Pump body assembly, compressor and refrigeration equipment

Abstract

The utility model discloses a pump body assembly, and discloses a compressor and refrigeration equipment wherein the pump body assembly comprises a crankshaft, a first cylinder, a second cylinder and a clapboard assembly, the eccentricity of a first eccentric part is e1, the eccentricity of a second eccentric part is e2, the width of the end face of a first piston is L1, and the width of the end face of a second piston is L2, the height of the first air cylinder is H1, the diameter of the low-pressure compression cavity is D1, the working volume of the first air cylinder is V1, the height of the second air cylinder is H2, the diameter of the high-pressure compression cavity is D2, the working volume of the second air cylinder is V2, the thickness of the first sliding sheet is T1, the thickness of the second sliding sheet is T2, and the specified relation U is met, U = (V2 / V1) * (Di * Li * Ti) / (Hi * ei), i = 1 or i = 2, 1 < = U < = 51, the sealing performance of the low-pressure compression cavity and the high-pressure compression cavity can be improved, and therefore the volume efficiency of the compressor is improved.

Description

TECHNICAL FIELD

[0001] The utility model relates to compressor technical field especially relates to a pump body subassembly, compressor and refrigeration plant. BACKGROUND

[0002] In order to realize carbon neutralization, the demand of heat pump is increasing, wherein the compressor is the core component in heat pump system, and the low-temperature and low-pressure refrigerant is compressed into high-temperature and high-pressure refrigerant, so that heat is absorbed from low-temperature environment and released to high-temperature environment. At present, the pump body assembly adopts multi-stage compression technology to share the pressure ratio of each compression chamber, so that the compression chamber is in a reasonable pressure ratio range, but the leakage of refrigerant is still large in the process of multi-stage compression, which leads to insufficient volumetric efficiency of the compressor. SUMMARY

[0003] The utility model discloses at least one of the technical problems existing in the prior art. To this end, the utility model provides a pump body subassembly, which can improve the volumetric efficiency of the compressor.

[0004] The utility model discloses still propose a kind of compressor with above pump body subassembly.

[0005] The utility model discloses still propose a kind of refrigeration plant with above compressor.

[0006] According to the pump body subassembly of the first aspect embodiment of the utility model, comprising:

[0007] Crankshaft, including first eccentric part and second eccentric part being arranged at interval along the axial direction of crankshaft, the eccentric amount of first eccentric part is e1, the eccentric amount of second eccentric part is e2, first piston is sleeved with first eccentric part, along the radial direction of first piston, the width of end face of first piston is L1, second piston is sleeved with second eccentric part, along the radial direction of second piston, the width of end face of first piston is L2;

[0008] First cylinder, being provided with low-pressure compression chamber and first sliding chute being communicated with low-pressure compression chamber, first piston is rotationally arranged in low-pressure compression chamber, the height of first cylinder along the axial direction of crankshaft is H1, the diameter of low-pressure compression chamber is D1, the working volume of first cylinder is V1;

[0009] Second cylinder, being provided with high-pressure compression chamber and second sliding chute being communicated with high-pressure compression chamber, second piston is rotationally arranged in high-pressure compression chamber, the height of second cylinder along the axial direction of crankshaft is H2, the diameter of low-pressure compression chamber is D2, the working volume of second cylinder is V2;

[0010] A partition plate assembly is connected between the first cylinder and the second cylinder, and is provided with a communication passage through which the exhaust port of the low-pressure compression cavity is communicated with the suction port of the high-pressure compression cavity.

[0011] A first sliding sheet and a second sliding sheet, the first sliding sheet is slidingly arranged in the first sliding groove, the first sliding sheet abuts against the outer circumferential surface of the first piston, the thickness of the first sliding sheet is T1, the second sliding sheet is slidingly arranged in the second sliding groove, the second sliding sheet abuts against the outer circumferential surface of the second piston, and the thickness of the second sliding sheet is T2.

[0012] Wherein, U=(V2 / V1)×(D i ×L i ×T i ) / (H i ×e i ), i=1 or i=2, and 1≤U≤51 is satisfied.

[0013] The pump body assembly has at least the following beneficial effects:

[0014] When the pump body assembly is in operation, refrigerant outside the pump body assembly is sucked into the low-pressure compression cavity from the suction port of the low-pressure compression cavity, and the refrigerant completes primary compression in the low-pressure compression cavity. Then, the refrigerant is discharged from the exhaust port of the low-pressure compression cavity into the communication channel, and the refrigerant in the communication channel is sucked into the high-pressure compression cavity from the suction port of the high-pressure compression cavity. The refrigerant completes secondary compression in the high-pressure compression cavity. The low-pressure compression cavity and the high-pressure compression cavity are in a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. When i = 1 and U is less than 1, the product of the height H1 of the first cylinder and the eccentricity e1 of the first eccentric part is too large. The height H1 of the first cylinder is too large, which leads to the length of the crankshaft being too long. The eccentricity e1 of the first eccentric part is too large, which leads to the weakening of the strength of the crankshaft. During the operation of the compressor, the deflection of the crankshaft increases, the sealing performance of the low-pressure compression cavity decreases, the leakage amount of the refrigerant in the low-pressure compression cavity increases, and the volumetric efficiency of the compressor decreases. When i = 1 and U is greater than 51, the product of the height H1 of the first cylinder and the eccentricity e1 of the first eccentric part is too small. The height H1 of the first cylinder is too small, which leads to the volume of the low-pressure compression cavity being too small. The eccentricity e1 of the first eccentric part is too small, which leads to the increase of the wall thickness of the first piston. During the operation of the compressor, the unbalanced inertia of the crankshaft increases, the crankshaft is prone to twist and deformation, the leakage amount of the refrigerant in the low-pressure compression cavity increases, and the volumetric efficiency of the compressor decreases. When i = 2 and U is less than 1, the product of the height H2 of the second cylinder and the eccentricity e2 of the second eccentric part is too large. The height H2 of the second cylinder is too large, which leads to the length of the crankshaft being too long. The eccentricity e2 of the second eccentric part is too large, which leads to the weakening of the strength of the crankshaft. During the operation of the compressor, the deflection of the crankshaft increases, the sealing performance of the high-pressure compression cavity decreases, the leakage amount of the refrigerant in the high-pressure compression cavity increases, and the volumetric efficiency of the compressor decreases. When i = 2 and U is greater than 51, the product of the height H2 of the second cylinder and the eccentricity e1 of the second eccentric part is too small. The height H2 of the second cylinder is too small, which leads to the volume of the high-pressure compression cavity being too small. The eccentricity e1 of the second eccentric part is too small, which leads to the increase of the wall thickness of the second piston. During the operation of the compressor, the unbalanced inertia of the crankshaft increases, the crankshaft is prone to twist and deformation, the leakage amount of the refrigerant in the low-pressure compression cavity increases, and the volumetric efficiency of the compressor decreases. Therefore, by reasonably designing the relationship between the ratio of the working volume of the second cylinder to the working volume of the first cylinder, the diameter of the low-pressure compression cavity, the diameter of the high-pressure compression cavity, the width of the end face of the first piston along the radial direction of the first piston, the width of the end face of the second piston along the radial direction of the second piston, the thickness of the first sliding vane, the thickness of the second sliding vane, the height of the first cylinder, the height of the second cylinder, the eccentricity of the first eccentric part, and the eccentricity of the second eccentric part, the sealing performance of the low-pressure compression cavity and the high-pressure compression cavity can be improved, the leakage amount of the refrigerant in the compression cavity can be reduced, and the volumetric efficiency of the compressor can be improved.

