Pump body assembly, compressor and refrigeration equipment

Abstract

According to the pump body assembly, the working volume of a low-pressure compression cavity is V1, the minimum radius of a first air suction port is R1, the working volume of a high-pressure compression cavity is V2, the minimum radius of a second air suction port is R2, the connecting line of the center of a first sliding piece groove and the axis of a crankshaft is L1, and the connecting line of the center of the first air suction port and the axis of the crankshaft is L2; the connecting line of the center of the first exhaust port and the axis of the crankshaft is L3, the connecting line of the center of the second sliding piece groove and the axis of the crankshaft is L4, the connecting line of the center of the second air suction port and the axis of the crankshaft is L5, the connecting line of the center of the second exhaust port and the axis of the crankshaft is L6, and in the rotating direction of the crankshaft, the included angle formed by L1 and L2 is theta 1, and the included angle formed by L1 and L3 is theta 2. The included angle formed by L4 and L5 is theta3, the included angle formed by L4 and L6 is theta4, U = (V1 * theta2 * theta3 * R2) / (V2 * theta1 * theta4 * R1), 0.6 < = U < = 5.2, and the volume efficiency of the compressor can be improved.

Description

Technical Field

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

[0002] At present, the pump body assembly adopts multi-stage compression technology to evenly distribute the pressure ratio of each stage of the compression assembly, so that the compression assembly is within a relatively reasonable pressure ratio range, thereby improving the volumetric efficiency of the compressor. The existing pump body assembly is provided with a low-pressure compression chamber, an intermediate chamber, and a high-pressure compression chamber. The exhaust port of the low-pressure compression chamber is communicated with the suction port of the high-pressure compression chamber through the intermediate chamber. The refrigerant compressed in the low-pressure compression chamber is temporarily stored in the intermediate chamber for transition and then is sucked into the high-pressure compression chamber for secondary compression. The clearance volume of the compression chamber of the existing pump body assembly is relatively large, resulting in a reduction in the effective suction volume of the compression chamber and a decrease in the volumetric efficiency of the compressor. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. For this purpose, the present invention provides a pump body assembly that can improve the volumetric efficiency of the compressor.

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

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

[0006] The pump body assembly according to the first aspect embodiment of the present invention includes:

[0007] A crankshaft including a first eccentric portion and a second eccentric portion spaced apart along the axial direction of the crankshaft;

[0008] A first compression assembly provided with a low-pressure compression chamber, a first suction port, a first exhaust port, and a first sliding vane groove communicating with the low-pressure compression chamber, and the first eccentric portion is rotatably disposed in the low-pressure compression chamber;

[0009] A second compression assembly provided with a high-pressure compression chamber, a second suction port, a second exhaust port, and a second sliding vane groove communicating with the high-pressure compression chamber, and the second eccentric portion is rotatably disposed in the high-pressure compression chamber;

[0010] A partition assembly connected between the first compression assembly and the second compression assembly, the partition assembly is provided with a first cavity, and the first exhaust port communicates with the second suction port through the first cavity;

[0011] Among them, the working volume of the low-pressure compression chamber is V1, the minimum radius of the first suction port is R1, the working volume of the high-pressure compression chamber is V2, the minimum radius of the second suction port is R2. On the projection plane along the axial projection of the crankshaft, the connection line between the center of the first sliding vane groove and the axis of the crankshaft is L1, the connection line between the center of the first suction port and the axis of the crankshaft is L2, the connection line between the center of the first exhaust port and the axis of the crankshaft is L3, the connection line between the center of the second sliding vane groove and the axis of the crankshaft is L4, the connection line between the center of the second suction port and the axis of the crankshaft is L5, the connection line between the center of the second exhaust port and the axis of the crankshaft is L6. Along the rotation direction of the crankshaft, the included angle formed by L1 and L2 is θ1, the included angle formed by L1 and L3 is θ2, the included angle formed by L4 and L5 is θ3, the included angle formed by L4 and L6 is θ4, and it satisfies: U=(V1×θ2×θ3×R2) / (V2×θ1×θ4×R1), 0.6≤U≤5.2.

[0012] The pump body assembly according to the embodiment of the present invention has at least the following beneficial effects:

[0013] When the pump body assembly is working, the refrigerant outside the pump body assembly is inhaled into the low-pressure compression chamber from the first suction port. The refrigerant completes the first-stage compression in the low-pressure compression chamber. After that, the refrigerant is discharged to the first cavity through the first exhaust port. The refrigerant in the first cavity is inhaled into the high-pressure compression chamber from the second suction port. The refrigerant completes the second-stage compression in the high-pressure compression chamber, so that the low-pressure compression chamber and the high-pressure compression chamber are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. Since U = (V1 × θ2 × θ3 × R2) / (V2 × θ1 × θ4 × R1), and 0.6 ≤ U ≤ 5.2, when U is less than 0.6, the working volume V2 of the high-pressure compression chamber is too large, which is equivalent to the working volume V1 of the low-pressure compression chamber being too small, resulting in too little suction volume in the high-pressure compression chamber, a decrease in the heating capacity of the compressor, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft being too large, an increased risk of gas leakage in the high-pressure area of the high-pressure compression chamber, resulting in an increased gas leakage volume, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft being too small, the premature closing of the second suction port, the high-pressure compression chamber not fully inhaling gas, the radius R2 of the second suction port being too small, resulting in an increased flow resistance during gas inhalation, an increased suction pressure loss, and the high-pressure compression chamber being unable to fully inhale gas. Under the combined action of the large working volume V2 of the high-pressure compression chamber, the large angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft, the small angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft, and the small radius R2 of the second suction port, the flow loss of the refrigerant inhaled by the high-pressure compression chamber increases, and the volumetric efficiency of the compressor decreases; when U is greater than 5.2, the working volume V2 of the high-pressure compression chamber is too small, the high-pressure compression chamber cannot completely consume the refrigerant discharged from the low-pressure compression chamber, resulting in performance surplus, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft being too small, the clearance volume of the high-pressure compression chamber increasing, the working volume V2 of the high-pressure compression chamber decreasing, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft being too large, resulting in a delayed closing time of the second suction port, causing the low-pressure area of the high-pressure compression chamber to still be connected to the suction side at the beginning of compression, generating a return loss and reducing the effective compressed gas volume, the radius R2 of the second suction port being too large, the high-pressure compression chamber being unable to close in time at the end of the suction stage, resulting in a reduction in the actual effective suction volume. Under the combined action of the large working volume V2 of the high-pressure compression chamber, the large angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft, the small angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft, and the small radius R2 of the second suction port, the closing time of the second suction port is delayed, and the actual effective suction volume of the high-pressure compression chamber decreases, resulting in a reduction in the volumetric efficiency of the compressor.Therefore, by reasonably designing the relationship between the working volume V1 of the low-pressure compression chamber, the minimum radius R1 of the first suction port, the working volume V2 of the high-pressure compression chamber, the minimum radius R2 of the second suction port, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft, the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft, and the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft, the suction structure and exhaust structure of the pump body assembly can be optimized. While increasing the effective suction volume of the high-pressure compression chamber, the flow loss of the refrigerant can be reduced, thereby improving the volumetric efficiency of the compressor.

