JPH04342895A - Vibration damping equipment for rotary compressor - Google Patents

Abstract

PURPOSE:To produce a vibration damping equipment which is applied to a rotary compressor and can yield extremely steady vibration damping effect, and has compact structure and high reliability. CONSTITUTION:A vibration damping equipment is provided with an inertia body 16 having a communicating hole 16a, two coil springs 17a, 17b whose end faces on their one sides are connected to the inertia body 16, fixing members 18a, 18b to fix the end faces on the other sides of the coil springs 17a, 17b, and a guider 19 which has the inertia body 16 and the coil springs 17a, 17b closedly in its inside, and restricts the movement of the above inertia body 16 only in an about circumferential direction to the rotary shaft of a compressing element 4 or a tangential direction to a circle having the rotary shaft as its center, and moreover seals up oil 20 inside.

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 a rotary compressor used in a refrigeration system or the like.

0002

2. Description of the Related Art In recent years, compressors used in refrigeration equipment, etc. have been shifting from reciprocating types to rotary types from the standpoint of energy and space saving. These rotary compressors usually have an electric compression element consisting of a compression element section and an electric motor section directly fixed and housed in a sealed case. The rotational vibrations generated around the axis directly vibrate the sealed case, and the vibrations vibrate the main body of the refrigerant piping, freezing and refrigerating equipment, etc., sometimes generating large noise.

Therefore, as a conventional technique for damping vibrations of a rotary compressor, for example, Japanese Patent Publication No. 58-5486
As shown in the publication, there is a vibration damping structure for a rotary hermetic electric compressor using a beam type dynamic vibration absorber.

An example of the vibration damping structure of the above-mentioned conventional rotary compressor will be described below with reference to the drawings.

FIG. 5 is a partial cross-sectional view of a conventional rotary compressor. In the figure, 1 is a rotary compressor, and 2 is a closed case. 3 is an electric motor, and 3a is a stator of the electric motor, which is fixed in the sealed case 2 by shrink fitting. 3b is a rotor of an electric motor, which is connected and fixed to the crankshaft 5 of the compression element 4 by shrink fitting. A piston 6 is rotatably mounted on the eccentric portion of the crankshaft 5. A cylinder 7 has a lower bearing 8 and an upper bearing 9 disposed at both ends thereof, and its outer peripheral portion is welded and fixed within the sealed case 2. Reference numeral 10 denotes a discharge cover, which is press-fitted and fixed to the upper bearing 9.

Reference numeral 11 designates a dynamic vibration absorber, which includes an inertial body 12 and a shaft-shaped connecting portion 13 with the inertial body 12 provided at an end 13a.
The other end 13b of the connecting portion 13
is fixed perpendicularly to the outer wall surface of the sealed case 2 by resistance welding. The first-order natural frequency of the dynamic vibration absorber 11 is determined by adjusting the weight and shape of the inertial body 12, the length of the connecting portion 13, the diameter of the cross section, etc. so that it almost matches the rotational frequency of the rotary compressor. I'm making adjustments. 14 is compression element 4
It is a lubricating oil that lubricates the

The operation of the vibration damping device for a rotary compressor constructed as described above will be explained below.

When the refrigerant is compressed in the cylinder 7, the pressure inside the cylinder 7 fluctuates greatly during one revolution of the crankshaft 5, causing fluctuations in the angular velocity of the rotation of the crankshaft 5, and as a reaction to this, the cylinder 7 Receives force from 7th magnitude. Therefore, vibrations occur in the rotational direction around the axis of the crankshaft 5, and the sealed case 2 vibrates greatly. However, as the inertial body 12 of the dynamic vibration absorber 11, which is arranged in the sealed case 2 and whose natural frequency is adjusted to almost match the rotational frequency of the rotary compressor 1, vibrates, the dynamic vibration absorber 11 becomes airtight. At the installation point in the case 2, a reaction torque is supplied to the sealed case 2 through the connection part 13 of the dynamic vibration absorber 11, and the vibration of the rotary compressor 1 is suppressed by canceling out the vibration torque of the rotary compressor 1. It is something that attenuates.

[0009]

[Problems to be Solved by the Invention] However, in the above configuration, since the peak of the natural vibration of the dynamic vibration absorber 11 is sharp, a large reaction torque is generated at the peak of the natural vibration, but when it deviates from the peak, the reaction torque increases. It will drop drastically. Therefore, due to changes in the rotation frequency due to changes in the operating conditions of the rotary compressor 1 and changes in natural vibration due to variations in the manufacturing process of the dynamic vibration absorber 11, the rotation frequency of the rotary compressor 1 and the dynamic vibration absorber 11 There is a problem in that when the frequency difference from the natural frequency becomes large, the vibration damping effect becomes insufficient.

