Pump body assembly, compressor and refrigeration equipment

Abstract

The utility model discloses a pump body assembly, compressor and refrigeration equipment, the pump body assembly comprises an air cylinder, a first bearing and a second bearing, the air cylinder is provided with a third through hole, and the third through hole penetrates through the end faces of the two sides of the air cylinder; the first bearing is installed on one side of the air cylinder and provided with a first through hole and a first resonant cavity, the first through hole penetrates through the end faces of the two sides of the first bearing, and the first resonant cavity is located on the end face, facing the air cylinder, of the first bearing and communicates with the first through hole. The second bearing is installed on the other side of the air cylinder and provided with a second through hole, the second through hole penetrates through the end faces of the two sides of the second bearing, and the second through hole, the third through hole and the first through hole are sequentially communicated to form an exhaust channel; the volume V1 of the first resonant cavity and the volume V2 of the first through hole meet the condition that V1 / V2 is larger than or equal to 0.2 and smaller than or equal to 0.6. The pump body assembly is good in noise reduction effect and high in structural strength.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a pump body component, a compressor and a refrigeration device. Background Art

[0002] When the compressor is running, high-pressure refrigerant will form strong gas pulses and pressure sound waves when it is discharged from the exhaust channel of the bearing, thereby generating gas noise, which leads to the problem of high noise during the operation of the compressor. In the related art, noise reduction is achieved by setting a resonance chamber connected to the exhaust channel. However, due to the unreasonable size setting of the resonance chamber, the noise reduction effect is not good when the compressor is running at high speed, and the overall structural strength of the pump body assembly in the compressor is affected, which is not conducive to noise reduction. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model provides a pump body assembly with good noise reduction effect and high structural strength.

[0004] The utility model also provides a compressor and a refrigeration device having the pump body assembly.

[0005] The pump assembly according to the first embodiment of the utility model comprises a cylinder having a center line, wherein the cylinder is provided with a third through hole, and the third through hole penetrates both side end surfaces of the cylinder along the direction of the center line;

[0006] A first bearing is installed on one side of the cylinder along the direction of the center line, the first bearing is provided with a first through hole and a first resonance cavity, the first through hole penetrates both side end surfaces of the first bearing along the direction of the center line, the first resonance cavity is located on the end surface of the first bearing facing the cylinder and is connected with the first through hole;

[0007] A second bearing is installed on the other side of the cylinder along the direction of the center line, the second bearing is provided with a second through hole, the second through hole penetrates the two side end surfaces of the second bearing along the direction of the center line, the second through hole, the third through hole and the first through hole are connected in sequence to form an exhaust channel;

[0008] The volume V1 of the first resonance cavity and the volume V2 of the first through hole satisfy: 0.2≤V1 / V2≤0.6.

[0009] The pump body assembly according to the first aspect of the utility model has at least the following beneficial effects: by arranging a first resonance chamber connected to the exhaust channel in the first bearing, during the process of high-pressure refrigerant being discharged through the exhaust channel, part of the refrigerant will first enter the first resonance chamber, and then be discharged from the first resonance chamber to the exhaust channel, thereby generating sound of a specific frequency band in the first resonance chamber, and the sound of the specific frequency band resonates with the noise of the exhaust channel with a frequency band of the specific frequency band, thereby weakening the noise of the frequency band in the exhaust channel to achieve noise reduction; at the same time, the volume V1 of the first resonance chamber and the volume V2 of the first through hole satisfy: 0.2≤V1 / V2≤0.6, thereby optimizing the volume of the first resonance chamber, so that the first resonance chamber can weaken high-frequency noise, with good noise reduction effect, and ensure the structural strength of the first bearing, that is, ensure the structural strength of the pump body assembly, and improve the reliability of the compressor.

[0010] According to some embodiments of the present invention, the first resonance cavity includes a first cavity and a first connecting channel, the first cavity is located on one radial side of the first through hole, and two ends of the first connecting channel are respectively connected to the first cavity and the first through hole.

[0011] According to some embodiments of the present invention, the volume V1 of the first resonance cavity, the volume V2 of the first through hole and the volume V3 of the cylinder satisfy: 9≤V3 / (V1+V2)≤15.

[0012] According to some embodiments of the present invention, the volume V1 of the first resonance chamber and the volume V3 of the cylinder satisfy: 0.2≤V1 / V3≤0.5.

[0013] According to some embodiments of the present invention, the first bearing is provided with a plurality of the first resonance cavities, and the plurality of the first resonance cavities are respectively connected to the first through holes.

[0014] According to some embodiments of the present invention, the number of the first resonance cavities is two, and on a cross section perpendicular to the center line, an angle θ is included between the centers of the two first cavities and a line connecting the center line, satisfying: 20°≤θ≤40°.

