Pump body assembly, compressor, and refrigeration device
Patent Information
- Application Number
- PCT/CN2025/144117
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- Priority Date
- 2025-04-18
- Filing Date
- 2025-12-19
- Publication Date
- 2026-10-22
Smart Images
Figure CN2025144117_22102026_PF_FP_ABST
Abstract
Description
Pump body assembly, compressor and refrigeration equipment Cross-references to related applications
[0001] This application claims priority to Chinese Patent Application No. 202510496352.9, filed on April 18, 2025, entitled "Pump Assembly, Compressor and Refrigeration Equipment", the entire contents of which are incorporated herein by reference. Technical Field
[0002] This application relates to the field of compressor technology, and in particular to a pump assembly, compressor and refrigeration equipment. Background Technology
[0003] Currently, pump assemblies employ multi-stage compression technology to distribute the pressure ratio of each stage, ensuring the compression components operate within a more reasonable pressure ratio range, thereby improving the compressor's volumetric efficiency. Existing pump assemblies consist of 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. However, the working volumes of the low-pressure compression chamber, intermediate chamber, and high-pressure compression chamber in existing pump assemblies are poorly designed, resulting in significant intake and exhaust pulsations in the compressor, negatively impacting its performance. Summary of the Invention
[0004] This application aims to address at least one of the technical problems existing in the prior art. To this end, this application proposes a pump body assembly that can reduce intake pulsation and exhaust pulsation, and improve compressor performance.
[0005] This application also proposes a compressor having the above-described pump body assembly.
[0006] This application also proposes a refrigeration device having the above-mentioned compressor.
[0007] The pump body assembly according to the first aspect of this application includes:
[0008] The first compression assembly includes a low-pressure compression chamber, a first cavity, and at least one communicating channel. The exhaust port of the low-pressure compression chamber is connected to the communicating channel through the first cavity.
[0009] The second compression assembly is equipped with a high-pressure compression chamber;
[0010] A partition assembly is connected between the first compression assembly and the second compression assembly. The partition assembly is provided with a second cavity, and the air intake of the high-pressure compression cavity is connected to the communication channel through the second cavity.
[0011] Wherein, the working volume of the low-pressure compression chamber is V1, the working volume of the high-pressure compression chamber is V2, the volume of the first chamber is V3, the volume of the second chamber is V4, the sum of the volumes of all the connecting channels is V5, and the sum of the minimum flow areas of all the connecting channels is S, satisfying: U = , 0.015≤U≤0.08.
[0012] The pump assembly according to the embodiments of this application has at least the following beneficial effects:
[0013] When the pump assembly is working, refrigerant from outside the pump assembly is drawn into the low-pressure compression chamber through the suction port. The refrigerant undergoes primary compression in the low-pressure compression chamber, and then is discharged into the first chamber through the exhaust port. The refrigerant in the first chamber flows into the second chamber through the connecting channel. The refrigerant in the second chamber is drawn into the high-pressure compression chamber through the suction port, where it undergoes secondary compression. This ensures that the low-pressure and high-pressure compression chambers are within a reasonable pressure ratio range, improving the compressor's volumetric efficiency. Furthermore, it effectively reduces suction and exhaust pulsations in the pump assembly, thereby improving compressor performance. Since the working volume of the low-pressure compression chamber is V1, the working volume of the high-pressure compression chamber is V2, the volume of the first chamber is V3, the volume of the second chamber is V4, the sum of the volumes of all connecting channels is V5, and the sum of the minimum flow areas of all connecting channels is S, the following condition is met: U = When U is less than 0.015, the sum of the volumes of the first cavity, the second cavity, and all connecting channels (V3+V4+V5) is too small. The gas discharged from the low-pressure compression chamber cannot diffuse sufficiently in the intermediate cavity, leading to a local pressure increase at the intake port of the high-pressure compression chamber. This is equivalent to increasing the exhaust resistance of the low-pressure compression chamber. The sum of the minimum flow areas of all connecting channels (S) is too large, resulting in low gas flow resistance. The exhaust pressure fluctuations of the low-pressure compression chamber are directly transmitted to the high-pressure compression chamber, affecting the stable intake of the high-pressure compression chamber. Furthermore, when U is too small, the sum of the volumes of the first cavity, the second cavity, and all connecting channels (V3+V4+V5) is also too small. When the total flow area S is too large, the compressor's intake and exhaust pulsations increase, affecting its performance. When U is greater than 0.008, the sum of the volumes of the first chamber, the second chamber, and all connecting channels (V3+V4+V5) is too large. This prolongs the transition time between the gas exhaust from the low-pressure compression chamber and the gas intake from the high-pressure compression chamber. Furthermore, the pressure rises slowly after the gas discharged from the low-pressure compression chamber enters the excessively large intermediate chamber. When the total minimum flow area S of all connecting channels is too small, the gas cannot smoothly enter the second chamber from the first chamber, leading to an increase in the exhaust back pressure of the low-pressure compression chamber and a delayed or insufficient intake flow in the high-pressure compression chamber. This increases the compressor's intake and exhaust pulsations, affecting its performance. Therefore, by rationally designing the relationship between the working volume V1 of the low-pressure compression chamber, the working volume V2 of the high-pressure compression chamber, the volume V3 of the first chamber, the volume V4 of the second chamber, the total volume V5 of all connecting channels, and the total minimum flow area S of all connecting channels, the structural layout of the low-pressure compression chamber, the first chamber, the connecting channels, the second chamber, and the high-pressure compression chamber can be optimized, reducing the intake and exhaust pulsations of the compressor and thus improving the performance of the compressor.
