JPS6029018B2 - Rotating liquid buffer - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary liquid shock absorber having a function of compensating for the volume of oil that changes due to temperature.

Rotating liquid shock absorbers, which generate resistance by filling a cylinder with high-viscosity oil and generating several shearing forces in the oil, have a simple structure and have been used for a long time as small-capacity devices. has been done.

Particularly in recent years, due to the rationalization of office work, typewriters, communication devices, and other office equipment are becoming faster, and this type of hydraulic shock absorber has come to be used as a vibration damping device. Conventionally, this type of rotary liquid shock absorber has an airtight structure such as a free piston inside the cylinder to compensate for changes in the volume of oil due to the temperature environment at the installation location and temperature changes during operation. A gas chamber was provided, and the gas chamber was used as a volume compensation chamber.

In addition, there have been some that provide the volume compensation chamber outside the cylinder and distribute it inside the cylinder. However, in this configuration, there are volume compensation chambers inside and outside the cylinder, which increases the number of parts, making the configuration complicated, increasing the number of assembly steps, and increasing costs. Furthermore, since a highly viscous oil, such as silicone oil, is used as the hydraulic fluid, and the shear force is used to obtain resistance, changes in viscosity due to temperature changes have a large effect on the generated resistance. This has disadvantages such as the inability to generate a stable resistance force.

The present invention solves the above-mentioned problems, and is characterized in that the change in volume of oil due to temperature change is compensated for by movement of a rod that receives input in the rotational direction. With this configuration, even if the viscosity of the oil changes due to temperature changes, the resistance characteristics generated are not affected by this viscosity change and stable characteristics can be obtained. .

Embodiments of the present invention will be described below with reference to the drawings.

In FIG. 1, reference numeral 1 denotes a cylinder containing a high-viscosity oil, and the inner peripheral wall of the cylinder 1 has two irregularly shaped holes ld.
' and a hole ld'', and a guide hole la on one end wall.
A drum hole lb is provided at the other end.

The cylinder 1 rotatably and slidably supports the rod 2 in the guide hole la and the drum hole lb. The inside of the joint hole lb is permanently connected to the cylinder oil chamber via a passage IC formed between the end wall of the cylinder 1 and the outer periphery of the rod 2.

A cylindrical rotor 3 having a bottom portion 3a is fixed to the rod 2 with a pin 4 so as to be rotated through the rod 2, and the rotor 3 has an outer peripheral surface 3b and a hole ld of a cylinder serving as a resistance member. A gap for generating a sea bream breaking force, that is, a break gap c, is formed between the inner circumferential wall of ``.Furthermore,
A spring 5 is interposed between one end wall of the cylinder and the bottom 3a of the rotor 3, and the spring 5 always urges the assembly of the rod 2 and rotor 3 inwardly into the cylinder 1. . The spring 5 is in elastic contact with the rotor 3 via a seat 6 and a spring seat 7 on the bottom 3a of the rotor 3. The seat 6 is made of a low-friction material such as a nylon plate, and is designed to be able to rotate with a strong resistance force between it and the rotor 3. In addition, in the embodiment, the rod 2 and the rotor 3,
Although a spring 5 is provided in the cylinder to always bias the assembly into the millinder, it is not limited to providing it inside the cylinder, and the spring 5 is provided outside the cylinder to bias the rod toward the inside of the cylinder. It may be provided as follows.

Now, a rotational force is applied to the rod 2 of the rotary liquid buffer, and when the rod 2 rotates, the rotor 3 also rotates, and a resistance force is generated according to the foot cutting gap c.

Note that the rod 2 is urged inward by the spring 5 to pressurize the oil inside the cylinder, so the oil film in the opening gap c does not break and the resistance becomes stable. When the oil in the cylinder expands due to the heat generation effect associated with operation and changes in the environmental temperature, the rod 2 is moved by a volume corresponding to the volume change of the oil due to the pressure difference between the inside and outside of the cylinder. It moves to the right (towards the outside of the cylinder) to compensate for the volume inside the cylinder.

