CN113883764B

CN113883764B - Liquid storage device, compressor assembly and refrigeration equipment

Info

Publication number: CN113883764B
Application number: CN202111315349.0A
Authority: CN
Inventors: 陈涛; 张肃; 叶容君
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: 2023-03-10
Anticipated expiration: 2041-11-08
Also published as: CN113883764A

Abstract

The invention discloses a liquid storage device, a compressor assembly and refrigeration equipment, wherein the liquid storage device comprises a shell and a vibration reduction element, and the shell is provided with an exhaust pipe; the damping component is installed in the casing, and the damping component includes balancing weight and the base plate that sets up around the circumference of balancing weight, base plate and casing fixed connection, and the base plate is equipped with logical groove, leads to the groove and extends the setting and run through along the thickness direction of base plate along the circumference of balancing weight, and the balancing weight is equipped with the through-hole, and the diameter of through-hole is greater than the external diameter of blast pipe, and the through-hole is worn to locate by the blast pipe. 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 liquid accumulator is reduced, the noise is reduced, and the vibration damping effect is good.

Description

Liquid storage device, compressor assembly and refrigeration equipment

Technical Field

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

Background

The main excitation force of rotary compressor is equipped with the reservoir by the effect of motor torque, gaseous resistance moment, and one side of rotary compressor is equipped with the reservoir, and in compressor working process, the vibration that the compressor produced will transmit for the reservoir, causes the reservoir vibration and produces the noise, influences user's experience and feels. In the related art, vibration is reduced by increasing the weight of the reservoir, but the vibration reduction effect is limited.

Disclosure of Invention

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

The invention also provides a compressor assembly with the liquid storage device and refrigeration equipment with the compressor assembly.

A reservoir according to an embodiment of the first aspect of the invention comprises a housing having an exhaust tube; the damping component, install in the casing, the damping component includes the balancing weight and centers on the base plate that the circumference of balancing weight set up, the base plate with casing fixed connection, the base plate is equipped with logical groove, it follows to lead to the groove the circumference of balancing weight extends the setting and follows the thickness direction of base plate runs through, the balancing weight is equipped with the through-hole, the diameter of through-hole is greater than the external diameter of blast pipe, the blast pipe is worn to locate the through-hole.

The reservoir according to the embodiment of the first aspect of the invention has at least the following advantages: through set up the logical groove that extends the setting along the circumference of balancing weight at the base plate, and it runs through along the thickness direction of base plate to lead to the groove, 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 in the reservoir passes through damping element, move through the balancing weight relative to the base plate and offset the vibration wave, the amplitude when making vibration wave transmit to the casing reduces, thereby reduce the vibration of reservoir, and the noise reduction, the damping is effectual, and simultaneously, because the balancing weight is provided with the through-hole that the diameter is greater than the internal diameter of blast pipe, make the balancing weight remove the in-process and can avoid the blast pipe, avoid vibration to transmit again to the blast pipe, further improve damping effect.

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 width of the through grooves along the spiral direction of the spiral line is equal, and the width is W, and satisfies the following condition: w is more than 0 and less than or equal to 3mm.

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 housing.

According to some embodiments of the invention, the outer edge of the substrate is provided with a convex plate extending along the thickness direction of the substrate, and the convex plate is attached to the inner wall of the shell.

According to some embodiments of the invention, the outer diameter of the exhaust pipe is D3, and the inner diameter of the through hole is D4, which satisfy: D4-D3 is more than or equal to 0.2mm.

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 compressor assembly according to an embodiment of the second aspect of the present invention includes the accumulator of the embodiment of the first aspect.

The compressor assembly according to the embodiment of the second aspect of the invention has at least the following advantages: compressor unit is owing to install the reservoir of above-mentioned first aspect embodiment, when the vibration wave in the reservoir passes through the damping component, the relative base plate of balancing weight removes and offsets the vibration wave, the amplitude when making the vibration wave transmit to the casing reduces, thereby reduce the vibration of reservoir, and the noise reduction, the damping is effectual, and simultaneously, because the balancing weight is provided with the through-hole that the diameter is greater than the internal diameter of blast pipe, make the balancing weight remove the in-process and can avoid the blast pipe, avoid vibration retransmission to the blast pipe, further improve the damping effect, and then reduce compressor unit's vibration, and reduce compressor unit's running noise.