[0015] According to some embodiments of the utility model, the first bearing includes a partition, which is located in the first resonance cavity, and the partition divides the first cavity into a first sub-cavity and a second sub-cavity, and the second sub-cavity is located at the outer periphery of the first sub-cavity, and the partition divides the first connecting channel into a first channel and two second channels, and the two second channels are located on both sides of the first channel, and the two ends of the first channel are respectively connected to the first sub-cavity and the first through hole, and the two ends of the two second channels are respectively connected to the second sub-cavity and the first through hole.

[0016] According to some embodiments of the utility model, a second resonance cavity is provided on the wall surface of the cylinder facing the first bearing, the second resonance cavity is connected to the third through hole, and the opening of the second resonance cavity is staggered with the opening of the first resonance cavity.

[0017] According to some embodiments of the present invention, the first bearing is further provided with a first exhaust valve port, the first exhaust valve port is communicated with the inner cavity of the cylinder, and the inner diameter D1 of the first exhaust valve port and the inner diameter D2 of the cylinder satisfy: 0.15≤D1 / D2≤0.2.

[0018] A compressor according to an embodiment of the second aspect of the utility model comprises a housing and a pump body assembly according to the embodiment of the first aspect, wherein the pump body assembly is installed in the housing.

[0019] The compressor according to the embodiment of the second aspect of the utility model has at least the following beneficial effects: since the compressor adopts the above-mentioned pump body assembly, a first resonance chamber connected to the exhaust channel is arranged on the first bearing. During the process of high-pressure refrigerant being discharged through the exhaust channel, part of the refrigerant will first enter the first resonance chamber, and then be discharged from the first resonance chamber to the exhaust channel, thereby generating sound of a specific frequency band in the first resonance chamber. The sound of the specific frequency band resonates with the noise of the exhaust channel with a frequency band of the specific frequency band, thereby weakening the noise of the frequency band in the exhaust channel to achieve noise reduction; at the same time, the volume V1 of the first resonance chamber and the volume V2 of the first through hole satisfy: 0.2≤V1 / V2≤0.6, thereby optimizing the volume of the first resonance chamber, enabling the first resonance chamber to weaken high-frequency noise, achieving good noise reduction effect, and ensuring the structural strength of the first bearing, that is, ensuring the structural strength of the pump body assembly, and improving the reliability of the compressor.

[0020] According to a third aspect of the present invention, a refrigeration device comprises a compressor according to the second aspect.

[0021] The refrigeration device according to the embodiment of the third aspect of the utility model has at least the following beneficial effects: since the refrigeration device adopts the above-mentioned compressor, a first resonance chamber connected to the exhaust channel is arranged in the first bearing. During the process of high-pressure refrigerant being discharged through the exhaust channel, part of the refrigerant will first enter the first resonance chamber, and then be discharged from the first resonance chamber to the exhaust channel, thereby generating a sound of a specific frequency band in the first resonance chamber. The sound of the specific frequency band resonates with the noise of the exhaust channel with a frequency band of the specific frequency band, thereby weakening the noise of the frequency band in the exhaust channel to achieve noise reduction; at the same time, the volume V1 of the first resonance chamber and the volume V2 of the first through hole satisfy: 0.2≤V1 / V2≤0.6, thereby optimizing the volume of the first resonance chamber, enabling the first resonance chamber to weaken high-frequency noise, achieving good noise reduction effect, and ensuring the structural strength of the first bearing, that is, ensuring the structural strength of the pump body assembly, and improving the reliability of the compressor.

[0022] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The present invention is further described below with reference to the accompanying drawings and embodiments, wherein:

[0024] Figure 1 is a cross-sectional view of a compressor in one embodiment of the utility model;

[0025] Figure 2 It is a partial cross-sectional view of the pump body assembly and the crankshaft after being assembled in one embodiment of the utility model;

[0026] Figure 3 is an axial schematic diagram of a first bearing in one embodiment of the utility model;

[0027] Figure 4 It is an axial schematic diagram of a cylinder in one embodiment of the utility model;

[0028] Figure 5 is an axial schematic diagram of a first bearing in another embodiment of the utility model;

[0029] Figure 6 is an axial schematic diagram of a first bearing in another embodiment of the utility model;

[0030] Figure 7 yes Figure 6 A in the enlarged view;

[0031] Figure 8 yes Figure 6 A cross-sectional view of the first bearing shown;

[0032] Fig. 9 It is a curve chart comparing the noise value of the compressor in one embodiment of the utility model with the prior art.

