JPH06117373A - Oscillation damping equipment - Google Patents

Abstract

PURPOSE:To provide an oscillation damping device which can reduce oscillations of vehicle-mounted equipment. CONSTITUTION:A friction plate 5 is fixed to a base 3 which supports a compressor 1 through a buffer member 2, while a pressing means is provided on the compressor 1 through an installation stay 9. The pressing means is made up of a pressing member 6, a spring 7 which presses the pressing member 6 to the side of a friction plate 5 by specified energizing force, and a spring support member 8 which supports the spring 7. When relative displacement occurs between the compressor 1 and the base 3 accompanied with oscillations of a vehicle, frictional sliding is generated between the pressing member 6 and the friction plate 5.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damping device for reducing the vibration of equipment mounted on a vehicle.

[0002]

2. Description of the Related Art Conventionally, there are hermetic compressors used in refrigeration cycles such as air conditioners and refrigerators. This hermetic compressor is one in which a compression element and an electric motor element (motor) are integrally arranged in a hermetic container, and vibrations due to rotational movement are generated. A structure in which it is supported through is general (Japanese Patent Laid-Open No. Sho 5).
8-88475).

[0003]

However, when the above-mentioned hermetic compressor is mounted on an automobile, vehicle vibration occurs in a wide frequency range due to running conditions or road surface conditions. , When the mass of the compressor and the natural frequency of the vibration system formed by the buffer match, the resonance phenomenon occurs. As a result, the compressor body vibrates greatly, which becomes a source of abnormal vehicle vibration and noise. The present invention is
The present invention has been made in view of the above circumstances, and an object thereof is to provide a vibration damping device capable of reducing vibration of a vehicle-mounted device mounted on a vehicle.

[0004]

In order to achieve the above object, the present invention provides either a vehicle-mounted device installed in a vehicle or a base supporting the vehicle-mounted device via an elastic member. An elastic deformation of the elastic member is provided, which includes a friction member provided and a pressing unit which is provided on the other of the vehicle-mounted device and the base and contacts the friction member with a predetermined pressing force. The technical means is to cause frictional sliding between the friction member and the pressing means when relative displacement occurs between the vehicle-mounted device and the base together with the above.

[0005]

According to the vibration damping device of the present invention having the above-mentioned structure, when the vehicle-mounted device and the base are displaced relative to each other due to the vibration of the vehicle, the frictional sliding is performed between the friction member and the pressing means. Cause As a result, the vibration energy of the vehicle is converted into heat generation energy due to frictional sliding between the friction member and the pressing means, and the vibration of the vehicle-mounted device is reduced.

[0006]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, one embodiment of the vibration damping device of the present invention will be described with reference to FIGS. FIG. 1 is a side view of a hermetic compressor provided with a vibration damping device. The hermetic compressor 1 (vehicle-mounted device, hereinafter abbreviated as compressor 1) of the present embodiment is a component of a refrigeration cycle mounted on an electric vehicle, and includes a scroll-type compression element (not shown) and this compression element. It is integrated with a DC brushless motor (not shown) for driving the above, and is housed in one closed container 1a.
This compressor 1 includes a base 3 (for example, a base 3) via four cushioning members 2 (elastic members of the present invention) formed of springs.
It is supported by the chassis of the vehicle). One end of each cushioning member 2 is a spring seat 1 of a mounting leg 1b provided on the compressor 1.
The other end is locked to a spring seat 3a provided on the base 3. Further, between the compressor 1 and the base 3, a vibration damping device 4 for reducing the vibration of the compressor 1 due to the vibration of the vehicle is provided.

