Pump body assembly, compressor and refrigeration equipment

Abstract

The utility model discloses a pump body assembly, and discloses 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] This utility model relates to the field of compressor technology, and in particular to a pump body assembly, a compressor and a refrigeration device. Background Technology

[0002] Currently, pump assemblies employ multi-stage compression technology to distribute the pressure ratio of each stage, keeping the compression components within a more reasonable pressure ratio range and thus improving the compressor's volumetric efficiency. Existing pump assemblies have 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 intake port of the high-pressure compression chamber through the intermediate chamber. The refrigerant compressed in the low-pressure chamber is temporarily stored in the intermediate chamber for transition, and then drawn into the high-pressure compression chamber for secondary compression. This intermediate chamber design increases the refrigerant's exhaust path, leading to increased compressor exhaust losses and affecting compressor performance. Utility Model Content

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

[0004] This utility model also proposes a compressor having the above-mentioned pump body assembly.

[0005] This utility model also proposes a refrigeration device having the above-mentioned compressor.

[0006] According to a first aspect embodiment of the present invention, the pump body assembly is provided with a low-pressure compression chamber, an intermediate chamber and a high-pressure compression chamber, the low-pressure compression chamber having a first exhaust port, the high-pressure compression chamber having a second exhaust port, and the first exhaust port being connected to the intake port of the high-pressure compression chamber through the intermediate chamber.

[0007] Wherein, the working volume of the low-pressure compression chamber is V1, the length of the first exhaust port along the axial direction of 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 length of the second exhaust port along the axial direction of 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.

[0008] The pump assembly according to the embodiments 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 drawn into the low-pressure compression chamber through the suction port. The refrigerant completes primary compression in the low-pressure compression chamber and is then discharged into the intermediate chamber. The refrigerant in the intermediate chamber is then drawn into the high-pressure compression chamber through the suction port. The refrigerant completes secondary compression in the high-pressure compression chamber. On the one hand, the low-pressure and high-pressure compression chambers 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 and discharge pulsations of the pump assembly, thereby improving the performance of the compressor. Since the working volume of the low-pressure compression chamber is V1, the minimum flow area of ​​the first exhaust port is S1, and the axial length of the first exhaust port along the pump assembly is T1, the working volume of the high-pressure compression chamber is V2, the axial length of the second exhaust port along the pump assembly is T2, and the minimum flow area of ​​the second exhaust port is S2, the following conditions must be met: U = (V1 × S1 ÷ T1) / (V2 × S2 ÷ T2), 0.5 ≤ U ≤ 5.6. When U is less than 0.5, (V2 × S2 ÷ T2) is too large. The working volume V2 of the high-pressure compression chamber is too large, causing the refrigerant discharged from the low-pressure compression chamber to be unable to be received by the high-pressure compression chamber in time, increasing the pressure in the intermediate chamber and increasing the exhaust back pressure of the low-pressure compression chamber. The minimum flow area S2 of the second exhaust port is too large, resulting in a low gas velocity in the second exhaust port. The axial length T2 of the second exhaust port along the pump assembly is too small, leading to increased exhaust pulsation. When the working volume V2 of the high-pressure compression chamber is too large and the minimum flow area S2 of the second exhaust port is too small, the following conditions must be met: The combined effect of an excessively large minimum flow area S2 and an excessively small length T2 of the second exhaust port along the axial direction of the pump assembly results in a gas velocity much greater in the first exhaust port than in the second exhaust port, leading to poor compressor exhaust and reduced compressor performance. When U is greater than 5.6, (V2×S2÷T2) is too small, resulting in an insufficient working volume V2 of the high-pressure compression chamber. This prevents the high-pressure compression chamber from fully consuming the refrigerant discharged from the low-pressure compression chamber, leading to performance overkill. The excessively small minimum flow area S2 of the second exhaust port increases gas flow resistance and exhaust losses. The excessively large length T2 of the second exhaust port along the axial direction of the pump assembly increases the exhaust path and exhaust losses. Under the combined effect of the excessively small working volume V2 of the high-pressure compression chamber, the excessively small minimum flow area S2 of the second exhaust port, and the excessively large length T2 of the second exhaust port along the axial direction of the pump assembly, the exhaust resistance of the high-pressure compression chamber increases, leading to reduced compressor performance. Therefore, by rationally designing the relationship between the working volume V1 of the low-pressure compression chamber, the minimum flow area S1 of the first exhaust port, the axial length T1 of the first exhaust port along the pump body assembly, the working volume V2 of the high-pressure compression chamber, the axial length T2 of the second exhaust port along the pump body assembly, and the minimum flow area S2 of the second exhaust port, the exhaust velocity of the first exhaust port is made similar to that of the second exhaust port, reducing exhaust resistance, ensuring smooth compressor exhaust, and thus improving compressor performance.