[0015] According to some embodiments of the present application, the ratio of the height of the first cylinder along the axial direction of the crankshaft to the diameter of the low-pressure compression chamber is W1, satisfying: 0.25≤W1≤0.5; and / or,

[0016] The ratio of the height of the second cylinder along the axial direction of the crankshaft to the diameter of the high-pressure compression chamber is W2, satisfying: 0.25≤W2≤0.5.

[0017] According to some embodiments of the present application, the ratio of the eccentricity of the first eccentric part to the diameter of the low-pressure compression chamber is X1, satisfying: 0.08≤X1≤0.11; and / or,

[0018] The ratio of the eccentricity of the second eccentric part to the diameter of the high-pressure compression chamber is X2, satisfying: 0.08≤X2≤0.11.

[0019] According to some embodiments of the present application, the length of the first sliding vane along the sliding direction of the first sliding vane is L3, and the height of the first sliding vane along the axial direction of the crankshaft is H3, satisfying: 0.8≤L3 / H3≤1.4; and / or,

[0020] The length of the second sliding vane along the sliding direction of the second sliding vane is L4, and the height of the second sliding vane along the axial direction of the crankshaft is H4, satisfying: 0.8≤L4 / H4≤1.4.

[0021] According to some embodiments of the present application, the height of the first sliding vane along the axial direction of the crankshaft is H3, satisfying: 0.1≤T1 / H3≤0.28; and / or,

[0022] The height of the second sliding vane along the axial direction of the crankshaft is H4, satisfying: 0.1≤T2 / H4≤0.28.

[0023] According to some embodiments of the present application, the ratio of the working volume of the second cylinder to the working volume of the first cylinder is V P , satisfying: 0.4≤V P ≤0.8.

[0024] According to some embodiments of the present application, the exhaust pressure of the communication passage is greater than the exhaust pressure of the low-pressure compression chamber and less than the exhaust pressure of the high-pressure compression chamber.

[0025] According to some embodiments of the present application, the baffle assembly comprises a first baffle and a second baffle oppositely arranged along the axial direction of the crankshaft, the first baffle and the second baffle enclosing the communication passage, the first baffle being connected with the first cylinder, and the second baffle being connected with the second cylinder.

[0026] According to some embodiments of the present invention, the pump body assembly further includes a lower bearing and a lower muffler, both of which are connected to the first cylinder. The lower bearing and the lower muffler together form a first cavity, and the exhaust port of the low-pressure compression chamber is connected to the communicating channel through the first cavity.

[0027] The compressor according to a second aspect of the present invention includes the pump assembly described in the above embodiments.

[0028] The refrigeration equipment according to a third aspect of the present invention includes the compressor described in the above embodiments.

[0029] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0030] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0031] Figure 1 This is a cross-sectional schematic diagram of a pump body assembly according to an embodiment of the present invention;

[0032] Figure 2 This is a cross-sectional schematic diagram of a pump body assembly according to an embodiment of the present invention from another perspective;

[0033] Figure 3 This is a cross-sectional schematic diagram of a compressor according to an embodiment of the present invention;

[0034] Figure 4 for Figure 3 Sectional view of line AA in the middle;

[0035] Figure 5 This is a cross-sectional view of a first piston, a first sliding vane, a second piston, and a second sliding vane according to an embodiment of the present invention, wherein the first cylinder, the second cylinder, the partition assembly, and the crankshaft are hidden;

[0036] Figure 6 This is a schematic diagram of a first or second slider according to an embodiment of the present invention;

[0037] Figure 7 (V2 / V1)×(D) is an embodiment of this utility model. i ×L i ×T i ) / (H i ×e i The relationship between volumetric efficiency and compressor volumetric efficiency is shown in the graph.

[0038] Icon labels:

[0039] The axis O1, the crankshaft 100, the first eccentric part 110, the second eccentric part 120, the first piston 130, the second piston 140, the first cylinder 200, the low-pressure compression chamber 210, the first sliding groove 220, the second cylinder 300, the high-pressure compression chamber 310, the second sliding groove 320, the partition assembly 400, the communication channel 401, the first partition 410, the second partition 420, the first sliding piece 510, the second sliding piece 520, the first cavity 601, the second cavity 602, the lower bearing 610, the lower muffler 620, the upper bearing 630, the upper muffler 640, the shell 700, the inner cavity 710, the motor assembly 800, the stator 810, and the rotor 820. DETAILED DESCRIPTION

[0040] The embodiments of the present application are described in detail below, examples of which are shown in the drawings, wherein the same or similar notations represent the same or similar elements having the same or similar functions throughout. The embodiments described below by reference to the drawings are exemplary only, and are merely intended to explain the present application, and should not be understood as a limitation of the present application.

[0041] In the description of the present application, it should be understood that, in relation to the orientation description, for example, the orientation or position relationship indicated by up, down, etc. is based on the orientation or position relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as a limitation of the present application, which indicates or implies that the device or element indicated must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present application.

[0042] In the description of the present application, multiple refers to two or more. If there is a description of first, second, etc., it is only for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features or implicitly indicating the sequence of indicated technical features.

[0043] In the description of the present application, unless otherwise explicitly limited, the words such as setting, installing, connecting, etc. should be broadly understood, and the person skilled in the art can reasonably determine the specific meaning of the above words in the present application in combination with the specific content of the technical solution.

[0044] In the related art, the pump body assembly adopts a multi-stage compression technology to share the pressure ratio of each compression chamber, so that the compression chamber is within a relatively reasonable pressure ratio range. However, during the multi-stage compression of the refrigerant, the leakage amount of the refrigerant is still relatively large, resulting in insufficient volumetric efficiency of the compressor. It can be understood that, in general, the pressure ratio of the compressor is the ratio of the inlet and outlet pressures, but there is a pressure ratio of different compression chambers here.