Conversely, if the operation stops and the temperature drops, the rod 2 will move to the left (inward of the cylinder) due to the pressure difference between the inside and outside of the cylinder 1 and the spring 5, by the amount of the reduced volume of the oil. Volume compensation within the cylinder 1 is performed. By the way, since the cylinder 10 serving as a resistance section is provided inside one end wall of the cylinder 1, the rotor 3 only forms a scale gap c between its outer circumferential surface 3b and the inner circumferential wall of the hole ld'. Moreover, a shear gap c is also formed between the inner circumferential surface 3c and the outer circumferential surface 10a of the cylinder 10.

Note that since the diameter of the hole ld' is larger than the diameter of the hole ld'', the inner circumferential wall of the hole ld' and the outer circumferential surface 3 of the rotor 3
There is almost no shear force between Nada and b.

Therefore, in this embodiment, the same operation as described above is performed regarding volume compensation of the oil in the cylinder due to temperature changes.

That is, the viscosity of the oil in the cylinder 1 decreases due to temperature rise, but in this case, the rotor 3 moves to the right in the axial direction together with the rod 2, changing so as to increase the deep cross-sectional area of the gap c. Therefore, it is possible to prevent the generated resistance force from decreasing.

Conversely, when the viscosity of the oil in the cylinder 1 increases due to a decrease in temperature, the rotor 3 moves to the left in the wisteria line direction together with the rod, changing so as to reduce the cross-sectional area of the several cross-sectional gaps c. Therefore, it is possible to prevent the generated resistance from becoming excessive. FIG. 2 shows still another embodiment of the present invention, in which two annular disks 1 are mounted on the inner wall ld of the cylinder 1 as resistance members.
0' are provided at predetermined intervals in the axial direction so as to be orthogonal to the marl line direction of the rod 2, and on the other hand, a disk-shaped rotor 3 is provided on the sleeve 3d of the rod and fixed with a pin 4, and the disk-shaped A rotor 3 is arranged adjacent to the annular disk 10' from the left side in the figure.

And discoid. A cutting gap c is formed between the motor 3 and the annular disc 10'. Note that the spring 5 is interposed between the end surface of the sleeve 3d and one end wall of the cylinder, and urges the rod 2 and rotor 3 assembly inwardly into the cylinder. In the case of this embodiment, the change in volume within the cylinder is compensated for by moving the rod 2 in the direction of the parallax. Furthermore, the interval of the cutting gap c between the rotor 3 and the annular disk 10' serving as a resistance portion changes, so that the cutting resistance can be kept almost uniform. Note that when transmitting an input to the rod 2 via a lever, for example, if the lever is connected directly to the rod 2, the lever will rotate the rod 2 and be displaced in all directions along its axis. If this is not desired, that is, in order to prevent the lever from moving in the direction of the bag line of the rod 2, a separate joint 9 as shown in FIG. This problem can be solved by connecting the shafts and attaching a lever for applying input to the shafts.

As described above, the rotary liquid shock absorber of the present invention is supported rotatably and slidably in the axial direction within the cylinder, and has one end facing inside the cylinder and the other end protruding outside the cylinder. Since a rod is provided to receive input in the rotational direction, changes in the volume of the oil in the cylinder 1 can be compensated for simply by moving the rod in the direction of the flywheel, eliminating the need for separate volume compensation chambers inside and outside the cylinder. , the manufacturing process can be simplified, and costs can be significantly reduced. Also,
Since the rotor is moved together with the rod to change the breaking resistance force, it is possible to compensate for changes in breaking resistance caused by temperature changes, and to generate stable resistance force.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view showing an embodiment of the present invention, and FIG. 2 is a sectional view showing another embodiment of the invention. 1...Cylinder, 2...Rod, 3...Rotor, 5...
Spring, 6... Seat, 7... Spring seat, c... Period gap. Figure 1 Figure 2

Claims (1)

[Claims] 1. A cylinder that houses a high-viscosity oil liquid inside, and a rod that is rotatably and slidably supported by the cylinder and has one end facing inside the cylinder and the other end protruding outside the cylinder; A shearing gap is formed between the rotor and the rotor, which is located in the cylinder and rotates and moves together with the rod, and the shearing gap is formed between the rotor and the rotor, and the shearing force is generated by following the movement of the rod. A rotary liquid shock absorber consisting of a resistance member that makes the resistance variable.