[0014] According to some embodiments of the present invention, the working volume of the low-pressure compression chamber is V1, the minimum radius of the first suction port is R1, the angle formed by L1 and L2 along the rotation direction of the crankshaft is θ1, and the angle formed by L1 and L3 along the rotation direction of the crankshaft is θ2, satisfying: 88 ≤ (V1 × θ2) / (θ1 × R1) ≤ 183.

[0015] According to some embodiments of the present invention, the working volume of the high-pressure compression chamber is V2, the minimum radius of the second suction port is R2, the angle formed by L4 and L5 along the rotation direction of the crankshaft is θ3, and the angle formed by L4 and L6 along the rotation direction of the crankshaft is θ4, satisfying: 35 ≤ (V2 × θ4) / (θ3 × R2) ≤ 147.

[0016] According to some embodiments of the present invention, the phase difference between the first compression assembly and the second compression assembly at the start of suction is within the range of 150° to 210°.

[0017] According to some embodiments of the present invention, the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft is within the range of 345° to 360°, and / or the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft is within the range of 345° to 360°.

[0018] According to some embodiments of the present invention, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft is less than or equal to the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft.

[0019] According to some embodiments of the present invention, on the projection plane along the axial direction of the crankshaft, the angle between L1 and L4 is within the range of 0° to 60°.

[0020] According to some embodiments of the present invention, the first compression assembly includes a first cylinder, a lower bearing, and a lower muffler. The lower bearing and the lower muffler are both connected to the first cylinder. The partition assembly is connected to a side of the first cylinder away from the lower bearing. The partition assembly, the first cylinder, and the lower bearing enclose to form the low-pressure compression chamber. The first cylinder is provided with a communication channel, a first suction port, and a first sliding vane slot. The first exhaust port is located in the lower bearing or the first cylinder. The lower bearing and the lower muffler enclose to form a second cavity. The first exhaust port discharges gas into the second cavity. Two ends of the communication channel are respectively communicated with the first cavity and the second cavity.

[0021] According to some embodiments of the present invention, the second compression assembly includes a second cylinder and an upper bearing. The partition assembly is connected to the second cylinder. The upper bearing is connected to a side of the second cylinder away from the partition assembly. The partition assembly, the second cylinder, and the upper bearing enclose to form the high-pressure compression chamber. The second cylinder is provided with a second suction port and a second sliding vane slot. The second exhaust port is located in the second cylinder or the upper bearing.

[0022] According to some embodiments of the present invention, the partition assembly includes a first partition and a second partition oppositely arranged along the axial direction of the pump body assembly. The first partition and the second partition enclose to form the first cavity. The first partition is connected to the first compression assembly. The second partition is connected to the second compression assembly.

[0023] The compressor according to the second aspect embodiment of the present invention includes the pump body assembly described in the above embodiments.

[0024] The refrigeration device according to the third aspect embodiment of the present invention includes the compressor described in the above embodiments.

[0025] Additional aspects and advantages of the present invention will be given in part in the following description, become apparent in part from the following description, or be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The present invention will be further described below in conjunction with the drawings and embodiments, where:

[0027] Figure 1 is a cross-sectional view of a pump body assembly according to an embodiment of the present invention;

[0028] Figure 2 is Figure 1 the cross-sectional view taken along line A-A in

[0029] Figure 3 is Figure 1 the cross-sectional view taken along line B-B in

[0030] Figure 4 It is a relationship diagram of U and the volumetric efficiency of the compressor according to an embodiment of the present invention.

[0031] Reference numerals in the drawings:

[0032] Axis O1, crankshaft 100, first eccentric part 110, second eccentric part 120, first cylinder 201, lower bearing 202, lower muffler 203, low-pressure compression chamber 210, first suction port 220, first exhaust port 230, first sliding vane groove 240, second cavity 250, communication channel 260, second cylinder 301, upper bearing 302, upper muffler 303, high-pressure compression chamber 310, second suction port 320, second exhaust port 330, second sliding vane groove 340, third cavity 350, partition assembly 400, first cavity 401, first partition 410, second partition 420, first piston 510, second piston 520, first sliding vane 610, second sliding vane 620. Detailed implementation manners

[0033] The embodiments of the present invention will be described in detail below. The examples of the embodiments are shown in the drawings, where 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 drawings are exemplary and are only used to explain the present invention and should not be construed as a limitation of the present invention.

[0034] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by terms such as up and down, etc., is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention.

[0035] In the description of the present invention, "a plurality" means more than two. If the first and second are described only for the purpose of distinguishing technical features, they should not be construed as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or implicitly indicating the sequence of the indicated technical features.

[0036] In the description of the present invention, unless otherwise clearly defined, terms such as "set", "installed", "connected", etc. should be understood in a broad sense. Those skilled in the art can reasonably determine the specific meanings of the above terms in the present invention in combination with the specific content of the technical solution.

[0037] In the related art, the pump body assembly adopts a multi-stage compression technology to evenly distribute the compression ratio of each stage of the compression assembly, so that the compression assembly is within a relatively reasonable compression ratio range, thereby improving the volumetric efficiency of the compressor. The existing pump body assembly is provided with a low-pressure compression chamber, an intermediate chamber, and a high-pressure compression chamber. The exhaust port of the low-pressure compression chamber is communicated with the suction port of the high-pressure compression chamber through the intermediate chamber. The refrigerant compressed in the low-pressure compression chamber is temporarily stored in the intermediate chamber for transition and then is sucked into the high-pressure compression chamber for secondary compression. The clearance volume of the compression chamber of the existing pump body assembly is relatively large, resulting in a reduction in the effective suction volume of the compression chamber and a decrease in the volumetric efficiency of the compressor. It can be understood that generally, the compression ratio of the compressor is the ratio of the inlet and outlet pressures, but there are compression ratios of different compression chambers here.