[0045] Reference Figure 1 , Figure 1For an embodiment of the utility model discloses a pump body assembly's cross section schematic view, for example Figure 1 As shown, the utility model discloses an embodiment of a pump body assembly, and the pump body assembly includes crankshaft 100, first cylinder 200, second cylinder 300, upper bearing 630, lower bearing 610 and baffle assembly 400, and the crankshaft 100 includes the first eccentric part 110 and the second eccentric part 120 that are arranged along the axial direction interval of crankshaft 100, the first eccentric part 110 is equipped with first piston 130, and the second eccentric part 120 is equipped with second piston 140, and lower bearing 610, first cylinder 200, baffle assembly 400, second cylinder 300 and upper bearing 630 are sequentially connected along the axial direction of crankshaft 100, and first cylinder 200 is equipped with low-pressure compression chamber 210 and first runner 220, and first runner 220 is communicated with low-pressure compression chamber 210, and first runner 220 is slidably provided with first sliding sheet 510, and first piston 130 is rotatably arranged in low-pressure compression chamber 210, and the both ends of first piston 130 are respectively abutted with upper bearing 630 and baffle assembly 400, and first sliding sheet 510 is abutted with the outer circumferential surface of first piston 130, and second cylinder 300 is equipped with high-pressure compression chamber 310 and second runner 320, and second runner 320 is communicated with high-pressure compression chamber 310, and second runner 320 is slidably provided with second sliding sheet 520, and second piston 140 is rotatably arranged in high-pressure compression chamber 310, and the both ends of second piston 140 are respectively abutted with baffle assembly 400 and upper bearing 630, and second sliding sheet 520 is abutted with the outer circumferential surface of second piston 140, and baffle assembly 400 is equipped with communication passage 401, and the exhaust port of low-pressure compression chamber 210 is communicated with the suction port of high-pressure compression chamber 310 through communication passage 401, and when the pump body assembly works, the refrigerant outside the pump body assembly is inhaled into low-pressure compression chamber 210 from the suction port of low-pressure compression chamber 210, and the refrigerant completes primary compression in low-pressure compression chamber 210, then the refrigerant is discharged to communication passage 401 through the exhaust port of low-pressure compression chamber 210, and the refrigerant in communication passage 401 is inhaled into high-pressure compression chamber 310 from the suction port of high-pressure compression chamber 310, and the refrigerant completes secondary compression in high-pressure compression chamber 310, and low-pressure compression chamber 210 and high-pressure compression chamber 310 are in the reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor.

[0046] Refer to Figures 1 to 4 And combine Figure 6 , Figure 2 The pump body assembly of an embodiment of the utility model is in another view's cross section view, Figure 3 The cross section view of the compressor of an embodiment of the utility model, Figure 4 For Figure 3 The cross section view of A-A line, Figure 6It is the schematic view of the first sliding vane 510 or the second sliding vane 520 of the embodiment of the utility model. As shown in the drawing, in the embodiment of the utility model, the eccentricity of the first eccentric part 110 is e1, the eccentricity of the second eccentric part 120 is e2, the width of the end face of the first piston 130 along the radial direction of the first piston 130 is L1, the width of the end face of the second piston 140 along the radial direction of the second piston 140 is L2, the height of the first cylinder 200 along the axial direction of the crankshaft 100 is H1, the diameter of the low-pressure compression chamber 210 is D1, the working volume of the first cylinder 200 is V1, the height of the second cylinder 300 along the axial direction of the crankshaft 100 is H2, the diameter of the high-pressure compression chamber 310 is D2, the working volume of the second cylinder 300 is V2, the thickness of the first sliding vane 510 is T1, the thickness of the second sliding vane 520 is T2, and the above-mentioned various parameters satisfy the specified relationship U, U = (V2 / V1) x (D i ×L i ×T i ) / (H i ×e i ), i = 1 or i = 2, which satisfies: 1 ≤ U ≤ 51, for example, U can be 1, 2, 4, 10, 20, 30, 40, 50, etc. It should be noted that the working volume generally refers to the remaining volume between the compression chamber of the cylinder and the piston rotatingly installed inside the compression chamber, the unit of the working volume is cc, the units of the diameter of the compression chamber, the width of the end face, the thickness of the sliding vane, the height of the cylinder and the eccentricity are all mm, and the same units are adopted in the subsequent embodiments. It can be understood that the end face of the first piston 130 refers to the surface of the first piston 130 abutting against the partition plate assembly 400, or the surface of the first piston 130 abutting against the lower bearing 610; the end face of the second piston 140 refers to the surface of the second piston 140 abutting against the partition plate assembly 400, or the surface of the second piston 140 abutting against the upper bearing 630; the eccentricity e1 of the first eccentric part 110 refers to the minimum distance between the axis O1 of the crankshaft 100 and the axis of the first eccentric part 110; the eccentricity e2 of the second eccentric part 120 refers to the minimum distance between the axis O1 of the crankshaft 100 and the axis of the second eccentric part 120.

[0047] It should be noted that the diameter of the compression chamber is too large, which increases the clearance volume of the cylinder (the clearance volume refers to the volume of the gas remaining in the cylinder after compression), the gas remaining in the clearance volume will expand again during the suction process, occupying part of the suction volume, and the actual suction volume of the compression chamber is reduced, thereby reducing the volumetric efficiency of the compressor; the diameter of the compression chamber is too small, which directly reduces the suction volume of the cylinder, resulting in a decrease in the amount of gas sucked into the compression chamber per cycle, thereby reducing the volumetric efficiency of the compressor.

[0048] It should be noted that the excessive width of the end surface of the piston along the radial direction of the piston leads to the deterioration of the high-clearance leakage of the piston, and the insufficient width of the end surface of the piston along the radial direction of the piston leads to the reduction of the contact area of the end surface of the piston, the increase of the risk of gas leakage, especially the leakage from the high-pressure side to the low-pressure side of the compression chamber, thereby reducing the amount of effectively compressed gas and reducing the volumetric efficiency of the compressor.

[0049] It should be noted that the excessive thickness of the sliding vane leads to the uneven gap between the sliding vane and the piston, and the insufficient thickness of the sliding vane leads to the insufficient strength of the sliding vane, easy bending deformation, and the increase of the risk of gas leakage, thereby reducing the volumetric efficiency of the compressor.

[0050] It should be noted that the influence of the height of the cylinder on the volumetric efficiency of the compressor is similar to the influence of the diameter of the compression chamber on the volumetric efficiency of the compressor. The excessive height of the cylinder leads to the increase of the clearance volume of the cylinder, and the gas remaining in the clearance volume will re-expand during the suction process, occupying part of the suction volume, thereby reducing the amount of gas actually sucked into the compression chamber and reducing the volumetric efficiency of the compressor. The excessive height of the cylinder directly reduces the suction volume of the cylinder, leading to the reduction of the amount of gas sucked into the compression chamber during each cycle, thereby reducing the volumetric efficiency of the compressor.

[0051] It should be noted that the excessive eccentricity of the eccentric part leads to the weakening of the strength of the crankshaft, the easy twisting and deformation of the crankshaft, the increase of the wear amount of the piston, the reduction of the sealing performance of the compression chamber, the increase of the risk of gas leakage, and the reduction of the volumetric efficiency of the compressor. The insufficient eccentricity of the eccentric part leads to the increase of the wall thickness of the piston, the increase of the unbalanced inertia of the crankshaft during the operation of the compressor, the easy twisting and deformation of the crankshaft, the increase of the wear amount of the piston, the reduction of the sealing performance of the compression chamber, the increase of the risk of gas leakage, and the reduction of the volumetric efficiency of the compressor.

[0052] It can be understood that the excessive product of the diameter of the compression chamber, the width of the end surface of the piston along the radial direction of the piston, and the thickness of the sliding vane leads to the increase of the clearance volume of the cylinder, and the gas remaining in the clearance volume will re-expand during the suction process, occupying part of the suction volume, thereby reducing the amount of gas actually sucked into the compression chamber and reducing the volumetric efficiency of the compressor. The insufficient product of the diameter of the compression chamber, the width of the end surface of the piston along the radial direction of the piston, and the thickness of the sliding vane leads to the reduction of the suction volume of the compression chamber and the weakening of the sealing performance of the compression chamber, the increase of the risk of gas leakage, and the reduction of the volumetric efficiency of the compressor.

