Pump body assembly, compressor and refrigeration equipment

Abstract

The invention discloses a pump body assembly, a compressor and refrigeration equipment, the pump body assembly is provided with a low-pressure compression cavity, a middle cavity and a high-pressure compression cavity, the low-pressure compression cavity is provided with a first exhaust port, the high-pressure compression cavity is provided with a second exhaust port, the first exhaust port is communicated with an air suction port of the high-pressure compression cavity through the middle cavity, the working volume of the low-pressure compression cavity is V1, the length of the first exhaust port in the axial direction of the pump body assembly is T1, the minimum through-flow area of the first exhaust port is S1, the working volume of the high-pressure compression cavity is V2, the length of the second exhaust port in the axial direction of the pump body assembly is T2, the minimum through-flow area of the second exhaust port is S2, and U = (V1 * S1 / T1) / (V2 * S2 / T2), 0.5 < = U < = 5.6. The exhaust speed of the first exhaust port is close to the exhaust speed of the second exhaust port, exhaust resistance is reduced, smooth exhaust of the compressor is guaranteed, and therefore the performance of the compressor is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a pump assembly, a compressor and a refrigeration device. Background Art

[0002] At present, the pump body assembly adopts multi-stage compression technology to evenly distribute the pressure ratio of each stage of the compression assembly, so that the compression assembly is within a more reasonable pressure ratio range, thereby improving the volumetric efficiency of the compressor. The existing pump body assembly is provided with a low-pressure compression chamber, an intermediate chamber and a high-pressure compression chamber. The exhaust port of the low-pressure compression chamber is connected to the suction port of the high-pressure compression chamber through the intermediate chamber. The refrigerant compressed in the low-pressure compression chamber is temporarily stored in the intermediate chamber for transition, and then sucked into the high-pressure compression chamber for secondary compression. Due to the design of the intermediate chamber, the exhaust path of the refrigerant is increased, resulting in an increase in the exhaust loss of the compressor, which affects the performance of the compressor. Summary of the invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a pump body assembly that can reduce exhaust loss and improve the performance of the compressor.

[0004] The present invention also provides a compressor having the pump body assembly.

[0005] The present invention also provides a refrigeration device having the compressor.

[0006] The pump body assembly according to the first embodiment of the present invention is provided with a low-pressure compression chamber, an intermediate chamber and a high-pressure compression chamber, wherein the low-pressure compression chamber has a first exhaust port, the high-pressure compression chamber has a second exhaust port, and the first exhaust port is connected to the air intake port of the high-pressure compression chamber through the intermediate chamber;

[0007] Among them, the working volume of the low-pressure compression chamber is V 1 The length of the first exhaust port along the axial direction of the pump body assembly is T 1 , the minimum flow area of ​​the first exhaust port is S 1 , the working volume of the high pressure compression chamber is V 2 The length of the second exhaust port along the axial direction of the pump body assembly is T 2 , the minimum flow area of ​​the second exhaust port is S 2 , satisfying: U=(V 1 ×S 1 ÷T 1 ) / (V 2 ×S 2 ÷T 2 ), 0.5≤U≤5.6.

[0008] The pump assembly according to the embodiment of the present invention has at least the following beneficial effects:

[0009] When the pump assembly is working, the refrigerant outside the pump assembly is sucked into the low-pressure compression chamber from the suction port of the low-pressure compression chamber, and the refrigerant completes the first-stage compression in the low-pressure compression chamber. After that, the refrigerant is discharged into the intermediate chamber, and the refrigerant in the intermediate chamber is sucked into the high-pressure compression chamber from the suction port of the high-pressure compression chamber, and the refrigerant completes the second-stage compression in the high-pressure compression chamber. On the one hand, the low-pressure compression chamber and the high-pressure compression chamber are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. On the other hand, it can effectively reduce the suction pulsation and exhaust pulsation of the pump assembly, thereby improving the performance of the compressor. Since the working volume of the low-pressure compression chamber is V 1 , the minimum flow area of ​​the first exhaust port is S 1 The length of the first exhaust port along the axial direction of the pump assembly is T 1 , the working volume of the high pressure compression chamber is V 2 The length of the second exhaust port along the axial direction of the pump assembly is T 2 , the minimum flow area of ​​the second exhaust port is S 2 , satisfying: U=(V 1 ×S 1 ÷T 1 ) / (V 2 ×S 2 ÷T 2 ), 0.5≤U≤5.6, when U is less than 0.5, (V 2 ×S 2 ÷T 2 ) is too large, the working volume V of the high-pressure compression chamber 2 If the refrigerant discharged from the low-pressure compression chamber is too large, the high-pressure compression chamber cannot receive it in time, the pressure in the middle chamber increases, the exhaust back pressure of the low-pressure compression chamber increases, and the minimum flow area S of the second exhaust port 2 Too large, resulting in a low gas flow rate in the second exhaust port, and the axial length T of the second exhaust port along the pump body assembly 2 Too small will increase the exhaust pulsation and the working volume V of the high-pressure compression chamber. 2 Too large, the minimum flow area S of the second exhaust port 2 The length T of the second exhaust port along the axial direction of the pump body assembly is too large. 2 Under too small synergy, the gas flow rate in the first exhaust port is much greater than the gas flow rate in the second exhaust port, and the compressor exhaust is not smooth, resulting in reduced compressor performance; when U is greater than 5.6, (V 2 ×S 2 ÷T 2 ) is too small, the working volume V of the high pressure compression chamber 2 Too small, resulting in the high-pressure compression chamber being unable to completely consume the refrigerant discharged from the low-pressure compression chamber, resulting in excess performance. The minimum flow area S of the second exhaust port 2Too small will increase the gas flow resistance and exhaust loss. The length T of the second exhaust port along the axial direction of the pump body assembly 2 Too large will increase the exhaust path and exhaust loss, and the working volume V of the high-pressure compression chamber will be 2 Too small, the minimum flow area S of the second exhaust port 2 Too small and the axial length T of the second exhaust port along the pump body assembly 2 Under excessive synergy, the exhaust resistance of the high-pressure compression chamber increases, resulting in reduced compressor performance. Therefore, by reasonably designing the working volume V of the low-pressure compression chamber 1 , the minimum flow area S of the first exhaust port 1 , the length T of the first exhaust port along the axial direction of the pump body assembly 1 , the working volume V of the high pressure compression chamber 2 , the length T of the second exhaust port along the axial direction of the pump body assembly 2 And the minimum flow area S of the second exhaust port 2 The relationship between them makes the exhaust speed of the first exhaust port close to the exhaust speed of the second exhaust port, reducing the exhaust resistance and ensuring smooth exhaust of the compressor, thereby improving the performance of the compressor.