[0014] According to some embodiments of this application, the ratio of the volume of the first cavity to the volume of the second cavity is V3 / V4, which satisfies: 0.2≤V3 / V4≤5.
[0015] According to some embodiments of this application, the ratio of the working volume of the high-pressure compression chamber to the volume of the low-pressure compression chamber is V2 / V1, satisfying: 0.4 ≤ V2 / V1 ≤ 0.8
[0016] According to some embodiments of this application, the first compression assembly includes a first cylinder, a lower bearing, and a lower muffler. The low-pressure compression chamber and the communicating channel are respectively located in the first cylinder. The lower bearing and the lower muffler are both connected to the first cylinder. The lower bearing and the lower muffler enclose each other to form the first cavity. The partition assembly is located on the side of the first cylinder away from the lower bearing.
[0017] According to some embodiments of this application, the second compression assembly includes a second cylinder, an upper bearing, and an upper muffler. The high-pressure compression chamber is located inside the second cylinder. The upper bearing and the upper muffler are both connected to the second cylinder. The partition assembly is located on the side of the second cylinder away from the upper bearing.
[0018] According to some embodiments of this application, the baffle assembly includes a first baffle and a second baffle disposed opposite to each other along the axial direction of the pump body assembly, the first baffle and the second baffle enclosing the second cavity, the first baffle being connected to the first compression assembly, and the second baffle being connected to the second compression assembly.
[0019] According to some embodiments of this application, a plurality of communication channels are configured, and the plurality of communication channels are spaced apart around the axis of the pump body assembly, with each communication channel connecting the first cavity and the second cavity at both ends respectively.
[0020] The compressor according to a second aspect of this application includes a first housing and a pump assembly as described in the above embodiments, the pump assembly being installed within the first housing.
[0021] According to some embodiments of this application, the compressor further includes an enthalpy-increasing component, which is installed outside the first housing. The first compression component is provided with an enthalpy-injection port communicating with the communicating channel. The enthalpy-increasing component includes an intake pipe that passes through the first housing and extends into the enthalpy-injection port. The enthalpy-increasing component delivers refrigerant to the second cavity through the enthalpy-injection port.
[0022] According to some embodiments of this application, the enthalpy-enhancing component further includes a second housing, the end of the air intake pipe away from the first housing extends into the second housing, the volume of the second housing is V6, and the minimum diameter of the injection enthalpy orifice is D, satisfying: 0.02 ≤ ≤11.11.
[0023] According to some embodiments of this application, the enthalpy-increasing component further includes a second housing, and the end of the intake pipe away from the first housing extends into the second housing, the volume of the second housing being V6, satisfying: ≤3, or, ≥15.
[0024] The refrigeration device according to a third aspect of this application includes the compressor described in the above embodiments.
[0025] Additional aspects and advantages of this application 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 this application. Attached Figure Description
[0026] The present application will be further described below with reference to the accompanying drawings and embodiments, wherein:
[0027] Figure 1 is a cross-sectional schematic diagram of a pump body assembly according to an embodiment of this application;
[0028] Figure 2 is a cross-sectional schematic diagram of a compressor according to an embodiment of this application;
[0029] Figure 3 is a cross-sectional view of line AA in Figure 3;
[0030] Figure 4 is a cross-sectional schematic diagram of a compressor according to another embodiment of this application; and
[0031] Figure 5 is a diagram showing the relationship between U and compressor COP in one embodiment of this application.
[0032] Icon labels:
[0033] Axis O1, first cylinder 101, lower bearing 102, lower muffler 103, low-pressure compression chamber 110, first cavity 120, connecting channel 130, injection enthalpy hole 140, second cylinder 201, upper bearing 202, upper muffler 203, high-pressure compression chamber 210, third cavity 220, partition assembly 300, second cavity 301, first partition 310, second partition 320, crankshaft 400, first eccentric part 410, second eccentric part 420, first piston 510, second piston 520, first housing 600, inner cavity 610, second housing 710, intake pipe 720, filter screen 730, air supply pipe 740, motor assembly 800, stator 810, rotor 820. Embodiments of the present invention
[0034] The embodiments of this application 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 application, and should not be construed as limiting this application.
[0035] In the description of this application, it should be understood that the orientation descriptions, such as up, down, etc., are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application 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, and therefore should not be construed as a limitation of this application.
[0036] In the description of this application, "multiple" refers to two or more. The use of "first" and "second" is for the purpose of distinguishing technical features only and should not be construed as indicating or implying relative importance, or implicitly indicating the number of technical features indicated, or the order in which the technical features are indicated.
[0037] In the description of this application, unless otherwise expressly defined, terms such as "setup," "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 application in conjunction with the specific content of the technical solution.
[0038] In related technologies, the pump assembly employs multi-stage compression technology to distribute the pressure ratio of each compression stage, ensuring the compression assembly operates 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. The working volumes of the low-pressure compression chamber, intermediate chamber, and high-pressure compression chamber in existing pump assemblies are poorly designed, resulting in significant intake and exhaust pulsations in the compressor, affecting its performance. It is understood that the compressor's pressure ratio is generally the ratio of the inlet and outlet pressures, but in this case, there are pressure ratios for different compression chambers.