[0010] According to some embodiments of the present invention, the diameter of the first exhaust port is D1 and the diameter of the second exhaust port is D2, satisfying: 0.25≤(D1×V2) / (D2×V2)≤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 V2 / V1, which satisfies: 0.4≤V2 / V1≤0.8.

[0012] According to some embodiments of the present invention, the pump body assembly is provided with an enthalpy injection hole communicating with the intermediate cavity, and the enthalpy injection hole is used for the enthalpy enhancement assembly to deliver 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, with two adjacent cavities connected through the connecting channel, and refrigerant flowing 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 partition assembly forms the first cavity of the intermediate cavity.

[0015] According to some embodiments of the present invention, the baffle assembly includes a first baffle and a second baffle arranged opposite to each other along the axial direction of the pump body assembly. The first baffle and the second baffle enclose the first cavity. The first baffle is connected to the first cylinder, and the second baffle is connected to the second cylinder. The first baffle 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 further 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 surround to form a second cavity of the intermediate cavity, the first cylinder is provided with the communicating channel, and the second cavity and the first cavity are connected through the communicating channel.

[0017] According to some embodiments of the present invention, multiple connecting channels are configured, and the multiple connecting channels are spaced apart around the axis of the pump body assembly, with each connecting channel connecting the first cavity and the second cavity at both ends respectively.

[0018] The compressor according to a second aspect of the present invention includes the pump assembly described in the above embodiments.

[0019] The refrigeration equipment according to a third aspect of the present invention includes the compressor described in the above embodiments.

[0020] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

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

[0022] Figure 1 This is a cross-sectional schematic diagram of a pump body assembly according to an embodiment of the present invention;

[0023] Figure 2 for Figure 1 A magnified view of part A in the middle;

[0024] Figure 3 for Figure 1 A magnified view of part B in the middle section;

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

[0026] Figure 5 This is a diagram showing the relationship between (V1×S1÷T1) / (V2×S2÷T2) and the compressor COP in one embodiment of the present invention.

[0027] Icon labels:

[0028] Axis O1, 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, enthalpy injection 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 enhancement assembly 500, exhaust pipe 510. Detailed Implementation

[0029] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0030] In the description of this utility model, it should be understood that the orientation descriptions, such as up, down, etc., are based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0031] In the description of this utility model, "multiple" refers to two or more. The use of "first" and "second" is for distinguishing technical features only and should not be construed as indicating or implying relative importance, or implicitly indicating the number of technical features or their sequential relationship.

[0032] In the description of this utility model, unless otherwise explicitly defined, terms such as "setting," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0033] In related technologies, compressors employ multi-stage compression technology to distribute the pressure ratio of each compression stage, ensuring the compression components operate within a more reasonable pressure ratio range, thereby improving the compressor's volumetric efficiency. Existing pump assemblies include a low-pressure compression chamber, an intermediate chamber, and a high-pressure compression chamber. The exhaust port of the low-pressure compression chamber connects to the intake port of the high-pressure compression chamber through the intermediate chamber. The refrigerant compressed in the low-pressure chamber is temporarily stored in the intermediate chamber for transition, and then drawn into the high-pressure compression chamber for secondary compression. This intermediate chamber design increases the refrigerant's exhaust path, leading to increased compressor exhaust losses and impacting compressor performance.