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

According to the refrigeration equipment of the third aspect of the invention, at least the following advantages are achieved: refrigeration plant is owing to install the compressor unit of the above-mentioned second aspect embodiment, when the vibration wave in the reservoir passes through the damping component, the relative base plate of balancing weight removes and offsets the vibration wave, the amplitude when making the vibration wave transmit to the casing reduces, thereby reduce the vibration of reservoir, and the noise reduction, the damping is effectual, and simultaneously, because the balancing weight is provided with the through-hole that the diameter is greater than the internal diameter of blast pipe, make the balancing weight remove the in-process and can avoid the blast pipe, avoid vibration retransmission to the blast pipe, further improve the damping effect, and then reduce compressor unit's vibration, reduce refrigeration plant's vibration, and reduce compressor unit and refrigeration plant's running 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 of 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 present invention;

FIG. 8 is a graph of frequency of vibration versus acceleration of vibration of a reservoir in accordance with an embodiment of the present invention.

Reference numerals:

a housing 100; a main case 110; an upper case 120; an exhaust pipe 130;

a damping element 200; a weight 210; a through hole 211; a substrate 220; a through groove 221; inner profile 2211; outer profile 2212; a flange 2213;

a compressor body 400; a motor 410; a compression mechanism 420;

a reservoir 500;

and a connection pipe 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. Known among the correlation technique, rotary compressor is at the operation in-process, and its main excitation receives the effect of motor torque, gas resistance moment, and rotary compressor installs the reservoir that is located week side usually, receives rotary compressor's rotor effect, can produce the vibration along rotary compressor circumference to the reservoir, and this vibration is the main vibration of reservoir to produce a large amount of noises, bring bad experience for the user. Some reservoirs reduce vibration by increasing weight, but the damping effect is poor, and the noise is still bigger, and is inconvenient to use.

To solve the above problem, referring to fig. 1, a first embodiment of the present invention provides an accumulator 500 applied to a compressor assembly, which may be a vertical rotary compressor.

The accumulator 500 according to an embodiment of the present invention will be described with reference to fig. 1 to 7, and in the following description, the accumulator 500 will be described by taking a compressor assembly 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, an accumulator 500 according to an embodiment of the first aspect of the present invention is applied to a compressor assembly, the compressor assembly includes a compressor body 400, an accumulator 500, and a connection pipe 600, the accumulator 500 is used to separate a gaseous refrigerant from a liquid refrigerant, the connection pipe 600 may be a copper pipe, the compressor body 400 is communicated with the accumulator 500 through the connection pipe 600, an exhaust pipe 130 is disposed in the accumulator 500 along an axial direction of the accumulator 500, the exhaust pipe 130 is communicated with the connection pipe 600, the exhaust pipe 130 extends to a top of the accumulator 500 and has a certain gap with the top of the accumulator 500, so that the compressor body 400 can normally suck the gaseous refrigerant from the accumulator 500 for compression and transportation. Specifically, the compressor body 400 is installed with a motor 410 and a compression mechanism 420, the compression mechanism 420 is located below the motor 410, and an output shaft of the motor 410 is connected to the compression mechanism 420, wherein the compression mechanism 420 is well known to those skilled in the art and will not be described in detail herein. The accumulator 500 includes a housing 100 and a damping element 200, the housing 100 includes a main casing 110 and an upper casing 120, the upper casing 120 is installed on the top of the main casing 110 by resistance welding, two ends of a connecting pipe 600 are respectively connected to the lower end of the compressor body 400 and the lower end of the main casing 110, the exhaust pipe 130 is located in the housing 100 and is arranged along the axial direction of the accumulator 500, and a certain gap is formed between the exhaust pipe 130 and the upper casing 120 to enable the compressor body 400 to suck gaseous refrigerant from the accumulator 500 for compression and transportation. Of course, the case 100 may further include a lower case (not shown), that is, the case 100 is composed of three parts, in which case the lower case is welded to the lower end of the main case 110.

