CN216114786U

CN216114786U - Compressor assembly and refrigeration equipment

Info

Publication number: CN216114786U
Application number: CN202122507882.9U
Authority: CN
Inventors: 谭书鹏; 王建华; 叶容君
Original assignee: Anhui Meizhi Precision Manufacturing Co Ltd
Current assignee: Anhui Meizhi Precision Manufacturing Co Ltd
Priority date: 2021-10-18
Filing date: 2021-10-18
Publication date: 2022-03-22
Anticipated expiration: 2031-10-18

Abstract

The utility model discloses a compressor assembly and discloses refrigeration equipment with the compressor assembly, wherein the compressor assembly comprises a compressor shell, a liquid storage device and a counterweight structure, wherein the liquid storage device is connected to the compressor shell; the counterweight structure includes a cantilever member and a counterweight member coupled to at least one of the compressor housing and the reservoir via the cantilever member. Through designing the counter weight structure into independent structure, this structure can be placed and realize the damping effect on arbitrary rotating machinery, can realize the modularization damping, has simple to operate, advantage that the reliability is high. In addition, the cantilever type counterweight installation mode can play a role of a dynamic vibration absorber while increasing the rotational inertia of the rotary machine, and plays a good role in inhibiting local vibration noise at the joint.

Description

Compressor assembly and refrigeration equipment

Technical Field

The utility model relates to the technical field of refrigeration, in particular to a compressor assembly and refrigeration equipment.

Background

In order to reduce the noise of the compressor housing during operation, in the related art, the compressor housing is generally fixed to a mounting base plate of the compressor housing through an elastic foot pad, which can reduce the vibration and noise of the compressor housing during operation to a certain extent, but the noise and vibration of the compressor housing during operation are still large.

SUMMERY OF THE UTILITY MODEL

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the utility model provides a compressor assembly which can improve the vibration reduction effect.

The utility model also provides refrigeration equipment with the compressor assembly.

A compressor assembly according to an embodiment of the first aspect of the utility model, comprising a compressor, an accumulator and a counterweight structure, the compressor comprising a compressor housing, the accumulator being connected to the compressor housing; the counterweight structure includes a cantilever member and a counterweight member coupled to at least one of the compressor housing and the reservoir via the cantilever member.

The compressor assembly according to the embodiment of the utility model has at least the following advantages: through designing the counter weight structure into independent structure, this structure can be placed and realize the damping effect on arbitrary rotating machinery, can realize the modularization damping, has simple to operate, advantage that the reliability is high. In addition, the cantilever type counterweight installation mode can play a role of a dynamic vibration absorber while increasing the rotational inertia of the rotary machine, and plays a good role in inhibiting local vibration noise at the joint.

According to some embodiments of the utility model, the weight is located below the reservoir.

According to some embodiments of the utility model, the cantilever member is connected to a lower portion of the compressor housing.

According to some embodiments of the utility model, the cantilever member is connected to a bottom of the reservoir.

According to some embodiments of the utility model, the cantilever member is connected to a lower portion of the compressor housing, and the weight member is located on a side of the compressor housing away from the accumulator.

According to some embodiments of the utility model, the weight member comprises a container and a weight material, the container is provided with a cavity, and the weight material is filled in the cavity.

According to some embodiments of the utility model, the weight material is a particulate solid material.

According to some embodiments of the utility model, the weight material comprises cement.

According to some embodiments of the utility model, the counterweight structure has a weight m1, and the compressor assembly has a weight m, satisfying: m1/m is more than or equal to 4 percent.

The refrigeration equipment according to the second aspect embodiment of the utility model comprises the compressor assembly of the first aspect embodiment of the utility model.

The refrigeration equipment provided by the embodiment of the utility model has at least the following beneficial effects: by adopting the compressor assembly of the embodiment of the first aspect of the utility model, the advantages of convenient installation and high reliability are achieved. In addition, the cantilever type counterweight installation mode can play a role of a dynamic vibration absorber while increasing the rotational inertia of the rotary machine, and plays a good role in inhibiting local vibration noise at the joint.