[0034] Reference Figure 1 , Figure 1 This is a cross-sectional schematic diagram of a pump body assembly according to an embodiment of the present invention. For example... Figure 1As shown, in one embodiment of the present invention, a pump body assembly includes 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 includes a first eccentric portion 210 and a second eccentric portion 220 spaced apart along the axial direction of the crankshaft 200. A first piston 230 is fitted onto the first eccentric portion 210, and a second piston 240 is fitted onto the second eccentric portion 220. The partition assembly 103 connects the first cylinder 102 and the second cylinder 104. The lower bearing 101 is connected to the lower end face of the first cylinder 102, and the upper bearing 105 is connected to the upper end face of the second cylinder 104. The first cylinder 102 is provided with a low-pressure compression chamber 110, and 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, and the second piston 240 is rotatably disposed in the high-pressure compression chamber 130. At least a portion of the intermediate chamber 120 is disposed in the partition assembly 103. The low-pressure compression chamber 110 is connected to the air intake of the high-pressure compression chamber 130 through the intermediate chamber 120. Understandably, when the pump assembly is working, refrigerant from outside the pump assembly is drawn into the low-pressure compression chamber 110 through the suction port. The refrigerant completes primary compression in the low-pressure compression chamber 110, and then is discharged into the intermediate chamber 120. The refrigerant in the intermediate chamber 120 is drawn into the high-pressure compression chamber 130 through the suction port. The refrigerant completes secondary 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 and discharge pulsations of the pump assembly, 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, the energy loss will be increased, and thus the performance of the compressor will be reduced. If the minimum flow area of ​​the exhaust port is too small, the gas flow resistance will be increased, the exhaust pressure will be increased, the exhaust loss will be increased, and thus the performance of the compressor will be reduced.

[0036] It should be noted that if the length of the exhaust port along the axial direction of the pump body assembly is too large, the exhaust path of the gas will increase, the exhaust loss of the compressor will increase, and thus reduce the performance of the compressor. If the length of the exhaust port along the axial direction of the pump body assembly is too small, the strength at the exhaust port will be insufficient, the exhaust port will be prone to deformation, resulting in increased exhaust pulsation, and thus 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. Both excessively high and low gas flow rates will affect the performance of the compressor.

[0038] Reference Figures 1 to 3 , Figure 2 for Figure 1 A magnified view of part A in the middle; Figure 2 for Figure 1 A partial enlarged view of part B. As shown in the figure, in this embodiment of the present invention, the working volume of the low-pressure compression chamber 110 is V1, the low-pressure compression chamber 110 has a first exhaust port 111, the minimum flow area of ​​the first exhaust port 111 is S1, and the length of the first exhaust port 111 along the axial direction of the pump body assembly is T1. The working volume of the high-pressure compression chamber 130 is V2, the high-pressure compression chamber 130 has a second exhaust port 131, the length of the second exhaust port 131 along the axial direction of the pump body assembly is T2, and the minimum flow area of ​​the second exhaust port 131 is S2, satisfying: U=(V1×S1÷T1) / (V2×S2÷T2), 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 remaining volume between the compression chamber and the piston rotatably installed inside the compression chamber, and the unit of flow area is mm. 2 The unit for length is mm, and the unit for working volume is cc. This unit will be used in all subsequent embodiments.

[0039] Understandably, with the working volume V1 of the low-pressure compression chamber 110, the minimum flow area S1 of the first exhaust port 111, and the axial length T1 of the first exhaust port 111 along the pump body assembly remaining constant, when U is less than 0.5, (V2×S2÷T2) becomes too large, resulting in an excessively large working volume V2 of the high-pressure compression chamber 130. This causes the refrigerant discharged from the low-pressure compression chamber 110 to be unable to be received by the high-pressure compression chamber 130 in a timely manner, increasing the pressure in the intermediate chamber 120 and increasing the exhaust back pressure of the low-pressure compression chamber 110. Furthermore, the excessively large minimum flow area S2 of the second exhaust port 131 leads to an excessively low gas velocity within the second exhaust port 131, while the excessively small axial length T2 of the second exhaust port 131 along the pump body assembly results in increased exhaust pulsation. This situation arises when the working volume V2 of the high-pressure compression chamber 130 is too large, the minimum flow area S2 of the second exhaust port 131 is too large, and the axial length T2 of the second exhaust port 131 along the pump body assembly is too small. Under the synergistic effect of the two factors, the gas velocity in the first exhaust port 111 is much greater than that in the second exhaust port 131, resulting in unsmooth compressor exhaust and reduced compressor performance. When U is greater than 5.6, (V2×S2÷T2) is too small, and the working volume V2 of the high-pressure compression chamber 130 is too small, causing the high-pressure compression chamber 130 to be unable to completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excess performance. The minimum flow area S2 of the second exhaust port 131 is too small, leading to increased gas flow resistance and exhaust loss. The length T2 of the second exhaust port 131 along the axial direction of the pump body assembly is too large, leading to an increased exhaust path and exhaust loss. Under the synergistic effect of the small working volume V2 of the high-pressure compression chamber 130, the small minimum flow area S2 of the second exhaust port 131, and the large length T2 of the second exhaust port 131 along the axial direction of the pump body assembly, the exhaust resistance of the high-pressure compression chamber 130 increases, resulting in reduced compressor performance. Therefore, by rationally designing the relationship between the working volume V1 of the low-pressure compression chamber 110, the minimum flow area S1 of the first exhaust port 111, the length T1 of the first exhaust port 111 along the axial direction of the pump body assembly, the working volume V2 of the high-pressure compression chamber 130, the length T2 of the second exhaust port 131 along the axial direction of the pump body assembly, and the minimum flow area S2 of the second exhaust port 131, the exhaust velocity of the first exhaust port 111 is made similar to that of the second exhaust port 131, reducing exhaust resistance, ensuring smooth compressor exhaust, and thus improving compressor performance.