Referring to fig. 2, it can be understood that the damping element 200 is installed in the housing 100, and 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 convenience of processing, the cross section of the weight 210 is circular, that is, 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. Since the exhaust pipe 130 is provided in the housing 100, the weight block 210 is provided with the through holes 211, the through holes 211 may be arranged along the axial direction of the weight block 210, and the inner diameter of the through holes 211 is larger than the outer diameter of the exhaust pipe 130, i.e., D4 > D3. When the damping element 200 is mounted, the exhaust pipe 130 passes through the through hole 211, the edge of the substrate 220 is fixed to the inner wall of the main case 110, and the upper case 120 is welded to the main case 110. On one hand, the vibration damping element 200 can be conveniently installed in the housing 100, and on the other hand, a gap is formed between the weight 210 of the vibration damping element 200 and the exhaust pipe 130, so that the weight 210 is prevented from being attached to the exhaust pipe 130 and transmitting vibration back to the exhaust pipe 130, and the vibration damping effect is effectively improved.

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 through the substrate 220 in the thickness direction, that is, the through groove 221 penetrates through the substrate 220 in the axial direction of the weight block 210, meanwhile, the through groove 221 extends along the circumferential direction of the weight block 210, the number of the through grooves 221 may be one or more, so as to reduce the rigidity of the substrate 220, at the position where the substrate 220 is connected with the weight block 210, the substrate 220 has certain elasticity, that is, the substrate 220 has certain elastic deformation amount, the direction of the elastic deformation amount may be along the axial direction of the weight block 210 or along the radial direction of the weight block 210, wherein the elastic deformation amount of the substrate 220 in the axial direction of the weight block 210 is greater than that in the radial direction of the weight block 210, that is, the rigidity of the substrate 220 in the axial direction of the weight block 210 is lower than that 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 handled efficiently. I.e., the greater the rigidity of the substrate 220, the higher the vibration frequency of the corresponding process and vice versa.

The vibration along the circumferential direction of the compressor body 400 is generated by the rotation of the rotor of the compressor body 400, the vibration is expressed as radial vibration along the reservoir 500 on the reservoir 500, because the rigidity of the substrate 220 is reduced and has certain elasticity, the weight 210 can move in the elastic deformation range of the substrate 220 relative to the substrate 220, when the vibration wave passes through the vibration damping element 200, the vibration wave is offset by the deformation of the substrate 220 and the back and forth movement of the weight 210 relative to the substrate 220 in the transmission direction of the vibration wave, because the movement range of the weight 210 is very small, the weight 210 does not touch the exhaust pipe 130, the amplitude when the vibration wave is transmitted to the shell 100 is reduced, thereby reducing the vibration of the reservoir 500, the vibration damping effect is good, and the noise can be reduced.

It will be appreciated that the vibration frequency of the reservoir 500 is typically greater than 90Hz, with the abscissa being the vibration frequency and the ordinate being the vibration acceleration (in m/s) according to the line graph of fig. 8 ² ) The broken line with the data marks as a square indicates the relationship between the vibration frequency and the vibration acceleration of the liquid reservoir 500 when the damping element 200 is not mounted, and the broken line with the data marks as a triangle indicates the relationship between the vibration frequency and the vibration acceleration of the liquid reservoir 500 when the damping element 200 is mounted, from whichIt is known that, when the vibration frequency is greater than 90Hz, the vibration acceleration of the reservoir 500 after the vibration damping element 200 is installed is significantly smaller than the vibration acceleration of the reservoir without the vibration damping element 200, that is, the vibration can be significantly reduced after the vibration damping element 200 is installed on the reservoir 500, the vibration damping effect is good, and the noise is reduced.

Referring to fig. 4, it can be understood that through slot 221 is provided as a spiral structure, that is, a projection of through slot 221 along an axial direction of counterweight block 210 is spiral, through slot 221 includes inner molded line 2211 and outer molded line 2212, inner molded line 2211 and outer molded line 2212 are arranged at intervals along a radial direction of counterweight block 210, and a distance between inner molded line 2211 and outer molded line 2212 is a slot width W of through slot 221. It should be noted that "inside" is defined as the side close to the weight 210, and "outside" is defined as the 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 provided around the weight block 210, the plurality of through grooves 221 are sequentially arranged around the weight block 210 at intervals in a spiral manner, inner molded lines 2211 of the plurality of through grooves 221 may coincide with a spiral continuous curve (i.e., a spiral), such as an archimedean spiral, inner molded lines 2211 of the plurality of through grooves 221 may also coincide with a plurality of sequentially connected segments in a spiral manner, such as a square spiral or other polygonal spiral, 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 ≦ 0.5, i.e., the number of turns of the archimedean spiral is at least 0.5 turns and at most 5 turns, e.g., N =2, N =3, N =4, etc., to ensure proper rigidity of the base plate 220, to enable the weight 210 to move relative to the base plate 220 to counteract vibration waves, to achieve vibration damping, and to reduce noise.