[0033] Reference numerals:

[0034] Housing 100; oil pool 110; exhaust pipe 120;

[0035] Pump assembly 200; cylinder 210; third through hole 211; second resonance chamber 212; second cavity 2121; second connecting channel 2122; inner cavity 213; air inlet 214; first bearing 220; first through hole 221; first resonance chamber 222; first cavity 2221; first sub-chamber 2222; second sub-chamber 2223; first connecting channel 2224; first channel 2225; second channel 2226; partition plate 223; enclosure plate 2231; extension plate 2232; first exhaust valve port 224; second bearing 230; second through hole 231; exhaust channel 240; isolation plate 250; fourth through hole 251; piston 260;

[0036] Motor assembly 300; stator 310; rotor 320;

[0037] Crankshaft 400; eccentric portion 410; central oil hole 420;

[0038] Liquid reservoir 500; air intake pipe 510. DETAILED DESCRIPTION

[0039] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0040] In the description of the present invention, it should be understood that descriptions involving orientation, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do 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 therefore cannot be understood as a limitation on the present invention.

[0041] In the description of the present utility model, "several" means one or more, "more" means more than two, "greater than", "less than", "exceed" etc. are understood to exclude the number itself, and "above", "below", "within" etc. are understood to include the number itself. If there is a description of "first" or "second", it is only used for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0042] In the description of the present utility model, unless otherwise clearly defined, terms such as setting, installing, connecting, assembling, and matching should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present utility model based on the specific content of the technical solution.

[0043] Reference Figures 1 to 9 As shown, the first embodiment of the utility model provides a pump body assembly 200, which is applied to the compressor of a refrigeration device. The refrigeration device can be a refrigerator, an air conditioner, a water dispenser, etc. The compressor compresses the refrigerant through the pump body assembly 200 and transports it to the refrigeration system of the refrigeration device, so that the refrigeration system can use the refrigerant to achieve heat exchange and refrigeration.

[0044] The specific structure of the pump body assembly 200 is described in detail below by taking a compressor as an example.

[0045] Reference Figure 1 As shown, it can be understood that the compressor includes a housing 100, a pump assembly 200, a motor assembly 300 and a crankshaft 400, and the pump assembly 200, the motor assembly 300 and the crankshaft 400 are all installed in the housing 100. The outer shape of the housing 100 is a vertically arranged columnar structure, and an oil pool 110 for storing refrigeration oil is formed at the bottom of the housing 100, and an exhaust pipe 120 is arranged at the top of the housing 100. The motor assembly 300 is located above the pump assembly 200, and the crankshaft 400 is arranged in the up and down direction and connected between the motor assembly 300 and the pump assembly 200. Specifically, the motor assembly 300 includes a stator 310 and a rotor 320, wherein the stator 310 is fixedly connected to the wall of the housing 100, such as welding, interference fit, etc., and the rotor 320 is rotatably arranged in the inner hole of the stator 310. The upper portion of the crankshaft 400 is passed through the rotor 320 and fixedly connected to the rotor 320, so that the rotor 320 can drive the crankshaft 400 to rotate. The lower portion of the crankshaft 400 protrudes downward from the rotor 320.

[0046] Reference Figure 1 and Figure 2 As shown, it can be understood that the pump body assembly 200 includes a cylinder 210, a first bearing 220 and a second bearing 230. In this embodiment, the number of cylinders 210 is two, and the two cylinders 210 are arranged at intervals in the up-down direction and an isolation plate 250 is provided between the two cylinders 210. The first bearing 220 is installed at the upper end of the upper cylinder 210, and the second bearing 230 is installed at the lower end of the lower cylinder 210. The first bearing 220, the two cylinders 210, the isolation plate 250 and the second bearing 230 are fixedly connected to each other by bolts. The first bearing 220 is fixedly connected to the housing 100, such as welding, interference fit, etc., so that the pump body assembly 200 is fixedly installed in the housing 100. Of course, it is easy to understand that the pump body assembly 200 can be fixedly installed in the housing 100 by any one or more of the first bearing 220, the cylinder 210 and the second bearing 230 being fixedly connected to the housing 100.

[0047] It is understandable that in other embodiments, the positions of the first bearing 220 and the second bearing 230 can be interchanged, that is, the first bearing 220 is installed at the lower end of the lower cylinder 210, and the second bearing 230 is installed at the upper end of the upper cylinder 210.