[0038] Referring to Figure 1 , Figure 1 is a schematic cross-sectional view of a pump body assembly according to an embodiment of the present invention. For example Figure 1As shown in the figure, a pump body assembly according to an embodiment of the present invention includes a crankshaft 100, a first compression assembly, a second compression assembly, and a partition assembly 400. Along the axial direction of the crankshaft 100, the crankshaft 100 includes a first eccentric portion 110 and a second eccentric portion 120 that are spaced apart. A first piston 510 is sleeved on the first eccentric portion 110, and a second piston 520 is sleeved on the second eccentric portion 120. The first compression assembly, the partition assembly 400, and the second compression assembly are sequentially connected and arranged along the axial direction of the crankshaft 100. The first compression assembly is provided with a low-pressure compression chamber 210, a first suction port 220, a first discharge port 230, and a first sliding vane groove 240. A first sliding vane 610 is slidably arranged in the first sliding vane groove 240. The first suction port 220, the first discharge port 230, and the first sliding vane groove 240 are respectively communicated with the low-pressure compression chamber 210. The first piston 510 is rotatably arranged in the low-pressure compression chamber 210. The front end of the first sliding vane 610 abuts against the outer peripheral surface of the first piston 510. The second compression assembly is provided with a high-pressure compression chamber 310, a second suction port 320, a second discharge port 330, and a second sliding vane groove 340. The second suction port 320, the second discharge port 330, and the second sliding vane groove 340 are respectively communicated with the high-pressure compression chamber 310. A second sliding vane 620 is arranged in the second sliding vane groove 340. The second piston 520 is rotatably arranged in the high-pressure compression chamber 310. The front end of the second sliding vane 620 abuts against the outer peripheral surface of the second piston 520. The partition assembly 400 is provided with a first cavity 401. The first discharge port 230 is communicated with the second suction port 320 through the first cavity 401. When the pump body assembly works, the refrigerant outside the pump body assembly is sucked into the low-pressure compression chamber 210 from the first suction port 220. The refrigerant completes the first-stage compression in the low-pressure compression chamber 210. Then, the refrigerant is discharged to the first cavity 401 from the first discharge port 230. The refrigerant in the first cavity 401 is sucked into the high-pressure compression chamber 310 from the second suction port 320. The refrigerant completes the second-stage compression in the high-pressure compression chamber 310, so that the low-pressure compression chamber 210 and the high-pressure compression chamber 310 are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor.

[0039] It should be noted that the first cavity 401, the second cavity 250, and the communication channel 260 form an intermediate cavity. When the refrigerant flows in the intermediate cavity, the refrigerant can be cooled to a certain extent, which is beneficial to reducing the input required for compression in the high-pressure compression chamber 310 and improving the energy efficiency of the compressor.

[0040] Refer to Figure 2 、 Figure 3 , Figure 2 is Figure 1 the sectional view taken along the line A-A in Figure 3 is Figure 1Cross-sectional view along line B-B in the figure. As shown in the figure, in the embodiment of the present invention, the working volume of the low-pressure compression chamber 210 is V1, the minimum radius of the first suction port 220 is R1, the working volume of the high-pressure compression chamber 310 is V2, the minimum radius of the second suction port 320 is R2. On the projection plane along the axial projection of the crankshaft 100, the connection line between the center of the first vane slot 240 and the axis O1 of the crankshaft 100 is L1, the connection line between the center of the first suction port 220 and the axis O1 of the crankshaft 100 is L2, the connection line between the center of the first discharge port 230 and the axis O1 of the crankshaft 100 is L3, the connection line between the center of the second vane slot 340 and the axis O1 of the crankshaft 100 is L4, the connection line between the center of the second suction port 320 and the axis O1 of the crankshaft 100 is L5, the connection line between the center of the second discharge port 330 and the axis O1 of the crankshaft 100 is L6. The angle formed by L1 and L2 along the rotation direction of the crankshaft 100 is θ1, the angle formed by L1 and L3 along the rotation direction of the crankshaft 100 is θ2, the angle formed by L4 and L5 along the rotation direction of the crankshaft 100 is θ3, the angle formed by L4 and L6 along the rotation direction of the crankshaft 100 is θ4, and it satisfies: U = (V1 × θ2 × θ3 × R2) / (V2 × θ1 × θ4 × R1), 0.6 ≤ U ≤ 5.2. For example, U can be 0.6, 0.8, 1, 1.5, 2, 2, 2.5, 3, 3.5, 4, 4.5, 5, 5.2, etc. It should be noted that the clearance volume refers to the volume of the gas remaining in the cylinder after compression. The working volume generally refers to the remaining volume between the compression chamber and the piston rotatably installed inside the compression chamber. The unit of the working volume is cc, the unit of the angle is radian, and the unit of the radius is mm. This unit will be used in subsequent embodiments.

[0041] It should be noted that when the ratio V2 / V1 of the working volume of the high-pressure compression chamber 310 to the working volume of the low-pressure compression chamber 210 is too small, the working volume V1 of the low-pressure compression chamber 210 is too large, and the high-pressure compression chamber 310 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 210, resulting in excessive performance and a decrease in the volumetric efficiency of the compressor; when the ratio V2 / V1 of the working volume of the high-pressure compression chamber 310 to the working volume of the low-pressure compression chamber 210 is too large, for the low-temperature heating condition, the working volume V2 of the high-pressure compression chamber 310 is too large, which is equivalent to the working volume V1 of the low-pressure compression chamber 210 being too small, resulting in insufficient suction volume of the high-pressure compression chamber 310 and insufficient heating capacity, and a poor user experience.

[0042] It should be noted that if the minimum radius of the suction port of the compression chamber is too large, the compression chamber cannot be closed in time at the end of the suction stage. Part of the inhaled gas flows back to the suction side through the suction port due to the pressure difference at the initial stage of compression, resulting in a reduction in the actual effective suction volume and a decrease in the volumetric efficiency. If the minimum radius of the suction port of the compression chamber is too small, it will increase the flow resistance during gas inhalation, leading to suction pressure loss. The compression chamber cannot fully inhale the gas, and the volumetric efficiency decreases.