Referring to fig. 3 and 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 =1, W =2, etc. 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.

Referring to fig. 4, it can be understood that, by defining an intersection point of a center line of the weight 210 and a plane where the substrate 220 is located as a circle center O, an x axis points to the right side, a y axis direction points to the rear side, a plane rectangular coordinate system is established with the circle center O, the x axis, and the y axis, and an archimedean spiral satisfies the equation: x = a × t × cos (t × 360), y = 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 block 210 as D1 and the smallest outer diameter of the base plate 220 as D2, since the weight block 210 has a cylindrical structure, i.e. the diameter of the cross section of the weight block 210 is the smallest outer diameter as D1, when the base plate 220 is a circular plate, the diameter of the circular plate is the smallest outer diameter as D2, and when the base plate 220 is a polygonal plate, for example, a rectangular plate, the width of the rectangular plate is the smallest outer diameter as D2, satisfies: 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 a t) 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: values a =9, W =2mm, D1=32mm, D2=76mm, then 0 ≦ t ≦ 11, obtainable from 0 ≦ t ≦ (D2-D1)/(2 × W), obtainable from D1 ≦ (2 × a × t) ≦ (D2-W), 1.77 ≦ t ≦ 4.1, that is, the number of turns N =4.1-1.77=2.33, so that the number of turns N of the archimedean spiral at this time is 2.33 turns.

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

Referring to fig. 2, it can be understood that the plane of the base plate 220 is perpendicular to the axial direction of the housing 100, the outer shape of the base plate 220 is set to be the same as the cross-sectional shape of the 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 housing 100, and the mounting stability of the damping element 200 is ensured. Because the vibration of reservoir 500 is mainly the circumference along compressor body 400, base plate 220 is perpendicular with the axial of casing 100, when the vibration wave passes through damping element 200, balancing weight 210 can follow the radial movement of casing 100 along base plate 220 relatively, because balancing weight 210's displacement range is very little, balancing weight 210 can not touch blast pipe 130, thereby offset the vibration wave, the amplitude when making vibration wave transmit casing 100 is littleer, thereby reduce the vibration of reservoir 500, the damping effect is better, simultaneously can reduce the noise better.

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 housing 100, that is, the base plate 220 is connected with the inner wall of the main shell 110, and the base plate 220 and the inner wall of the main shell 110 may be in welded connection or interference fit, and the vibration damping element 200 is installed more stably and connected more firmly when the base plate 220 is welded with the inner wall of the main shell 110.

Referring to fig. 2 and 3, it can be understood that the outer edge of the base plate 220 is provided with a convex plate 2213, the convex plate 2213 extends along the thickness direction of the base plate 220, since the plane of the base plate 220 is perpendicular to the axial direction of the housing 100, the base plate 220 is a circular plate, and the convex plates 2213 are arranged around the circumference of the weight block 210, i.e. the convex plates 2213 are annular plates, for example, the convex plates 2213 may be provided on both the upper side and the lower side of the base plate 220, or the convex plates 2213 may be provided only on the upper side of the base plate 220, or the convex plates 2213 may be provided only on the lower side of the base plate 220. When the damping element 200 is mounted, the projection 2213 is attached to the inner wall of the main housing 110, so that the contact area between the base plate 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.

Referring to fig. 2 and 3, it can be understood that, the outer diameter of the exhaust pipe 130 is defined as D3, and the inner diameter D4 of the through hole 211, in order to ensure that the weight 210 does not touch the exhaust pipe 130 when the weight 210 moves relative to the substrate 220 in the vibration damping process of the vibration damping element 200, the following requirements are satisfied: D4-D3. Gtoreq.0.2 mm, for example: D4-D3=0.5mm, D4-D3=1mm, and the like, so that a sufficient gap is provided between the weight 210 and the exhaust pipe 130, thereby preventing vibration from being transmitted back to the exhaust pipe 130, and further improving the vibration reduction effect.