[0010] According to some embodiments of the present invention, the diameter of the first exhaust port is D 1 , the diameter of the second exhaust port is D 2 , satisfying: 0.25≤(D 1 ×V 2 ) / (D 2 ×V 2 )≤1.2.

[0011] According to some embodiments of the present invention, the ratio of the working volume of the high-pressure compression chamber to the working volume of the low-pressure compression chamber is V 2 / V 1 , satisfying: 0.4≤V 2 / V 1 ≤0.8.

[0012] According to some embodiments of the present invention, the pump body assembly is provided with an enthalpy injection hole connected to the intermediate cavity, and the enthalpy injection hole is used for the enthalpy increasing assembly to transport refrigerant to the intermediate cavity.

[0013] According to some embodiments of the present invention, the intermediate cavity includes at least one connecting channel and at least two cavities, two adjacent cavities are connected through the connecting channel, and the refrigerant flows through each cavity through the connecting channel.

[0014] According to some embodiments of the present invention, the pump body assembly includes a lower bearing, a first cylinder, a partition assembly, a second cylinder and an upper bearing connected in sequence, and the first cavity of the intermediate cavity is formed in the partition assembly.

[0015] According to some embodiments of the present invention, the partition assembly includes a first partition and a second partition arranged opposite to each other along the axial direction of the pump body assembly, the first partition and the second partition enclose the first cavity, the first partition is connected to the first cylinder, the second partition is connected to the second cylinder, the first partition is provided with a first valve seat located in the first cavity, and the first valve seat is provided with the first exhaust port.

[0016] According to some embodiments of the present invention, the pump body assembly also includes a lower muffler connected to the lower bearing, the lower bearing is provided with a second valve seat, the second valve seat is provided with the first exhaust port, the lower muffler and the lower bearing enclose a second cavity of the intermediate cavity, the first cylinder is provided with the connecting channel, and the second cavity and the first cavity are connected through the connecting channel.

[0017] According to some embodiments of the present invention, a plurality of the communicating channels are provided, and the plurality of communicating channels are spaced apart around the axis of the pump body assembly, and both ends of each communicating channel are respectively connected to the first cavity and the second cavity.

[0018] The compressor according to the second embodiment of the present invention comprises the pump body assembly described in the above embodiment.

[0019] A refrigeration device according to an embodiment of the third aspect of the present invention comprises the compressor described in the above embodiment.

[0020] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0022] Figure 1 A schematic cross-sectional view of a pump assembly according to an embodiment of the present invention;

[0023] Figure 2 for Figure 1 A partial enlarged view of part A;

[0024] Figure 3 for Figure 1 A partial enlarged view of part B;

[0025] Figure 4A schematic cross-sectional view of a compressor according to an embodiment of the present invention;

[0026] Figure 5 For an embodiment of the present invention (V 1 ×S 1 ÷T 1 ) / (V 2 ×S 2 ÷T 2 ) and compressor COP.

[0027] Figure Number:

[0028] Axis O 1 , lower bearing 101, first cylinder 102, partition assembly 103, first partition 1031, second partition 1032, second cylinder 104, upper bearing 105, lower muffler 106, upper muffler 107, low-pressure compression chamber 110, first exhaust port 111, intermediate chamber 120, connecting channel 121, first cavity 122, second cavity 123, high-pressure compression chamber 130, second exhaust port 131, injection enthalpy hole 140, third cavity 150, crankshaft 200, first eccentric part 210, second eccentric part 220, first piston 230, second piston 240, housing 300, inner cavity 310, motor assembly 400, stator 410, rotor 420, enthalpy increase assembly 500, outlet pipe 510. DETAILED DESCRIPTION

[0029] Embodiments of the present invention are described in detail below, examples of which 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.