The vibration damping device 4 comprises a friction plate 5 (friction member) fixed to the base 3 and a pressing means (described below) provided in the compressor 1. As shown in FIG. 1, the friction plate 5 is made of a material having excellent wear resistance and a large wear coefficient, and is fixed on the base 3 in an upright state. The pressing means are provided on both sides of the friction plate 5, and the pressing members 6,
It is composed of a spring 7 and a spring support member 8, and is attached to the bottom surface of the compressor 1 via an attachment stay 9. Like the friction plate 5, the pressing member 6 is made of a material having excellent wear resistance and a large wear coefficient, and as shown in FIG. 2 (a perspective view of the pressing member 6), the rear end side is provided in a rod shape. Thus, the tip side has a hemispherical shape formed with a constant curvature. Therefore, the pressing member 6 can generate a normal frictional force between the pressing member 6 and the friction plate 5 by making point contact with the friction plate 5 at the contact portion A, even if the compressor 1 tilts.

The spring 7 is coaxially arranged on the outer periphery of the rear end of the pressing member 6 having a rod shape, the rear end of which is locked by the spring support member 8 and the front end of which is the jaw of the pressing member 6. , And presses the pressing member 6 toward the tip side (the friction plate 5 side) with a predetermined biasing force. Therefore, the pressing member 6 frictionally slides on the friction plate 5 when a relative displacement occurs between the compressor 1 and the base 3 due to the vibration of the vehicle. As shown in FIG. 3, the frictional force generated between the friction plate 5 and the pressing member 6 has an optimum value e that minimizes the relative displacement amplitude between the compressor 1 and the base 3 at the time of resonance. To do. Therefore, it is desirable to set the load of the spring 7 so that the optimum frictional force can be obtained. The spring support member 8 has a cylindrical shape with an open front end, and the pressing member 6 is provided inside the cylinder.
And the spring 7. The mounting stay 9 has a substantially L shape, and supports the spring support member 8 such that the pressing members 6 face each other with the friction plate 5 interposed therebetween.

Next, the operation of this embodiment will be described. When vehicle vibration occurs in a wide frequency range due to the running state or road surface state of the vehicle, relative displacement occurs between the base 3 and the compressor 1 due to elastic deformation of the cushioning member 2. That is, the compressor 1 vibrates with respect to the base 3. When the relative displacement between the base 3 and the compressor 1 occurs, the friction plate 5 and the pressing member 6
Friction and sliding occur between and, and the vibration energy is absorbed by the friction and sliding, and the vibration of the compressor 1 is reduced. As a result, it is possible to prevent abnormal vehicle vibration and noise from being generated due to the large vibration of the compressor 1.

FIGS. 4 to 6 show a second embodiment of the present invention. FIG. 4 is a side view of the hermetic compressor 1 including the vibration damping device 4. In the vibration damping device 4 of the present embodiment, the friction plate 5 shown in the first embodiment has the base 3 via the spring 10.
It is a structure supported by. Therefore, when relative displacement occurs between the base 3 and the compressor 1 due to the vibration of the vehicle, the friction plate 5 and the pressing member 6 are in a range in which the frictional force at the contact portion A is larger than the repulsive force of the spring 10. There is no frictional sliding between and. In this case, since the spring constant of the entire vibration system is the sum of the spring constant Kb of the buffer member 2 and the spring constant Ka of the spring 10, the resonance frequency is higher than that of the buffer member 2 alone, as shown in FIG. Move to frequency range f ₁ . Note that FIG. 5 is a graph showing the relationship between the relative displacement amplitude of the compressor 1 and the base 3 and the vibration frequency. When the graph shown by the broken line a uses only the buffer member 2, the graph shown by the broken line b buffers. When the member 2 and the spring 10 are used together, the graph of the solid line c is the case of this embodiment. Since the optimum value e of the frictional force at the contact portion A changes depending on the spring constant Ka of the spring 10 as shown in FIG. 6, the set load of the spring 7 is adjusted according to the spring constant Ka of the spring 10.

After that, when the relative displacement amplitude between the base 3 and the compressor 1 increases as the vibration frequency increases, the repulsive force of the spring 10 increases. When the repulsive force of the spring 10 exceeds the frictional force between the friction plate 5 and the pressing member 6, frictional sliding occurs between the friction plate 5 and the pressing member 6 (point d in FIG. 5). In this case, since the elastic force of the spring 10 supporting the friction plate 5 does not act, the spring constant of the entire vibration system is only the spring constant Kb of the buffer member 2, and the vibration frequency is as shown by the broken line a in FIG. Move to the lower frequency range f ₂ . As described above, in this embodiment, the vibration of the compressor 1 can be reduced, and the resonance point can be avoided by switching the entire spring constant when the amplitude of the vibration is large.