[0039] For example, referring to Figures 1 to 3, Figure 1 is a cross-sectional schematic diagram of a pump body assembly according to an embodiment of this application. As shown in Figure 1, the pump body assembly according to an embodiment of this application includes a crankshaft 400, a first compression assembly, a second compression assembly, and a baffle assembly 300. Along the axial direction of the crankshaft 400, the first compression assembly, the baffle assembly 300, and the second compression assembly are sequentially connected. The first compression assembly has a low-pressure compression chamber 110, a first cavity 120, and multiple communicating channels 130. The exhaust port of the low-pressure compression chamber 110 and the communicating channels 130 are respectively connected to the first cavity 120. The second compression assembly has a high-pressure compression chamber 210, and the baffle assembly 300 has a second cavity 301. The intake port of the high-pressure compression chamber 210 and the communicating channels 130 are respectively connected to the second cavity 301. When the pump body assembly is working, the external cooling... The refrigerant is drawn into the low-pressure compression chamber 110 through the intake port. Within the low-pressure compression chamber 110, the refrigerant undergoes primary compression. Then, it is discharged into the first chamber 120 through the exhaust port of the low-pressure compression chamber 110. The refrigerant in the first chamber 120 flows into the second chamber 301 through the connecting channel 130. The refrigerant in the second chamber 301 is drawn into the high-pressure compression chamber 210 through the intake port. Within the high-pressure compression chamber 210, the refrigerant undergoes secondary compression. On one hand, the low-pressure compression chamber 110 and the high-pressure compression chamber 210 are within a reasonable pressure ratio range, which improves the volumetric efficiency of the compressor. On the other hand, it effectively reduces the intake and exhaust pulsations of the pump assembly, thereby improving the performance of the compressor.
[0040] It should be noted that, along the axial direction of the crankshaft 400, the crankshaft 400 includes a first eccentric part 410 and a second eccentric part 420 spaced apart. The first eccentric part 410 is fitted with a first piston 510, and the second eccentric part 420 is fitted with a second piston 520. The first piston 510 is rotatably disposed in the low-pressure compression chamber 110, and the second piston 520 is rotatably disposed in the high-pressure compression chamber 210.
[0041] It should be noted that the axis O1 of the pump body assembly coincides with the axis of the crankshaft 400, which will not be described in detail here.
[0042] It should be noted that the first cavity 120, the second cavity 301 and the connecting channel 130 constitute an intermediate cavity. When the refrigerant flows in the intermediate cavity, the refrigerant can be cooled to a certain extent, which helps to reduce the input force required for compression in the high-pressure compression cavity 210 and improve the energy efficiency of the compressor.
[0043] For example, as shown in Figure 1, in the embodiment of this application, the working volume of the low-pressure compression chamber 110 is V1, the working volume of the high-pressure compression chamber 210 is V2, the volume of the first chamber 120 is V3, the volume of the second chamber 301 is V4, the sum of the volumes of all connecting channels 130 is V5, and the sum of the minimum flow areas of all connecting channels 130 is S, satisfying: U = 0.015 ≤ U ≤ 0.08, for example, U can be 0.45, 0.5, 0.8, 1, 1.5, 2, 2.5, 3, etc. It should be noted that the working volume usually refers to the remaining volume between the compression chamber and the piston that is rotated and installed inside the compression chamber. The unit of working volume is cc, and the unit of flow area is mm. 2 This unit will be used in all subsequent embodiments.
[0044] It should be noted that when there is one connecting channel 130, the total volume V5 of all connecting channels 130 refers to the volume of a single connecting channel 130, and the total minimum flow area S of all connecting channels 130 refers to the minimum flow area of a single connecting channel 130. When there are multiple connecting channels 130, the total volume V5 of all connecting channels 130 refers to the sum of the volumes of multiple connecting channels 130, and the total minimum flow area S of all connecting channels 130 refers to the sum of the minimum flow areas of multiple connecting channels 130. The volume of each connecting channel 130 may be equal or unequal, and the minimum flow area of each connecting channel 130 may be equal or unequal.
[0045] It should be noted that if the ratio of the working volume of the high-pressure compression chamber to that of the low-pressure compression chamber, V2 / V1, is too small, the working volume V1 of the low-pressure compression chamber 110 will be too large. This means the high-pressure compression chamber 210 cannot fully consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excess performance and reduced volumetric efficiency of the compressor. Conversely, if the ratio of the working volume of the high-pressure compression chamber to that of the low-pressure compression chamber, V2, is too large for low-temperature heating conditions. This is equivalent to the working volume of the low-pressure compression chamber 110 being too small, leading to insufficient air intake and heating capacity in the high-pressure compression chamber 210, resulting in a poor user experience.
[0046] It should be noted that if the sum of the volumes of the first chamber 120, the second chamber 301, and all the connecting channels 130 (V3+V4+V5) is too large, the transition time between the gas exhaust from the low-pressure compression chamber 110 and the gas intake from the high-pressure compression chamber 210 will be prolonged. Furthermore, the pressure rise will be slow after the gas exhaust from the low-pressure compression chamber 110 enters the excessively large intermediate chamber, increasing the compressor's intake and exhaust pulsations and affecting its performance. Conversely, if the sum of the volumes of the first chamber 120, the second chamber 301, and all the connecting channels 130 (V3+V4+V5) is too small, the gas exhaust from the low-pressure compression chamber 110 cannot diffuse sufficiently in the intermediate chamber, leading to a localized pressure increase at the intake port of the high-pressure compression chamber 210. This is equivalent to increasing the exhaust resistance of the low-pressure compression chamber 110. An excessively small intermediate chamber will result in insufficient gas supply during the intake of the high-pressure compression chamber 210, causing intermittent intake and increasing the compressor's intake and exhaust pulsations, thus affecting its performance.