[0043] It should be noted that along the rotation direction of the crankshaft 100, if the included angle between the connecting line of the center of the sliding vane groove and the axis O1 of the crankshaft 100 and the connecting line of the center of the suction port and the axis O1 of the crankshaft 100 is too large, it will cause a delay in the closing time of the suction port, making the low-pressure area of the compression chamber still communicate with the suction side at the initial stage of compression. At this time, part of the inhaled gas is pushed back to the suction side due to the continuous rotation of the piston, resulting in a backflow loss, reducing the effective compressed gas volume, and the volumetric efficiency of the compressor decreases. If the included angle between the connecting line of the center of the sliding vane groove and the axis O1 of the crankshaft 100 and the connecting line of the center of the suction port and the axis O1 of the crankshaft 100 is too small along the rotation direction of the crankshaft 100, it will cause the suction port to close prematurely, and the compression chamber cannot fully inhale the gas.

[0044] It should be noted that along the rotation direction of the crankshaft 100, if the included angle between the connecting line of the center of the sliding vane groove and the axis O1 of the crankshaft 100 and the connecting line of the center of the exhaust port and the axis O1 of the crankshaft 100 is too large, the gas in the high-pressure area of the compression chamber is likely to leak from the gap between the sliding vane and the cylinder, resulting in an increase in the gas leakage volume and a decrease in the volumetric efficiency of the compressor. If the included angle between the connecting line of the center of the sliding vane groove and the axis O1 of the crankshaft 100 and the connecting line of the center of the exhaust port and the axis O1 of the crankshaft 100 is too small along the rotation direction of the crankshaft 100, it will cause an increase in the clearance volume of the compression chamber and a decrease in the working volume of the compression chamber, and the volumetric efficiency of the compressor decreases.

[0045] It can be understood that, on the basis that the working volume V1 of the low-pressure compression chamber 210, the minimum radius R1 of the first suction port 220, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft 100, and the angle formed by L1 and L3 along the rotation direction of the crankshaft 100 is θ2 remain unchanged, when U is less than 0.6, the working volume V2 of the high-pressure compression chamber 310 is too large, which is equivalent to the working volume V1 of the low-pressure compression chamber 210 being too small, resulting in too little suction volume in the high-pressure compression chamber 310, a decrease in the heating capacity of the compressor, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 being too large, an increase in the risk of gas leakage in the high-pressure area of the high-pressure compression chamber 310, resulting in an increase in the gas leakage volume, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 being too small, the second suction port 320 closing too early, the high-pressure compression chamber 310 not fully inhaling gas, the radius R2 of the second suction port 320 being too small, an increase in the flow resistance during gas inhalation, an increase in the suction pressure loss, and the high-pressure compression chamber 310 being unable to fully inhale gas. Under the combined action of the working volume V2 of the high-pressure compression chamber 310 being too large, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 being too large, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 being too small, and the radius R2 of the second suction port 320 being too small, the flow loss of the refrigerant inhaled by the high-pressure compression chamber 310 increases, and the volumetric efficiency of the compressor decreases; when U is greater than 5.2, the working volume V2 of the high-pressure compression chamber 310 is too small, the high-pressure compression chamber 310 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 210, resulting in performance surplus, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 being too small, an increase in the clearance volume of the high-pressure compression chamber 310, a decrease in the working volume V2 of the high-pressure compression chamber 310, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 being too large, resulting in a delay in the closing time of the second suction port 320, causing the low-pressure area of the high-pressure compression chamber 310 to still be connected to the suction side at the beginning of compression, generating a reflux loss and reducing the effective compressed gas volume, the radius R2 of the second suction port 320 being too large, and the high-pressure compression chamber 310 being unable to close in time at the end of the inhalation stage, resulting in a reduction in the actual effective suction volume. Under the combined action of the working volume V2 of the high-pressure compression chamber 310 being too large, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 being too large, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 being too small, and the radius R2 of the second suction port 320 being too small, the closing time of the second suction port 320 is delayed, and the actual effective suction volume of the high-pressure compression chamber 310 decreases, resulting in a decrease in the volumetric efficiency of the compressor.Therefore, by rationally designing the relationships among the working volume V1 of the low-pressure compression chamber 210, the minimum radius R1 of the first suction port 220, the working volume V2 of the high-pressure compression chamber 310, the minimum radius R2 of the second suction port 320, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft 100, the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100, and the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100, the suction structure and exhaust structure of the pump body assembly can be optimized. While increasing the effective suction volume of the high-pressure compression chamber 310, the flow loss of the refrigerant can be reduced, thereby improving the volumetric efficiency of the compressor.

[0046] Refer to Figure 4 , Figure 4 which is the relationship diagram of U and the volumetric efficiency of the compressor in an embodiment of the present invention. Figure 4 The values in Figure 4 are the volumetric efficiency values of the compressor at different values of U, and the dashed line in

[0047] is the fitting curve of multiple cylinders. As shown in the figure, when the value of U gradually increases, within the range of 0.6 to 5.2, the volumetric efficiency of the compressor first gradually increases and then decreases, and the volumetric efficiency of the compressor is greater than 90%. Therefore, by rationally designing the relationships among the working volume V1 of the low-pressure compression chamber 210, the minimum radius R1 of the first suction port 220, the working volume V2 of the high-pressure compression chamber 310, the minimum radius R2 of the second suction port 320, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft 100, the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100, and the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100, the volumetric efficiency of the compressor can be improved. Figure 2 As shown in the embodiment of the present invention, the working volume V1 of the low-pressure compression chamber 210, the minimum radius R1 of the first suction port 220, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft 100, and the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100 satisfy the following relational expression: 88 ≤ (V1×θ2) / (θ1×R1) ≤ 183. For example, (V1×θ2) / (θ1×R1) can be 88, 90, 95, 100, 105, 110, 115, 120, 125, 130, 135, 140, 145, 150, 155, 160, 165, 170, 175, 180, 183, etc., which can increase the actual effective inhalation volume of the low-pressure compression chamber 210, thereby improving the volumetric efficiency of the compressor.