[0030] In the description of the present invention, it should be understood that descriptions involving orientation, such as orientation or positional relationship indicated as up, down, etc., are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0031] In the description of the present invention, "a plurality" means more than two. If there is a description of "first" or "second", it is only used for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0032] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. 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 invention based on the specific content of the technical solution.

[0033] In the related art, the compressor adopts multi-stage compression technology to evenly distribute the pressure ratio of each stage of the compression assembly, so that the compression assembly is within a more reasonable pressure ratio range, thereby improving the volumetric efficiency of the compressor. The existing pump body assembly is provided with a low-pressure compression chamber, an intermediate chamber and a high-pressure compression chamber. The exhaust port of the low-pressure compression chamber is connected to the suction port of the high-pressure compression chamber through the intermediate chamber. The refrigerant compressed in the low-pressure compression chamber is temporarily stored in the intermediate chamber for transition, and then sucked into the high-pressure compression chamber for secondary compression. Due to the design of the intermediate chamber, the exhaust path of the refrigerant is increased, resulting in an increase in the exhaust loss of the compressor, which affects the performance of the compressor.

[0034] Reference Figure 1 , Figure 1 FIG. 1 is a cross-sectional schematic diagram of a pump assembly according to an embodiment of the present invention. Figure 1 As shown, a pump body assembly of an embodiment of the present invention comprises a crankshaft 200, a lower bearing 101, a first cylinder 102, a partition assembly 103, a second cylinder 104 and an upper bearing 105. The crankshaft 200 comprises a first eccentric portion 210 and a second eccentric portion 220 spaced apart along the axial direction of the crankshaft 200. The first eccentric portion 210 is sleeved with a first piston 230, and the second eccentric portion 220 is sleeved with a second piston 240. The partition assembly 103 is connected between the first cylinder 102 and the second cylinder 104. The lower bearing 101 is connected to the first cylinder 102 and the second cylinder 104. The bearing 101 is connected to the lower end surface of the first cylinder 102, the upper bearing 105 is connected to the upper end surface of the second cylinder 104, the first cylinder 102 is provided with a low-pressure compression chamber 110, the first piston 230 is rotatably disposed in the low-pressure compression chamber 110, the second cylinder 104 is provided with a high-pressure compression chamber 130, the second piston 240 is rotatably disposed in the high-pressure compression chamber 130, at least part of the intermediate chamber 120 is disposed in the partition assembly 103, and the low-pressure compression chamber 110 is connected to the suction port of the high-pressure compression chamber 130 through the intermediate chamber 120. It can be understood that when the pump body assembly is working, the refrigerant outside the pump body assembly is sucked into the low-pressure compression chamber 110 from the suction port of the low-pressure compression chamber 110, and the refrigerant completes the first-level compression in the low-pressure compression chamber 110. After that, the refrigerant is discharged into the intermediate chamber 120, and the refrigerant in the intermediate chamber 120 is sucked into the high-pressure compression chamber 130 from the suction port of the high-pressure compression chamber 130, and the refrigerant completes the second-level compression in the high-pressure compression chamber 130. On the one hand, the low-pressure compression chamber 110 and the high-pressure compression chamber 130 are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. On the other hand, the suction pulsation and exhaust pulsation of the pump body assembly can be effectively reduced, thereby improving the performance of the compressor.

[0035] It should be noted that if the minimum flow area of ​​the exhaust port is too large, the gas flow rate will be too low, the residence time of the gas in the exhaust port will be prolonged, and the energy loss will increase, thereby reducing the performance of the compressor; if the minimum flow area of ​​the exhaust port is too small, the gas flow resistance will increase, resulting in increased exhaust pressure and increased exhaust loss, thereby reducing the performance of the compressor.

[0036] It should be noted that if the axial length of the exhaust port along the pump body assembly is too large, the exhaust path of the gas will be increased and the exhaust loss of the compressor will be increased, thereby reducing the performance of the compressor; if the axial length of the exhaust port along the pump body assembly is too small, the strength of the exhaust port will be insufficient and deformation will easily occur at the exhaust port, resulting in increased exhaust pulsation and reducing the performance of the compressor.

[0037] It should be noted that the working volume of the compression chamber, the minimum flow area of ​​the exhaust port and the axial length of the exhaust port along the pump body assembly work together to affect the gas flow rate. Too high or too low a gas flow rate will affect the performance of the compressor.