[0047] It should be noted that if the sum of the minimum flow areas S of all connecting channels 130 is too large, the gas flow resistance is small, and the exhaust pressure fluctuation of the low-pressure compression chamber 110 is directly transmitted to the high-pressure compression chamber 210, affecting the stable intake of the high-pressure compression chamber 210. If the sum of the minimum flow areas S of all connecting channels 130 is too small, the gas cannot smoothly enter the second chamber 301 from the first chamber 120, resulting in an increase in the exhaust back pressure of the low-pressure compression chamber 110, and the intake of the high-pressure compression chamber 210 is delayed or insufficient, affecting the performance of the compressor.
[0048] Understandably, with the working volumes of the low-pressure compression chamber 110 and the high-pressure compression chamber 210 remaining constant, when U is less than 0.015, the sum of the volumes of the first chamber 120, the second chamber 301, and all connecting channels 130 (V3+V4+V5) is too small. This results in insufficient diffusion of the gas discharged from the low-pressure compression chamber 110 within the intermediate chamber, leading to a localized pressure increase at the intake port of the high-pressure compression chamber 210. This is equivalent to increasing the exhaust resistance of the low-pressure compression chamber 110. Conversely, the sum of the minimum flow areas of all connecting channels 130 is too large, resulting in low gas flow resistance. Consequently, pressure fluctuations in the low-pressure compression chamber 110 are directly transmitted to the high-pressure compression chamber 210, affecting its stable intake. The sum of the volumes of the first chamber 120, the second chamber 301, and all connecting channels 130 (V3+V4+V5) is insufficient. When V5 is too small, the combined effect of the excessively large sum of the minimum flow areas of all connecting channels 130 increases the suction and discharge pulsations of the compressor, affecting its performance. When U is greater than 0.08, the sum of the volumes of the first chamber 120, the second chamber 301, and all connecting channels 130 (V3+V4+V5) is too large. This prolongs the transition time between the gas discharge from the low-pressure compression chamber 110 and the gas intake from the high-pressure compression chamber 210. Furthermore, the pressure rises slowly after the gas discharged from the low-pressure compression chamber 110 enters the excessively large intermediate chamber. When the sum of the minimum flow areas of all connecting channels 130 is too small, the gas cannot smoothly enter the second chamber 301 from the first chamber 120, resulting in an increase in the back pressure of the low-pressure compression chamber 110 and a delayed or insufficient flow rate in the high-pressure compression chamber 210. This increases the suction and discharge pulsations of the compressor, affecting its performance. Therefore, by rationally designing the relationship between the working volume V1 of the low-pressure compression chamber 110, the working volume V2 of the high-pressure compression chamber 210, the volume V3 of the first chamber 120, the volume V4 of the second chamber 301, the sum of the volumes of all connecting channels 130 V5, and the sum of the minimum flow areas of all connecting channels 130 S, the structural layout of the low-pressure compression chamber 110, the first chamber 120, the connecting channels 130, the second chamber 301, and the high-pressure compression chamber 210 can be optimized, reducing the intake and exhaust pulsations of the compressor and thus improving the performance of the compressor.
[0049] Referring to Figure 5, which is a graph showing the relationship between U and the compressor COP according to an embodiment of this application, the values in Figure 5 represent the compressor performance improvement at different U values, and the dashed lines in Figure 5 represent the fitting curves of multiple bars. As shown in the figure, when the value of U gradually increases, the compressor COP improvement gradually increases and then decreases within the range of 0.015 to 0.08. Therefore, by rationally designing the relationship between the working volume of the low-pressure compression chamber 110, the working volume of the high-pressure compression chamber 210, the volume of the first chamber 120, the volume of the second chamber 301, the sum of the volumes of all connecting channels 130, and the sum of the minimum flow areas of all connecting channels 130, the compressor performance can be improved. It should be noted that during cooling, COP refers to the ratio of the compressor's cooling capacity to the input power; during heating, it is COP+1. The higher the COP value, the higher the compressor efficiency and the more energy-saving it is.
[0050] In the embodiments of this application, the ratio of the volume of the first cavity 120 to the volume of the second cavity 301 is V3 / V4, which satisfies: 0.2≤V3 / V4≤5, so that the gas pressure in the first cavity 120 is similar to the gas pressure in the second cavity 301, thereby reducing the pressure fluctuation in the intermediate cavity. This helps to reduce the intake pulsation of the high-pressure compression cavity 210 and the exhaust pulsation of the low-pressure compression cavity 110, and can improve the performance of the compressor.