Additional aspects and advantages of the utility model will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the utility model.

Drawings

The utility model is further described with reference to the following figures and examples, in which:

FIG. 1 is a schematic view of a compressor assembly of the related art;

FIG. 2 is a schematic view of a compressor assembly according to one embodiment of the present invention;

FIG. 3 is a schematic view of a compressor assembly according to another embodiment of the present invention;

FIG. 4 is a schematic view of a compressor assembly according to another embodiment of the present invention;

FIG. 5 is a schematic view of a compressor assembly according to another embodiment of the present invention;

FIG. 6 is a schematic view of a compressor assembly according to another embodiment of the present invention;

FIG. 7 is a schematic view of a compressor assembly according to another embodiment of the present invention;

FIG. 8 is a graph comparing noise of a compressor assembly without a counterweight structure and a compressor assembly with a counterweight structure according to an embodiment of the present invention;

FIG. 9 is a graph illustrating the vibration effect of the suspension members with different lengths of the compressor assembly according to the embodiment of the present invention;

fig. 10 is a graph showing the comparison of vibration effects of the counterweight structures of the compressor assembly according to the embodiment of the present invention installed at different positions.

Reference numerals:

101. a compressor housing; 102. a reservoir; 103. an upper cup body; 104. a main cup body; 105. a lower cup body; 106. an exhaust pipe; 107. an air intake duct;

201. a cantilever member; 202. a counterweight; 203. a first connection portion; 204. a second connecting portion; 205. a container; 206. a weight material;

501. an axis of revolution.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

In the description of the present invention, it should be understood that the orientation or positional relationship referred to in the description of the orientation, such as the upper, lower, front, rear, left, right, etc., is based on the orientation or positional relationship shown in the drawings, and is only for convenience of description and simplification of description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.

In the description of the present invention, the meaning of a plurality of means is one or more, the meaning of a plurality of means is two or more, and larger, smaller, larger, etc. are understood as excluding the number, and larger, smaller, inner, etc. are understood as including the number. If the first and second are described for the purpose of distinguishing technical features, they are not to be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.

In the description of the present invention, unless otherwise explicitly limited, terms such as arrangement, installation, connection and the like should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above terms in the present invention in combination with the specific contents of the technical solutions.

A compressor is the heart of a refrigeration appliance, which is a driven fluid machine that raises low pressure gas to high pressure gas. The refrigerating cycle is powered by sucking low-temperature and low-pressure refrigerant gas from the air suction pipe, driving the piston to compress the refrigerant gas through the operation of the motor, and discharging high-temperature and high-pressure refrigerant gas to the exhaust pipe.

In the compressor, the accumulator is an important component, is assembled at the air conditioner evaporator and the suction pipe of the compressor, and is a protective component for preventing liquid refrigerant from flowing into the compressor to generate liquid impact. During the operation of the air conditioning system, the refrigerant can not be completely vaporized; namely, the liquid refrigerant can enter the liquid storage device from the refrigerant coming out of the evaporator, the liquid refrigerant which is not vaporized can directly fall on the cylinder bottom of the liquid storage device because the refrigerant is heavier than gas, and the vaporized refrigerant enters the compressor from the outlet of the liquid storage device, so that the liquid impact caused by the liquid refrigerant sucked by the compressor is prevented.

In order to reduce the noise of the compressor during operation, in the related art, the compressor is generally fixed to a mounting base plate of the compressor through an elastic foot pad, which can reduce the vibration and noise of the compressor during operation to a certain extent, but the noise and vibration of the compressor during operation are still large.

Then, through research, the overall weight of the compressor is an important factor influencing the vibration of the compressor, and in the compressor in the related art, the compressor is poor in stability during operation due to the fact that the compressor is light in weight, and large working vibration is generated, so that the working performance and reliability of the compressor are influenced, and the working noise of the compressor is large. In the related art, the moment of inertia of the whole compressor is improved by adding a counterweight on the compressor or the liquid storage device, but the improved effect cannot meet the requirement.

Referring to fig. 1 to 10, a compressor assembly and a refrigeration device according to an embodiment of the present invention will be described to solve the problems of noise and vibration.