[0048] Reference Figures 1 to 4 As shown, it can be understood that the cylinder 210 is provided with an inner cavity 213 (i.e., a compression cavity). Generally speaking, the inner cavity 213 is a cylindrical cavity structure and has a center line. The center line of the inner cavity 213 is the center line of the cylinder 210 and is arranged in the up and down direction. Generally speaking, the center line of the inner cavity 213 coincides with the rotation axis of the crankshaft 400. The cylinder 210 is also provided with an air inlet 214 and an exhaust port respectively connected to the inner cavity 213, wherein the air inlet 214 is provided on the peripheral wall of the cylinder 210, and the openings of the air inlets 214 of the two cylinders 210 are oriented in the same direction, the exhaust port of the upper cylinder 210 is located on the upper end surface of the cylinder 210, and the exhaust port of the lower cylinder 210 is located on the lower end surface of the cylinder 210. Correspondingly, the first bearing 220 is provided with a first exhaust valve port 224 communicating with the exhaust port of the upper cylinder 210, and the second bearing 230 is provided with a second exhaust valve port communicating with the exhaust port of the lower cylinder 210. Generally speaking, the first bearing 220 is equipped with a valve plate for opening or closing the first exhaust valve port 224, and similarly, the second bearing 230 is also equipped with a valve plate for opening or closing the second exhaust valve port.

[0049] Reference Figure 1 As shown, it can be understood that a liquid reservoir 500 is installed on one circumferential side of the compressor, and the two air inlets 214 are respectively connected to the liquid reservoir 500 through the air inlet pipes 510, so that the low-pressure gaseous refrigerant in the liquid reservoir 500 can enter the inner cavity 213 of the cylinder 210 through the air inlet pipes 510.

[0050] Reference Figure 1 and Figure 2 As shown, it can be understood that a piston 260 is rotatably installed in the inner cavity 213 of the cylinder 210, and the central axis of the piston 260 deviates from the center line of the cylinder 210. The lower part of the crankshaft 400 passes through the first bearing 220, the two cylinders 210 and the isolation plate 250, and the second bearing 230 in sequence, and the lower part of the crankshaft 400 is provided with an eccentric part 410 that is respectively rotatably matched with the two pistons 260. Therefore, when the motor assembly 300 drives the crankshaft 400 to rotate, the crankshaft 400 drives the two pistons 260 to rotate respectively through the eccentric part 410, thereby realizing the compression of the refrigerant in the inner cavity 213 of the cylinder 210.

[0051] Reference Figure 1As shown, it can be understood that, generally speaking, the crankshaft 400 is provided with a central oil hole 420 extending through the up-down direction, and the central oil hole 420 is connected to the oil pool 110, so that the refrigerant oil can be transported to the top of the motor assembly 300 through the central oil hole 420, thereby providing lubrication to the motor assembly 300, the crankshaft 400 and the pump body assembly 200.

[0052] Reference Figure 2 As shown, it can be understood that the first bearing 220 is provided with a first through hole 221, which penetrates the upper and lower end faces of the first bearing 220 in the up-down direction. Similarly, the second bearing 230 is provided with a second through hole 231, which penetrates the upper and lower end faces of the second bearing 230 in the up-down direction. Both cylinders 210 are provided with a third through hole 211, which penetrates the upper and lower end faces of the cylinder 210 in the up-down direction, and the third through hole 211 is located outside the inner cavity 213. Similarly, the isolation plate 250 is provided with a fourth through hole 251, which penetrates the upper and lower end faces of the isolation plate 250 in the up-down direction. The center lines of the first through hole 221, the second through hole 231, the third through hole 211 and the fourth through hole 251 coincide and have the same inner diameters, and the first through hole 221, the two third through holes 211 and the fourth through hole 251 therebetween, and the second through hole 231 are sequentially connected to form an exhaust passage 240. Therefore, the exhaust passage 240 connects the upper space of the pump body assembly 200 with the lower space.

[0053] Reference Figure 1 and Figure 2 As shown, it can be understood that the high-temperature and high-pressure refrigerant compressed in the upper cylinder 210 is discharged to the upper space of the pump body assembly 200 through the exhaust port and the first exhaust valve port 224; the high-temperature and high-pressure refrigerant compressed in the lower cylinder 210 is discharged to the lower space of the pump body assembly 200 through the exhaust port and the second exhaust valve port, and then discharged to the upper space of the pump body assembly 200 through the exhaust channel 240. The high-temperature and high-pressure refrigerant in the upper space of the pump body assembly 200 is further discharged through the air gap in the rotor 320 and the exhaust pipe 120 at the top of the housing 100.

[0054] It is understandable that in other embodiments, the number of cylinders 210 may be one, in which case the pump assembly 200 does not include the isolation plate 250. The first through hole 221, the third through hole 211, and the second through hole 231 are sequentially connected to form an exhaust passage 240. The high-temperature and high-pressure refrigerant compressed in the cylinder 210 is mainly discharged to the upper space of the pump assembly 200 through the exhaust port and the first exhaust valve port 224, and part of the high-temperature and high-pressure refrigerant is mainly discharged to the lower space of the pump assembly 200 through the exhaust port and the second exhaust valve port, and then discharged to the upper space of the pump assembly 200 through the exhaust passage 240.