[0038] Reference Figures 1 to 3 , Figure 2 for Figure 1 A partial enlarged view of part A; Figure 2 for Figure 1 As shown in the figure, in the embodiment of the present invention, the working volume of the low-pressure compression chamber 110 is V 1 The low-pressure compression chamber 110 has a first exhaust port 111, and the minimum flow area of ​​the first exhaust port 111 is S 1 The length of the first exhaust port 111 along the axial direction of the pump assembly is T 1 , the working volume of the high pressure compression chamber 130 is V 2 The high pressure compression chamber 130 has a second exhaust port 131, and the length of the second exhaust port 131 along the axial direction of the pump body assembly is T 2 , the minimum flow area of ​​the second exhaust port 131 is S 2 , satisfying: U=(V 1 ×S 1 ÷T 1 ) / (V 2 ×S 2 ÷T 2 ), 0.5≤U≤5.6, for example, U can be 0.5, 1, 1.5, 2, 2.5, 3, 3.5, 4, 4.5, 5, 5.6, etc. It should be noted that the working volume usually refers to the residual volume between the compression chamber and the piston rotatably mounted inside the compression chamber, and the unit of the flow area is mm 2 The unit of length is mm, and the unit of working volume is cc, which will be used in the subsequent embodiments.

[0039] It can be understood that the working volume V of the low-pressure compression chamber 110 1 , the minimum flow area S of the first exhaust port 111 1 and the length T of the first exhaust port 111 along the axial direction of the pump body assembly 1 On the basis of unchanged, when U is less than 0.5, (V 2 ×S 2 ÷T 2 ) is too large, the working volume V of the high pressure compression chamber 130 2 If the refrigerant discharged from the low-pressure compression chamber 110 cannot be received in time by the high-pressure compression chamber 130, the pressure in the intermediate chamber 120 increases, the exhaust back pressure of the low-pressure compression chamber 110 increases, and the minimum flow area S of the second exhaust port 131 increases. 2 If the gas velocity in the second exhaust port 131 is too low, the length T of the second exhaust port 131 along the axial direction of the pump body assembly is too large. 2 Too small will increase the exhaust pulsation. 2 Too large, the minimum flow area S of the second exhaust port 131 2 The length T of the second exhaust port 131 along the axial direction of the pump body assembly is too large. 2 Under too small synergy, the gas flow rate in the first exhaust port 111 is much greater than the gas flow rate in the second exhaust port 131, and the compressor exhaust is not smooth, resulting in reduced compressor performance; when U is greater than 5.6, (V 2 ×S 2 ÷T 2 ) is too small, the working volume V of the high pressure compression chamber 130 2 If the refrigerant discharged from the low-pressure compression chamber 110 is too small, the high-pressure compression chamber 130 cannot completely consume the refrigerant, resulting in excess performance. The minimum flow area S of the second exhaust port 131 is 2 If the gas flow resistance is too small, the exhaust loss will increase. The length T of the second exhaust port 131 along the axial direction of the pump body assembly 2 Too large will increase the exhaust path and exhaust loss. 2 Too small, the minimum flow area S of the second exhaust port 131 2 The length T of the second exhaust port 131 along the axial direction of the pump body assembly is too small. 2 Under excessive synergy, the exhaust resistance of the high-pressure compression chamber 130 increases, resulting in reduced performance of the compressor. 1 , the minimum flow area S of the first exhaust port 111 1 , the length T of the first exhaust port 111 along the axial direction of the pump body assembly 1 , the working volume V of the high pressure compression chamber 130 2, the length T of the second exhaust port 131 along the axial direction of the pump body assembly 2 and the minimum flow area S of the second exhaust port 131 2 The relationship between the first exhaust port 111 and the second exhaust port 131 makes the exhaust speed of the first exhaust port 111 close to the exhaust speed of the second exhaust port 131, reducing the exhaust resistance and ensuring smooth exhaust of the compressor, thereby improving the performance of the compressor.

[0040] Reference Figure 5 , Figure 5 The figure is a relationship diagram between U and the COP of the compressor according to an embodiment of the present invention. The cylinder in the figure refers to the performance improvement of the compressor at different values ​​of U, and the dotted line in the figure refers to the fitting curve of the performance improvement of the compressor at different values ​​of U. As shown in the figure, when the value of U gradually increases, within the range of 0.5 to 6, the COP improvement of the compressor first gradually increases and then decreases. Therefore, the working volume V of the low-pressure compression chamber 110 is reasonably designed. 1 , the minimum flow area S of the first exhaust port 111 1 , the length T of the first exhaust port 111 along the axial direction of the pump body assembly 1 , the working volume V of the high pressure compression chamber 130 2 , the length T of the second exhaust port 131 along the axial direction of the pump body assembly 2 and the minimum flow area S of the second exhaust port 131 2 The relationship between the two can improve the performance of the compressor. It should be noted that in cooling, COP refers to the ratio of the compressor's cooling capacity to its input power; in heating, it is the COP in cooling + 1. The higher the COP value, the higher the efficiency of the compressor, and the more power it saves.

[0041] In the embodiment of the present invention, the shape of the first exhaust port 111 and the shape of the second exhaust port 131 are both circular structures, and the diameter of the first exhaust port 111 is D 1 , the diameter of the second exhaust port 131 is D 2 , satisfying: 0.25≤(D 1 ×V 2 ) / (D 2 ×V 2 )≤1.2, for example, (D 1 ×V 2 ) / (D 2 ×V 2 ) can be 0.25, 0.3, 0.4, 0.5, 0.6, 0.7, 0.8, 0.9, 1, 1.1, 1.2, etc. By properly designing the diameter D of the first exhaust port 111 1 , the working volume V of the low pressure compression chamber 110 1 , the diameter D of the second exhaust port 131 2 , the working volume V of the high pressure compression chamber 1302 The relationship between them can reduce exhaust loss and ensure smooth exhaust of the compressor, thereby improving the performance of the compressor.