Referring to fig. 1, it can be understood that, in the related art, the compressor assembly includes a compressor 101 and a reservoir 102, the compressor includes a compressor housing 101, a main bearing assembly, a pump body and an auxiliary bearing assembly, the main bearing assembly, the pump body and the auxiliary bearing assembly are disposed in the compressor housing 101, the main bearing assembly and the auxiliary bearing assembly are respectively disposed at two axial ends of the cylinder assembly, an air inlet of the pump body is formed on the main bearing assembly or the auxiliary bearing assembly, and an exhaust pipe 106 of the reservoir 102 is communicated with the air inlet of the pump body.

The liquid storage device 102 comprises an upper cup body 103, a main cup body 104 and a lower cup body 105, the liquid storage device 102 is provided with an exhaust pipe 106 and an air suction pipe 107, the upper cup body 103, the main cup body 104 and the lower cup body 105 are sequentially connected from top to bottom to form a complete container 205 cup body, the upper cup body 103 is further connected with the air suction pipe 107, the lower cup body 105 is connected with the exhaust pipe 106, and the exhaust pipe 106 is connected with a compressor.

It can be understood that, in the conventional three-segment reservoir 102, the upper cup 103, the main cup 104 and the lower cup 105 are welded to each other to form the complete container 205 cup, and the parts are combined together by welding, which can reduce the difficulty of production and manufacture and can facilitate the processing of the parts.

It can be understood that the upper cup 103, the main cup 104 and the lower cup 105 of the spinning type liquid accumulator 102 are integrally formed, that is, the cup of the liquid accumulator 102 is a metal cylinder, and both ends of the metal cylinder are extruded and formed. Specifically, a metal cylinder with a proper inner diameter is selected according to actual requirements, then the two ends of the metal cylinder are extruded, so that the inner diameters of the two ends of the metal cylinder are narrowed to form an upper cup 103 and a lower cup 105, and a main body of the metal cylinder is reserved as a main cup 104, so that the upper cup 103, the main cup 104 and the lower cup 105 are integrally formed. Meanwhile, after the openings at the two ends of the metal cylinder are extruded, an exhaust hole in butt joint with the exhaust pipe 106 and an air suction hole in butt joint with the air suction pipe 107 are respectively formed.

It can be understood that the exhaust pipe 106 is welded with the lower cup 105, specifically, the exhaust pipe 106 is connected with the lower cup 105 through a flame brazing process, the flame brazing is performed by using flame formed by mixing and burning gasification products of combustible gas or liquid fuel and oxygen or air, the universality is high, the process is simple, the operation technology is easy to master, the automatic operation is easy to realize, the flame brazing can be completed in air, no protective gas is needed, meanwhile, the selection range of the brazing filler metal is wide, the brazing filler metal can be applied from low-temperature silver-based brazing filler metal to high-temperature nickel-copper-based brazing filler metal, the shape of the brazing filler metal is almost not required, and the brazing filler metal is simple and easy to use. The flame brazing process is known in the art and will not be described in detail herein.

In addition, the exhaust pipe 106 and the lower cup body 105 can be connected together through a high-frequency induction brazing process, the induction brazing is a welding method which utilizes high-frequency, medium-frequency or power-frequency induction current as a heat source, metal workpieces to be welded are placed in an induction coil, high-frequency alternating current is conducted, an induction electromagnetic field is generated, induction electromotive force is generated by coupling at the connecting position of the exhaust pipe 106 and the lower cup body 105, induction eddy current is formed on the metal surface, heat is generated by means of eddy current generated on the metal surface, welding powder is coated on the welding position, and the lower cup body and the exhaust pipe can be welded when the melting temperature of brazing filler metal is reached, so that the high-frequency induction brazing method is quick and efficient, is less in pollution, and is beneficial to environmental protection. The induction brazing process belongs to the prior art and is not described in detail herein.