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 the radius 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 = 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 arranged at intervals along the direction far away from the weight block 210, so as 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 =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 weight block 210 can move in an elastic deformation range of the substrate 220 relative to the substrate 220 to counteract vibration waves, reduce the vibration of the 500 liquid reservoir, have good vibration reduction effect, and can reduce the operating noise of the liquid reservoir 500. Of course, it is understood that θ may also be θ =330 °, θ =350 °, and so on.

Referring to fig. 1 and 2, a compressor assembly according to an embodiment of the second aspect of the present invention includes the accumulator 500 of the above-described embodiment of the first aspect, wherein the compressor assembly includes, but is not limited to, a vertical rotary compressor.

The compressor assembly is provided with the reservoir 500 according to the first aspect of the present invention, when the vibration wave in the reservoir 500 passes through the vibration damping element 200, the vibration wave is offset by moving the counter weight 210 relative to the base plate 220, so that the amplitude of the vibration wave transmitted to the housing 100 is reduced, thereby reducing the vibration of the reservoir 500, and reducing the noise, the vibration damping effect is good, and meanwhile, the counter weight 210 is provided with the through hole 211 having a diameter larger than the inner diameter of the exhaust pipe 130, so that the exhaust pipe 130 can be avoided during the movement of the counter weight 210, and the vibration is prevented from being retransmitted to the exhaust pipe 130, thereby further improving the vibration damping effect, and further reducing the vibration of the compressor assembly, and reducing the operation noise of the compressor assembly.

According to an embodiment of the third aspect of the present invention, the refrigeration apparatus includes the compressor assembly of the embodiment of the second aspect, wherein the refrigeration apparatus 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 second aspect embodiment, when the vibration wave in the reservoir 500 passes through damping element 200, move through balancing weight 210 relative base plate 220 and offset the vibration wave, the amplitude when making the vibration wave transmit to casing 100 reduces, thereby reduce the vibration of reservoir 500, and the noise reduction, the damping is effectual, simultaneously, because balancing weight 210 is provided with the through-hole 211 that the diameter is greater than the internal diameter of blast pipe 130, make balancing weight 210 remove the in-process and can avoid blast pipe 130, avoid vibration retransmission to blast pipe 130, further improve the damping effect, and then reduce compressor unit's vibration, reduce refrigeration plant's vibration, the damping is effectual, and reduce compressor unit and refrigeration plant's running noise.

The embodiments of the present invention have been described in detail with reference to the drawings, but the present invention is not limited to the 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. Reservoir, characterized in that it comprises:

a housing having an exhaust pipe therein;

the vibration reduction element is arranged in the shell and comprises a balancing weight and a substrate arranged around the balancing weight in the circumferential direction, the substrate is fixedly connected with the shell, the substrate is provided with a through groove, the through groove extends in the circumferential direction of the balancing weight and penetrates through the substrate in the thickness direction, the balancing weight is provided with a through hole, the diameter of the through hole is larger than the outer diameter of the exhaust pipe, and the exhaust pipe penetrates through the through hole;

wherein, the through groove is of a spiral structure;

or the through groove is circular-arc and is provided with a plurality of, the through groove has the inboard molded lines for the major arc, and is a plurality of the through groove is along deviating from the direction interval setting of balancing weight.

2. The reservoir of claim 1, wherein: the through groove is provided with an inner side molded line which is a continuous spiral line.

3. The reservoir of claim 2, 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.

4. A reservoir according to claim 2 or 3, characterized in that: 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 3mm.

5. The reservoir of claim 1, wherein: the through groove is provided with an inner side molded line, the inner side molded line is a plurality of segments which are connected in sequence, and the plurality of segments which are connected in sequence are arranged around the balancing weight.

6. The reservoir of claim 1, wherein: the substrate is perpendicular to the axial direction of the housing.

7. Reservoir according to claim 1 or 6, characterized in that: the outer edge of the substrate is provided with a convex plate extending along the thickness direction of the substrate, and the convex plate is attached to the inner wall of the shell.

8. The reservoir of claim 1, wherein: the external diameter of blast pipe is D3, the internal diameter of through-hole is D4, satisfies: D4-D3 is more than or equal to 0.2mm.

9. Compressor unit spare, its characterized in that: comprising a reservoir according to any of claims 1-8.

10. Refrigeration plant, its characterized in that: comprising a compressor assembly according to claim 9.