Furthermore, in order to obtain a sufficient vibration damping effect, the amount of displacement of the inertial body 12 must be increased by making the inertial body 12 sufficiently heavy or by making the length of the connecting portion 13 sufficiently long. Therefore, the connecting portion 13 may be damaged due to strong impact, etc., especially during transportation, or the connecting portion 1 may be damaged due to vibration of the inertial body 12.
The vibration damping effect may not be obtained due to fatigue failure of the connecting portion 13 due to stress concentration due to the deformation of the connecting portion 3. Furthermore, since the dynamic vibration absorber 11 protrudes from the side of the compressor for a long time, the packaging for transporting the compressor becomes large and complicated, resulting in poor workability when incorporating the compressor into a product. It also had

[0011] The present invention solves the above-mentioned problems, and it is possible to obtain an extremely stable vibration damping effect by preventing the vibration damping effect from deteriorating due to fluctuations in the rotational frequency of the rotary compressor, manufacturing variations, etc. The object of the present invention is to provide a vibration damping device for a rotary compressor that is compact and highly reliable.

0012

Means for Solving the Problems In order to solve the above problems, a vibration damping device for a rotary compressor according to the present invention includes: an inertial body having a communication hole; a coil spring having one end surface connected to the inertial body; a fixture for fixing the other end surface of the coil spring; the inertial body and the coil spring are hermetically sealed; a guider that restrains only in the tangential direction of a circle to be compressed and seals oil inside, and compresses the fixture so that the guider is located on a plane perpendicular to the rotation axis of the compression element part. An electric compression element section consisting of an element section and an electric motor section is fixed in a sealed case. Further, the electric compression element is configured to be fixed to a component that is not a rotating body.

[0013]

[Operation] According to the above-described structure, the present invention reduces vibrations generated during operation of a rotary compressor by a dynamic vibration absorber composed of a fixture fixed to the rotary compressor main body, an inertial body, a coil spring, and a guider. The vibration of the rotary compressor is damped by supplying reaction torque, and the behavior of the inertial body is restrained by the guider so that reaction torque is supplied only to the main vibration of the rotary compressor, resulting in stability without loss. can be attenuated. In addition, by sealing oil inside the guider and providing a communication hole through which the oil communicates with the inertial body, the damping effect caused by the viscosity of the oil can be appropriately adjusted, and vibration damping is achieved through the appropriate damping effect. The range of effect is widened, and it is possible to prevent a decrease in the vibration damping effect due to fluctuations in the rotational frequency of the rotary compressor or variations in the manufacturing process of the dynamic vibration absorber.

Furthermore, the guider prevents the inertial body from being significantly deformed during transportation, and prevents the vibration damping effect from being lost due to damage to the dynamic vibration absorber or changes in characteristics due to rust in the movable parts. Can be done. Furthermore, if a dynamic vibration absorber is attached to a non-rotating component of an electric compression element, the packaging for transporting a rotary compressor can be exactly the same as that for a rotary compressor without a dynamic vibration absorber. It is also possible to completely prevent a decrease in work efficiency due to the presence of a dynamic vibration absorber during assembly.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of a vibration damping device for a rotary compressor according to the present invention will be described below with reference to the drawings. In order to avoid duplication of explanation, the same parts as in the conventional example are given the same reference numerals and the explanation will be omitted.

FIGS. 1 and 2 show a first embodiment of a vibration damping device for a rotary compressor according to the present invention.

In the figure, reference numeral 15 is a dynamic vibration absorber, and the communication hole 1
6a, coil springs 17a, 17b,
It is composed of fixtures 18a and 18b, a guider 19, and oil 20. One end surface of each of the two coil springs 17a, 17b is connected to the inertial body 16, and the other end surface is fixed to fixtures 18a, 18b, respectively. or,
The inertia body 16 and the coil springs 17a, 17b are connected to the fixture 1.
The inside of the guider 19 is hermetically sealed inside the guider 19 attached to 8a and 18b, and the inside of the guider 19 is a sealed chamber 1 due to the inertial body 16.
It is divided into 9a and 19b.

Furthermore, fixtures 18a and 18b are welded and fixed to the outer wall surface of the sealed case 2 so that the guider 19 restricts the behavior of the inertial body 16 only in the tangential direction of a circle centered on the axis of the crankshaft 5. By doing so, the dynamic vibration reducer 15 is fixed to the rotary compressor 1. Furthermore, oil 20 is sealed inside the guider 19, and the communication hole 16 of the inertial body 16 is sealed.
The sealed chambers 19a and 19b inside the guider 19 are communicated with each other through oil 20.

In addition, the dynamic vibration absorber 15 is configured such that the wire diameter and average diameter of the coil springs 17a and 17b, the weight and weight of the inertial body 16 are adjusted so that the first-order natural frequency almost matches the rotational frequency of the rotary compressor 1. Adjusting the shape etc.

