CN114017341A

CN114017341A - Compressor assembly and refrigeration equipment

Info

Publication number: CN114017341A
Application number: CN202111313380.0A
Authority: CN
Inventors: 叶容君; 张肃; 陈涛
Original assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Current assignee: Guangdong Meizhi Compressor Co Ltd; Guangdong Meizhi Precision Manufacturing Co Ltd
Priority date: 2021-11-08
Filing date: 2021-11-08
Publication date: 2022-02-08
Anticipated expiration: 2041-11-08
Also published as: CN114017341B

Abstract

The invention discloses a compressor assembly and refrigeration equipment, wherein the compressor assembly comprises a compressor shell and a vibration reduction element, the vibration reduction element is arranged in the compressor shell and comprises a balancing weight and a base plate arranged around the balancing weight in the circumferential direction, the base plate is fixedly connected with the compressor shell, the base plate is provided with a through groove, and the through groove extends in the circumferential direction of the balancing weight and penetrates in the thickness direction of the base plate. According to the invention, the through groove extending along the circumferential direction of the balancing weight is formed in the substrate, and the through groove penetrates along the thickness direction of the substrate, so that the rigidity of the substrate is reduced and the substrate has elasticity, the balancing weight can move in the elastic deformation range of the substrate relative to the substrate, and when vibration waves pass through the vibration damping element, the vibration waves are counteracted by the movement of the balancing weight relative to the substrate, so that the vibration of the compressor assembly is reduced, the vibration damping effect is good, and meanwhile, the running noise of the compressor assembly can be reduced.

Description

Compressor assembly and refrigeration equipment

Technical Field

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

Background

The main excitation force of the rotary compressor is influenced by motor torque and gas resistance torque, wherein the compressor generates vibration and noise due to magnetic tension caused by gas flow impact, discharge pressure pulsation and height difference between a stator and a rotor. In the related art, the vibration is reduced by increasing the weight of the compressor, but the vibration reduction effect is poor and the noise is large.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the compressor assembly provided by the invention can effectively reduce the vibration of the compressor assembly through the vibration reduction element, reduce the operation noise of the compressor assembly and has a good vibration reduction effect.

The invention also provides refrigeration equipment with the compressor assembly.

A compressor assembly according to an embodiment of the first aspect of the invention comprises a compressor housing; the vibration reduction element is installed in the compressor shell, the vibration reduction element comprises a balancing weight and a substrate which is arranged in the circumferential direction of the balancing weight, the substrate is fixedly connected with the compressor shell, a through groove is formed in the substrate, and the through groove is arranged along the circumferential direction of the balancing weight in an extending mode and penetrates through the thickness direction of the substrate.

The compressor assembly according to the embodiment of the first aspect of the invention has at least the following advantages: through offering the logical groove that the circumference extension of following the balancing weight set up at the base plate, and lead to the groove and run through along the thickness direction of base plate, make the rigidity of base plate reduce and have elasticity, the balancing weight can move at the elastic deformation volume within range of base plate relative to the base plate, when the vibration wave that produces by compressor unit spare passes through the damping component, move through the balancing weight relative to the base plate and offset the vibration wave, the amplitude when making vibration wave transmit to compressor housing reduces, thereby reduce compressor unit spare's vibration, the damping is effectual, can reduce compressor unit spare's running noise simultaneously.

According to some embodiments of the invention, the through-slots are helical in structure.

According to some embodiments of the invention, the through slot has an inside contour, the inside contour being a continuous spiral.

According to some embodiments of the invention, the spiral is an archimedean spiral and the number of turns N of the spiral satisfies: n is more than or equal to 0.5 and less than or equal to 5.

According to some embodiments of the invention, the through slots have equal width in the spiral direction of the spiral line, and the width is W, and satisfies: w is more than 0 and less than or equal to 3 mm.