[0055] It is easy to understand that when the high-temperature and high-pressure refrigerant passes through the exhaust passage 240 , noise will be generated in the exhaust passage 240 due to gas pulsation.

[0056] Reference Figure 2 and Figure 3 As shown, it can be understood that the first bearing 220 is also provided with a first resonance cavity 222, the first resonance cavity 222 is located at the end surface (i.e., the lower end surface) of the first bearing 220 facing the cylinder 210, and the opening of the first resonance cavity 222 faces the cylinder 210, and the upper end surface of the cylinder 210 located on the upper side closes the opening of the first resonance cavity 222. The first resonance cavity 222 is located at one side of the first through hole 221 and is connected to the first through hole 221. Specifically, the first resonance cavity 222 includes a first cavity 2221 and a first connecting channel 2224, the first cavity 2221 is located at one radial side of the first through hole 221 and is recessed, and the inner circumferential wall of the first cavity 2221 is a cylindrical wall surface. The first connecting channel 2224 is a groove structure with an opening toward the cylinder 210. The first connecting channel 2224 is located between the first cavity 2221 and the first through hole 221, and the two ends of the first connecting channel 2224 extend to the inner circumferential wall of the first cavity 2221 and the inner circumferential wall of the first through hole 221, respectively, so that the two ends of the first connecting channel 2224 are connected to the first cavity 2221 and the first through hole 221, respectively. At this time, the upper end surface of the cylinder 210 located on the upper side closes the lower opening of the first cavity 2221 and the first connecting channel 2224. Generally speaking, along the direction of the center line of the cylinder 210, the depth of the first connecting channel 2224 is less than the depth of the first cavity 2221, so as to ensure the structural strength of the first bearing 220.

[0057] Reference Figure 2 As shown, it can be understood that, therefore, in the process of high-temperature and high-pressure refrigerant being discharged through the exhaust channel 240, part of the high-temperature and high-pressure refrigerant will first enter the first resonance cavity 222, that is, enter the first cavity 2221 through the first connecting channel 2224, and then be discharged from the first cavity 2221 through the first connecting channel 2224 to the exhaust channel 240, thereby generating a sound of a specific frequency band in the first resonance cavity 222, and the sound of the specific frequency band resonates with the noise of the exhaust channel 240 with a frequency band of the specific frequency band, thereby weakening the noise of the frequency band in the exhaust channel 240, thereby achieving noise reduction.

[0058] Reference Figure 3 As shown, it can be understood that the volume of the first resonance cavity 222 is defined as V1, that is, V1 is the sum of the volume of the first cavity 2221 and the volume of the first connecting channel 2224; the volume of the first through hole 221 is defined as V2. The volume V1 of the first resonance cavity 222 and the volume V2 of the first through hole 221 satisfy 0.2≤V1 / V2≤0.6.

[0059] Reference Figure 3 As shown, it can be understood that if V1 / V2 is less than 0.2, the volume of the first resonance chamber 222 is too small, the silencing effect on high-frequency noise is poor, and the noise reduction effect is deteriorated, or the volume of the first through hole 221 is too large, which will cause the structural strength of the first bearing 220 to decrease and cause the exhaust pressure to decrease; if V1 / V2 is greater than 0.6, the volume of the first resonance chamber 222 is too large, which will cause the structural strength of the first bearing 220 to decrease, or the volume of the first through hole 221 is too small, which will cause the flow resistance to increase and the flow rate of the refrigerant to decrease.

[0060] Therefore, making 0.2≤V1 / V2≤0.6, for example, the value of V1 / V2 is 0.2, 0.3, 0.4, 0.5 or 0.6, etc., on the one hand, it can weaken high-frequency noise and improve the noise reduction effect, refer to Fig. 9 As shown, for noise with a frequency of 1500 Hz to 2000 Hz, the first resonance cavity 222 of this embodiment can reduce the noise value by about 5 dB compared with the prior art, which can significantly reduce the noise value. On the other hand, the structural strength of the first bearing 220 and the displacement of the refrigerant can be ensured, thereby improving the reliability of the compressor and meeting the requirements of the refrigeration capacity.

[0061] Reference Figure 3 and Figure 4 As shown, it can be understood that the volume of the cylinder 210 is defined as V3, and V3 is the volume of the inner cavity 213 of the cylinder 210. The volume V1 of the first resonance cavity 222 and the volume V3 of the cylinder 210 satisfy 0.2≤V1 / V3≤0.5.