[0042] It should be noted that if the diameter of the exhaust port is too large, the gas flow rate will be too low, the gas residence time in the exhaust port will be prolonged, and the energy loss will increase, thereby reducing the performance of the compressor; if the diameter of the exhaust port is too small, the gas flow resistance will increase, resulting in an increase in exhaust pressure and exhaust loss, thereby reducing the performance of the compressor. 1 and the working volume V of the low pressure compression chamber 110 1 On the basis of unchanged, when (D 1 ×V 2 ) / (D 2 ×V 2 ) is less than 0.25, the working volume V of the high pressure compression chamber 130 2 If the diameter D of the second exhaust port 131 is too small, the high-pressure compression chamber 130 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excess performance. 2 If the working volume V of the high-pressure compression chamber 130 is too small, part of the gas in the high-pressure compression chamber 130 will flow back from the high-pressure side to the low-pressure side, increasing the exhaust loss. 2 The diameter of the second exhaust port 131 is too large D 2 Under the synergistic effect of (D 1 ×V 2 ) / (D 2 ×V 2 ) is greater than 1.2, the working volume V of the high pressure compression chamber 130 2 If the diameter D of the second exhaust port 131 is too large, the refrigerant discharged from the low-pressure compression chamber 110 cannot be received in time by the high-pressure compression chamber 130, the pressure in the intermediate chamber 120 increases, the exhaust back pressure of the low-pressure compression chamber 110 increases, and the diameter D of the second exhaust port 131 increases. 2 If the working volume V of the high-pressure compression chamber 130 is too small, the gas flow resistance will increase, and the exhaust loss will increase. 2 The diameter D of the second exhaust port 131 is too large. 2 Under too small synergy, the exhaust resistance increases and the compressor exhaust is not smooth. Therefore, by reasonably designing the diameter D of the first exhaust port 111 1 , the working volume V of the low pressure compression chamber 110 1 , the diameter D of the second exhaust port 131 2 , the working volume V of the high pressure compression chamber 130 2 The relationship between them can reduce exhaust loss and ensure smooth exhaust of the compressor, thereby improving the performance of the compressor.

[0043] As another embodiment, the shape of the first exhaust port 111 can also be waist-shaped, elliptical, polygonal or irregular, and / or the shape of the second exhaust port 131 can be waist-shaped, elliptical, polygonal or irregular, which is not limited here.

[0044] In the embodiment of the present invention, the ratio of the working volume of the high-pressure compression chamber 130 to the working volume of the low-pressure compression chamber 110 is V 2 / V 1 , satisfying: 0.4≤V 2 / V 1 ≤0.8, the unit of working volume is cc, for example V 2 / V 1 It can be 0.4, 0.5, 0.6, 0.7, 0.8, etc. Taking the working volume of the high pressure compression chamber 130 as an example, when V 2 / V 1 When it is less than 0.4, the working volume V of the low-pressure compression chamber 110 1 If V is too large, the high-pressure compression chamber 130 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excess performance and reduced volumetric efficiency of the compressor. 2 / V 1 When it is greater than 0.8, for low temperature heating conditions, the working volume V of the high pressure compression chamber 130 2 If the working volume of the low-pressure compression chamber 110 is too large, the working volume of the high-pressure compression chamber 130 is insufficient, the heating capacity is insufficient, and the user experience is poor. Therefore, by reasonably designing the ratio of the working volume of the high-pressure compression chamber 130 to the working volume of the low-pressure compression chamber 110, the suction pulsation and exhaust pulsation can be reduced, the vibration and noise can be reduced, and the volumetric efficiency of the compressor can be improved.

[0045] Reference Figure 4 , Figure 4 2 is a cross-sectional view of a compressor according to an embodiment of the present invention. Figure 4 As shown, in the embodiment of the present invention, the pump body assembly is provided with an enthalpy spray hole 140, and the enthalpy spray hole 140 is connected with the intermediate cavity 120, and the outlet pipe 510 of the enthalpy increasing assembly 500 is inserted in the enthalpy spray hole 140, so that the enthalpy increasing assembly 500 can deliver refrigerant to the intermediate cavity 120. It can be understood that since the low-pressure compression chamber 110 will discharge the refrigerant into the intermediate cavity 120 after compressing the refrigerant, the refrigerant delivered by the enthalpy increasing assembly 500 to the intermediate cavity 120 can be mixed with the refrigerant in the intermediate cavity 120, and finally enter the interior of the high-pressure compression cavity 130 through the air intake port of the high-pressure compression cavity 130. Therefore, the intermediate cavity 120 can make the refrigerant inside it and the refrigerant of the enthalpy increasing assembly 500 fully mixed, reduce the problem of excessive pulsation when the two refrigerants are mixed, and improve the mixing efficiency.