[0051] For example, when V3 / V4 is less than 0.2, the volume of the first chamber 120 is too small. After the low-pressure compression chamber 110 discharges gas, it quickly enters the second chamber 301. However, the second chamber 301 is too large, making it difficult to quickly establish a stable pressure. Furthermore, the large volume of the second chamber 301 causes the pressure to rise slowly after the gas flows into the first chamber 120, resulting in delayed intake of the high-pressure compression chamber 210, which is not conducive to the intake of the high-pressure compression chamber 210. When V3 / V4 is greater than 5, the volume of the first chamber 120 is too large, and the pressure builds up slowly after the gas is discharged, resulting in increased exhaust resistance of the low-pressure compression chamber 110 and increased exhaust pulsation of the low-pressure compression chamber 110. The heating volume of the second chamber 301 is too small, and the pressure changes rapidly when the high-pressure compression chamber 210 is intake, resulting in discontinuous intake of the high-pressure compression chamber 210 and exhaust pulsation of the high-pressure compression chamber 210, which affects the performance of the compressor. Therefore, by rationally designing the relationship between the volume of the first cavity 120 and the volume of the second cavity 301, the gas pressure in the first cavity 120 is made similar to that in the second cavity 301, thereby reducing pressure fluctuations in the intermediate cavity, which helps to reduce the intake pulsation of the high-pressure compression chamber 210 and improves the performance of the compressor.
[0052] In the embodiments of this application, the ratio of the displacement of the high-pressure compression chamber 210 to the displacement of the low-pressure compression chamber 110 is V2 / V1, satisfying: 0.4≤V2 / V1≤0.8, where the unit of displacement is cc. For example, V2 / V1 can be 0.4, 0.5, 0.6, 0.7, or 0.8. Taking the displacement of the high-pressure compression chamber 210 as an example, when V2 / V1 is less than 0.4, the displacement of the low-pressure compression chamber 110 is too large, and the high-pressure compression chamber 210 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excess performance and a decrease in the volumetric efficiency of the compressor. When V2 / V1 is greater than 0.8, for low-temperature heating conditions, the displacement of the low-pressure compression chamber 110 is too small, and the intake volume of the high-pressure compression chamber 210 is too small, resulting in a decrease in the heating capacity of the compressor and a poor user experience. Therefore, by rationally designing the ratio of the displacement of the high-pressure compression chamber 210 to the displacement of the low-pressure compression chamber 110, it is possible to reduce intake pulsation and exhaust pulsation, reduce vibration and noise, and improve the volumetric efficiency of the compressor.
[0053] In the embodiments of this application, the first compression assembly includes a first cylinder 101, a lower bearing 102, and a lower muffler 103. The lower bearing 102 is connected to the lower end face of the first cylinder 101, and the lower muffler 103 is connected to the lower bearing 102. The lower bearing 102 and the lower muffler 103 enclose a first cavity 120. The low-pressure compression cavity 110 and the connecting channel 130 are respectively located in the first cylinder 101. The refrigerant in the low-pressure compression cavity 110 enters the first cavity 120, the connecting channel 130, and the second cavity 301 in sequence, and finally enters the high-pressure compression cavity 210, which helps to reduce exhaust pulsation and improve the performance of the compressor.
[0054] In the embodiments of this application, the second compression assembly includes a second cylinder 201, an upper bearing 202, and an upper muffler 203. The lower end face of the partition assembly 300 is connected to the upper end face of the first cylinder 101, and the upper end face of the partition assembly 300 is connected to the lower end face of the second cylinder 201. The upper bearing 202 is connected to the upper end face of the second cylinder 201, and the upper muffler 203 is connected to the upper bearing 202. A third cavity 220 is formed between the upper bearing 202 and the upper muffler 203. The exhaust port of the high-pressure compression chamber 210 is connected to the third cavity 220. The refrigerant discharged from the high-pressure compression chamber 210 can enter the third cavity 220 and then be discharged into the inner cavity 610 of the first housing 600 of the compressor, which helps to reduce exhaust noise and improve the user experience.
[0055] It is understood that the lower bearing 102 is provided with a valve seat, allowing the refrigerant in the low-pressure compression chamber 110 to enter the first chamber 120 through the valve seat. In another embodiment of this application, both the lower bearing 102 and the partition assembly 300 are provided with valve seats, allowing the refrigerant in the low-pressure compression chamber 110 to enter the first chamber 120 and the second chamber 301 through the two valve seats respectively. That is, the low-pressure compression chamber 110 adopts a dual-exhaust scheme, which can effectively reduce exhaust losses and improve the performance of the compressor.
[0056] In the embodiments of this application, the partition assembly 300 includes a first partition 310 and a second partition 320. The first partition 310 and the second partition 320 are arranged opposite to each other along the axial direction of the pump body assembly. The first partition 310 is located below the second partition 320. The first partition 310 and the second partition 320 enclose each other to form a second cavity 301. The first partition 310 is connected to the first compression assembly, and the second partition 320 is connected to the second compression assembly. The first partition 310 and the second partition 320 can be processed separately, which is beneficial to process and manufacture the second cavity 301 on the partition assembly 300 and can reduce the processing and manufacturing cost of the partition assembly 300.
[0057] For example, the second cavity 301 has a petal-shaped structure and is arranged around the axis O1 of the pump body assembly. By dividing the partition assembly 300 into a first partition 310 and a second partition 320, the first partition 310 and the second partition 320 can be processed separately, which is beneficial to process and manufacture the second cavity 301 on the partition assembly 300 and can reduce the processing and manufacturing cost of the partition assembly 300.