[0053] It can be understood that when V2 / V1 is too small, the working volume V1 of the first cylinder 200 is too large, the high-pressure compression chamber 310 cannot completely consume the refrigerant discharged by the low-pressure compression chamber 210, the performance is excessive, and the volumetric efficiency of the compressor is reduced; when V2 / V1 is too large, for the low-temperature heating working condition, the working volume V2 of the second cylinder 300 is too large, which is equivalent to that the working volume V1 of the first cylinder 200 is too small, the suction amount of the second cylinder 300 is insufficient, the heating capacity is insufficient, and the user experience is poor.

[0054] For example, when i=1, U=(V2 / V1)×(D1×L1×T1) / (H1×e1). Taking the ratio of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 V2 / V1, the diameter D1 of the low-pressure compression chamber 210, the width L1 of the end surface of the first piston 130 along the radial direction of the first piston 130, and the thickness T1 of the first sliding vane 510 as examples, when U is less than 1, the product of the height H1 of the first cylinder 200 and the eccentric amount e1 of the first eccentric part 110 is too large, the height H1 of the first cylinder 200 is too large, which leads to that the length of the crankshaft 100 is too long, the eccentric amount e1 of the first eccentric part 110 is too large, which leads to that the strength of the crankshaft 100 is weakened, under the joint action of the height H1 of the first cylinder 200 being too large and the eccentric amount e1 of the first eccentric part 110 being too large, the deflection of the crankshaft 100 increases during the operation of the compressor, the crankshaft 100 is prone to twisting and deformation, the wear amount of the first piston 130 increases, the sealing performance of the low-pressure compression chamber 210 decreases, and the leakage amount of the refrigerant in the low-pressure compression chamber 210 increases, which leads to that the volumetric efficiency of the compressor is reduced; when U is greater than 51, the product of the height H1 of the first cylinder 200 and the eccentric amount e1 of the first eccentric part 110 is too small, the height H1 of the first cylinder 200 is too small, which leads to that the volume of the low-pressure compression chamber 210 is too small, the eccentric amount e1 of the first eccentric part 110 is too small, which leads to that the wall thickness of the first piston 130 increases, the unbalanced inertia amount of the crankshaft 100 increases during the operation of the compressor, the crankshaft 100 is prone to twisting and deformation, the wear amount of the first piston 130 increases, the sealing performance of the low-pressure compression chamber 210 decreases, and the leakage amount of the refrigerant in the low-pressure compression chamber 210 increases, under the joint action of the height of the first cylinder 200 being too small and the eccentric amount of the first eccentric part 110 being too small, the volumetric efficiency of the compressor is reduced. Therefore, reasonably designing the relationship between the ratio V2 / V1 of the working volume of the second cylinder 300 to the working volume of the first cylinder 200, the diameter D1 of the low-pressure compression chamber 210, the width L1 of the end surface of the first piston 130 along the radial direction of the first piston 130, the thickness T1 of the first sliding vane 510, the height H1 of the first cylinder 200, and the eccentric amount e1 of the first eccentric part 110 can improve the sealing performance of the low-pressure compression chamber 210 to reduce the leakage amount of the refrigerant in the low-pressure compression chamber 210, thereby improving the volumetric efficiency of the compressor.

[0055] As another implementation, when i = 2, U = (V2 / V1) x (D2 x L2 x T2) / (H2 x e2). With the ratio of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 V2 / V1 unchanged, the diameter D2 of the high-pressure compression chamber 310 unchanged, the width L2 of the end face of the second piston 140 along the radial direction of the second piston 140 unchanged, and the thickness T2 of the second sliding sheet 520 unchanged, when U is less than 1, the product of the height H2 of the second cylinder 300 and the eccentric amount e2 of the second eccentric part 120 is too large, the height H2 of the second cylinder 300 is too large, which causes the length of the crankshaft 100 to be too long, the eccentric amount e2 of the second eccentric part 120 is too large, which causes the strength of the crankshaft 100 to be weakened, under the joint action of the height H2 of the second cylinder 300 being too large and the eccentric amount e2 of the second eccentric part 120 being too large, the deflection of the crankshaft 100 increases during the operation of the compressor, the crankshaft 100 is prone to twisting and deformation, the wear amount of the second piston 140 increases, the sealing performance of the high-pressure compression chamber 310 decreases, the leakage amount of the refrigerant in the high-pressure compression chamber 310 increases, and the volumetric efficiency of the compressor is reduced; when U is greater than 51, the product of the height H2 of the second cylinder 300 and the eccentric amount e2 of the second eccentric part 120 is too small, the height H2 of the second cylinder 300 is too small, which causes the volume of the low-pressure compression chamber 210 to be too small, the eccentric amount e2 of the second eccentric part 120 is too small, which causes the wall thickness of the second piston 140 to increase, the unbalanced inertia amount of the crankshaft 100 increases during the operation of the compressor, the crankshaft 100 is prone to twisting and deformation, the wear amount of the second piston 140 increases, the sealing performance of the high-pressure compression chamber 310 decreases, the leakage amount of the refrigerant in the high-pressure compression chamber 310 increases, and the volumetric efficiency of the compressor is reduced under the joint action of the height H2 of the second cylinder 300 being too small and the eccentric amount e2 of the second eccentric part 120 being too small. Therefore, reasonable design of the relationship between the ratio of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 V2 / V1, the diameter D2 of the high-pressure compression chamber 310, the width L2 of the end face of the second piston 140 along the radial direction of the second piston 140, the thickness T2 of the second sliding sheet 520, the height H2 of the second cylinder 300, and the eccentric amount e2 of the second eccentric part 120 can improve the sealing performance of the high-pressure compression chamber 310 to reduce the leakage amount of the refrigerant in the high-pressure compression chamber 310, thereby improving the volumetric efficiency of the compressor.

[0056] Referring to Figure 7 , Figure 7 (V2 / V1) x (D i x L i x T i ) / (H i x e i) and the volumetric efficiency of the compressor, the column in the figure refers to the volumetric efficiency of the compressor at different values of U, and the dotted line in the figure refers to the fitting curve of the volumetric efficiency of the compressor at different values of U. As shown in the figure, when the value of U gradually increases, in the range of 1 to 51, the volumetric efficiency of the compressor is greater than 90%, and the volumetric efficiency of the compressor first gradually increases and then decreases. Therefore, by reasonably designing the ratio V2 / V1 of the working volume of the second cylinder 300 to the working volume of the first cylinder 200, the diameter D1 of the low-pressure compression chamber 210, the diameter D2 of the high-pressure compression chamber 310, the width L1 of the end face of the first piston 130 along the radial direction of the first piston 130, the width L2 of the end face of the second piston 140 along the radial direction of the second piston 140, the thickness T1 of the first sliding vane 510, the thickness T2 of the second sliding vane 520, the height H1 of the first cylinder 200, the height H2 of the second cylinder 300, the eccentricity e1 of the first eccentric part 110, and the eccentricity e2 of the second eccentric part 120, the sealing performance of the low-pressure compression chamber 210 and the high-pressure compression chamber 310 can be improved to reduce the leakage amount of the refrigerant in the compression chamber, thereby improving the volumetric efficiency of the compressor.