[0046] As another embodiment, the enthalpy injection hole 140 can also be connected to the low-pressure compression chamber 110 or the high-pressure compression chamber 130. When the enthalpy injection hole 140 is connected to the low-pressure compression chamber 110, the enthalpy increase component 500 can deliver refrigerant to the low-pressure compression chamber 110, which can increase the exhaust volume of the low-pressure compression chamber 110; when the enthalpy injection hole 140 is connected to the high-pressure compression chamber 130, the enthalpy increase component 500 can deliver refrigerant to the high-pressure compression chamber 130, which can increase the exhaust volume of the high-pressure compression chamber 130, which will not be repeated here. It can be understood that the gaseous refrigerant used by the enthalpy increase component 500 for replenishing air can be provided by a flash evaporator, and the flash evaporator is set in the circulation loop of the refrigeration system or the heating system. Take the heating system as an example: after the liquid refrigerant releases heat through the condenser, it flows through the first throttling device, and under the action of the first throttling device, it changes from a fully liquid refrigerant to a gas-liquid mixed refrigerant. The gas-liquid mixed refrigerant then enters the flash evaporator, and the gaseous refrigerant flows along the gas outlet of the flash evaporator to the enthalpy increasing component 500. The liquid refrigerant flows out from the liquid outlet of the flash evaporator and enters the evaporator after passing through the second throttling device. Finally, the refrigerant after absorbing heat enters the low-pressure compression chamber 110 through the liquid reservoir. In another embodiment of the present invention, the flash evaporator can also be replaced by a plate heat exchanger, that is, the refrigerant used for replenishing air in the enthalpy increasing component 500 can also be provided by a plate heat exchanger, and a suitable solution can be selected according to the actual situation.

[0047] In an embodiment of the present invention, the intermediate cavity 120 includes a first cavity 122, a second cavity 123 and a connecting channel 121, and the two ends of the connecting channel 121 are connected to the first cavity 122 and the second cavity 123 respectively. Since the working volume of the low-pressure compression chamber 110 is usually larger than the working volume of the high-pressure compression chamber 130, the low-pressure compression chamber 110 can be exhausted to the two end faces respectively and then mixed into the high-pressure compression chamber 130, that is, the low-pressure compression chamber 110 can be exhausted to the first cavity 122 and the second cavity 123. When the refrigerant flows in the first cavity 122 and the second cavity 123, the refrigerant can be cooled to a certain extent, which is beneficial to reduce the input force required for compression of the high-pressure compression chamber 130210 and improve the energy efficiency of the compressor.

[0048] In an embodiment of the present invention, the pump assembly further includes a lower muffler 106, the lower muffler 106 is connected to the lower bearing 101, a second cavity 123 is formed between the lower muffler 106 and the lower bearing 101, the first cavity 122 is formed in the partition member, and the connecting channel 121 is formed in the first cylinder 102. When the compressor is running, the low-pressure compression chamber 110 can discharge the refrigerant to the second cavity 123, and then enter the first cavity 122 through the connecting channel 121. Alternatively, the low-pressure compression chamber 110 discharges the refrigerant to the first cavity 122 and the second cavity 123 at the same time to improve the exhaust efficiency.

[0049] In an embodiment of the present invention, the partition assembly 103 includes a first partition 1031 and a second partition 1032. The first partition 1031 and the second partition 1032 are arranged opposite to each other along the axial direction of the pump body assembly. The first partition 1031 is located below the second partition 1032. The first partition 1031 and the second partition 1032 enclose a first cavity 122. The first partition 1031 is connected to the upper end surface of the first cylinder 102, and the second partition 1032 is connected to the lower end surface of the second cylinder 104. The first partition 1031 and the second partition 1032 can be processed separately, which is conducive to processing and manufacturing the first cavity 122 on the partition assembly 103, and can reduce the processing and manufacturing cost of the partition assembly 103.

[0050] For example, the second cavity 123 is a petal-shaped structure, and the second cavity 123 surrounds the axis O of the pump assembly. 1 By dividing the partition assembly 103 into a first partition 1031 and a second partition 1032 , the first partition 1031 and the second partition 1032 can be processed separately, which is beneficial to processing and manufacturing the first cavity 122 on the partition assembly 103 and can reduce the processing and manufacturing cost of the partition assembly 103 .

[0051] It should be noted that a connection structure is provided between the first partition 1031 and the second partition 1032, and the connection structure is used to connect and fix the first partition 1031 and the second partition 1032. For example, the connection structure includes a connection member, and the connection member is a screw or a bolt, and the connection member includes a rod and a head at one end of the rod of the connection member, the rod is inserted into the second partition 1032 and is threadedly connected to the first partition 1031, and the head is installed in the second partition 1032, which can facilitate the connection and fixation of the first partition 1031 and the second partition 1032. As another embodiment, the connection member is a pin, one end of the connection member is fixedly connected to the first partition 1031, and the other end of the connection member is fixedly connected to the second partition 1032, which can also facilitate the connection and fixation of the first partition 1031 and the second partition 1032, which will not be repeated here.