[0058] It should be noted that a connecting structure is provided between the first partition 310 and the second partition 320. This connecting structure is used to connect and fix the first partition 310 and the second partition 320. 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 320 and is threadedly connected to the first partition 310. The head is installed inside the second partition 320, facilitating the connection and fixation of the first partition 310 and the second partition 320. Alternatively, the connector can be a pin. One end of the connector is fixedly connected to the first partition 310, and the other end is fixedly connected to the second partition 320. This also facilitates the connection and fixation of the first partition 310 and the second partition 320, and will not be elaborated further here.
[0059] 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 310 and the second baffle 320, which will not be described in detail here.
[0060] Referring to Figures 2 and 3, Figure 2 is a cross-sectional schematic diagram of a compressor according to an embodiment of this application, and Figure 3 is a cross-sectional view along line AA in Figure 2. In the embodiment of this application, multiple connecting channels 130 are configured, and the multiple connecting channels 130 are spaced apart around the axis O1 of the pump body assembly. The two ends of each connecting channel 130 are respectively connected to the first cavity 120 and the second cavity 301. By setting multiple connecting channels 130, the total flow area of the multiple connecting channels 130 is increased, which can reduce the flow rate of the refrigerant and thus reduce flow loss.
[0061] It is understandable that the more connecting channels 130 there are, the lower the radial strength of the first cylinder 101 will be. In this embodiment, in order to ensure the radial strength of the first cylinder 101, the number of connecting channels 130 is configured to be less than or equal to 5, for example, the number of connecting channels 130 is 2, 3, 4, 5, etc.
[0062] As another implementation, the number of communication channels 130 can also be configured to be one, and there is no limitation here.
[0063] For example, as shown in FIG2, the compressor of the second aspect embodiment of this application includes a first housing 600 and a pump assembly of the above embodiments. The first housing 600 has an inner cavity 610, and the pump assembly is installed in the inner cavity 610. By employing the pump assembly described in the above embodiment, when the pump assembly is in operation, refrigerant outside the pump assembly is drawn into the low-pressure compression chamber 110 through the intake port 111. The refrigerant completes primary compression in the low-pressure compression chamber 110. Afterward, the refrigerant is discharged into the first chamber 120 through the exhaust port of the low-pressure compression chamber 110. The refrigerant in the first chamber 120 flows into the second chamber 301 through the connecting channel 130. The refrigerant in the second chamber 301 is drawn into the high-pressure compression chamber 210 through the intake port. The refrigerant completes secondary compression in the high-pressure compression chamber 210. On the one hand, the low-pressure compression chamber 110 and the high-pressure compression chamber 210 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 intake pulsation and exhaust pulsation of the pump assembly.Since the working volume of the low-pressure compression chamber 110 is V1, the working volume of the high-pressure compression chamber 210 is V2, the volume of the first chamber 120 is V3, the volume of the second chamber 301 is V4, the sum of the volumes of all connecting channels 130 is V5, and the sum of the minimum flow areas of all connecting channels 130 is S, the following conditions are met: U = V2 × (V3 + V4 + V5) / (V1 × S), 0.015 ≤ U ≤ 0.08. When U is less than 0.015, the volume of the first chamber 120 and the second chamber 301... If the total volume of the low-pressure compression chamber 110 and the sum of the volumes of all connecting channels 130 (V3+V4+V5) is too small, the gas discharged from the low-pressure compression chamber 110 cannot diffuse sufficiently in the intermediate chamber, resulting in a local pressure increase at the intake port of the high-pressure compression chamber 210. This is equivalent to increasing the exhaust resistance of the low-pressure compression chamber 110. If the total minimum flow area of all connecting channels 130 is too large, the gas flow resistance is small, and the exhaust pressure fluctuation of the low-pressure compression chamber 110 is directly transmitted to the high-pressure compression chamber 210, affecting the stable intake of the high-pressure compression chamber 210. When the sum of the volumes of the first cavity 120, the second cavity 301, and all connecting channels 130 (V3+V4+V5) is too small, and the sum of the minimum flow areas of all connecting channels 130 is too large, the compressor's intake and exhaust pulsations increase, affecting the compressor's performance. When U is greater than 0.008, the sum of the volumes of the first cavity 120, the second cavity 301, and all connecting channels 130 (V3+V4+V5) is too large. The large size of the intermediate chamber results in a prolonged transition time between the gas exhaust from the low-pressure compression chamber 110 and the gas intake from the high-pressure compression chamber 210. Furthermore, the gas exhaust from the low-pressure compression chamber 110 enters the excessively large intermediate chamber, causing a slow pressure rise. The sum of the minimum flow areas of all connecting channels 130 is too small, preventing the gas from smoothly entering the second chamber 301 from the first chamber 120. This leads to an increase in the exhaust back pressure of the low-pressure compression chamber 110 and a delayed or insufficient intake flow in the high-pressure compression chamber 210. Consequently, the intake and exhaust pulsations of the compressor increase, affecting the compressor's performance. Therefore, by rationally designing the relationship between the working volume V1 of the low-pressure compression chamber 110, the working volume V2 of the high-pressure compression chamber 210, the volume V3 of the first chamber 120, the volume V4 of the second chamber 301, the sum of the volumes of all connecting channels 130 V5, and the sum of the minimum flow areas of all connecting channels 130 S, the structural layout of the low-pressure compression chamber 110, the first chamber 120, the connecting channels 130, the second chamber 301, and the high-pressure compression chamber 210 can be optimized, reducing the intake and exhaust pulsations of the compressor and thus improving the performance of the compressor.