[0040] Reference Figure 5 , Figure 5This diagram illustrates the relationship between U and the compressor's COP according to an embodiment of this invention. The bars in the diagram represent the performance improvement of the compressor under different U values, and the dashed lines represent the fitting curves of the performance improvement of the compressor under different U values. As shown, when the value of U gradually increases, within the range of 0.5 to 6, the compressor's COP first gradually increases and then decreases. Therefore, rationally designing the relationships between the working volume V1 of the low-pressure compression chamber 110, the minimum flow area S1 of the first exhaust port 111, the axial length T1 of the first exhaust port 111 along the pump assembly, the working volume V2 of the high-pressure compression chamber 130, the axial length T2 of the second exhaust port 131 along the pump assembly, and the minimum flow area S2 of the second exhaust port 131 can improve the compressor's performance. It should be noted that during cooling, COP refers to the ratio of the compressor's cooling capacity to its input power; during heating, it is COP+1. A higher COP value indicates higher compressor efficiency and greater energy savings.

[0041] In the embodiments of this utility model, the shapes of the first exhaust port 111 and the second exhaust port 131 are both circular structures. The diameter of the first exhaust port 111 is D1, and the diameter of the second exhaust port 131 is D2, satisfying the condition: 0.25 ≤ (D1×V2) / (D2×V2) ≤ 1.2. For example, (D1×V2) / (D2×V2) 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 rationally designing the relationship between the diameter D1 of the first exhaust port 111, the working volume V1 of the low-pressure compression chamber 110, the diameter D2 of the second exhaust port 131, and the working volume V2 of the high-pressure compression chamber 130, exhaust loss can be reduced and smooth exhaust of the compressor can be ensured, 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 residence time of the gas in the exhaust port will be prolonged, increasing energy loss and thus reducing the performance of the compressor. If the diameter of the exhaust port is too small, the gas flow resistance will be increased, leading to an increase in exhaust pressure and exhaust loss, thus reducing the performance of the compressor. With the diameter D1 of the first exhaust port 111 and the working volume V1 of the low-pressure compression chamber 110 remaining constant, when (D1×V2) / (D2×V2) is less than 0.25, the working volume V2 of the high-pressure compression chamber 130 is too small, causing the high-pressure compression chamber 130 to be unable to completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excess performance. Conversely, the diameter D2 of the second exhaust port 131 is too large, causing some gas in the high-pressure compression chamber 130 to flow back from the high-pressure side to the low-pressure side, increasing exhaust loss. Under the combined effect of the small working volume V2 of the high-pressure compression chamber 130 and the large diameter D2 of the second exhaust port 131, the exhaust... Increased gas loss and reduced compressor performance; when (D1×V2) / (D2×V2) is greater than 1.2, the working volume V2 of the high-pressure compression chamber 130 is too large, causing the refrigerant discharged from the low-pressure compression chamber 110 to be unable to be received by the high-pressure compression chamber 130 in time, increasing the pressure in the intermediate chamber 120, increasing the exhaust back pressure of the low-pressure compression chamber 110, and causing the diameter D2 of the second exhaust port 131 to be too small, resulting in increased gas flow resistance and increased exhaust loss. Under the combined effect of the excessively large working volume V2 of the high-pressure compression chamber 130 and the excessively small diameter D2 of the second exhaust port 131, the exhaust resistance increases, and the compressor exhaust is not smooth. Therefore, by rationally designing the relationship between the diameter D1 of the first exhaust port 111, the working volume V1 of the low-pressure compression chamber 110, the diameter D2 of the second exhaust port 131, and the working volume V2 of the high-pressure compression chamber 130, exhaust loss can be reduced and the compressor exhaust can be ensured to be smooth, thereby improving the performance of the compressor.