[0052] It should be noted that there are multiple connectors, and the multiple connectors surround the axis O of the pump body assembly. 1 The arrangement can increase the connection stability between the first partition plate 1031 and the second partition plate 1032, which will not be described in detail here.

[0053] In an embodiment of the present invention, the first partition plate 1031 is provided with a first valve seat, the first valve seat is provided with a first exhaust port 111, the low-pressure compression chamber 110 can discharge the refrigerant into the first cavity 122 through the first valve seat, the lower bearing 101 is provided with a second valve seat, the second valve seat is provided with a first exhaust port 111, that is, there are two first exhaust ports 111, so that the refrigerant in the low-pressure compression chamber 110 enters the first cavity 122 and the second cavity 123 respectively through the two first exhaust ports 111 after compression, that is, the low-pressure compression adopts a double exhaust solution, which can effectively reduce the exhaust loss and improve the performance of the compressor.

[0054] As shown in the figure, in an embodiment of the present invention, the pump body assembly also includes an upper muffler 107, which is connected to the upper bearing 105, and a third cavity 150 is formed between the upper muffler 107 and the upper bearing 105. The high-pressure compression chamber 130 can discharge the compressed refrigerant into the third cavity 150, and finally enter the inner cavity 310 of the compressor shell 300. By setting the upper muffler 107, the noise during the discharge of the refrigerant can be reduced, thereby improving the user experience.

[0055] In the embodiment of the present invention, the communication channel 121 is configured in plurality, and the plurality of communication channels 121 surround the axis O of the pump body assembly. 1 By setting up multiple connecting channels 121 at intervals, the total flow area of ​​the multiple connecting channels 121130 is increased, which can reduce the flow rate of the refrigerant and thus reduce the flow loss.

[0056] It can be understood that a greater number of connecting channels 121 leads to a decrease in the radial strength of the first cylinder 102. In this embodiment, in order to ensure the radial strength of the first cylinder 102, the number of connecting channels 121 is configured to be less than or equal to 5, for example, the number of connecting channels 121 is 2, 3, 4, 5, etc.

[0057] As another implementation, the number of the connecting channel 121 may also be configured to be one, which is not limited herein.

[0058] For example Figure 4As shown, the compressor of the second embodiment of the present invention includes a housing 300 and a pump body assembly of the above embodiment, wherein the housing 300 has an inner cavity 310, and the pump body assembly is installed in the inner cavity 310. The compressor adopts the pump body assembly of the above embodiment, and the refrigerant outside the pump body assembly is sucked into the low-pressure compression chamber 110 from the suction port of the low-pressure compression chamber 110. The refrigerant completes the first-stage compression in the low-pressure compression chamber 110. After that, the refrigerant is discharged into the intermediate cavity 120. The refrigerant in the intermediate cavity 120 is sucked into the high-pressure compression chamber 130 from the suction port of the high-pressure compression chamber 130. The refrigerant completes the second-stage compression in the high-pressure compression chamber 130. On the one hand, the low-pressure compression chamber 110 and the high-pressure compression chamber 130 are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. On the other hand, it can effectively reduce the suction pulsation and exhaust pulsation of the pump body assembly, thereby improving the performance of the compressor. Since the working volume of the low-pressure compression chamber 110 is V 1 , the minimum flow area of ​​the first exhaust port 111 is S 1 The length of the first exhaust port 111 along the axial direction of the pump assembly is T 1 , the working volume of the high pressure compression chamber 130 is V 2 The length of the second exhaust port 131 along the axial direction of the pump assembly is T 2 , the minimum flow area of ​​the second exhaust port 131 is S 2 , satisfying: U=(V 1 ×S 1 ÷T 1 ) / (V 2 ×S 2 ÷T 2 ), 0.5≤U≤5.6. When U is less than 0.5, (V 2 ×S 2 ÷T 2 ) is too large, the working volume V of the high pressure compression chamber 130 2 If the refrigerant discharged from the low-pressure compression chamber 110 is too large, the high-pressure compression chamber 130 cannot receive it in time, the pressure in the intermediate chamber 120 increases, the exhaust back pressure of the low-pressure compression chamber 110 increases, and the minimum flow area S of the second exhaust port 131 increases. 2 If the length T of the second exhaust port 131 along the axial direction of the pump body assembly is too large, the gas velocity in the second exhaust port 131 will be too low. 2 Too small will increase the exhaust pulsation. 2 Too large, the minimum flow area S of the second exhaust port 131 2 The length T of the second exhaust port 131 along the axial direction of the pump body assembly is too large. 2Under too small synergy, the gas flow rate in the first exhaust port 111 is much greater than the gas flow rate in the second exhaust port 131, and the compressor exhaust is not smooth, resulting in reduced compressor performance; when U is greater than 5.6, (V 2 ×S 2 ÷T 2 ) is too small, the working volume V of the high pressure compression chamber 130 2 If the refrigerant discharged from the low-pressure compression chamber 110 is too small, the high-pressure compression chamber 130 cannot completely consume the refrigerant, resulting in excess performance. The minimum flow area S of the second exhaust port 131 is 2 If the gas flow resistance is too small, the exhaust loss will increase. The length T of the second exhaust port 131 along the axial direction of the pump body assembly 2 Too large will increase the exhaust path and exhaust loss. 2 Too small, the minimum flow area S of the second exhaust port 131 2 The length T of the second exhaust port 131 along the axial direction of the pump body assembly is too small. 2 Under excessive synergy, the exhaust resistance of the high-pressure compression chamber 130 increases, resulting in reduced performance of the compressor. 1 , the minimum flow area S of the first exhaust port 111 1 , the length T of the first exhaust port 111 along the axial direction of the pump body assembly 1 , the working volume V of the high pressure compression chamber 130 2 , the length T of the second exhaust port 131 along the axial direction of the pump body assembly 2 and the minimum flow area S of the second exhaust port 131 2 The relationship between the first exhaust port 111 and the second exhaust port 131 makes the exhaust speed of the first exhaust port 111 close to the exhaust speed of the second exhaust port 131, reducing the exhaust resistance and ensuring smooth exhaust of the compressor, thereby improving the performance of the compressor.