[0064] For example, as shown in Figure 1, in an embodiment of this application, the first cylinder 101 is provided with an enthalpy injection hole 140, which is connected to the connecting channel 130. The compressor also includes an enthalpy enhancement component, which is installed on the outside of the first housing 600. The enthalpy enhancement component includes a second housing 710 and an intake pipe 720. The second housing 710 is fixedly connected to the first housing 600. One end of the intake pipe 720 passes through the first housing 600 and extends into the enthalpy injection hole 140. The intake pipe 720 is fixedly connected to the first cylinder 101. The other end of the intake pipe 720 extends into the second housing 710. The enthalpy enhancement component delivers refrigerant to the second cavity 301 through the enthalpy injection hole 140. Understandably, since the low-pressure compression chamber 110 discharges refrigerant into the second chamber 301 after compressing the refrigerant, the refrigerant supplied to the second chamber 301 by the enthalpy-enhancing component 700 can mix with the refrigerant in the second chamber 301, and finally enter the interior of the high-pressure compression chamber 210 through the suction port. Therefore, the second chamber 301 can ensure that the refrigerant inside it and the refrigerant in the enthalpy-enhancing component 700 are fully mixed, reducing the problem of excessive pulsation when the two refrigerants are mixed and improving the mixing efficiency.
[0065] It is understandable that the enthalpy injection hole 140 can also be set on the lower bearing 102, or the enthalpy injection hole 140 can be directly set on the partition assembly 300, as long as it can facilitate the enthalpy increasing assembly to deliver refrigerant to the second cavity 301, and there are no restrictions here.
[0066] It should be noted that the enthalpy enhancement component also includes a filter 730, which is installed inside the second housing 710. The filter 730 blocks one end of the intake pipe 720 to filter impurities and improve the service life of the pump assembly.
[0067] Referring to Figure 4, which is a cross-sectional schematic diagram of a compressor according to another embodiment of this application, the enthalpy-increasing assembly includes an intake pipe 720 and a supplementary air pipe 740. One end of the intake pipe 720 passes through the first housing 600 and is fixedly connected to the first cylinder 101. The other end of the intake pipe 720 extends to the outside of the first housing 600. The supplementary air pipe 740 is installed on the outside of the first housing 600. One end of the supplementary air pipe 740 is inserted into the end of the intake pipe 720 away from the first housing 600. A filter screen 730 is provided inside the end of the supplementary air pipe 740 away from the intake pipe 720. The filter screen 730 is used to filter impurities and can also facilitate the delivery of refrigerant to the second cavity 301. No limitation is made here.
[0068] In the embodiments of this application, the volume of the second housing 710 is V6, the minimum diameter of the injection enthalpy orifice 140 is D, and the working volume V1 of the low-pressure compression chamber 110, the working volume V2 of the high-pressure compression chamber 210, the volume V6 of the second housing 710, and the minimum diameter D of the injection enthalpy orifice 140 satisfy the following relationship: 0.02 ≤ ≤11.11 can increase the amount of gas supplied to the second chamber 301 and reduce gas supply pulsation, which can reduce the flow loss of the refrigerant supplied by the enthalpy enhancement component, thereby improving the performance of the compressor.
[0069] For example, with the working volume V1 of the low-pressure compression chamber 110 and the working volume V2 of the high-pressure compression chamber 210 remaining unchanged, when When the volume V6 of the second housing 710 is less than 0.02, the enthalpy-increasing component cannot store enough refrigerant. During peak gas supply periods (such as high-frequency operation), the enthalpy-increasing component supplies insufficient gas, resulting in insufficient gas supply to the second cavity 301. The minimum diameter D of the enthalpy-increasing orifice 140 is too large, meaning the minimum flow area of the enthalpy-increasing orifice 140 is too large, leading to excessively low refrigerant pressure supplied by the enthalpy-increasing component. This results in a large pressure difference between the refrigerant supplied by the enthalpy-increasing component and the refrigerant in the connecting channel 130, causing the refrigerant in the connecting channel 130 to easily flow back into the enthalpy-increasing component, resulting in large gas supply pulsations. When the volume is greater than 11.11, the volume of the second housing 710 is too large. This causes low-frequency pressure pulsations during the refrigerant replenishment process by the enthalpy-enhancing component, resulting in unstable gas replenishment and affecting the pressure balance of the intermediate chamber. Furthermore, the minimum diameter of the enthalpy injection orifice 140 is too small, limiting the flow rate of refrigerant replenished from the enthalpy-enhancing component, leading to insufficient gas replenishment and affecting compressor performance. Therefore, by rationally designing the relationship between the working volume V1 of the low-pressure compression chamber 110, the working volume V2 of the high-pressure compression chamber 210, the volume V6 of the second housing 710, and the minimum diameter D of the enthalpy injection orifice 140, the gas replenishment volume of the second chamber 301 can be increased, gas replenishment pulsations reduced, and the flow loss of the refrigerant replenished by the enthalpy-enhancing component decreased, thereby improving compressor performance.
[0070] In the embodiments of this application, the compressor further includes a motor assembly 800, which includes a stator 810 and a rotor 820 rotatably disposed within the stator 810. The outer peripheral surface of the rotor 820 abuts against the inner peripheral surface of the first housing 600. The rotor 820 is fixedly connected to the upper end of the crankshaft 400, and the stator 810 drives the crankshaft 400 to rotate through the rotor 820.