The operation of the vibration damping device for a rotary compressor constructed as described above will be explained below.

When the refrigerant is compressed in the cylinder 7, the pressure inside the cylinder 7 changes greatly during one revolution of the crankshaft 5, causing a change in the angular velocity of the rotation of the crankshaft 5, and as a reaction, the cylinder 7 Receives force from 7th magnitude. This causes vibrations in the rotational direction around the axis of the crankshaft 5, causing the sealed case 2 to vibrate greatly. However, as the inertial body 16 of the dynamic vibration absorber 15, which is arranged in the sealed case 2 and whose natural frequency is adjusted to almost match the rotational frequency of the rotary compressor 1, vibrates, the dynamic vibration absorber 15 becomes airtight. At the installation location in the case 2, a reaction torque is supplied to the sealed case 2 via the fixtures 18a and 18b of the dynamic vibration absorber 15, and vibrations are damped by canceling the vibration torque of the rotary compressor 1.

At this time, the behavior of the inertial body 16 is restrained by the guider 19 so as to supply a reaction torque only to the vibration in the rotational direction, which is the main vibration of the rotary compressor 1. The reaction torque acts to damp all vibrations in the rotational direction without loss, and an extremely stable vibration damping effect can be obtained.

Furthermore, since the oil 20 is sealed inside the guider 19, the oil 20 is released when the inertial body 16 vibrates.
A damping effect is obtained due to the viscosity of . At this time, since the communication hole 16a allows the oil 20 to freely flow between the sealed chambers 19a and 19b, the magnitude of the damping effect can be adjusted appropriately by the flow path resistance determined by the diameter and length of the communication hole 16a. I can control it. Therefore, when the inertial body 16 vibrates, the viscosity of the oil 20 provides an appropriate damping effect, thereby widening the peak width of the natural vibration of the dynamic vibration absorber 15. As a result, the width of the vibration damping effect generated by the coupling of the natural vibration of the dynamic vibration reducer 15 and the natural vibration of the support system of the rotary compressor 1 becomes wider, and the vibration damping effect can be obtained in a wide frequency band. A sufficient vibration damping effect can be obtained even if there is a change in the rotational frequency due to a change in the operating conditions of the rotary compressor 1 or a change in the natural vibration due to variations in the manufacturing process of the dynamic vibration absorber 15.

Furthermore, by using the coil springs 17a and 17b, the stress added to the coil springs 17a and 17b for the same displacement of the inertial body 16 is smaller than that of beams made of the same material and the same wire diameter, and the guider 19 body 1
Since the behavior of the coil spring 17a is constrained, even if the inertial body 16 is greatly deformed due to fatigue due to vibration or impact, the coil spring 17a
, 17b will not break. Furthermore, since all the movable parts of the dynamic vibration absorber 15 are immersed in the oil 20, even if the dynamic vibration absorber 15 is enclosed in the sealed case 2, the characteristics will not change due to rust, making it extremely reliable. It can be made into something with high quality.

Furthermore, the dynamic vibration reducer 15 has an extremely compact shape because the inertial body 16 is restrained to move only in the tangential direction of a circle centered on the axis of the crankshaft 5. This allows the dynamic vibration absorber 15 to minimize the size of the packaging for transporting the rotary compressor 1.

Next, a second embodiment of the vibration damping device for a rotary compressor according to the present invention will be described with reference to the drawings. In order to avoid duplication of explanation, the same parts as those of the conventional example and the first embodiment are given the same reference numerals and the explanation thereof will be omitted.

3 and 4 show a second embodiment of the vibration damping device for a rotary compressor according to the present invention.

In the figure, 21 is a dynamic vibration absorber, and the communication hole 1
6a, coil springs 17a, 17b,
It is composed of fixtures 22a and 22b, a guider 19, and oil 20. One end surface of each of the two coil springs 17a, 17b is connected to the inertial body 16, and the other end surface is fixed to fixtures 22a, 22b, respectively. or,
The inertia body 16 and the coil springs 17a, 17b are connected to the fixture 2.
The inside of the guider 19 is hermetically sealed inside the guider 19 attached to 2a and 22b, and the inside of the guider 19 is a sealed chamber 1 due to the inertial body 16.
It is divided into 9a and 19b. Furthermore, fixtures 18a,
By fixing 18b to the cylinder 7, the dynamic vibration reducer 21 is fixed to the rotary compressor 1. Furthermore, oil 20 is sealed inside the guider 19, and the sealed chambers 19a and 19b inside the guider 19 are sealed by the communication hole 16a of the inertial body 16.
are communicated by oil 20.

In addition, the dynamic vibration absorber 21 has the wire diameters and average diameters of the coil springs 17a and 17b, the weight and weight of the inertial body 16 so that the first-order natural frequency almost matches the rotational frequency of the rotary compressor 1. Adjusting the shape etc.