[0062] Reference Figure 3 and Figure 4 As shown, it can be understood that if V1 / V3<0.2, the volume of the first resonance chamber 222 is too small, the silencing effect of high-frequency noise is not good, the noise reduction effect is deteriorated, or the volume of the cylinder 210 is too large, and the structural strength of the cylinder 210 decreases under the premise of a certain outer diameter of the cylinder 210; if V1 / V3>0.5, the volume of the first resonance chamber 222 is too large, which will cause the structural strength of the first bearing 220 to decrease, or the volume of the cylinder 210 is too small, the compression amount of the refrigerant is reduced, and the refrigeration capacity requirement cannot be met. Therefore, 0.2≤V1 / V3≤0.5, for example, the value of V1 / V3 is 0.2, 0.3, 0.4 or 0.5, etc., which can take into account the noise reduction effect of high-frequency noise, the structural strength of the cylinder 210 and the first bearing 220, and the refrigeration capacity requirement, so as to improve the noise reduction effect, ensure the structural strength of the cylinder 210 and the first bearing 220 and ensure the compression amount of the refrigerant, improve the reliability of the compressor and meet the refrigeration capacity requirement.

[0063] Reference Figure 3 and Figure 4As shown, it can be understood that the volume V1 of the first resonance chamber 222, the volume V2 of the first through hole 221 and the volume V3 of the cylinder 210 satisfy 9≤V3 / (V1+V2)≤15. If V3 / (V1+V2) is less than 9, the volume of the cylinder 210 is too small, the compression amount of the refrigerant is reduced, and the refrigeration capacity requirement cannot be met; or the sum of the volumes of the first resonance chamber 222 and the first through hole 221 is too large, that is, the volume of the first resonance chamber 222 is too large, which will cause the structural strength of the first bearing 220 to decrease, or the volume of the first through hole 221 is too large, which will cause the structural strength of the first bearing 220 to decrease and cause the exhaust pressure to decrease; V3 / (V1+V2)>15, the volume of the cylinder 210 is too large, and under the premise that the outer diameter of the cylinder 210 is constant, the structural strength of the cylinder 210 decreases; or the sum of the volumes of the first resonance chamber 222 and the first through hole 221 is too small, that is, the volume of the first resonance chamber 222 is too small, the silencing effect of high-frequency noise is poor, and the noise reduction effect is poor, or the volume of the first through hole 221 is too small, which will increase the flow resistance and reduce the flow rate of the refrigerant. Therefore, making 9≤V3 / (V1+V2)≤15, for example, the value of V3 / (V1+V2) is 9, 10, 11, 12, 13, 14 or 15, etc., can further take into account the noise reduction effect on high-frequency noise, the structural strength of the cylinder 210 and the first bearing 220, and the refrigeration capacity requirement, so as to improve the noise reduction effect, ensure the structural strength of the cylinder 210 and the first bearing 220, and ensure the displacement and compression of the refrigerant, thereby improving the reliability of the compressor and meeting the refrigeration capacity requirement.

[0064] Reference Figure 5 As shown, it can be understood that in other embodiments, the first bearing 220 is provided with two first resonance chambers 222, and the structure of the first resonance chamber 222 can refer to the above description, which will not be repeated here. The two first resonance chambers 222 are respectively located on both sides of the radial direction of the first through hole 221 and are connected to the first through hole 221. The two first resonance chambers 222 are arranged symmetrically or centrally symmetrically about the center line of the cylinder 210. Therefore, the two first resonance chambers 222 can respectively achieve noise reduction, which is conducive to expanding the sound-absorbing band of the compressor, and the sound-absorbing band is the frequency range corresponding to the weakened noise. By making a first through hole 221 correspondingly connected to two first resonance chambers 222, the noise with a frequency of 3000Hz to 5000Hz in the compressor with a rotation frequency higher than 120Hz can be weakened, and the noise reduction effect on high-frequency noise can be significantly improved, and the noise value can be reduced by about 3dB.

[0065] Reference Figure 5As shown, it can be understood that, on the cross section perpendicular to the central axis of the cylinder 210, the angle between the center of the two first cavities 2221 and the connecting line of the center line of the cylinder 210 is θ, which satisfies 20°≤θ≤40°, wherein the cross section of the first cavity 2221 is circular, and the center of the first cavity 2221 is the center of the cross section of the first cavity 2221. θ reflects the arrangement range of the two first resonance cavities 222 relative to the first through hole 221 to a certain extent. If θ<20°, the distance between the two or one of the first resonance cavities 222 and the first through hole 221 is too close, and the noise reduction effect is not good; if θ>40°, the distance between the first resonance cavity 222 and the first through hole 221 is too far, which affects the layout of other holes of the first bearing 220 and affects the structural strength of the first bearing 220. Therefore, making 20°≤θ≤40°, for example, the value of θ is 20°, 30° or 40°, etc., can improve the reduction effect, and the structural design of the first bearing 220 is more reasonable.