[0057] For example Figure 2 As shown in the figure, in the embodiment of the utility model, the ratio of the height H1 of the first cylinder 200 along the axial direction of the crankshaft 100 to the diameter D1 of the low-pressure compression chamber 210 is W1, W1=H1 / D1, which satisfies: 0.25≤W1≤0.5, for example, W1 can be 0.25, 0.3, 0.35, 0.4, 0.45, 0.5, by reasonably designing the relationship between the height H1 of the first cylinder 200 along the axial direction of the crankshaft 100 and the diameter D1 of the low-pressure compression chamber 210, when designing the first cylinder 200 with any working volume, the compressor can have better performance, ensuring that the first cylinder 200 has better expandability.

[0058] For example, when the diameter D1 of the low-pressure compression chamber 210 is constant, when W1 is less than 0.25, the height H1 of the first cylinder 200 along the axial direction of the crankshaft 100 is too small, the working volume of the first cylinder 200 is insufficient, which leads to the decrease of the volumetric efficiency of the compressor, when W1 is greater than 0.5, the height H1 of the first cylinder 200 along the axial direction of the crankshaft 100 is too large, the contact area between the first piston 130 and the side wall of the low-pressure compression chamber 210 increases, the friction between the first piston 130 and the first cylinder 200 increases, the mechanical efficiency of the compressor decreases and the energy consumption increases, which leads to the decrease of the performance of the compressor. Therefore, by reasonably designing the relationship between the height H1 of the first cylinder 200 along the axial direction of the crankshaft 100 and the diameter D1 of the low-pressure compression chamber 210, when designing the first cylinder 200 with any working volume, the compressor can have better performance, ensuring that the first cylinder 200 has better expandability.

[0059] Similarly, the ratio of the height H2 of the second cylinder 300 along the axial direction of the crankshaft 100 to the diameter D2 of the high-pressure compression chamber 310 is W2, W2 = H2 / D2, and 0.25 ≤ W2 ≤ 0.5 is satisfied, for example, W2 can be 0.25, 0.3, 0.35, 0.4, 0.45, or 0.5. By reasonably restricting the relationship between the height H2 of the second cylinder 300 along the axial direction of the crankshaft 100 and the diameter D2 of the high-pressure compression chamber 310, the compressor can have better performance when the second cylinder 300 with any working volume is designed, and the second cylinder 300 has better expandability.

[0060] For example, when the diameter D2 of the high-pressure compression chamber 310 is constant, when W2 is less than 0.25, the height H2 of the second cylinder 300 along the axial direction of the crankshaft 100 is too small, the working volume V2 of the second cylinder 300 is insufficient, and the volumetric efficiency of the compressor is reduced; when W2 is greater than 0.5, the height H2 of the second cylinder 300 along the axial direction of the crankshaft 100 is too large, the contact area between the second piston and the side wall of the high-pressure compression chamber 310 increases, the friction between the second piston 140 and the second cylinder 300 increases, the mechanical efficiency of the compressor is reduced, the energy consumption is increased, and the performance of the compressor is reduced. Therefore, by reasonably restricting the relationship between the height H2 of the second cylinder 300 along the axial direction of the crankshaft 100 and the diameter D2 of the high-pressure compression chamber 310, the compressor can have better performance when the second cylinder 300 with any working volume is designed, and the second cylinder 300 has better expandability.

[0061] For example Figure 1 As shown in the embodiment of the utility model, the ratio of the eccentric amount e1 of the first eccentric part 110 to the diameter D1 of the low-pressure compression chamber 210 is X1, X1 = e1 / D 1， 0.08 ≤ X1 ≤ 0.11 is satisfied, for example, X1 can be 0.08, 0.09, 0.10, or 0.11. By reasonably designing the relationship between the eccentric amount e1 of the first eccentric part 110 and the diameter D1 of the low-pressure compression chamber 210, the service life and performance of the compressor can be improved.

[0062] For example, when the ratio of the eccentricity e1 of the first eccentric portion 110 to the diameter D1 of the low-pressure compression chamber 210 is X1, X1 = e1 / D1, and X1 is less than 0.08, the eccentricity e1 of the first eccentric portion 110 is too small, the wall thickness of the first piston 130 is increased, the width of the end surface of the first piston 130 along the radial direction of the first piston 130 is increased, the friction pair between the first piston 130 and the partition assembly 400 is increased, or the friction pair between the first piston 130 and the lower bearing 610 is increased, which leads to the performance of the compressor being reduced; when X1 is greater than 0.11, the eccentricity e1 of the first eccentric portion 110 is too large, which leads to the strength of the crankshaft 100 being weakened, the crankshaft 100 is prone to being twisted and deformed, and the service life of the compressor is affected. Therefore, by reasonably designing the relationship between the eccentricity e1 of the first eccentric portion 110 and the diameter D1 of the low-pressure compression chamber 210, the service life and performance of the compressor can be improved.

[0063] Similarly, the ratio of the eccentricity e2 of the second eccentric portion 120 to the diameter D2 of the high-pressure compression chamber 310 is X2, X2 = e2 / D2. 2， Satisfying: 0.08≤X2≤0.11, for example, X2 can be 0.08, 0.09, 0.10, 0.11, by reasonably designing the relationship between the eccentricity e2 of the second eccentric portion 120 and the diameter D2 of the high-pressure compression chamber 310, the service life and performance of the compressor can be improved.

[0064] For example, when the ratio of the eccentricity e2 of the second eccentric portion 120 to the diameter D2 of the high-pressure compression chamber 310 is X2, X2 = e2 / D2, and X2 is less than 0.08, the eccentricity e2 of the second eccentric portion 120 is too small, the wall thickness of the second piston 140 is increased, the width of the end surface of the second piston 140 along the radial direction of the second piston 140 is increased, the friction pair between the second piston 140 and the partition assembly 400 is increased, or the friction pair between the second piston 140 and the upper bearing 630 is increased, which leads to the performance of the compressor being reduced; when X2 is greater than 0.11, the eccentricity e2 of the second eccentric portion 120 is too large, which leads to the strength of the crankshaft 100 being weakened, the crankshaft 100 is prone to being twisted and deformed, and the service life of the compressor is affected. Therefore, by reasonably designing the relationship between the eccentricity of the second eccentric portion 120 and the diameter of the high-pressure compression chamber 310, the service life and performance of the compressor can be improved.

[0065] Referring to Figure 5 , Figure 5 is a sectional view of the first piston 130, the first sliding vane 510, the second piston 140, and the second sliding vane 520 of an embodiment of the utility model. For example Figure 5As shown, in the embodiment of the utility model, along the sliding direction of first sliding piece 510, the maximum length of first sliding piece 510 is L3, the height of first sliding piece 510 along the axial direction of crankshaft 100 is H3, satisfy: 0.8≤L3 / H3≤1.4, for example, L3 / H3 can be 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, by the reasonable design between the maximum length L3 of first sliding piece 510 along the sliding direction of first sliding piece 510 and the height H3 of first sliding piece 510 along the axial direction of crankshaft 100, can reduce the leakage of refrigerant in low-pressure compression chamber 210, thereby improving the volumetric efficiency of compressor.