In addition, the exhaust pipe 106 and the lower cup 105 may also be connected together by a CMT (cold metal transfer technology) welding process, the CMT welding process uses two sets of front and rear cooperating wire feeding mechanisms to make the feeding process of the welding wire be intermittent wire feeding, the rear wire feeding mechanism feeds the welding wire forward at a constant wire feeding speed, the front wire feeding mechanism controls the pulse type wire feeding at a frequency of Hz according to an instruction of the control system, the digital welding control system can automatically reduce the welding current according to the start time of arc generation until the arc is extinguished, and adjust the middle pulse type wire feeding, after the molten droplet drops from the welding wire, the digital control system increases the welding current again, further sends the welding wire forward, and then regenerates the welding arc to start a new round of welding process. This alternating "cold-hot" greatly reduces the generation of welding heat and reduces the conduction of welding heat in the welded parts. The CMT welding process belongs to the prior art and is not described herein.

It will be appreciated that the suction pipe 107 and the upper cup 103 may also be welded using the welding method described above.

Referring to fig. 2 to 7, a compressor assembly according to an embodiment of the present invention includes a compressor housing 101, an accumulator 102, and a weight structure, which may be connected to the compressor housing 101 or the accumulator 102, and which may be connected to an upper portion, a middle portion, or a lower portion of the compressor housing 101, and similarly, which may be connected to an upper portion, a middle portion, or a lower portion of the accumulator 102.

It should be noted that in other embodiments, a counterweight structure may be installed on both the compressor housing 101 and the accumulator 102.

Referring to fig. 2 to 7, it will be appreciated that the counterweight structure includes a cantilever member 201 and a counterweight member 202, the cantilever member 201 serving as a connection for connecting the counterweight member 202 to the compressor housing 101 or the reservoir 102. The counterweight structure is made into an independent structure, so that modular vibration reduction can be realized, namely the counterweight structure can be placed on any rotating machinery to realize the vibration reduction effect, and the counterweight structure has the advantages of convenience in installation and high reliability.

Referring to fig. 8, it can be understood that the abscissa represents frequency (unit: Hz), the ordinate represents noise value (unit: dB), the filled bars in fig. 8 represent values obtained by testing the compressor assembly without the counterweight structure in fig. 1, and the unfilled bars represent values obtained by testing the compressor assembly with the counterweight structure in fig. 4.

It can be seen that by adopting the compressor component of the embodiment of the utility model, noise values can be effectively reduced under a plurality of frequencies, particularly when the frequency reaches 4000Hz, the noise value obtained by testing the compressor component without the counterweight structure reaches 69dB, while the noise value obtained by testing the compressor component of the embodiment of the utility model is only 63.6dB, and the noise reduction effect is obvious.

It can be understood that the cantilever member 201 can also increase the distance from the weight member 202 to the center of the rotating structure, thereby improving the damping effect. Research shows that when the counterweight structure is far away from the center of the rotating structure, the vibration reduction effect is better, because under the condition that the weight of the counterweight structure is not changed, the farther the counterweight structure is from the center of the rotating structure, the larger the moment of inertia is.

The moment of Inertia (moment of Inertia) is a measure of the Inertia (the characteristic of a rotating object keeping its uniform circular motion or being stationary) of a rigid body when the rigid body rotates around a shaft. For a particle, the moment of inertia, I, mr2, where m is its mass and r is the perpendicular distance of the particle from the axis of rotation.

The role of moment of inertia in rotational dynamics is equivalent to the mass in linear dynamics, and can be formally understood as the inertia of an object to rotational motion, which is used to establish the relationship between several quantities, such as angular momentum, angular velocity, moment and angular acceleration.

The moment of inertia is determined only by the shape, mass distribution and position of the rotating shaft of the rigid body, and is independent of the rotating state (such as the magnitude of angular velocity) of the rigid body around the shaft. Therefore, when the shape and mass distribution of the rigid body are not changed, different moments of inertia can be obtained by changing the position of the rotation axis.

Therefore, the cantilever member 201 can increase the distance from the weight member 202 to the center of the rotating structure, increase the moment of inertia, and play a role in improving the vibration damping effect.