[0043] As another implementation, 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, without limitation.

[0044] In the embodiments of this utility model, 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 V2 / V1, satisfying: 0.4≤V2 / V1≤0.8. The unit of working volume is cc, for example, V2 / V1 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 / When V1 is less than 0.4, the working volume V1 of the low-pressure compression chamber 110 is too large, and the high-pressure compression chamber 130 cannot fully consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excess performance and reduced volumetric efficiency of the compressor. When V2 / V1 is greater than 0.8, for low-temperature heating conditions, the working volume V2 of the high-pressure compression chamber 130 is too large, which is equivalent to the working volume of the low-pressure compression chamber 110 being too small. This results in insufficient intake of the high-pressure compression chamber 130, insufficient heating capacity, and a poor user experience. Therefore, by rationally designing the ratio of the working volume of the high-pressure compression chamber 130 to that of the low-pressure compression chamber 110, intake and exhaust pulsations can be reduced, vibration and noise can be decreased, and the volumetric efficiency of the compressor can be improved.

[0045] Reference Figure 4 , Figure 4 This is a cross-sectional view of the compressor according to an embodiment of the present invention. For example... Figure 4 As shown in the embodiment of this utility model, the pump body assembly is provided with an enthalpy injection hole 140, which is connected to the intermediate cavity 120. The outlet pipe 510 of the enthalpy-increasing assembly 500 is inserted into the enthalpy injection 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 discharges 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 mix with the refrigerant in the intermediate cavity 120, and finally enter the interior of the high-pressure compression chamber 130 through the suction port of the high-pressure compression chamber 130. Therefore, the intermediate cavity 120 can fully mix the refrigerant inside it with the refrigerant of the enthalpy-increasing assembly 500, reducing the problem of excessive pulsation when the two refrigerants are mixed, and improving the mixing efficiency.

[0046] In another implementation, the enthalpy injection orifice 140 can also be connected to either the low-pressure compression chamber 110 or the high-pressure compression chamber 130. When the enthalpy injection orifice 140 is connected to the low-pressure compression chamber 110, the enthalpy-increasing component 500 can supply refrigerant to the low-pressure compression chamber 110, thereby increasing the exhaust volume of the low-pressure compression chamber 110. When the enthalpy injection orifice 140 is connected to the high-pressure compression chamber 130, the enthalpy-increasing component 500 can supply refrigerant to the high-pressure compression chamber 130, thereby increasing the exhaust volume of the high-pressure compression chamber 130. Further details will not be elaborated here. It is understood that the gaseous refrigerant used for replenishment by the enthalpy-increasing component 500 can be provided by a flash evaporator, which is installed in the circulation loop of the refrigeration or heating system. Taking a heating system as an example: After the liquid refrigerant releases heat in the condenser, it flows through the first throttling device. Under the action of the first throttling device, it changes from a completely liquid refrigerant to a gas-liquid mixture. The gas-liquid mixture then enters the flash evaporator. The gaseous refrigerant flows along the outlet of the flash evaporator to the enthalpy-increasing component 500, while 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 receiver. In another embodiment of this invention, the flash evaporator can also be replaced by a plate heat exchanger. That is, the refrigerant used for replenishing the gas in the enthalpy-increasing component 500 can also be provided by a plate heat exchanger. The appropriate solution is selected according to the actual situation.

[0047] In this embodiment of the present invention, the intermediate cavity 120 includes a first cavity 122, a second cavity 123, and a connecting channel 121. The two ends of the connecting channel 121 are respectively connected to the first cavity 122 and the second cavity 123. Since the working volume of the low-pressure compression cavity 110 is usually larger than the working volume of the high-pressure compression cavity 130, the low-pressure compression cavity 110 can exhaust gas to both end faces and then mix it into the high-pressure compression cavity 130. That is, the low-pressure compression cavity 110 can exhaust gas 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 reducing the input force required for compression in the high-pressure compression cavity 130210 and improving the energy efficiency of the compressor.