[0066] It can be understood that L3 / H3 represents the relationship between the height gap leakage and the radial leakage of low-pressure compression chamber 210, when L3 / H3 is less than 0.8, the height gap leakage increases rapidly, when L3 / H3 is greater than 1.4, the radial sealing distance decreases, the radial leakage deteriorates obviously, resulting in the volumetric efficiency of compressor decreases significantly. Therefore, by reasonably designing the relationship between the maximum length L3 of first sliding piece 510 along the sliding direction of first sliding piece 510 and the height H3 of first sliding piece 510 along the axial direction of crankshaft 100, the leakage of refrigerant in low-pressure compression chamber 210 can be reduced, thereby improving the volumetric efficiency of compressor.

[0067] In the embodiment of the utility model, the ratio of the thickness T1 of first sliding piece 510 and the height H3 of first sliding piece 510 along the axial direction of crankshaft 100 is T1 / H3, satisfy: 0.1≤T1 / H3≤0.28, for example, T1 / H3 can be 0.1, 0.12, 0.14, 0.16, 0.18, 0.2, 0.22, 0.24, 0.26, 0.28, by reasonably designing the relationship between the thickness T1 of first sliding piece 510 and the height H3 of first sliding piece 510 along the axial direction of crankshaft 100, the volumetric efficiency of compressor can be increased and the performance of compressor can be improved.

[0068] It can be understood that T1 / H3 represents the relationship between the front end leakage of first sliding piece 510 and the contact force of the front end of first sliding piece 510, the front end of first sliding piece 510 refers to the end of first sliding piece 510 abutting with the outer circumferential surface of first piston 130. Taking the thickness T1 of first sliding piece 510 as an example, when T1 / H3 is less than 0.1, the contact force of the front end of first sliding piece 510 decreases, the leakage of refrigerant in low-pressure compression chamber 210 increases, resulting in the volumetric efficiency of compressor decreases, when T1 / H3 is greater than 0.28, the contact force of the front end of first sliding piece 510 increases, resulting in the abrasion between first sliding piece 510 and first piston 130 increases, the performance of compressor decreases. Therefore, by reasonably designing the relationship between the thickness T1 of first sliding piece 510 and the height H3 of first sliding piece 510 along the axial direction of crankshaft 100, the volumetric efficiency of compressor can be increased and the performance of compressor can be improved.

[0069] Similarly, along the sliding direction of the second sliding vane 520, the maximum length of the second sliding vane 520 is L4, and the height of the second sliding vane 520 along the axial direction of the crankshaft 100 is H4, and the following is satisfied: 0.8≤L4 / H4≤1.4, for example, L4 / H4 can be 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, by reasonably designing the relationship between the maximum length L4 of the second sliding vane 520 along the sliding direction of the second sliding vane 520 and the height H4 of the second sliding vane 520 along the axial direction of the crankshaft 100, the leakage amount of the refrigerant in the high-pressure compression chamber 310 can be reduced, thereby improving the volumetric efficiency of the compressor.

[0070] For example, L4 / H4 represents the relationship between the height gap leakage and the radial leakage of the high-pressure compression chamber 310, when L4 / H4 is less than 0.8, the height gap leakage increases rapidly, when L4 / H4 is greater than 1.4, the radial sealing distance decreases, and the radial leakage deteriorates obviously, resulting in a significant decrease in the volumetric efficiency of the compressor. Therefore, by reasonably designing the relationship between the maximum length L4 of the second sliding vane 520 along the sliding direction of the second sliding vane 520 and the height H4 of the second sliding vane 520 along the axial direction of the crankshaft 100, the leakage amount of the refrigerant in the high-pressure compression chamber 310 can be reduced, thereby improving the volumetric efficiency of the compressor.

[0071] It can be understood that T2 / H4 represents the relationship between the front end leakage of the second sliding vane 520 and the contact force of the front end of the second sliding vane 520. The front end of the second sliding vane 520 refers to the end of the second sliding vane 520 abutting against the outer peripheral surface of the second piston 140. Taking the thickness T2 of the second sliding vane 520 as an example, when T2 / H4 is less than 0.1, the contact force of the front end of the second sliding vane 520 decreases, the leakage amount of the refrigerant in the high-pressure compression chamber increases, and the volumetric efficiency of the compressor decreases; when T2 / H4 is greater than 0.28, the contact force of the front end of the second sliding vane 520 increases, resulting in an increase in the wear between the second sliding vane 520 and the second piston 140, and a decrease in the performance of the compressor. Therefore, by reasonably designing the relationship between the thickness T2 of the second sliding vane 520 and the height H4 of the second sliding vane 520 along the axial direction of the crankshaft 100, the volumetric efficiency of the compressor can be increased and the performance of the compressor can be improved.

[0072] In the embodiment of the utility model, the ratio of the working volume V2 of the second cylinder 300 and the working volume V1 of the first cylinder 200 is V P , V P = V2 / V1 satisfies: 0.4≤V P ≤0.8, the unit of working volume is cc, for example, V P =0.4, V P =0.5, V P =0.6, V P =0.7, VP =0.8. Taking the working volume of the second cylinder 300 as an example, when V P is less than 0.4, the working volume of the first cylinder 200 is too large, the high-pressure compression chamber 310 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 210, the performance is excessive, and the volumetric efficiency of the compressor is reduced; when V P is greater than 0.8, for the low-temperature heating working condition, the working volume of the first cylinder 200 is too small, the suction amount of the high-pressure compression chamber 310 is insufficient, the heating capacity of the compressor is reduced, and the user experience is poor. Therefore, by reasonably designing the ratio of the working volume of the second cylinder 300 to the working volume of the first cylinder 200, the suction pulsation and the exhaust pulsation can be reduced, the vibration and the noise can be reduced, and the volumetric efficiency of the compressor can be improved.

[0073] In the embodiment of the utility model, the exhaust pressure of the communication passage 401 is greater than the exhaust pressure of the low-pressure compression chamber 210, and the exhaust pressure of the communication passage 401 is less than the exhaust pressure of the high-pressure compression chamber 310, the communication passage is petal-shaped structure, the communication passage 401 can buffer the refrigerant discharged from the low-pressure compression chamber 210, when the pump body assembly operates, the refrigerant discharged from the exhaust port of the low-pressure compression chamber 210 enters the communication passage 401, which is conducive to reducing the exhaust pulsation and improving the performance of the compressor.

[0074] As another implementation mode, the communication passage 401 can also be a through hole, a plurality of through holes are arranged, the plurality of through holes are arranged at intervals around the axis O1 of the crankshaft 100, and the two ends of each through hole are respectively communicated with the first cavity 601 and the suction port of the high-pressure compression chamber 310, which can effectively reduce the exhaust loss of the low-pressure compression chamber 210 and improve the performance of the compressor.