[0066] Of course, it is understandable that the number of the first resonance cavities 222 may also be three, four or more, and the plurality of first resonance cavities 222 are all connected to the first through hole 221 .

[0067] Reference Figures 6 to 8As shown, it can be understood that in other embodiments, the first bearing 220 includes a partition 223, and the partition 223 is located in the first resonance cavity 222. Specifically, the partition 223 is connected to the bottom wall of the first resonance cavity 222 and extends to the end surface of the first bearing 220 along the direction of the center line of the cylinder 210. The partition 223 includes a surrounding plate 2231 and two extension plates 2232. The surrounding plate 2231 is arranged around the center of the first cavity 2221 and is formed with an opening radially outward. The two extension plates 2232 are respectively connected to the two ends of the surrounding plate 2231 and extend toward the first through hole 221. Therefore, the partition 223 divides the first cavity 2221 into a first sub-cavity 2222 and a second sub-cavity 2223, wherein the first sub-cavity 2222 is the space surrounded by the surrounding plate 2231, and the second sub-cavity 2223 is the space between the outer peripheral wall of the surrounding plate 2231 and the inner peripheral wall of the first cavity 2221, that is, the second sub-cavity 2223 is located at the outer periphery of the first sub-cavity 2222; at the same time, the partition 223 divides the first connecting channel 2224 into a first channel 2225 and two second channels 2226, wherein the first channel 2225 is the space between the two extension plates 2232, and the two ends of the first channel 2225 are respectively connected to the first sub-cavity 2222 and the first through hole 221, and the two second channels 2226 are respectively located on the back sides of the two extension plates 2232, that is, the second channel 2226 is the space between the extension plate 2232 and the inner wall of the first connecting channel 2224, and the two second channels 2226 are located on both sides of the first channel 2225, and the two ends of the two second channels 2226 are respectively connected to the second sub-cavity 2223 and the first through hole 221. Therefore, the first resonance chamber 222 is divided into two spaces respectively connected to the first through hole 221. The two spaces are independent of each other and can achieve noise reduction respectively, which is beneficial to expanding the sound elimination band of the compressor and can weaken the noise with a frequency of 4000Hz to 5000Hz in the compressor with a rotation frequency higher than 150Hz, thereby significantly improving the noise reduction effect on high-frequency noise.

[0068] Reference Figure 4As shown, it can be understood that the cylinder 210 located on the upper side is also provided with a second resonance chamber 212, the second resonance chamber 212 is located on the wall of the cylinder 210 facing the first bearing 220, and the second resonance chamber 212 is located on the outside of the inner cavity 213, and the structure of the second resonance chamber 212 can refer to the structure of the first resonance chamber 222, which will not be repeated here. The opening of the second resonance chamber 212 faces the first bearing 220, and the second resonance chamber 212 is connected to the third through hole 211. Specifically, the second resonance chamber 212 includes a second cavity 2121 and a second connecting channel 2122, the second cavity 2121 is located on one radial side of the third through hole 211, and the two ends of the second connecting channel 2122 are respectively connected to the second cavity 2121 and the third through hole 211. Therefore, the second resonance chamber 212 can also weaken the noise in a specific frequency band to achieve noise reduction. In this embodiment, the opening of the second resonance cavity 212 is staggered from the opening of the first resonance cavity 222, that is, on the projection plane perpendicular to the center line of the cylinder 210, the projection of the second resonance cavity 212 does not overlap with the projection of the first resonance cavity 222. The first bearing 220 closes the opening of the second resonance cavity 212 at the end surface facing the cylinder 210. Therefore, the first resonance cavity 222 and the second resonance cavity 212 are independent of each other, so that the first resonance cavity 222 and the second resonance cavity 212 can respectively weaken noises of different frequencies, thereby expanding the sound-absorbing band of the compressor and further improving the noise reduction effect.

[0069] Reference Figure 3 and Figure 4 As shown, it can be understood that, generally speaking, the cross section of the first exhaust valve port 224 is circular, and the inner diameter of the first exhaust valve port 224 is defined as D1, and the inner diameter of the cylinder 210 is defined as D2, where D2 is the diameter of the inner cavity 213, and satisfies 0.15≤D1 / D2≤0.2. If D1 / D2<0.15, the first exhaust valve port 224 is too small, the flow resistance is large, and the displacement of the refrigerant is reduced, or the inner cavity 213 of the cylinder 210 is too large, and the structural strength of the cylinder 210 is reduced under the premise that the outer diameter of the cylinder 210 is constant; if D1 / D2>0.2, the first exhaust valve port 224 is too large, and the clearance volume increases, which also leads to a reduction in the displacement of the refrigerant, and at the same time, it will lead to an increase in the vibration of the valve plate and an increase in noise, or the inner cavity 213 of the cylinder 210 is too small, and the compression of the refrigerant is reduced, which cannot meet the requirements of the cooling capacity. Therefore, by making 0.15≤D1 / D2≤0.2, for example, the value of D1 / D2 is 0.15, 0.16, 0.17, 0.18 or 0.2, etc., the structural strength of the cylinder 210 can be ensured and the refrigeration capacity requirements can be met, and the noise can be reduced. It is easy to understand that by optimizing the size of the first exhaust valve port 224, the first exhaust valve port 224 can also weaken the noise of a specific frequency band during the exhaust process to a certain extent. Combined with the noise reduction effect of the first resonance cavity 222 and the second resonance cavity 212, the sound elimination band of the compressor can be expanded, and the noise reduction effect can be further improved.