According to some embodiments of the invention, the through groove has an inner molded line, the inner molded line is a plurality of sequentially connected line segments, and the plurality of sequentially connected line segments are arranged around the weight block.

According to some embodiments of the invention, the base plate is perpendicular to an axial direction of the compressor housing.

According to some embodiments of the invention, the base plate is parallel to an axial direction of the compressor housing.

According to some embodiments of the invention, the outer edge of the base plate is provided with a protruding plate extending in the thickness direction of the base plate, and the protruding plate is attached to the inner wall of the compressor housing.

According to some embodiments of the invention, the through groove is arc-shaped and provided with a plurality of through grooves, the through groove has an inner molded line which is a major arc, and the plurality of through grooves are arranged at intervals along a direction departing from the counterweight block.

A refrigeration device according to an embodiment of a second aspect of the present invention comprises the compressor assembly of the embodiment of the first aspect described above.

The refrigeration equipment according to the embodiment of the second aspect of the invention has at least the following advantages: refrigeration plant is owing to install the compressor unit of above-mentioned first aspect embodiment, and when the vibration wave that produces by compressor unit passes through the damping component, the relative base plate of balancing weight removes and offsets the vibration wave, and the amplitude when making the vibration wave transmit to compressor housing reduces to reduce compressor unit's vibration, and then reduce refrigeration plant's vibration, the damping is effectual, can reduce compressor unit's operating noise simultaneously, and then reduce refrigeration plant's operating noise.

Additional aspects and advantages of the invention 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 invention.

Drawings

FIG. 1 is a schematic view of a compressor assembly according to an embodiment of the present invention;

FIG. 2 is a front cross-sectional view of a compressor assembly in accordance with an embodiment of the present invention;

FIG. 3 is a cross-sectional view of the damping element shown in FIG. 2;

FIG. 4 is a top view of a damping element according to a first embodiment of the invention;

FIG. 5 is a top view of a damping element according to a second embodiment of the present invention;

FIG. 6 is a top view of a damping element according to a third embodiment of the present invention;

fig. 7 is a top view of a damping element according to a fourth embodiment of the invention.

Reference numerals:

a compressor housing 100; a main housing 110; an upper case 120; a motor 130; a compression mechanism 140;

a damping element 200; a weight 210; a substrate 220; a through groove 221; inner profile 2211; outer profile 2212; a flange 2213;

a compressor body 400;

a reservoir 500;

connecting tube 600.

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 defined, terms such as set, mounted, connected, assembled, matched and the like should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the terms in the present invention by combining the specific contents of the technical solutions.

The rotary compressor is widely applied to air conditioners, especially small household air conditioners, because of the advantages of high compression efficiency, few parts, small volume, light weight, low power consumption and the like. It can be known in the related art that, during the operation of the rotary compressor, the main excitation force of the rotary compressor is affected by the torque of the motor and the gas resistance torque, wherein the rotary compressor is affected by the airflow impact, the exhaust pressure pulsation, and the axial magnetic pulling force caused by the height difference between the stator and the rotor, and generates axial vibration, and the vibration in this direction is also the main source of the vibration of the rotary compressor during the operation, and generates a lot of noise, which seriously affects the operation of the rotary compressor and brings bad experience to users. Some rotary compressors reduce vibration by increasing weight, but have poor vibration reduction effect and still have high noise, so that the rotary compressors are inconvenient to use.

To solve the above problem, referring to fig. 1, a first embodiment of the present invention provides a compressor assembly, which may be a vertical rotary compressor.

A compressor assembly according to an embodiment of the present invention will be described with reference to fig. 1 to 7, and in the following description, the compressor assembly will be described as an example of a vertical type rotary compressor. Of course, it will be understood by those skilled in the art that the compressor assembly may also be other types of rotary compressors, and is not limited to a vertical rotary compressor.