[0048] For example, when (V1×θ2) / (θ1×R1) is less than 88, the minimum radius R1 of the first suction port 220 is too large, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft 100 is too large, and the low-pressure compression chamber 210 cannot be closed in time at the end of the suction stage. Part of the inhaled gas flows back to the suction side through the first suction port 220 due to the pressure difference at the initial stage of compression, resulting in a reduction in the actual effective suction volume and a decrease in the volumetric efficiency of the compressor. When (V1×θ2) / (θ1×R1) is greater than 183, the minimum radius R1 of the first suction port 220 is too small, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft 100 is too small, the flow resistance of the gas when inhaled from the first suction port 220 into the low-pressure compression chamber 210 increases, and the first suction port 220 closes too early, the low-pressure compression chamber 210 does not fully inhale the gas, the flow loss of the refrigerant increases, and the volumetric efficiency of the compressor decreases. Therefore, by reasonably designing the relationship between the working volume V1 of the low-pressure compression chamber 210, the minimum radius R1 of the first suction port 220, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft 100, and the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100, the actual effective suction volume of the low-pressure compression chamber 210 can be increased, thereby improving the volumetric efficiency of the compressor.

[0049] For example Figure 3 As shown in the embodiments of the present invention, the working volume V2 of the high-pressure compression chamber 310, the minimum radius R2 of the second suction port 320, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100, and the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 satisfy the following relationship: 35 ≤ (V2×θ4) / (θ3×R2) ≤ 147. For example, (V2×θ4) / (θ3×R2) can be 35, 40, 45, 50, 55, 60, 65, 70, 75, 80, 85, 90, 95, 100, 105, 110, 115, 120, 125, 130, 135, 140, 145, 147, etc., which can increase the actual effective suction volume of the high-pressure compression chamber 310, thereby improving the volumetric efficiency of the compressor.

[0050] For example, when (V2×θ4) / (θ3×R2) is less than 35, the minimum radius R2 of the second suction port 320 is too large, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 is too large, and the high-pressure compression chamber 310 cannot be closed in time at the end of the suction stage. Part of the inhaled gas flows back to the suction side through the second suction port 320 due to the pressure difference at the initial stage of compression, resulting in a reduction in the actual effective suction volume and a decrease in the volumetric efficiency of the compressor. When (V2×θ4) / (θ3×R2) is greater than 147, the minimum radius R2 of the second suction port 320 is too small, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 is too small, the flow resistance of the gas when inhaled from the second suction port 320 into the high-pressure compression chamber 310 increases, and the second suction port 320 closes prematurely. The high-pressure compression chamber 310 does not fully inhale the gas, the flow loss of the refrigerant increases, and the volumetric efficiency of the compressor decreases. Therefore, by reasonably designing the relationship between the working volume V2 of the high-pressure compression chamber 310, the minimum radius R2 of the second suction port 320, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100, and the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100, the actual effective inhalation volume of the high-pressure compression chamber 310 can be increased, thereby improving the volumetric efficiency of the compressor.

[0051] For example Figure 2 As shown, in the embodiment of the present invention, the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100 is greater than or equal to 345° and less than or equal to 360°, which can increase the working volume of the low-pressure compression chamber 210 and reduce the clearance volume of the low-pressure compression chamber 210, thereby improving the volumetric efficiency of the compressor. For example, when the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100 is less than 345°, part of the refrigerant in the low-pressure compression chamber 210 cannot be discharged from the first exhaust port 230 in time, the working volume of the low-pressure compression chamber 210 decreases, and the volumetric efficiency of the compressor decreases.

[0052] For example Figure 3 As shown, in the embodiment of the present invention, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 is greater than or equal to 345° and less than or equal to 360°, which can increase the working volume of the high-pressure compression chamber 310 and reduce the clearance volume of the high-pressure compression chamber 310, thereby improving the volumetric efficiency of the compressor. For example, when the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 is less than 345°, part of the refrigerant in the high-pressure compression chamber 310 cannot be discharged from the first exhaust port 230 in time, the working volume of the high-pressure compression chamber 310 decreases, and the volumetric efficiency of the compressor decreases.

[0053] In an embodiment of the present invention, the included angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 and the included angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100 satisfy the following specified relationship: θ4 ≤ θ2, which can increase the exhaust volume of the low-pressure compression chamber 210 and the high-pressure compression chamber 310, reduce the flow loss of the refrigerant, and thus improve the volumetric efficiency of the compressor. For example, when θ2 is less than θ4, the first exhaust port 230 closes late, and the compressed gas expands and flows back when the first piston 510 continues to rotate. Part of the high-pressure gas flows back to the low-pressure compression chamber 210, resulting in a reduction in the exhaust volume of the effective low-pressure compression chamber 210. The second exhaust port 330 closes early, causing the gas to be intercepted before being fully compressed to the target high pressure, indirectly reducing the effective exhaust volume of the high-pressure compression chamber 310, increasing the exhaust pulsation of the high-pressure compression chamber 310, increasing the flow loss of the refrigerant, and reducing the volumetric efficiency of the compressor. Therefore, by reasonably designing the relationship between the included angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 and the included angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100, the volumetric efficiency of the compressor can be improved.

[0054] It should be noted that when θ2 is 350°, θ4 can be 348°; when θ2 is 355°, θ4 can be 352°, which will not be elaborated here.

[0055] In an embodiment of the present invention, the ratio of the working volume of the high-pressure compression chamber 310 to the working volume of the low-pressure compression chamber 210 is V2 / V1, satisfying: 0.4 ≤ V2 / V1 ≤ 0.8. The unit of the working volume is cc. For example, V2 / V1 can be 0.4, 0.5, 0.6, 0.7, 0.8. Taking the working volume of the high-pressure compression chamber 310 as unchanged as an example, when V2 / V1 is less than 0.4, the working volume of the low-pressure compression chamber 210 is too large, and the high-pressure compression chamber 310 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 210, resulting in performance surplus and reducing the volumetric efficiency of the compressor; when V2 / V1 is greater than 0.8, for the low-temperature heating condition, the working volume of the low-pressure compression chamber 210 is too small, the suction volume of the high-pressure compression chamber 310 is too small, the heating capacity of the compressor decreases, and the user experience is poor. Therefore, by reasonably designing the ratio of the working volume of the high-pressure compression chamber 310 to the working volume of the low-pressure compression chamber 210, the suction pulsation and exhaust pulsation can be reduced, the vibration can be reduced, the noise can be reduced, and the volumetric efficiency of the compressor can be improved.

[0056] In an embodiment of the present invention, on the projection plane along the axial projection of the crankshaft 100, the included angle between the connecting line L1 between the center of the first sliding vane groove 240 and the axis O1 of the crankshaft 100 and the connecting line L4 between the center of the second sliding vane groove 340 and the axis O1 of the crankshaft 100 is greater than or equal to 0° and less than or equal to 60°. The exhaust of the low-pressure compression chamber 210 is synchronized with the suction of the high-pressure compression chamber 310, which can reduce the inter-stage pressure fluctuation and the flow loss of the refrigerant, thereby improving the volumetric efficiency of the compressor.