Referring to fig. 9, it will be understood that the abscissa indicates the different schemes, and the ordinate indicates the vibration value (unit: m/s2), the filled bars in fig. 9 indicate the vibration value detected in the middle of the shell of the compressor shell 101, and the unfilled bars indicate the vibration value detected in the middle of the cup of the reservoir 102. The plan of the structure without counterweight is shown in the abscissa, in which the plan shown in fig. 1 is adopted; the solution with the length of the cantilever member 201 is shown in order to adopt the position of the counterweight structure arranged in fig. 4.

Referring to fig. 9, it can be understood that, when no weight structure is provided, the value detected at the middle of the shell of the compressor shell 101 is 15.1m/s²The value detected in the middle of the cup of the reservoir 102 was 13.3m/s²(ii) a When the counterweight structure is arranged and the length of the cantilever part 201 is 20mm, the value detected in the middle of the shell of the compressor shell 101 is 14.2m/s²The value detected in the middle of the cup of the reservoir 102 was 12.5m/s²(ii) a When the counterweight structure is arranged and the length of the cantilever part 201 is 50mm, the value detected in the middle of the shell of the compressor shell 101 is 12.4m/s²The value detected in the middle of the cup of the reservoir 102 was 10.6m/s²(ii) a When the counterweight structure is arranged and the length of the cantilever part 201 is 100mm, the value detected in the middle of the shell of the compressor shell 101 is 10.7m/s²The value detected in the middle of the cup of the reservoir 102 was 9.8m/s²。

Therefore, it can be seen that as the length of the cantilever member 201 increases, the distance from the counterweight member 202 to the center of the rotating structure increases, and the moment of inertia increases, so that the effect of improving vibration damping is more obvious.

In addition, the natural frequency of the counterweight structure can be adjusted, and the vibration under different frequencies can be restrained. The weight 202 corresponds to a mass, the cantilever 201 corresponds to a spring, and a specific system natural frequency can be formed between the weight 202 and the cantilever 201. The length or thickness or width of the cantilever 201 affects the stiffness of the spring, thereby causing the fixed frequency of the system to vary.

It can be understood that the cantilever type counterweight installation mode can play a role of a dynamic vibration absorber while increasing the rotational inertia of the rotary machine, and plays a good role in inhibiting local vibration noise at the joint. The dynamic vibration absorber is a device which absorbs vibration energy of an object by using a resonance system to reduce the vibration of the object. The principle is that a mass spring resonance system is added on a vibrating object, and the reaction force generated by the additional system during resonance can reduce the vibration of the vibrating object.

Referring to fig. 2 to 7, it can be understood that the suspension 201 includes a first connection portion 203 and a second connection portion 204, the first connection portion 203 is used for connecting the compressor housing 101 or the liquid reservoir 102, the first connection portion 203 is vertically disposed, the second connection portion 204 is horizontally disposed, that is, the first connection portion 203 is perpendicular to the second connection portion 204, and the width of the first connection portion 203 is greater than the width of the second connection portion 204.

By providing the first connection portion 203, the contact area of the cantilever member 201 with the compressor housing 101 or the reservoir 102 can be increased, thereby increasing the stability of the connection. Moreover, since the second connecting portion 204 is horizontally disposed and connected to the weight 202, the first connecting portion 203, which is vertically disposed, may be conveniently connected to the sidewall of the compressor housing 101 or the sidewall of the accumulator 102, thereby improving the convenience of assembly. It is understood that the cantilever member 201 may be welded or connected to the compressor housing 101 or the accumulator 102 by a fastener such as a screw.

Referring to fig. 2 to 7, it can be understood that the weight 202 includes a container 205 and a weight material 206, the container 205 is provided with a cavity (not shown), the container 205 is further provided with an opening (not shown) matched with the cavity, and the weight material 206 is filled in the cavity through the opening.

The moment of inertia of the compressor assembly is changed by filling the weight material 206 so that the weight structure is more convenient to install, and the weight of the weight material 206 is also convenient to adjust to adapt to different working conditions or equipment.