Referring to fig. 1 and 2, a compressor assembly according to an embodiment of the present invention includes a compressor body 400, an accumulator 500 and a connecting pipe 600, wherein the accumulator 500 is used for separating a gaseous refrigerant and a liquid refrigerant, the connecting pipe 600 may be a copper pipe, and the compressor body 400 is communicated with the accumulator 500 through the connecting pipe 600, so that the compressor body 400 can normally suck the gaseous refrigerant for compression and transportation. Specifically, the compressor body 400 includes a compressor housing 100 and a vibration reduction member 200, the compressor housing 100 includes a main housing 110 and an upper housing 120, and the upper housing 120 is mounted on the top of the main housing 110 by resistance welding. Of course, the compressor housing 100 may further include a lower housing (not shown), that is, the compressor housing 100 is composed of three parts, in which case the lower housing is welded to the lower end of the main housing 110. Generally speaking, the motor 130 and the compression mechanism 140 are installed in the inner cavity of the main housing 110, the motor 130 and the compression mechanism 140 are both located in the lower inner cavity of the main housing 110, the compression mechanism 140 is located below the motor 130, and the output shaft of the motor 130 is connected with the compression mechanism 140 to suck the gaseous refrigerant for compression and transportation. The compressing mechanism 140 is well known to those skilled in the art and will not be described in detail herein.

Referring to fig. 2, it can be appreciated that the vibration reduction element 200 is installed in the compressor housing 100, and since the motor 130 and the compression mechanism 140 are both located in the lower inner cavity of the main housing 110, the vibration reduction element 200 is installed in the upper inner cavity of the main housing 110 for easy installation, i.e., the vibration reduction element 200 is located between the motor 130 and the upper housing 120. When the vibration damping element 200 is mounted, the vibration damping element is fixed in the main housing 110, and then the upper housing 120 and the main housing 110 are welded.

Referring to fig. 2, 3 and 4, it can be understood that the damping element 200 includes a weight 210 and a base plate 220, wherein the cross section of the weight 210 may be circular, elliptical or polygonal, and for the convenience of processing, the cross section of the weight 210 is circular, i.e. the weight 210 has a cylindrical structure. The base plate 220 is disposed around the circumferential direction of the weight 210, that is, the base plate 220 is perpendicular to the axial direction of the weight 210, the outer shape of the base plate 220 may be polygonal or circular, and the vibration damping element 200 is fixed to the main housing 110 by connecting the base plate 220 with the inner wall of the main housing 110. The substrate 220 may be located at any position of the weight 210 along the axial direction of the weight 210, for example, the substrate 220 is connected to the end of the weight 210, or the substrate 220 is connected to the middle of the weight 210 along the axial direction of the weight 210, and the relative position of the substrate 220 and the weight 210 is not specifically limited herein.

Referring to fig. 3 and 4, it can be understood that the substrate 220 is provided with a through groove 221, the through groove 221 penetrates in a thickness direction of the substrate 220, that is, the through grooves 221 penetrate through the base plate 220 in the axial direction of the weight block 210, and at the same time, the through grooves 221 extend in the circumferential direction of the weight block 210, and the number of the through grooves 221 may be one or more, so that the rigidity of the base plate 220 is reduced, at the position where the substrate 220 is connected with the weight 210, the substrate 220 has a certain elasticity, that is, the substrate 220 has a certain amount of elastic deformation, which may be along the axial direction of the weight 210, or along the radial direction of the weight 210, wherein the amount of elastic deformation of the substrate 220 along the axial direction of the weight block 210 is greater than the amount of elastic deformation along the radial direction of the weight block 210, i.e., the rigidity of the base plate 220 in the axial direction of the weight block 210 is lower than the rigidity in the radial direction of the weight block 210. Thereby enabling the weight 210 to move within a range of elastic deformation relative to the substrate 220.

It will be appreciated that the vibrations have a frequency and the rigidity of the substrate 220 determines the frequency at which the corresponding vibrations can be processed efficiently. I.e., the greater the rigidity of the substrate 220, the higher the vibration frequency of the corresponding process, and vice versa.

