧‧‧pressure side attenuation path

10‧‧‧Inhalation pathway

11‧‧‧Attenuation factor

12‧‧‧ check valve

13‧‧‧Spring components

Claims (7)

A damper (D, D1), comprising: a cylinder (1); a piston (2) slidably inserted into the cylinder (1), and dividing the cylinder (1) into an extension chamber ( R1) and the pressure side chamber (R2); the rod member (3, 15) is movably inserted into the cylinder (1) and coupled to the piston (2); the oil tank (R, R3) is disposed on the rod member In (3, 15), the volume change in the cylinder (1) accompanying expansion and contraction is compensated; the tank (R, R3) communicates with the pressure side chamber (R2). The damper (D, D1) of the first aspect of the patent application, further comprising: a pressure side attenuation passage (9, 20) disposed between the oil tank (R, R3) and the pressure side chamber (R2), Only the flow of the liquid from the pressure side chamber (R2) to the above tank (R, R3) is allowed, and the flow of the liquid is applied; the suction passage (10, 21) is disposed in the above tank (R, R3) and Between the pressure side chambers (R2), only the flow of the liquid from the tank (R, R3) to the pressure side chamber (R2) is allowed. A damper (D) according to claim 1 or 2, further comprising a free piston (8) slidably inserted into the rod member (3), wherein the free piston (8) is used The oil tank (R) is divided into a liquid chamber (L) on the side of the piston (2) and a pressurizing chamber (P) for pressurizing the liquid chamber (L), and is disposed in the pressurizing chamber (P) for The above-mentioned liquid chamber (L) is pressed by the elastic means (13). The damper (D1) of claim 1 or 2, further comprising: a partition member (18) fixed to the cylinder (1), and forming a pressure side chamber (R2) together with the piston (2); a pipe member (16) connected to the partition member (18), the inside of which is in communication with the pressure side chamber (R2), the rod member (15) is cylindrical, and the pipe member (16) is inserted into the rod member (15). The oil tank (R3) is a space (A) formed by the above-mentioned rod member (15) and the above-mentioned tube member (16). The damper (D1) of claim 4, further comprising: closing a side of the pressure side chamber (R2) of the cylinder (1), and forming a space (17) with the partition member (18) The cover body (5) is provided with the pressure side attenuation passage (20) and the suction passage (21) in the partition member (18), and the inside of the pipe member (16) communicates with the space (17). A damper (D1) according to claim 4, further comprising a free piston (24) slidably inserted into the pipe member (16), wherein the oil tank (R3) is provided by the free piston (24) The space (A) is divided into a liquid chamber (L1) on the side of the pipe member (16) and a pressurizing chamber (P1) on the side of the rod member (15) for pressurizing the liquid chamber (L1). The damper (D1) of claim 6 further comprising: a package member (19) for enclosing the anti-cylinder (1) side end of the rod member (15); and a biasing means (25) The liquid chamber (L1) is pressurized between the package member (19) and the free piston (24).