[0070] The compressor of the second embodiment of the utility model comprises a housing 100 and a pump body assembly 200 of the first embodiment of the utility model. The pump body assembly 200 is installed in the housing 100 and will not be described in detail here.

[0071] Since the compressor adopts all the technical solutions of the pump body assembly 200 of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment.

[0072] The refrigeration device of the embodiment of the third aspect of the utility model comprises the compressor of the embodiment of the second aspect of the utility model. The refrigeration device may be a refrigerator, an air conditioner or a water dispenser.

[0073] Since the refrigeration equipment adopts all the technical solutions of the compressor of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment.

[0074] The embodiments of the present invention are described in detail above in conjunction with the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A pump assembly, characterized in that: include: A cylinder having a center line, wherein the cylinder is provided with a third through hole, and the third through hole penetrates both side end surfaces of the cylinder along the direction of the center line; A first bearing is installed on one side of the cylinder along the direction of the center line, the first bearing is provided with a first through hole and a first resonance cavity, the first through hole penetrates both side end surfaces of the first bearing along the direction of the center line, the first resonance cavity is located on the end surface of the first bearing facing the cylinder and is connected with the first through hole; A second bearing is installed on the other side of the cylinder along the direction of the center line, the second bearing is provided with a second through hole, the second through hole penetrates the two side end surfaces of the second bearing along the direction of the center line, the second through hole, the third through hole and the first through hole are connected in sequence to form an exhaust channel; The volume V1 of the first resonance cavity and the volume V2 of the first through hole satisfy: 0.2≤V1 / V2≤0.

6.

2. The pump assembly according to claim 1, characterized in that: The first resonance cavity includes a first cavity body and a first connecting channel. The first cavity body is located on one radial side of the first through hole. Two ends of the first connecting channel are respectively connected to the first cavity body and the first through hole.

3. The pump assembly according to claim 1 or 2, characterized in that: The volume V1 of the first resonance chamber, the volume V2 of the first through hole and the volume V3 of the cylinder satisfy: 9≤V3 / (V1+V2)≤15.

4. The pump assembly according to claim 1 or 2, characterized in that: The volume V1 of the first resonance chamber and the volume V3 of the cylinder satisfy: 0.2≤V1 / V3≤0.

5.

5. The pump assembly according to claim 2, characterized in that: The first bearing is provided with a plurality of the first resonance cavities, and the plurality of the first resonance cavities are respectively communicated with the first through holes.

6. The pump assembly according to claim 5, characterized in that: The number of the first resonance cavities is two. On a cross section perpendicular to the center line, an angle θ is formed between the centers of the two first cavities and a line connecting the center line, satisfying: 20°≤θ≤40°.

7. The pump assembly according to claim 2, characterized in that: The first bearing includes a partition, which is located in the first resonance cavity. The partition divides the first cavity into a first sub-cavity and a second sub-cavity, and the second sub-cavity is located at the outer periphery of the first sub-cavity. The partition divides the first connecting channel into a first channel and two second channels, and the two second channels are located on both sides of the first channel. The two ends of the first channel are respectively connected to the first sub-cavity and the first through hole, and the two ends of the two second channels are respectively connected to the second sub-cavity and the first through hole.

8. The pump assembly according to claim 1, characterized in that: A second resonance cavity is provided on the wall surface of the cylinder facing the first bearing. The second resonance cavity is communicated with the third through hole. The opening of the second resonance cavity is staggered with the opening of the first resonance cavity.

9. The pump assembly according to claim 1, characterized in that: The first bearing is further provided with a first exhaust valve port, the first exhaust valve port is communicated with the inner cavity of the cylinder, and the inner diameter D1 of the first exhaust valve port and the inner diameter D2 of the cylinder satisfy: 0.15≤D1 / D2≤0.

2.

10. A compressor, characterized in that The invention comprises a housing and a pump body assembly according to any one of claims 1 to 9, wherein the pump body assembly is installed in the housing.

11. Refrigeration equipment, characterized in that Comprising the compressor of claim 10.

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