[0059] In this embodiment, the compressor also includes a motor assembly 400, which includes a stator 410 and a rotor 420 rotatably disposed in the stator 410. The outer circumferential surface of the rotor 420 abuts against the inner circumferential surface of the shell 300. The rotor 420 is fixedly connected to the upper end of the crankshaft 200. The stator 410 drives the crankshaft 200 to rotate through the rotor 420.

[0060] Since the compressor adopts all the technical solutions of the pump body assembly of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment, which will not be described in detail here.

[0061] The refrigeration equipment of the third embodiment of the present invention comprises the compressor of the above embodiment. The refrigeration equipment can be a central air conditioner, a package air conditioner, a split air conditioner, a duct air conditioner, a window air conditioner or the like.

[0062] The embodiments of the present invention are described in detail above 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 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: A low-pressure compression chamber, an intermediate chamber and a high-pressure compression chamber are provided, wherein the low-pressure compression chamber has a first exhaust port, the high-pressure compression chamber has a second exhaust port, and the first exhaust port is connected to the air intake port of the high-pressure compression chamber through the intermediate chamber; Among them, the working volume of the low-pressure compression chamber is V1, the axial length of the first exhaust port along the pump body assembly is T1, the minimum flow area of ​​the first exhaust port is S1, the working volume of the high-pressure compression chamber is V2, the axial length of the second exhaust port along the pump body assembly is T2, and the minimum flow area of ​​the second exhaust port is S2, satisfying: U = (V1×S1÷T1) / (V2×S2÷T2), 0.5≤U≤5.

6.

2. The pump assembly according to claim 1, characterized in that: The diameter of the first exhaust port is D1, and the diameter of the second exhaust port is D2, which satisfies: 0.25≤(D1×V2) / (D2×V2)≤1.

2.

3. The pump assembly according to claim 1, characterized in that: The ratio of the working volume of the high-pressure compression chamber to the working volume of the low-pressure compression chamber is V2 / V1, which satisfies: 0.4≤V2 / V1≤0.

8.

4. The pump assembly according to claim 1, characterized in that: The pump body component is provided with an enthalpy spray hole connected to the middle cavity, and the enthalpy spray hole is used for the enthalpy increasing component to transport refrigerant to the middle cavity.

5. The pump assembly according to claim 1, characterized in that: The intermediate cavity includes at least one connecting channel and at least two cavities. Two adjacent cavities are connected through the connecting channel, and the refrigerant flows through each cavity through the connecting channel.

6. The pump assembly according to claim 5, characterized in that: The pump body assembly comprises a lower bearing, a first cylinder, a partition assembly, a second cylinder and an upper bearing which are connected in sequence, and a first cavity of the intermediate cavity is formed in the partition assembly.

7. The pump assembly according to claim 6, characterized in that: The partition assembly includes a first partition and a second partition arranged opposite to each other along the axial direction of the pump body assembly, the first partition and the second partition enclose the first cavity, the first partition is connected to the first cylinder, the second partition is connected to the second cylinder, the first partition is provided with a first valve seat located in the first cavity, and the first valve seat is provided with the first exhaust port.

8. The pump assembly according to claim 6 or 7, characterized in that: The pump body assembly also includes a lower muffler connected to the lower bearing, the lower bearing is provided with a second valve seat, the second valve seat is provided with the first exhaust port, the lower muffler and the lower bearing enclose a second cavity of the intermediate cavity, the first cylinder is provided with the connecting channel, and the second cavity and the first cavity are connected through the connecting channel.

9. The pump assembly according to claim 8, characterized in that: There are a plurality of the communication channels, and the plurality of communication channels are arranged at intervals around the axis of the pump body assembly. Two ends of each of the communication channels are respectively connected to the first cavity and the second cavity.

10. A compressor, characterized in that: include: A pump assembly as claimed in any one of claims 1 to 9.

11. Refrigeration equipment, characterized in that: Comprising the compressor as claimed in claim 10.

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