In the operation process of the compressor assembly, the compressor assembly is impacted by airflow, the exhaust pressure pulsates, and the axial magnetic pulling force caused by the height difference between the stator and the rotor of the motor 130 generates vibration along the axial direction of the compressor body 400 to the compressor body 400, the vibration is expressed as vibration wave transmitted along the axial direction of the compressor body 400, because the rigidity of the base plate 220 is reduced and has certain elasticity, the counterweight 210 can move in the elastic deformation range of the base plate 220 relative to the base plate 220, when the vibration wave passes through the vibration damping element 200, the vibration wave is offset by the deformation of the base plate 220 and the reciprocating movement of the counterweight 210 relative to the base plate 220 in the transmission direction of the vibration wave, so that the amplitude of the vibration wave transmitted to the compressor shell 100 is reduced, thereby reducing the vibration of the compressor assembly, having good vibration damping effect, and simultaneously reducing the operation noise of the compressor assembly.

Referring to fig. 4, it can be understood that the through groove 221 is provided in a spiral structure, that is, a projection of the through groove 221 along an axial direction of the weight block 210 is spiral, the through groove 221 includes an inner molded line 2211 and an outer molded line 2212, the inner molded line 2211 and the outer molded line 2212 are arranged at intervals along a radial direction of the weight block 210, and a distance between the inner molded line 2211 and the outer molded line 2212 is a groove width W of the through groove 221. Note that "inside" is defined as a side close to the weight 210, and "outside" is defined as a side far from the weight 210. For example, the inner-side line 2211 and the outer-side line 2212 are both helical continuous curves, i.e. helices, such as archimedes helices, and the through groove 221 of such a structure only needs one feed during machining, and a machining tool (e.g. a milling cutter) is continuously moved along the helical direction of the helices, so as to facilitate machining. Meanwhile, the rigidity of the substrate 220 having the through groove 221 of such a structure is low.

Referring to fig. 5, it can be understood that the inside molded line 2211 of the through groove 221 may also be a line segment formed by multiple segments connected in sequence, the multiple segments connected in sequence are arranged around the weight block 210 and are spiral, such as a square spiral line or other polygonal spiral lines, the through groove 221 with such a structure can also reduce the rigidity of the substrate 220, and the substrate 220 has a certain elastic deformation amount, and only one feeding is needed when the through groove 221 is processed, and a processing tool (such as a milling cutter) is continuously moved along the spiral direction of the spiral line, so as to facilitate processing.

Referring to fig. 6, it can be understood that a plurality of through grooves 221 may be provided, each through groove 221 is disposed around the weight block 210, the plurality of through grooves 221 are sequentially spaced around the weight block 210 in a spiral manner, the inner molded lines 2211 of the plurality of through grooves 221 may coincide with a spiral continuous curve (i.e., a spiral line), such as an archimedean spiral, the inner molded lines 2211 of the plurality of through grooves 221 may also coincide with a plurality of sequentially connected segments, such as a square spiral line or other polygonal spiral lines, which are disposed in a spiral manner, and the plurality of through grooves 221 in this arrangement may also reduce the rigidity of the substrate 220 and enable the substrate 220 to have a certain amount of elastic deformation. The substrate 220 provided with the plurality of through grooves 221 of this arrangement is relatively rigid with respect to the through groove 221 structure provided in the above two embodiments.

It is understood that the above spiral is an archimedean spiral, and the number of turns of the spiral is defined as N, which satisfies: n is 0.5 ≦ N ≦ 5, that is, the number of turns of the archimedean spiral is at least 0.5 turns and at most 5 turns, for example, N ═ 2, N ═ 3, N ═ 4, and the like, so as to ensure that the substrate 220 has suitable rigidity, and the counterweight 210 can move relative to the substrate 220 to cancel out the vibration wave, achieve vibration reduction, and reduce noise.