[0075] For example Figure 1 , Figure 2 As shown in the utility model, the pump body assembly further comprises a lower muffler 620, the lower muffler 620 is connected to the lower bearing 610, and the lower muffler 620 is located on the side of the lower bearing 610 away from the first cylinder 200, the lower muffler 620 and the lower bearing 610 form the first cavity 601, the exhaust port of the low-pressure compression chamber 210 is communicated with the communication passage 401 through the first cavity 601, which is conducive to reducing the exhaust noise and improving the user experience.

[0076] It can be understood that the lower bearing 610 is provided with a valve seat, and the refrigerant in the low-pressure compression chamber 210 can enter the first cavity 601 through the valve seat. In another embodiment of the utility model, the lower bearing 610 and the partition assembly 400 are both provided with valve seats, and the refrigerant in the low-pressure compression chamber 210 enters the first cavity 601 and the communication passage 401 through the two valve seats respectively. 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.

[0077] In the embodiment of the utility model, the baffle assembly 400 includes the first baffle 410 and the second baffle 420, the first baffle 410 and the second baffle 420 are oppositely arranged along the axial direction of the crankshaft 100, the first baffle 410 is below the second baffle 420, the first baffle 410 and the second baffle 420 enclose the communication passage 401, the first baffle 410 is connected with the upper end surface of the first cylinder 200, the second baffle 420 is connected with the lower end surface of the second cylinder 300, the first baffle 410 and the second baffle 420 can be machined respectively, which is conducive to machining the communication passage 401 on the baffle assembly 400, and the machining cost of the baffle assembly 400 can be reduced.

[0078] It should be noted that the first baffle 410 and the second baffle 420 are provided with a connecting structure, and the connecting structure is used for connecting and fixing the first baffle 410 and the second baffle 420. For example, the connecting structure includes a connecting piece, the connecting piece is a screw or a bolt, the connecting piece includes a rod part and a connecting part, the rod part is provided with a head at one end, the rod part is threaded through the second baffle 420 and is connected with the first baffle 410, and the head is installed in the second baffle 420, which can facilitate the connection and fixation of the first baffle 410 and the second baffle 420. As another embodiment, the connecting piece is a pin, one end of the connecting piece is fixedly connected with the first baffle 410, and the other end of the connecting piece is fixedly connected with the second baffle 420, which can also facilitate the connection and fixation of the first baffle 410 and the second baffle 420, and details are not repeated here.

[0079] It should be noted that the connecting piece is provided with multiple connecting pieces, and the multiple connecting pieces are arranged around the axis O1 of the crankshaft 100, which can increase the connection stability of the first baffle 410 and the second baffle 420, and details are not repeated here.

[0080] In the embodiment of the utility model, the pump body assembly further includes an upper muffler 640, the upper muffler 640 is connected to the upper bearing 630, a second cavity 602 is formed between the upper bearing 630 and the upper muffler 640, the exhaust port of the high-pressure compression cavity 310 is communicated with the second cavity 602, and the refrigerant discharged from the high-pressure compression cavity 310 can enter the third cavity and then be discharged to the inner cavity 710 of the shell 700 of the compressor, which is conducive to reducing the exhaust noise and improving the user experience.

[0081] For example Figure 3As shown, the compressor of the second aspect embodiment of the utility model, including shell 700 and the pump body assembly of above embodiment, shell 700 has inner chamber 710, and pump body assembly is installed in inner chamber 710.Compressor by adopting the pump body assembly of above embodiment, when pump body assembly works, the refrigerant outside pump body assembly is inhaled low pressure compression chamber 210 from the suction port of low pressure compression chamber 210, and the refrigerant completes primary compression in low pressure compression chamber 210, then, the refrigerant is discharged to the communication passage 401 through the exhaust port of low pressure compression chamber 210, and the refrigerant in communication passage 401 is inhaled high pressure compression chamber 310 from the suction port of high pressure compression chamber 310, and the refrigerant completes secondary compression in high pressure compression chamber 310, and low pressure compression chamber 210 and high pressure compression chamber 310 are in reasonable pressure ratio range, can improve the volumetric efficiency of compressor.Because the eccentricity of first eccentric part 110 is e1, the eccentricity of second eccentric part 120 is e2, the width of the end face of first piston 130 along the radial direction of first piston 130 is L1, the width of the end face of second piston 140 along the radial direction of second piston 140 is L2, the height of first cylinder 200 along the axial direction of crankshaft 100 is H1, the diameter of low pressure compression chamber 210 is D1, the working volume of first cylinder 200 is V1, the height of second cylinder 300 along the axial direction of crankshaft 100 is H2, the diameter of high pressure compression chamber 310 is D2, the working volume of second cylinder 300 is V2, the thickness of first sliding vane 510 is T1, the thickness of second sliding vane 520 is T2, and the above-mentioned various parameters satisfy the specified relationship U, U=(V2 / V1)×(D i ×L i ×T i ) / (H i ×e i), i = 1 or i = 2, satisfies: 1≤U≤51. When i = 1 and U is less than 1, the product of the height H1 of the first cylinder 200 and the eccentricity e1 of the first eccentric portion 110 is too large, the height H1 of the first cylinder 200 is too large to cause the length of the crankshaft 100 to be too long, the eccentricity e1 of the first eccentric portion 110 is too large to cause the strength of the crankshaft 100 to be weakened, the deflection of the crankshaft 100 is increased during the operation of the compressor, the sealing performance of the low-pressure compression chamber 210 is decreased, the leakage amount of the refrigerant in the low-pressure compression chamber 210 is increased, and the volumetric efficiency of the compressor is reduced. When i = 1 and U is greater than 51, the product of the height H1 of the first cylinder 200 and the eccentricity e1 of the first eccentric portion 110 is too small, the height H1 of the first cylinder 200 is too small to cause the volume of the low-pressure compression chamber 210 to be too small, the eccentricity e1 of the first eccentric portion 110 is too small to cause the wall thickness of the first piston 130 to be increased, the unbalanced inertia amount of the crankshaft 100 is increased during the operation of the compressor, the crankshaft 100 is prone to be twisted and deformed, the leakage amount of the refrigerant in the low-pressure compression chamber 210 is increased, and the volumetric efficiency of the compressor is reduced. When i = 2 and U is less than 1, the product of the height H2 of the second cylinder 300 and the eccentricity e2 of the second eccentric portion 120 is too large, the height H2 of the second cylinder 300 is too large to cause the length of the crankshaft 100 to be too long, the eccentricity e2 of the second eccentric portion 120 is too large to cause the strength of the crankshaft 100 to be weakened, the deflection of the crankshaft 100 is increased during the operation of the compressor, the sealing performance of the high-pressure compression chamber 310 is decreased, the leakage amount of the refrigerant in the high-pressure compression chamber 310 is increased, and the volumetric efficiency of the compressor is reduced. When i = 2 and U is greater than 51, the product of the height H2 of the second cylinder 300 and the eccentricity e2 of the second eccentric portion 120 is too small, the height H2 of the second cylinder 300 is too small to cause the volume of the high-pressure compression chamber 310 to be too small, the eccentricity e2 of the second eccentric portion 120 is too small to cause the wall thickness of the second piston 140 to be increased, the unbalanced inertia amount of the crankshaft 100 is increased during the operation of the compressor, the crankshaft 100 is prone to be twisted and deformed, the leakage amount of the refrigerant in the low-pressure compression chamber 210 is increased, and the volumetric efficiency of the compressor is reduced. Therefore, the reasonable design of the relationship between the ratio V2 / V1 of the working volume of the second cylinder 300 to the working volume of the first cylinder 200, the diameter D1 of the low-pressure compression chamber 210, the diameter D2 of the high-pressure compression chamber 310, the width L1 of the end face of the first piston 130 along the radial direction of the first piston 130, the width L2 of the end face of the second piston 140 along the radial direction of the second piston 140, the thickness T1 of the first vane 510, the thickness T2 of the second vane 520, the height H1 of the first cylinder 200, the height H2 of the second cylinder 300, the eccentricity e1 of the first eccentric portion 110, and the eccentricity e2 of the second eccentric portion 120 can improve the sealing performance of the low-pressure compression chamber 210 and the high-pressure compression chamber 310, reduce the leakage amount of the refrigerant in the compression chamber, and thus improve the volumetric efficiency of the compressor.