[0057] For example, when the included angle between the connecting line L1 between the center of the first sliding vane groove 240 and the axis O1 of the crankshaft 100 and the connecting line L4 between the center of the second sliding vane groove 340 and the axis O1 of the crankshaft 100 is greater than 60°, the phase difference between the first sliding vane 610 and the second sliding vane 620 is too large, and the exhaust of the low-pressure compression chamber 210 is not synchronized with the suction of the high-pressure compression chamber 310. The gas in the first cavity 401 cannot transition smoothly, resulting in inter-stage pressure fluctuation, an increase in the flow loss of the refrigerant, and a decrease in the volumetric efficiency of the compressor. Therefore, by reasonably designing the included angle between the connecting line L1 between the center of the first sliding vane groove 240 and the axis O1 of the crankshaft 100 and the connecting line L4 between the center of the second sliding vane groove 340 and the axis O1 of the crankshaft 100, the volumetric efficiency of the compressor can be improved. It can be understood that the included angle between the connecting line L1 between the center of the first sliding vane groove 240 and the axis O1 of the crankshaft 100 and the connecting line L4 between the center of the second sliding vane groove 340 and the axis O1 of the crankshaft 100 can be 0°, 10°, 20°, 30°, 40°, 50°, 60°, etc.

[0058] For example Figure 1 As shown, in an embodiment of the present invention, the first compression assembly includes a first cylinder 201, a lower bearing 202, and a lower muffler 203. The lower bearing 202 is connected to the lower end face of the first cylinder 201, and the lower muffler 203 is connected to the lower bearing 202. The lower bearing 202 and the lower muffler 203 enclose a second cavity 250. The first cylinder 201, the lower bearing 202, and the partition assembly 400 enclose a low-pressure compression chamber 210. The first cylinder 201 is provided with a communication channel 260 and a first suction port 220. The lower bearing 202 is provided with a first exhaust port 230. The lower muffler 203 and the lower bearing 202 enclose a second cavity 250. The low-pressure compression chamber 210 communicates with the geothermal cavity through the first exhaust port 230. The two ends of the communication channel 260 are respectively communicated with the first cavity 401 and the second cavity 250. The refrigerant in the low-pressure compression chamber 210 sequentially enters the second cavity 250, the communication channel 260, and the first cavity 401, and finally enters the high-pressure compression chamber 310, which is beneficial to reducing the exhaust pulsation and improving the performance of the compressor.

[0059] For example Figure 1As shown, in the embodiment of the present invention, the second compression assembly includes a second cylinder 301, an upper bearing 302, and an upper silencer 303. The lower end surface of the partition assembly 400 is connected to the upper end surface of the first cylinder 201, and the upper end surface of the partition assembly 400 is connected to the lower end surface of the second cylinder 301. The upper bearing 302 is connected to the upper end surface of the second cylinder 301, and the upper silencer 303 is connected to the upper bearing 302. A third cavity 350 is formed between the upper bearing 302 and the upper silencer 303. The exhaust port of the high-pressure compression chamber 310 is communicated with the third cavity 350. The refrigerant discharged from the high-pressure compression chamber 310 can enter the third cavity 350 and then be discharged into the inner cavity of the compressor housing, which is beneficial to reducing the exhaust noise and improving the user experience.

[0060] It can be understood that the lower bearing 202 is provided with a first valve seat, and the first valve seat is used to open or close the first exhaust port 230. The refrigerant in the low-pressure compression chamber 210 can enter the second cavity 250 through the valve seat, which will not be elaborated here. In another embodiment of the present invention, the partition assembly 400 is provided with a third exhaust port and a second valve seat. The low-pressure compression chamber 210 exhausts to the first cavity 401 through the third exhaust port, and the second valve seat is used to open or close the third exhaust port. The refrigerant in the low-pressure compression chamber 210 enters the second cavity 250 through the first valve seat and enters the first cavity 401 through the second valve seat. That is, the low-pressure compression chamber 210 adopts a double-exhaust scheme, which can effectively reduce the exhaust loss and improve the performance of the compressor.

[0061] In the embodiment of the present invention, the phase difference between the first compression assembly and the second compression assembly at the start of suction is greater than or equal to 150° and less than or equal to 210°. Therefore, when the first compression assembly is near the exhaust peak, the second compression assembly is exactly near the suction peak; or, when the second compression assembly is near the exhaust peak, the first compression assembly is near the suction peak. In this way, the second compression assembly can timely suck away the gas discharged by the first compression assembly, avoiding excessive pressure pulsation in the first cavity 401 caused by the accumulation of gas in the first cavity 401, and ensuring the continuity and smoothness of the suction of the first compression assembly and the second compression assembly, thereby improving the performance of the compressor.

[0062] It can be understood that the phase difference between the first compression assembly and the second compression assembly at the start of suction refers to the phase difference between the first cylinder 201 and the second cylinder 301 at the start of suction. The so-called phase difference at the start of suction means that the suction start position of a certain cylinder is defined as 0°. When the eccentric part in the cylinder rotates to X°, the other cylinder starts to suck. Then the phase difference between this cylinder and the other cylinder at the start of suction is X°. It should be noted that the phase difference between the first compression assembly and the second compression assembly at the start of suction can be 150°, 160°, 170°, 180°, 190°, 200°, 210°, which is not limited here.

[0063] For example Figure 1 Figure 1 As shown, in an embodiment of the present invention, the partition assembly 400 includes a first partition 410 and a second partition 420. The first partition 410 and the second partition 420 are disposed opposite to each other along the axial direction of the pump body assembly. The first partition 410 is located below the second partition 420. A second cavity 250 is formed by enclosing between the first partition 410 and the second partition 420. The first partition 410 is connected to the first compression assembly, and the second partition 420 is connected to the second compression assembly. The first partition 410 and the second partition 420 can be processed separately, which is beneficial to machining and manufacturing the second cavity 250 on the partition assembly 400, and can reduce the machining and manufacturing cost of the partition assembly 400.