The interior of the container 205 can be filled with a low cost solid structure, and since the solid material has a higher density than the liquid material, the damping effect is better for the same volume. In addition, the small-particle solid materials can be placed in the cavity, when the counterweight structure and the vibrating object move together, the small-particle solid structures in the cavity collide with each other to dissipate vibration energy, and therefore a better vibration reduction effect is achieved.

It is understood that the weight material 206 may be a solid such as vibration dampening particles, vibration dampening powder, or vibration dampening liquid. For example, the weight material 206 may be rubber particles, silica gel particles, resin particles, perlite particles, vermiculite particles, rubber powder, silica gel powder, resin powder, perlite powder, vermiculite powder, or the like, and has low cost and good vibration damping effect.

It is understood that the weight material 206 may be selected from cement, which is a powdered hydraulic inorganic cementitious material. Water is added and stirred to form slurry which can be hardened in air or water and can firmly bond sand, stone and other materials together. Meanwhile, the cement is also a filler with low price and high density, and can meet the use requirements in various aspects.

It can be understood that the weight material 206 can also be a liquid such as water or oil, which has low cost and good damping effect, and the weight material 206 can be selected more flexibly.

The cavity has an open structure to facilitate filling of the weight material 206 without obstructions above, making installation more convenient. Meanwhile, after the filling of the weight material 206 is completed, a cover body can be covered at the opening to seal the cavity.

It will be appreciated that the counterweight structure has a weight m1 and the compressor assembly has a weight m, satisfying: m1/m is more than or equal to 4 percent, namely the weight of the counterweight structure accounts for more than 4 percent of the weight of the whole compressor assembly. A large number of experiments show that when m1/m is less than 4%, the vibration reduction effect is not improved sufficiently, and when m1/m is more than or equal to 4%, the vibration reduction effect can be effectively improved, and the reliability is high.

As will be appreciated with reference to fig. 5 to 7, since the accumulator 102 is connected to one side of the compressor housing 101, the axis of revolution 501 of the compressor assembly is not the axis of the compressor housing 101, but is inclined at an angle towards the accumulator 102. As shown in fig. 5 in particular, the accumulator 102 is disposed on the right side of the compressor housing 101, and the upper end of the rotation axis 501 is inclined toward the accumulator 102.

Referring to fig. 5, it can be understood that the cantilever member 201 is connected to the lower portion of the compressor housing 101, the weight member 202 is located on one side of the compressor housing 101 close to the accumulator 102, and the weight member 202 is located below the accumulator 102. As can be seen from fig. 5, the weight 202 is disposed away from the rotation axis 501, so that the distance from the weight 202 to the rotation axis 501 can be increased, thereby increasing the moment of inertia and improving the vibration damping effect.

Referring to fig. 6, it will be appreciated that the cantilever member 201 is attached to the bottom of the reservoir 102 and the weight member 202 is located below the reservoir 102. As can be seen from fig. 6, the weight 202 is disposed away from the rotation axis 501, so that the distance from the weight 202 to the rotation axis 501 can be increased, thereby increasing the moment of inertia and improving the vibration damping effect.

Referring to fig. 7, it can be understood that the cantilever member 201 is connected to the upper portion of the compressor housing 101, and the weight member 202 is located on the side of the compressor housing 101 away from the accumulator 102. As can be seen from fig. 7, the weight 202 is disposed away from the rotation axis 501, so that the distance from the weight 202 to the rotation axis 501 can be increased, thereby increasing the moment of inertia and improving the vibration damping effect.

Referring to fig. 10, it will be understood that the abscissa indicates the different schemes, and the ordinate indicates the vibration value (unit: m/s2), the filled bars in fig. 10 indicate the vibration value detected in the middle of the shell of the compressor shell 101, and the unfilled bars indicate the vibration value detected in the middle of the cup of the accumulator 102. In the abscissa, the solution one represents the solution without the counterweight structure, and the solution shown in fig. 1 is adopted; the second scheme shows that the counterweight structure is placed at the lower part of the compressor shell 101 and is located opposite to the liquid reservoir 102, that is, the counterweight structure position set in fig. 4 is adopted. Scheme three shows that the counterweight structure is placed in the middle of the reservoir 102, i.e., in the position where the counterweight structure set in fig. 3 is used. Scheme four shows the placement of the counterweight structure in the lower portion of the reservoir 102, i.e., in the position where the counterweight structure is used as set forth in fig. 6.