[0048] In an embodiment of this utility model, the pump body assembly further includes a lower muffler 106, which is connected to a lower bearing 101. A second cavity 123 is formed between the lower muffler 106 and the lower bearing 101. A first cavity 122 is formed within a partition member, and a connecting channel 121 is formed within the first cylinder 102. When the compressor is running, the low-pressure compression chamber 110 can discharge refrigerant to the second cavity 123, and then into the first cavity 122 through the connecting channel 121. Alternatively, the low-pressure compression chamber 110 can simultaneously discharge refrigerant to both the first cavity 122 and the second cavity 123 to improve exhaust efficiency.

[0049] In an embodiment of this utility model, 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 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 each other to form a first cavity 122. The first partition 1031 is connected to the upper end face of the first cylinder 102, and the second partition 1032 is connected to the lower end face of the second cylinder 104. The first partition 1031 and the second partition 1032 can be processed separately, which is beneficial to process and manufacture 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 has a petal-shaped structure and is arranged around the axis O1 of the pump body assembly. 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. This facilitates the processing and manufacturing of 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 connecting structure is provided between the first partition 1031 and the second partition 1032. This connecting structure is used to connect and fix the first partition 1031 and the second partition 1032. For example, the connecting structure includes a connector, which is a screw or bolt. The connector includes a rod and a head at one end of the rod. The rod passes through the second partition 1032 and is threadedly connected to the first partition 1031. The head is installed inside the second partition 1032, facilitating the connection and fixation of the first partition 1031 and the second partition 1032. Alternatively, the connector can be a pin. One end of the connector is fixedly connected to the first partition 1031, and the other end is fixedly connected to the second partition 1032. This also facilitates the connection and fixation of the first partition 1031 and the second partition 1032, and will not be elaborated further here.

[0052] It should be noted that there are multiple connectors arranged around the axis O1 of the pump body assembly, which can increase the connection stability between the first baffle 1031 and the second baffle 1032, which will not be described in detail here.

[0053] In this embodiment of the present invention, the first partition 1031 is provided with a first valve seat, and the first valve seat is provided with a first exhaust port 111. The low-pressure compression chamber 110 can discharge refrigerant into the first cavity 122 through the first valve seat. The lower bearing 101 is provided with a second valve seat, and 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 can enter 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 dual exhaust scheme, which can effectively reduce exhaust loss and improve the performance of the compressor.

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

[0055] In the embodiments of this utility model, multiple connecting channels 121 are configured, and the multiple connecting channels 121 are arranged at intervals around the axis O1 of the pump body assembly. By setting multiple connecting channels 121, the total flow area of ​​the multiple connecting channels 121130 is increased, which can reduce the flow rate of the refrigerant and thus reduce flow loss.

[0056] It is understandable that the more connecting channels 121 there are, the lower the radial strength of the first cylinder 102 will be. 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 communication channels 121 can also be configured to be one, and there is no limitation here.