[0064] For example, the second cavity 250 has a petal-shaped structure. The second cavity 250 is arranged around the axis O1 of the pump body assembly. By dividing the partition assembly 400 into the first partition 410 and the second partition 420, the first partition 410 and the second partition 420 can be processed separately, which is beneficial to machining and manufacturing the second cavity 250 on the partition assembly 400, and can reduce the machining and manufacturing cost of the partition assembly 400.

[0065] It should be noted that a connection structure is provided between the first partition 410 and the second partition 420. The connection structure is used to connect and fix the first partition 410 and the second partition 420. For example, the connection structure includes a connecting member. The connecting member is a screw or a bolt. The connecting member includes a rod portion and a head at one end of the rod portion. The rod portion passes through the second partition 420 and is threadedly connected to the first partition 410. The head is installed inside the second partition 420, which can facilitate connecting and fixing the first partition 410 and the second partition 420. As another implementation manner, the connecting member is a pin. One end of the connecting member is fixedly connected to the first partition 410, and the other end of the connecting member is fixedly connected to the second partition 420, which can also facilitate connecting and fixing the first partition 410 and the second partition 420, and will not be elaborated here.

[0066] It should be pointed out that a plurality of connecting members are configured. The plurality of connecting members are arranged around the axis O1 of the pump body assembly, which can increase the connection stability between the first partition 410 and the second partition 420, and will not be described in detail here.

[0067] For example Figure 2 Figure 2 As shown, in an embodiment of the present invention, a plurality of communication channels 260 are configured. The plurality of communication channels 260 are arranged at intervals around the axis O1 of the pump body assembly. Both ends of each communication channel 260 are respectively communicated with the first cavity 401 and the second cavity 250. By providing the plurality of communication channels 260, the total flow area of the plurality of communication channels 260 is increased, the flow rate of the refrigerant can be reduced, and thus the flow loss can be reduced.

[0068] It can be understood that the more the number of the communication channels 260, the more the strength in the radial direction of the first cylinder 201 decreases. In this embodiment, in order to ensure the strength in the radial direction of the first cylinder 201, the number of the communication channels 260 is configured to be less than or equal to 5, for example, the number of the communication channels 260 is 2, 3, 4, 5, etc.

[0069] As another implementation manner, the number of the communication channels 260 can also be configured to be one, which is not limited herein.

[0070] The compressor according to the second aspect embodiment of the present invention includes a housing and the pump body assembly of the above embodiment. The housing has an inner cavity, and the pump body assembly is installed in the inner cavity. By adopting the pump body assembly of the above embodiment, when the pump body assembly works, the refrigerant outside the pump body assembly is sucked into the low-pressure compression chamber 210 from the first suction port 220. The refrigerant completes the first-stage compression in the low-pressure compression chamber 210. Then, the refrigerant is discharged to the first cavity 401 through the first discharge port 230. The refrigerant in the first cavity 401 is sucked into the high-pressure compression chamber 310 from the second suction port 320. The refrigerant completes the second-stage compression in the high-pressure compression chamber 310, so that the low-pressure compression chamber 210 and the high-pressure compression chamber 310 are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. Since the working volume of the low-pressure compression chamber 210 is V1, the minimum radius of the first suction port 220 is R1, the working volume of the high-pressure compression chamber 310 is V2, and the minimum radius of the second suction port 320 is R2. On the projection plane along the axial projection of the crankshaft 100, the connection line between the center of the first sliding vane groove 240 and the axis O1 of the crankshaft 100 is L1, the connection line between the center of the first suction port 220 and the axis O1 of the crankshaft 100 is L2, the connection line between the center of the first discharge port 230 and the axis O1 of the crankshaft 100 is L3, the connection line between the center of the second sliding vane groove 340 and the axis O1 of the crankshaft 100 is L4, the connection line between the center of the second suction port 320 and the axis O1 of the crankshaft 100 is L5, and the connection line between the center of the second discharge port 330 and the axis O1 of the crankshaft 100 is L6. The included angle formed by L1 and L2 along the rotation direction of the crankshaft 100 is θ1, the included angle formed by L1 and L3 along the rotation direction of the crankshaft 100 is θ2, the included angle formed by L4 and L5 along the rotation direction of the crankshaft 100 is θ3, and the included angle formed by L4 and L6 along the rotation direction of the crankshaft 100 is θ4, satisfying: U=(V1×θ2×θ3×R2) / (V2×θ1×θ4×R1), 0.6≤U≤5.2.When U is less than 0.6, the working volume V2 of the high-pressure compression chamber 310 is too large, which is equivalent to the working volume V1 of the low-pressure compression chamber 210 being too small, resulting in too little suction volume of the high-pressure compression chamber 310, a decrease in the heating capacity of the compressor, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 being too large, an increased risk of gas leakage in the high-pressure area of the high-pressure compression chamber 310, leading to an increase in the gas leakage volume, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 being too small, the second suction port 320 closing too early, the high-pressure compression chamber 310 not fully inhaling gas, the radius R2 of the second suction port 320 being too small, resulting in an increase in the flow resistance during gas inhalation, an increase in the suction pressure loss, and the high-pressure compression chamber 310 being unable to fully inhale gas. Under the combined effect of the working volume V2 of the high-pressure compression chamber 310 being too large, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 being too large, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 being too small, and the radius R2 of the second suction port 320 being too small, the flow loss of the refrigerant inhaled by the high-pressure compression chamber 310 increases, and the volumetric efficiency of the compressor decreases; when U is greater than 5.2, the working volume V2 of the high-pressure compression chamber 310 is too small, the high-pressure compression chamber 310 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 210, resulting in performance surplus, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 being too small, the clearance volume of the high-pressure compression chamber 310 increasing, the working volume V2 of the high-pressure compression chamber 310 decreasing, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 being too large, resulting in a delay in the closing time of the second suction port 320, causing the low-pressure area of the high-pressure compression chamber 310 to still be connected to the suction side at the beginning of compression, generating a return flow loss and reducing the effective compressed gas volume, the radius R2 of the second suction port 320 being too large, and the high-pressure compression chamber 310 being unable to close in time at the end of the suction stage, resulting in a reduction in the actual effective suction volume. Under the combined effect of the working volume V2 of the high-pressure compression chamber 310 being too large, the angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft 100 being too large, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100 being too small, and the radius R2 of the second suction port 320 being too small, the closing time of the second suction port 320 is delayed, and the actual effective suction volume of the high-pressure compression chamber 310 decreases, resulting in a decrease in the volumetric efficiency of the compressor.Therefore, by rationally designing the relationships among the working volume V1 of the low-pressure compression chamber 210, the minimum radius R1 of the first suction port 220, the working volume V2 of the high-pressure compression chamber 310, the minimum radius R2 of the second suction port 320, the angle θ1 formed by L1 and L2 along the rotation direction of the crankshaft 100, the angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft 100, the angle θ3 formed by L4 and L5 along the rotation direction of the crankshaft 100, and the angle θ4 formed by L = and L6 along the rotation direction of the crankshaft 100, the suction structure and the exhaust structure of the pump body assembly can be optimized. While increasing the effective suction volume of the high-pressure compression chamber 310, the flow loss of the refrigerant can be reduced, thereby improving the volumetric efficiency of the compressor.