FIG. 7 shows a third embodiment of the present invention. As shown in FIG. 7, the vibration damping device 4 of the present embodiment has the friction plate 5 fixed to the compressor 1 side and the pressing means provided on the base 3 side, and the same effect as the first embodiment. Can be obtained. Figure 8
The fourth embodiment of the present invention is shown in FIG. As shown in FIG. 8, the vibration damping device 4 of the present embodiment has the spring 10 and the friction plate 5 shown in the second embodiment provided on the compressor 1 side and the pressing means provided on the base 3 side. Thus, the same effect as the second embodiment can be obtained. FIG. 9 shows a fifth embodiment of the present invention.
As shown in FIG. 9, the vibration damping device 4 of this embodiment has a structure in which the friction plate 5 is fixed to the base 3 and the pressing means is supported by the compressor 1 via the spring 10. The same effect as the embodiment can be obtained. FIG. 10 shows a sixth embodiment of the present invention. As shown in FIG. 10, the vibration damping device 4 of the present embodiment has a structure in which the friction plate 5 is fixed to the compressor 1 and the pressing means is supported by the base 3 via the spring 10. The same effect as the embodiment can be obtained.

[Modification] In this embodiment, the pressing members 6 are arranged on both sides of the friction plate 5. However, the pressing member 6 that comes into contact with the friction member has a polygonal or circular cross section. You may provide three or more. Although the contact between the friction plate 5 and the pressing member 6 is a point contact, it may be a surface contact. Instead of the cushioning member 2 (spring), the spring 7 and the spring 10, another elastic body can be used.

[0014]

According to the vibration damping device of the present invention, when a relative displacement occurs between the vehicle-mounted device and the base, friction sliding occurs between the friction member and the pressing means, so that the vehicle-mounted device is mounted. Vibration can be reduced. As a result, it is possible to prevent abnormal vehicle vibration and noise that are caused by the vehicle-mounted device as a vibration source.

[Brief description of drawings]

FIG. 1 is a side view of a hermetic compressor including a vibration damping device according to a first embodiment.

FIG. 2 is a perspective view of a pressing member according to the present embodiment.

FIG. 3 is a graph showing the relationship between the peak value of the relative displacement amplitude between the compressor and the base and the frictional force.

FIG. 4 is a side view of a hermetic compressor including a vibration damping device according to a second embodiment.

FIG. 5 is a graph showing the relationship between the relative displacement amplitude of the compressor and the base and the vibration frequency.

FIG. 6 is a graph showing the relationship between the optimum value of frictional force and the spring constant of a spring.

FIG. 7 is a side view of a vibration damping device according to a third embodiment.

FIG. 8 is a side view of a vibration damping device according to a fourth embodiment.

FIG. 9 is a side view of a vibration damping device according to a fifth embodiment.

FIG. 10 is a side view of a vibration damping device according to a sixth embodiment.

[Explanation of reference numerals] 1 hermetic compressor (equipment mounted on vehicle) 2 cushioning member (elastic member) 3 base 4 vibration damping device 5 friction plate (friction member) 6 pressing member (pressing means) 7 spring (pressing means) 8 Spring support member (pressing means)

Claims (1)

[Claims] 1. A friction member provided on one of a) a vehicle-mounted device installed in a vehicle and a base supporting the vehicle-mounted device via an elastic member; and b) the vehicle-mounted device. A pressing means provided on either of the base and the other for contacting the friction member with a predetermined pressing force; and the vehicle-mounted device and the base together with elastic deformation of the elastic member. A vibration damping device that causes frictional sliding between the friction member and the pressing means when a relative displacement occurs between them.