[0071] In the embodiments of this application, the volume V6 of the second housing 710, the working volume V1 of the low-pressure compression chamber 110, the volume V3 of the first cavity 120, the sum of the volumes V5 of all connecting channels 130, and the volume V4 of the second cavity 301 satisfy the following relationship: ≤3, or, ≥15, under different operating conditions, the intake and exhaust pulsations of the compressor can be reduced by adjusting the volume V6 of the second housing 710.
[0072] Understandably, when the compressor is operating at low frequency, the motor assembly 800 operates at a lower speed and the refrigerant flow is smaller. ≤3 can reduce the volume V6 of the second housing 710, thereby reducing the amount of gas supplied to the enthalpy-increasing component to prevent excessive gas pressure in the second cavity 301. This is equivalent to reducing the exhaust resistance of the low-pressure compression chamber 110, thus reducing the exhaust pulsation of the low-pressure compression chamber 110. When the compressor is in high-frequency operation, the motor assembly 800 rotates at a higher speed, and the refrigerant flow rate increases. ≥15 ensures that the intermediate cavity has a sufficiently large buffer space, thereby reducing the intake pulsation of the high-pressure compression chamber 210 and improving the performance of the compressor.
[0073] In the embodiments of this application, the upper bearing 202 of the pump body assembly is fixedly connected to the inner circumferential surface of the inner cavity 610, or the first cylinder 101 and / or the second cylinder 201 are fixedly connected to the inner circumferential surface of the inner cavity 610. The fixed connection can be achieved by welding or interference fit, wherein the welding method includes, but is not limited to, resistance welding and laser welding.
[0074] 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.
[0075] The refrigeration equipment according to the third aspect of this application includes the compressor described in the above embodiments. The refrigeration equipment may be a central air conditioner, a packaged air conditioner, a split air conditioner, a ducted air conditioner, a window air conditioner, or the like.
[0076] The embodiments of this application have been described in detail above with reference to the accompanying drawings. However, this application 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 this application.
Claims
1. Pump body assembly, including: The first compression assembly includes a low-pressure compression chamber, a first cavity, and at least one communicating channel. The exhaust port of the low-pressure compression chamber is connected to the communicating channel through the first cavity. The second compression assembly includes a high-pressure compression chamber; and A partition assembly is connected between the first compression assembly and the second compression assembly. The partition assembly is provided with a second cavity, and the air intake of the high-pressure compression cavity is connected to the communication channel through the second cavity. Wherein, the working volume of the low-pressure compression chamber is V1, the working volume of the high-pressure compression chamber is V2, the volume of the first chamber is V3, the volume of the second chamber is V4, the sum of the volumes of all the connecting channels is V5, and the sum of the minimum flow areas of all the connecting channels is S, satisfying: U = ，0.015≤U≤0.08。 2. The pump body assembly according to claim 1, wherein, The ratio of the volume of the first cavity to the volume of the second cavity is V3 / V4, which satisfies: 0.2≤V3 / V4≤5.
3. The pump body assembly according to claim 1 or 2, wherein, The ratio of the working volume of the high-pressure compression chamber to the 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 any one of claims 1 to 3, wherein, The first compression assembly includes a first cylinder, a lower bearing, and a lower muffler. The low-pressure compression chamber and the connecting channel are respectively located in the first cylinder. The lower bearing and the lower muffler are both connected to the first cylinder. The lower bearing and the lower muffler enclose the first cavity. The partition assembly is located on the side of the first cylinder away from the lower bearing.
5. The pump body assembly according to any one of claims 1 to 4, wherein, The second compression assembly includes a second cylinder, an upper bearing, and an upper muffler. The high-pressure compression chamber is located inside the second cylinder. The upper bearing and the upper muffler are both connected to the second cylinder. The partition assembly is located on the side of the second cylinder away from the upper bearing.
6. The pump body assembly according to any one of claims 1 to 5, wherein, The baffle assembly includes a first baffle and a second baffle disposed opposite to each other along the axial direction of the pump body assembly. The first baffle and the second baffle enclose the second cavity. The first baffle is connected to the first compression assembly, and the second baffle is connected to the second compression assembly.
7. The pump body assembly according to any one of claims 1 to 6, wherein, 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.
8. A compressor comprising a first housing and a pump assembly as claimed in any one of claims 1 to 7, wherein the pump assembly is mounted within the first housing.
9. The compressor according to claim 8 further includes an enthalpy-increasing component, wherein, The enthalpy-enhancing component is installed outside the first housing. The first compression component is provided with an enthalpy-spraying orifice that connects to the connecting channel. The enthalpy-enhancing component includes an air inlet pipe that passes through the first housing and extends into the enthalpy-spraying orifice. The enthalpy-enhancing component delivers refrigerant to the second cavity through the enthalpy-spraying orifice.
10. The compressor according to claim 9, wherein, The enthalpy-enhancing assembly further includes a second housing, with the end of the intake pipe away from the first housing extending into the second housing. The volume of the second housing is V6, and the minimum diameter of the injection enthalpy orifice is D, satisfying: 0.02 ≤ ≤11.
11.
11. The compressor according to claim 9, wherein, The enthalpy-increasing assembly further includes a second housing, and the end of the intake pipe away from the first housing extends into the second housing. The volume of the second housing is V6, satisfying: ≤3, or, ≥15.
12. A refrigeration device, comprising the compressor according to any one of claims 8 to 11.