With the vibration damping device for a rotary compressor constructed as described above, as shown in the first embodiment,
Even if there is a change in the natural vibration due to variations in the manufacturing process of the dynamic vibration absorber 21, an extremely stable vibration damping effect can be obtained, and it can be highly reliable.

Furthermore, since the dynamic vibration reducer 21 is attached to the cylinder 7, the external shape of the rotary compressor 1 can be made exactly the same as that without the dynamic vibration absorber installed. It is possible to prevent the packaging from becoming larger and more complicated when transporting the rotary compressor 1 due to installation, and also improve workability when incorporating the rotary compressor 1 into a product due to the installation of the dynamic vibration absorber 21. It is also possible to prevent a decrease in

[0032]

As described above, the present invention provides an inertial body having a communication hole, a coil spring having one end surface connected to the inertial body, a fixture for fixing the other end surface of the coil spring, and an inertial body having a communication hole. The body and the coil spring are hermetically sealed, and the behavior of the inertial body is restricted only in the substantially circumferential direction with respect to the rotation axis of the compression element portion or in the tangential direction of a circle centered on the rotation axis, and oil is kept inside. a sealing guider, the fixture is fixedly housed in a manner that the guider is positioned on a plane perpendicular to the rotational axis of the compression element, and an electric compression element comprising a compression element and an electric motor. By forming a vibration damping device for a rotary compressor fixed to a case or a part of the electric compression element part that is not a rotating body, a dynamic vibration absorber structure is formed by an inertial body, a coil spring, a fixture, a guider, and oil, Loss is reduced by attenuating the vibrations that occur during operation of the rotary compressor, and by restricting the behavior of the inertial body using the guider so that it only supplies reaction torque to the vibration in the direction of rotation, which is the main vibration of the rotary compressor. It is possible to achieve stable attenuation without any noise. In addition, the damping effect that occurs when the inertial body vibrates due to the oil sealed inside the guider is optimized by allowing the oil to move freely through the communication hole provided in the inertial body, and by using the flow path resistance due to the shape of the communication hole. Since a vibration damping effect can be obtained in a wide frequency band due to the damping effect, a sufficient vibration damping effect can be obtained even if there is a change in the rotational frequency due to a change in the operating conditions of the rotary compressor.

Furthermore, the guider prevents the inertial body from being significantly deformed during transportation, and by immersing all the movable parts of the dynamic vibration absorber in oil, it is possible to prevent damage to the dynamic vibration absorber or rust on the movable parts. It is possible to prevent vibration damping effects from becoming impossible to obtain due to changes in characteristics.

In addition, if a dynamic vibration reducer is attached to a non-rotating component of an electric compression element, the same packaging for transporting a rotary compressor as that without a dynamic vibration absorber can be used. Preventing larger and more complicated packaging,
Furthermore, it is possible to completely prevent a decrease in work efficiency due to the attachment of a dynamic vibration absorber when a rotary compressor is incorporated into a product.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of a vibration damping device section of a rotary compressor showing an embodiment of the present invention.

[Fig. 2] A vertical cross-sectional view of a rotary compressor showing an embodiment of the present invention.

FIG. 3 is a cross-sectional view of a vibration damping device section of a rotary compressor showing another embodiment of the present invention.

FIG. 4 is a vertical cross-sectional view of a rotary compressor showing another embodiment of the present invention.

[Figure 5] Cross-sectional view of a conventional rotary compressor

[Explanation of symbols]

2 Sealed case 7 Cylinder 15 Dynamic vibration absorber 16 Inertial body 16a Communication hole 17a, 17b Coil spring 18a, 18b Fixing tool 19 Guider 20 Oil 21 Dynamic vibration absorber 22a, 22b Fixing tool

Claims (3)

[Claims] 1. An inertial body having a communication hole, a coil spring having one end surface connected to the inertial body, a fixture for fixing the other end surface of the coil spring, and the inertial body and coil spring sealed inside, and a guider that restricts the behavior of the inertial body only in the substantially circumferential direction with respect to the rotation axis of the compression element portion or in the tangential direction of a circle centered on the rotation axis, and that seals oil inside. Vibration damping device for mold compressor. [Claim 2] The fixing device is fixed to a sealed case in which an electric compression element section consisting of a compression element section and an electric motor section is fixedly housed so that the guider is positioned on a plane perpendicular to the rotation axis of the compression element section. The vibration damping device for a rotary compressor according to claim 1. Claim 3: The fixture is fixed to a non-rotating component of the electric compression element section consisting of the compression element section and the electric motor section so that the guider is located on a plane perpendicular to the rotation axis of the compression element section. The vibration damping device for a rotary compressor according to claim 1.