[0071] In an embodiment of the present invention, the compressor further includes a motor assembly. The motor assembly includes a stator and a rotor rotatably disposed within the stator. The outer peripheral surface of the rotor abuts against the inner peripheral surface of the housing. The rotor is fixedly connected to the upper end of the crankshaft 100, and the stator drives the crankshaft 100 to rotate through the rotor.

[0072] Since the compressor adopts all the technical solutions of the pump body assembly in the above embodiment, it at least has all the beneficial effects brought by the technical solutions of the above embodiment, which will not be elaborated here.

[0073] The refrigeration device according to the third aspect embodiment of the present invention includes the compressor of the above embodiment. The refrigeration device can be a central air conditioner, an integrated air conditioner, a split air conditioner, an air duct machine, a window machine, or the like.

[0074] The embodiments of the present invention have been described in detail above in conjunction with the drawings. However, the present invention is not limited to the above embodiments. Various changes can be made without departing from the spirit of the present invention within the scope of knowledge possessed by those of ordinary skill in the art.

Claims

1. A pump assembly, characterized in that: include: A crankshaft, comprising a first eccentric portion and a second eccentric portion spaced apart in an axial direction of the crankshaft; A first compression assembly is provided with a low-pressure compression chamber and a first air intake port, a first air discharge port, and a first vane groove communicating with the low-pressure compression chamber, wherein the first eccentric portion is rotatably disposed in the low-pressure compression chamber; The second compression assembly is provided with a high-pressure compression chamber and a second air intake port, a second air discharge port, and a second sliding vane groove communicating with the high-pressure compression chamber, and the second eccentric portion is rotatably disposed in the high-pressure compression chamber; a partition assembly connected between the first compression assembly and the second compression assembly, the partition assembly being provided with a first cavity, the first exhaust port being connected to the second intake port through the first cavity; The working volume of the low-pressure compression chamber is V1, the minimum radius of the first air intake port is R1, the working volume of the high-pressure compression chamber is V2, the minimum radius of the second air intake port is R2, and on the projection plane along the axial direction of the crankshaft, the line connecting the center of the first vane groove and the axis of the crankshaft is L1, the line connecting the center of the first air intake port and the axis of the crankshaft is L2, the line connecting the center of the first exhaust port and the axis of the crankshaft is L3, and the line connecting the center of the second vane groove and the axis of the crankshaft is L4. is L4, the line connecting the center of the second intake port and the axis of the crankshaft is L5, the line connecting the center of the second exhaust port and the axis of the crankshaft is L6, along the rotation direction of the crankshaft, the angle formed by L1 and L2 is θ1, the angle formed by L1 and L3 is θ2, the angle formed by L4 and L5 is θ3, and the angle formed by L4 and L6 is θ4, satisfying: U = (V1×θ2×θ3×R2) / (V2×θ1×θ4×R1), 0.6≤U≤5.

2.

2. The pump assembly according to claim 1, characterized in that: The working volume of the low-pressure compression chamber is V1, the minimum radius of the first air intake port is R1, the angle formed by L1 and L2 along the rotation direction of the crankshaft is θ1, and the angle formed by L1 and L3 along the rotation direction of the crankshaft is θ2, satisfying: 88≤(V1×θ2) / (θ1×R1)≤183.

3. The pump assembly according to claim 1, characterized in that: The working volume of the high-pressure compression chamber is V2, the minimum radius of the second air intake port is R2, the angle formed by L4 and L5 along the rotation direction of the crankshaft is θ3, and the angle formed by L4 and L6 along the rotation direction of the crankshaft is θ4, satisfying: 35≤(V2×θ4) / (θ3×R2)≤147.

4. The pump assembly according to claim 1, characterized in that: The phase difference between the first compression assembly and the second compression assembly at the start of inhalation is within a range of 150° to 210°.

5. The pump assembly according to claim 1, characterized in that: The angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft is within the range of 345° to 360°; and / or, An included angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft is within a range of 345° to 360°.

6. The pump assembly according to claim 1, characterized in that: An angle θ4 formed by L4 and L6 along the rotation direction of the crankshaft is less than or equal to an angle θ2 formed by L1 and L3 along the rotation direction of the crankshaft.

7. The pump assembly according to claim 1, characterized in that: On the projection plane along the axial direction of the crankshaft, the included angle between L1 and L4 is within the range of 0° to 60°.

8. The pump assembly according to claim 1, characterized in that: The first compression assembly includes a first cylinder, a lower bearing and a lower muffler, the lower bearing and the lower muffler are both connected to the first cylinder, the partition assembly is connected to the side of the first cylinder away from the lower bearing, the partition assembly, the first cylinder and the lower bearing enclose the low-pressure compression chamber, the first cylinder is provided with a connecting passage, the first air intake port and the first vane groove, the first exhaust port is located at the lower bearing or the first cylinder, the lower bearing and the lower muffler enclose a second cavity, the first exhaust port exhausts to the second cavity, and the two ends of the connecting passage are respectively connected to the first cavity and the second cavity.

9. The pump assembly according to claim 1, characterized in that: The second compression assembly includes a second cylinder and an upper bearing, the partition assembly is connected to the second cylinder, the upper bearing is connected to the side of the second cylinder away from the partition assembly, the partition assembly, the second cylinder and the upper bearing enclose the high-pressure compression chamber, the second cylinder is provided with the second intake port and the second vane groove, and the second exhaust port is located in the second cylinder or the upper bearing.

10. The pump assembly according to claim 1, characterized in that: The partition assembly includes a first partition and a second partition arranged opposite to each other along the axial direction of the pump body assembly. The first partition and the second partition enclose the first cavity. The first partition is connected to the first compression assembly, and the second partition is connected to the second compression assembly.

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

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

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