[0082] In the embodiment, the upper bearing 630 of the pump body assembly is fixedly connected with the inner circumferential surface of the inner cavity 710, or the first cylinder 200 and / or the second cylinder 300 is fixedly connected with the inner circumferential surface of the inner cavity 710, and the fixedly connected manner can be welding or interference fit, wherein the welding manner includes but is not limited to resistance welding and laser welding.

[0083] In the embodiment, the compressor further comprises a motor assembly 800, the motor assembly 800 comprises a stator 810 and a rotor 820 rotatably arranged in the stator 810, the outer circumferential surface of the rotor 820 abuts against the inner circumferential surface of the shell 700, the rotor 820 is fixedly connected with the upper end of the crankshaft 100, and the stator 810 drives the crankshaft 100 to rotate through the rotor 820.

[0084] Since the compressor adopts all the technical solutions of the pump body assembly of the above-mentioned embodiments, at least all the beneficial effects brought by the technical solutions of the above-mentioned embodiments are achieved, and details are not repeated here.

[0085] The refrigeration equipment of the third aspect embodiment of the utility model comprises the compressor of the above-embodiment.

[0086] The utility model embodiments are described in detail above in combination with the drawings, but the utility model is not limited to the above-mentioned embodiments, and various changes can be made within the knowledge range possessed by those skilled in the art without departing from the purpose of the utility model.

Claims

1. A pump body assembly, characterized by, The application relates to a crankshaft, a first cylinder, a second cylinder, a partition assembly, a first sliding sheet and a second sliding sheet. The crankshaft comprises a first eccentric part and a second eccentric part which are arranged at intervals along the axial direction of the crankshaft, the eccentricity of the first eccentric part is e1, the eccentricity of the second eccentric part is e2, the first eccentric part is sleeved with a first piston, the width of the end surface of the first piston along the radial direction of the first piston is L1, the second eccentric part is sleeved with a second piston, the width of the end surface of the second piston along the radial direction of the second piston is L2; The first cylinder is provided with a low-pressure compression chamber and a first sliding groove which is communicated with the low-pressure compression chamber, the first piston is arranged in rotation in the low-pressure compression chamber, the height of the first cylinder along the axial direction of the crankshaft is H1, the diameter of the low-pressure compression chamber is D1, and the working volume of the first cylinder is V1; The second cylinder is provided with a high-pressure compression chamber and a second sliding groove which is communicated with the high-pressure compression chamber, the second piston is arranged in rotation in the high-pressure compression chamber, the height of the second cylinder along the axial direction of the crankshaft is H2, the diameter of the low-pressure compression chamber is D2, and the working volume of the second cylinder is V2; The partition assembly is connected between the first cylinder and the second cylinder, and the partition assembly is provided with a communication channel, the exhaust port of the low-pressure compression chamber is communicated with the air inlet port of the high-pressure compression chamber through the communication channel; The first sliding sheet is arranged in sliding in the first sliding groove, the first sliding sheet is in abutment with the outer circumferential surface of the first piston, the thickness of the first sliding sheet is T1, the second sliding sheet is arranged in sliding in the second sliding groove, the second sliding sheet is in abutment with the outer circumferential surface of the second piston, and the thickness of the second sliding sheet is T2; wherein U = (V2 / V1) x (D i x L i x T i ) / (H i x e i ), i = 1 or i = 2, with 1 < U < 51.

2. The pump body assembly of claim 1, wherein: The ratio of the height of the first cylinder along the axial direction of the crankshaft to the diameter of the low-pressure compression chamber is W1, and 0.25<=W1<=0.5 is met; and / or The ratio of the height of the second cylinder along the axial direction of the crankshaft to the diameter of the high-pressure compression chamber is W2, and 0.25<=W2<=0.5 is met.

3. The pump body assembly of claim 1, wherein: The ratio of the eccentricity of the first eccentric part to the diameter of the low-pressure compression chamber is X1, and 0.08<=X1<=0.11 is met; and / or The ratio of the eccentricity of the second eccentric part to the diameter of the high-pressure compression chamber is X2, and 0.08<=X2<=0.11 is met.

4. The pump body assembly of claim 1, wherein: The maximum length of the first sliding sheet along the sliding direction of the first sliding sheet is L3, the height of the first sliding sheet along the axial direction of the crankshaft is H3, and 0.8<=L3 / H3<=1.4 is met; and / or The maximum length of the second sliding sheet along the sliding direction of the second sliding sheet is L4, the height of the second sliding sheet along the axial direction of the crankshaft is H4, and 0.8<=L4 / H4<=1.4 is met.

5. The pump body assembly of claim 1, wherein: The height of the first sliding sheet along the axial direction of the crankshaft is H3, and 0.1<=T1 / H3<=0.28 is met; and / or The height of the second sliding sheet along the axial direction of the crankshaft is H4, and 0.1<=T2 / H4<=0.28 is met.

6. The pump body assembly of claim 1, wherein: The ratio of the working volume of the second cylinder to the working volume of the first cylinder is V P , and satisfies: 0.4≤V P ≤0.

8.

7. The pump body assembly of claim 1, wherein: The exhaust pressure of the communication channel is greater than the exhaust pressure of the low-pressure compression chamber and smaller than the exhaust pressure of the high-pressure compression chamber.

8. The pump body assembly of claim 7, wherein: The partition assembly comprises a first partition and a second partition arranged in axial opposition along the crankshaft, the first partition and the second partition enclosing the communication passage, the first partition being connected with the first cylinder, and the second partition being connected with the second cylinder.

9. The pump body assembly of claim 1, wherein: The pump body assembly further comprises a lower bearing and a lower muffler, both connected with the first cylinder, the lower bearing and the lower muffler enclosing a first cavity, the exhaust port of the low-pressure compression chamber being communicated with the communication passage through the first cavity.

10. A compressor characterized by, The pump body assembly of any one of claims 1-9. The compressor of claim 10.

11. A refrigeration appliance characterised in that: The compressor of claim 10.

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