Referring to fig. 4, it can be understood that the archimedean spiral is also an equidistant spiral, and therefore, along the spiral direction of the spiral, the width of the through groove 221 is equal, defining the width W of the through groove 221, satisfying: 0 < W.ltoreq.3 mm, for example, W.ltoreq.1, W.ltoreq.2, and the like. When the through groove 221 is machined, only one specification of machining tool (such as a milling cutter) is needed, the outer diameter of the machining tool is matched with the width of the through groove 221, the machining tool is fed once along the spiral direction of the spiral line, and the through groove 221 is simple in structure and convenient to machine.

It can be understood that, defining the intersection point of the center line of the counterweight 210 and the plane of the base plate 220 as the center O, the x-axis pointing to the right side, the y-axis pointing to the rear side, and establishing a rectangular plane coordinate system with the center O, x and the y-axis, the archimedean spiral satisfies the equation: x is a, t cos (t 360), y is a, t sin (t 360), where t is a variable and the value of a defines the distance between two adjacent curves of the archimedean spiral within a certain range.

Referring to fig. 3, it can be understood that, defining the smallest outer diameter of the weight 210 as D1 and the smallest outer diameter of the base plate 220 as D2, since the weight 210 is of a cylindrical structure, i.e. the diameter of the cross section of the weight 210 is D1, when the base plate 220 is a circular plate, the diameter of the circular plate is D2, and when the base plate 220 is a polygonal plate, such as a rectangular plate, the width of the rectangular plate is D2, the following requirements are satisfied: t is more than or equal to 0 and less than or equal to (D2-D1)/(2W), and D1 is more than or equal to (2 aT) and less than or equal to (D2-W). That is, the range of the archimedean spiral is limited on the substrate 220, that is, the spiral through groove 221 is ensured to be arranged on the substrate 220, so that the rigidity of the substrate 220 is reduced.

It is understood that, for example: the values a 9, W2 mm, D1 32mm, D2 76mm, t 0 ≦ t (D2-D1)/(2 × W) may be 0 ≦ t 11, D1 ≦ (2 × a t ≦ t) (D2-W), t 1.77 ≦ t ≦ 4.1, i.e., t 1.77 ≦ t ≦ 4.1, that is, the number of turns N is 4.1-1.77 ≦ 2.33, so that the number of turns N of the archimedean spiral is 2.33 turns at this time. Since the vibration of the compressor body 400 is mainly in the axial direction of the compressor housing 100, and the vibration frequency is generally in a low frequency band of about 60Hz to 120 Hz. According to the relation table between the number of turns N and the corresponding vibration reduction frequency band, when N is 2.33, the vibration reduction element 200 can just process the low-frequency-band vibration between 60Hz and 120Hz, the vibration reduction effect is good, and the noise is low.

Relation table of number of turns N and corresponding vibration reduction frequency band

Of course, the spiral line may be in other forms, such as an equiangular spiral, a hyperbolic spiral, etc., and the archimedean spiral has a simple structure and the corresponding through groove 221 is easy to machine compared with other forms of spiral lines.

Referring to fig. 2, it can be understood that the plane of the base plate 220 is perpendicular to the axial direction of the compressor housing 100, the outer shape of the base plate 220 is set to be the same as the cross-sectional shape of the compressor housing 100, and generally, the outer shape of the base plate 220 is circular, that is, the base plate 220 is a circular plate, so that the outer edge of the base plate 220 can be connected with the inner wall of the compressor housing 100, and the mounting stability of the vibration damping element 200 is ensured. Since the vibration of the compressor body 400 is mainly in the axial direction of the compressor housing 100, and the vibration frequency is generally in a low frequency band of about 60Hz to 120 Hz. When base plate 220 is perpendicular with compressor housing 100's axial, the axial rigidity of base plate 220 along compressor housing 100 is minimum, when the vibration wave passes through damping element 200, the relative base plate 220 of balancing weight 210 is bigger along compressor housing 100's axial displacement's scope, can offset the vibration wave of low-frequency channel better, the amplitude when making vibration wave transmit to compressor housing 100 is littleer, thereby reduce compressor assembly's vibration, the damping effect is better, can reduce compressor assembly's running noise better simultaneously.