[0058] For example Figure 4As shown, the compressor of the second aspect embodiment of this utility model includes a housing 300 and a pump assembly as described in the above embodiments. The housing 300 has an inner cavity 310, and the pump assembly is installed in the inner cavity 310. By employing the pump assembly of the above embodiments, refrigerant outside the pump assembly is drawn into the low-pressure compression chamber 110 from the suction port. The refrigerant completes primary compression in the low-pressure compression chamber 110, and then is discharged into the intermediate chamber 120. The refrigerant in the intermediate chamber 120 is drawn into the high-pressure compression chamber 130 from the suction port, and completes secondary 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 and discharge pulsations of the pump assembly, thereby improving the performance of the compressor. Since the working volume of the low-pressure compression chamber 110 is V1, the minimum flow area of ​​the first exhaust port 111 is S1, the length of the first exhaust port 111 along the axial direction of the pump body assembly is T1, the working volume of the high-pressure compression chamber 130 is V2, the length of the second exhaust port 131 along the axial direction of the pump body assembly is T2, and the minimum flow area of ​​the second exhaust port 131 is S2, the following conditions are met: U=(V1×S1÷T1) / (V2×S2÷T2), 0.5≤U≤5.6. When U is less than 0.5, (V2×S2÷T2) is too large. The working volume V2 of the high-pressure compression chamber 130 is too large, causing the refrigerant discharged from the low-pressure compression chamber 110 to be unable to be received by the high-pressure compression chamber 130 in time. This increases the pressure in the intermediate chamber 120, increases the exhaust back pressure of the low-pressure compression chamber 110, and causes the minimum flow area S2 of the second exhaust port 131 to be too large, resulting in a low gas velocity in the second exhaust port 131. Furthermore, the axial length T2 of the second exhaust port 131 along the pump assembly is too small, leading to increased exhaust pulsation. Under the combined effect of the excessively large working volume V2 of the high-pressure compression chamber 130, the excessively large minimum flow area S2 of the second exhaust port 131, and the excessively small axial length T2 of the second exhaust port 131 along the pump assembly, the gas velocity in the first exhaust port 111 is much greater than that in the second exhaust port 131. The flow rate is too low, and the compressor exhaust is not smooth, which leads to a decrease in compressor performance. When U is greater than 5.6, (V2×S2÷T2) is too small, and the working volume V2 of the high-pressure compression chamber 130 is too small, which means that the high-pressure compression chamber 130 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excess performance. The minimum flow area S2 of the second exhaust port 131 is too small, which leads to an increase in gas flow resistance and exhaust loss. The length T2 of the second exhaust port 131 along the axial direction of the pump body assembly is too large, which leads to an increase in the exhaust path and exhaust loss. Under the combined effect of the small working volume V2 of the high-pressure compression chamber 130, the small minimum flow area S2 of the second exhaust port 131, and the large length T2 of the second exhaust port 131 along the axial direction of the pump body assembly, the exhaust resistance of the high-pressure compression chamber 130 increases, which leads to a decrease in compressor performance.Therefore, by rationally designing the relationship between the working volume V1 of the low-pressure compression chamber 110, the minimum flow area S1 of the first exhaust port 111, the length T1 of the first exhaust port 111 along the axial direction of the pump body assembly, the working volume V2 of the high-pressure compression chamber 130, the length T2 of the second exhaust port 131 along the axial direction of the pump body assembly, and the minimum flow area S2 of the second exhaust port 131, the exhaust velocity of the first exhaust port 111 is made similar to that of the second exhaust port 131, reducing exhaust resistance, ensuring smooth compressor exhaust, and thus improving compressor performance.

[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 peripheral surface of the rotor 420 abuts against the inner peripheral surface of the housing 300. The rotor 420 is fixedly connected to the upper end of the crankshaft 200, and 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 embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0061] The refrigeration equipment according to the third aspect of this utility model includes the compressor described in the above embodiments. The refrigeration equipment can be a central air conditioning system, a packaged air conditioner, a split air conditioner, a ducted air conditioner, a window air conditioner, etc.

[0062] The embodiments of the present utility model have been described in detail above with reference to the accompanying drawings. However, the present utility model is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present utility model.

Claims

1. A pump body assembly, characterized in that, The device includes a low-pressure compression chamber, an intermediate chamber, and a high-pressure compression chamber. The low-pressure compression chamber has a first exhaust port, and the high-pressure compression chamber has a second exhaust port. The first exhaust port is connected to the intake port of the high-pressure compression chamber through the intermediate chamber. Wherein, the working volume of the low-pressure compression chamber is V1, the length of the first exhaust port along the axial direction of 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 length of the second exhaust port along the axial direction of 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 body 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, satisfying: 0.25≤(D1×V2) / (D2×V2)≤1.

2.

3. The pump body 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 body assembly according to claim 1, characterized in that: The pump body assembly is provided with an enthalpy injection hole that communicates with the intermediate cavity. The enthalpy injection hole is used to supply refrigerant to the intermediate cavity by the enthalpy enhancement assembly.

5. The pump body assembly according to claim 1, characterized in that: The intermediate cavity includes at least one connecting channel and at least two cavities, with two adjacent cavities connected by the connecting channel, and refrigerant flowing through each of the cavities through the connecting channel.

6. The pump body assembly according to claim 5, characterized in that: The pump body assembly includes a lower bearing, a first cylinder, a partition assembly, a second cylinder, and an upper bearing connected in sequence, with the first cavity forming the intermediate cavity within the partition assembly.

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

9. The pump body assembly according to claim 8, characterized in that: The communication channels are configured in multiple ways, and the multiple communication channels are arranged at intervals around the axis of the pump body assembly. The two ends of each communication channel are respectively connected to the first cavity and the second cavity.

10. A compressor, characterized in that, include: The pump assembly according to any one of claims 1-9.

11. A refrigeration device, characterized in that: Includes the compressor as described in claim 10.

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