Referring to fig. 10, it can be understood that, in the first embodiment, the value detected in the middle of the shell of the compressor shell 101 is 15.1m/s²The value detected in the middle of the cup of the reservoir 102 was 13.3m/s²(ii) a In the second embodiment, the value detected in the middle of the shell of the compressor shell 101 is 14.2m/s²The value detected in the middle of the cup of the reservoir 102 was 12.5m/s²(ii) a In the third embodiment, the value detected in the middle of the shell of the compressor shell 101 is 13.4m/s²The value detected in the middle of the cup of the reservoir 102 was 11.4m/s²(ii) a In the fourth case, the value detected in the middle of the shell of the compressor shell 101 was 12.3m/s²The value detected in the middle of the cup of the reservoir 102 was 10.5m/s²。

Referring to fig. 10, it can be understood that, in comparison between the first and second solutions, the measured values of the middle of the shell of the compressor shell 101 and the middle of the cup of the accumulator 102 are smaller in the second solution, that is, the counterweight structure is placed at the lower part of the compressor shell 101 and opposite to the accumulator 102, and the damping effect is better than that of the solution without the counterweight structure.

In the comparison of the second, third and fourth solutions, the measured values of the middle portion of the shell of the compressor housing 101 and the middle portion of the cup of the reservoir 102 are smaller than those of the second solution and the fourth solution is smaller than those of the third solution, i.e., it is proved that the vibration damping effect can be improved because the weight member 202 of the third solution is farther away from the rotation axis 501 than the weight member 202 of the second solution, and the weight member 202 of the fourth solution is farther away from the rotation axis 501 than the weight member 202 of the third solution, so that the distance from the weight member 202 to the rotation axis 501 is increased.

It can be understood that, in addition to the counterweight 202 of the fourth embodiment being further away from the rotation axis 501, the damping effect can be improved, and the counterweight 202 is further disposed below the accumulator 102, so that the original empty space of the compressor assembly is utilized, and the position does not increase the outer diameter of the compressor assembly, does not occupy the extra space of the refrigeration equipment, and has higher feasibility.

The refrigeration equipment comprises the compressor assembly.

The refrigeration equipment provided by the embodiment of the utility model has the advantages of convenience in installation and high reliability by adopting the compressor assembly provided by the embodiment of the utility model. In addition, the cantilever type counterweight installation mode can play a role of a dynamic vibration absorber while increasing the rotational inertia of the rotary machine, and plays a good role in inhibiting local vibration noise at the joint.

The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge of those skilled in the art without departing from the gist of the present invention.

Claims

1. A compressor assembly, comprising:

a compressor including a compressor housing;

a reservoir connected to the compressor housing;

a counterweight structure including a cantilever member and a counterweight member, the counterweight member coupled to at least one of the compressor housing and the reservoir via the cantilever member.

2. The compressor assembly of claim 1, wherein the counterweight is located below the accumulator.

3. The compressor assembly of claim 2, wherein the cantilever member is coupled to a lower portion of the compressor housing.

4. The compressor assembly of claim 2, wherein the cantilever member is coupled to a bottom of the accumulator.

5. The compressor assembly of claim 1, wherein the cantilever member is coupled to an upper portion of the compressor housing, the counterweight member being located on a side of the compressor housing away from the accumulator.

6. The compressor assembly of any one of claims 1-5, wherein the weight includes a reservoir and a weight material, the reservoir defining a cavity, the weight material filling the cavity.

7. The compressor assembly of claim 6, wherein the weight material is a particulate solid material.

8. The compressor assembly of claim 6, wherein the weight material comprises cement.

9. The compressor assembly of claim 1, wherein the counterweight structure has a weight of m1, and the compressor assembly has a weight of m, such that: m1/m is more than or equal to 4 percent.

10. Refrigeration appliance, characterized in that it comprises a compressor assembly according to any one of claims 1 to 9.