Of course, it is understood that the base plate 220 may also be parallel to the axial direction of the compressor housing 100, in which case the base plate 220 may have a rectangular shape, and both side edges of the base plate 220 are parallel to the central axis of the compressor housing 100 and connected to the inner wall of the compressor housing 100, so that the vibration damping element 200 is more stably installed. The base plate 220 can also achieve the vibration damping effect in a state where it is parallel to the axial direction of the compressor housing 100, but in this case, the rigidity of the base plate 220 in the axial direction of the compressor housing 100 is greater than the rigidity of the base plate 220 perpendicular to the axial direction of the compressor housing 100, and the vibration damping effect on the low-frequency vibration is inferior to the vibration damping effect of the base plate 220 perpendicular to the axial direction of the compressor housing 100.

It can be understood that, the vibration damping element 200 is installed by fixedly connecting the outer edge of the base plate 220 with the inner wall of the compressor housing 100, that is, the base plate 220 is connected with the inner wall of the main housing 110, and the base plate 220 and the inner wall of the main housing 110 may be in welded connection or interference fit, etc., wherein when the base plate 220 is welded with the inner wall of the main housing 110, the vibration damping element 200 is installed more stably and the connection is firmer.

Referring to fig. 2 and 3, it can be understood that the outer edge of the base plate 220 is provided with a projection 2213, the projection 2213 extends in the thickness direction of the base plate 220, when the plane of the base plate 220 is perpendicular to the axial direction of the compressor housing 100, the base plate 220 is a circular plate, and the projection 2213 is arranged around the circumference of the counterweight 210, i.e. the projection 2213 is an annular plate, for example, the projection 2213 may be provided on both the upper side and the lower side of the base plate 220, or the projection 2213 may be provided only on the upper side of the base plate 220, or the projection 2213 may be provided only on the lower side of the base plate 220. When the damping element 200 is mounted, the protruding plate 2213 is attached to the inner wall of the main housing 110, so that the contact area between the substrate 220 and the inner wall of the main housing 110 can be increased, the damping element 200 is prevented from being inclined, the mounting is convenient, and the mounting is more stable and reliable.

When the plane of the substrate 220 is installed in parallel with the axial direction of the compressor housing 100, the substrate 220 may have a rectangular shape, the two ends of the substrate 220 are provided with the protruding plates 2213, and the protruding plates 2213 are arc-shaped and attached to the inner wall of the main housing 110, so that the contact area between the substrate 220 and the inner wall of the main housing 110 can be increased, the damping element 200 is prevented from being inclined, the installation is convenient, and the installation is more stable and reliable.

Referring to fig. 7, it can be understood that the through groove 221 has a circular arc shape and is provided with a plurality of through grooves, for example, the substrate 220 is provided with three through grooves 221, and the groove widths of the three through grooves 221 may be equal to facilitate processing. Inside molded line 2211 and outside molded line 2212 of three through grooves 221 are both arc segments, and the centers of reference circles where inside molded line 2211 and outside molded line 2212 are may be coincident. It is easily understood that, in the same through groove 221, the radius of the reference circle where the outer-side molded line 2212 is located is larger than that of the reference circle where the inner-side molded line 2211 is located, that is, R2 > R1, and the difference between R2 and R1 is the groove width W of the through groove 221, that is, W is R2-R1. In two adjacent through grooves 221, the radius of the reference circle on which the inner molded line 2211 of the through groove 221 far away from the weight block 210 is larger than the radius of the reference circle on which the outer molded line 2212 of the through groove 221 near the weight block 210 is located, that is, R3 > R2. That is, the three through grooves 221 are spaced apart in a direction away from the weight block 210 to reduce the rigidity of the substrate 220. Of course, it is understood that four, five or more through slots 221 may be provided.

Referring to fig. 7, it can be understood that, when the through groove 221 is arc-shaped, both the inner profile 2211 and the outer profile 2212 of the through groove 221 are arc segments, a central angle corresponding to the inner profile 2211 and the outer profile 2212 of the through groove 221 is defined as θ, in order to ensure that the substrate 220 has lower rigidity, θ satisfies 180 ° < θ < 360 °, that is, both the inner profile 2211 and the outer profile 2212 are major arcs, for example, θ is 340 °, that is, the through groove 221 is one segment of an annular groove, so that the rigidity of the substrate 220 can be effectively reduced and the substrate 220 has certain elasticity, the counterweight 210 can move in an elastic deformation range of the substrate 220 relative to the substrate 220, so as to cancel out vibration waves, reduce the vibration of the compressor assembly, have good vibration reduction effect, and reduce the operating noise of the compressor assembly. Of course, it is understood that θ may also be 330 °, 350 °, and so on.

The refrigeration equipment according to the second aspect of the present invention includes the compressor assembly of the first aspect of the present invention, wherein the refrigeration equipment includes, but is not limited to, an air conditioner, a refrigerator, and the like, so as to implement compression of a gaseous refrigerant by the compressor assembly.

Refrigeration plant is owing to install the compressor unit of the above-mentioned first aspect embodiment, when the axial vibration wave that produces by compressor unit passes through damping element 200, moves through balancing weight 210 relative base plate 220 and offsets the vibration wave, and the amplitude when making the vibration wave transmit to compressor housing 100 reduces to reduce compressor unit's vibration, and then reduce refrigeration plant's vibration, the damping is effectual, can reduce compressor unit's running noise simultaneously, and then reduce refrigeration plant's running noise.

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 housing;

the vibration reduction element is installed in the compressor shell, the vibration reduction element comprises a balancing weight and a substrate which is arranged in the circumferential direction of the balancing weight, the substrate is fixedly connected with the compressor shell, a through groove is formed in the substrate, and the through groove is arranged along the circumferential direction of the balancing weight in an extending mode and penetrates through the thickness direction of the substrate.

2. The compressor assembly of claim 1, wherein: the through groove is of a spiral structure.

3. The compressor assembly of claim 2, wherein: the through groove is provided with an inner side molded line which is a continuous spiral line.

4. The compressor assembly of claim 3, wherein: the helix is an Archimedes helix, and the number of turns N of the helix satisfies: n is more than or equal to 0.5 and less than or equal to 5.

5. The compressor assembly of claim 3 or 4, wherein: the width of the through groove along the spiral direction of the spiral line is equal, the width is W, and the requirements are met: w is more than 0 and less than or equal to 3 mm.

6. The compressor assembly of claim 2, wherein: the through groove is provided with an inner side molded line, the inner side molded line is a plurality of sections of line sections which are sequentially connected, and the plurality of sections of line sections which are sequentially connected are arranged around the balancing weight.

7. The compressor assembly of claim 1, wherein: the base plate is perpendicular to an axial direction of the compressor housing.

8. The compressor assembly of claim 1, wherein: the base plate is parallel to an axial direction of the compressor housing.

9. The compressor assembly of claim 7 or 8, wherein: the outer edge of the base plate is provided with a convex plate extending along the thickness direction of the base plate, and the convex plate is attached to the inner wall of the compressor shell.

10. The compressor assembly of claim 1, wherein: the through groove is circular-arc and is provided with a plurality ofly, it has for the inboard molded lines of major arc to lead to the groove, and is a plurality of it sets up along deviating from to lead to the groove the direction interval of balancing weight.

11. Refrigeration plant, its characterized in that: comprising a compressor assembly according to any one of claims 1 to 10.