Pump body assembly, compressor and refrigeration equipment

Abstract

The invention discloses a pump body assembly, a compressor and refrigeration equipment, the pump body assembly comprises a crankshaft, a first air cylinder, a second air cylinder and a partition plate 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, the width of the end face of a second piston is L2, and the height of the first air cylinder is H1; the diameter D1 of the low-pressure compression cavity, the working volume V1 of the first air cylinder, the height H2 of the second air cylinder, the diameter D2 of the high-pressure compression cavity, the working volume V2 of the second air cylinder, the thickness T1 of the first sliding sheet and the thickness T2 of the second sliding sheet meet the specified relation U, U = (V2 / V1) * (Di * Li * Ti) / (Hi * ei), i = 1 or i = 2, and 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 present invention relates to the technical field of compressors, and in particular to a pump assembly, a compressor and a refrigeration device. Background Art

[0002] The demand for heat pumps is increasing day by day, and the compressor is the core component of the heat pump system, which compresses the low-temperature and low-pressure refrigerant into a high-temperature and high-pressure refrigerant, thereby absorbing heat from the low-temperature environment and releasing it into the high-temperature environment. At present, the pump body assembly adopts multi-stage compression technology to evenly distribute the pressure ratio of each compression chamber, so that the compression chamber is within a more reasonable pressure ratio range. However, in the process of multi-stage compression of refrigerant, the leakage of refrigerant is still large, resulting in insufficient 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. To this end, the present invention provides a pump body assembly that can improve the volumetric efficiency of a compressor.

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

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

[0006] A pump assembly according to a first aspect of the present invention comprises:

[0007] The crankshaft comprises a first eccentric portion and a second eccentric portion spaced apart in the axial direction of the crankshaft, wherein the eccentricity of the first eccentric portion is e 1 , the eccentricity of the second eccentric part is e 2 The first eccentric part is sleeved with a first piston, and along the radial direction of the first piston, the width of the end surface of the first piston is L 1 The second eccentric part is sleeved with a second piston. Along the radial direction of the second piston, the width of the end surface of the first piston is L 2 ;

[0008] The first cylinder is provided with a low-pressure compression chamber and a first slide groove connected to the low-pressure compression chamber. The first piston is rotatably arranged in the low-pressure compression chamber. The height of the first cylinder along the axial direction of the crankshaft is H 1 , the diameter of the low pressure compression chamber is D 1 , the working volume of the first cylinder is V 1 ;

[0009] The second cylinder is provided with a high-pressure compression chamber and a second slide groove communicating with the high-pressure compression chamber. The second piston is rotatably arranged in the high-pressure compression chamber. The height of the second cylinder along the axial direction of the crankshaft is H 2 , the diameter of the low pressure compression chamber is D 2, the working volume of the second cylinder is V 2 ;

[0010] a partition assembly connected between the first cylinder and the second cylinder, the partition assembly being provided with a communication passage, the exhaust port of the low-pressure compression chamber being communicated with the suction port of the high-pressure compression chamber through the communication passage;

[0011] A first sliding plate and a second sliding plate, wherein the first sliding plate is slidably disposed in the first sliding groove, the first sliding plate abuts against the outer peripheral surface of the first piston, and the thickness of the first sliding plate is T 1 The second sliding plate is slidably disposed in the second sliding groove, the second sliding plate abuts against the outer peripheral surface of the second piston, and the thickness of the second sliding plate is T 2 ;

[0012] Where U = (V 2 / V 1 )×(D i ×L i ×T i ) / (H i ×e i ), i=1 or i=2, satisfying: 1≤U≤51.

[0013] The pump assembly according to the embodiment of the present invention has at least the following beneficial effects:

[0014] When the pump assembly is working, the refrigerant outside the pump assembly is sucked into the low-pressure compression chamber from the air inlet of the low-pressure compression chamber, and the refrigerant completes the first-stage compression in the low-pressure compression chamber. After that, the refrigerant is discharged into the connecting channel through the exhaust port of the low-pressure compression chamber. The refrigerant in the connecting channel is sucked into the high-pressure compression chamber from the air inlet of the high-pressure compression chamber, and the refrigerant completes the second-stage compression in the high-pressure compression chamber. 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. When i=1 and U is less than 1, the height H of the first cylinder 1 The eccentricity e of the first eccentric part 1 The product of is too large, the height H of the first cylinder 1 Too large will cause the crankshaft to be too long, and the eccentricity of the first eccentric part e 1 If the height H of the first cylinder is too large, the strength of the crankshaft will be weakened. During the operation of the compressor, the deflection of the crankshaft will increase, the sealing performance of the low-pressure compression chamber will decrease, and the leakage of the refrigerant in the low-pressure compression chamber will increase, resulting in a decrease in the volumetric efficiency of the compressor. When i=1 and U is greater than 51, the height H of the first cylinder 1 The eccentricity e of the first eccentric part 1 The product of is too small, the height H of the first cylinder 1 Too small leads to too small volume of low-pressure compression chamber, and the eccentricity of the first eccentric part e 1If the height H of the first piston is too small, the wall thickness of the first piston will increase. During the operation of the compressor, the unbalanced inertia of the crankshaft will increase, the crankshaft will be easily twisted and deformed, the leakage of the refrigerant in the low-pressure compression chamber will increase, and the volumetric efficiency of the compressor will decrease. When i=2 and U is less than 1, the height H of the second cylinder 2 The eccentricity e of the second eccentric part 2 The product of is too large, the height H of the second cylinder 2 Too large will cause the crankshaft to be too long, and the eccentricity of the second eccentric part e 2 If the height H of the second cylinder is too large, the strength of the crankshaft will be weakened. During the operation of the compressor, the deflection of the crankshaft will increase, the sealing performance of the high-pressure compression chamber will decrease, and the leakage of the refrigerant in the high-pressure compression chamber will increase, resulting in a decrease in the volumetric efficiency of the compressor. When i=2 and U is greater than 51, the height H of the second cylinder 2 The eccentricity e of the second eccentric part 1 The product of is too small, the height H of the second cylinder 2 Too small leads to too small volume of high pressure compression chamber, and the eccentricity of the second eccentric part e 1 If the working volume of the second cylinder is too small, the wall thickness of the second piston will increase. During the operation of the compressor, the unbalanced inertia of the crankshaft will increase, the crankshaft will be easily twisted and deformed, the leakage of the refrigerant in the low-pressure compression chamber will increase, and the volumetric efficiency of the compressor will decrease. Therefore, by reasonably designing 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 chamber, the diameter of the high-pressure compression chamber, the radial width of the end face of the first piston along the first piston, the radial width of the end face of the second piston along the second piston, the thickness of the first slide, the thickness of the second slide, 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 chamber and the high-pressure compression chamber can be improved to reduce the leakage of the refrigerant in the compression chamber, thereby improving the volumetric efficiency of the compressor.

[0015] According to some embodiments of the present invention, 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 W. 1 , satisfying: 0.25≤W 1 ≤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 W. 2 , satisfying: 0.25≤W 2 ≤0.5.

[0017] According to some embodiments of the present invention, the ratio of the eccentricity of the first eccentric portion to the diameter of the low-pressure compression chamber is X 1 , satisfying: 0.08≤X 1 ≤0.11; and / or,

[0018] The ratio of the eccentricity of the second eccentric portion to the diameter of the high-pressure compression chamber is X 2 , satisfying: 0.08≤X 2 ≤0.11.

[0019] According to some embodiments of the present invention, the length of the first sliding sheet along the sliding direction of the first sliding sheet is L 3 , the height of the first sliding plate along the axial direction of the crankshaft is H 3 , satisfying: 0.8≤L 3 / H 3 ≤1.4; and / or,

[0020] The length of the second sliding plate along the sliding direction of the second sliding plate is L4, and the height of the second sliding plate along the axial direction of the crankshaft is H4, which satisfies: 0.8≤L 4 / H 4 ≤1.4.

[0021] According to some embodiments of the present invention, the height of the first sliding plate along the axial direction of the crankshaft is H 3 , satisfying: 0.1≤T 1 / H 3 ≤0.28; and / or,

[0022] The height of the second sliding plate along the axial direction of the crankshaft is H 4 , satisfying: 0.1≤T 2 / H 4 ≤0.28.

[0023] According to some embodiments of the present invention, 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 invention, 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 invention, the partition assembly includes a first partition and a second partition arranged opposite to each other along the axial direction of the crankshaft, the first partition and the second partition enclose the connecting channel, the first partition is connected to the first cylinder, and the second partition is connected to the second cylinder.

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

[0027] The compressor according to the second embodiment of the present invention comprises the pump body assembly described in the above embodiment.

[0028] A refrigeration device according to an embodiment of the third aspect of the present invention comprises the compressor described in the above embodiment.

[0029] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0031] Figure 1 A schematic cross-sectional view of a pump assembly according to an embodiment of the present invention;

[0032] Figure 2 A schematic cross-sectional view of a pump assembly according to an embodiment of the present invention at another viewing angle;

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

[0034] Figure 4 for Figure 3 Sectional view along line AA;

[0035] Figure 5 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 A schematic diagram of a first sliding sheet or a second sliding sheet according to an embodiment of the present invention;

[0037] Figure 7 For an embodiment of the present invention (V 2 / V 1 )×(D i ×L i ×T i ) / (H i ×e i ) and the volumetric efficiency of the compressor.

[0038] Figure Number:

[0039] Axis O 1, crankshaft 100, first eccentric portion 110, second eccentric portion 120, first piston 130, second piston 140, first cylinder 200, low pressure compression chamber 210, first slide groove 220, second cylinder 300, high pressure compression chamber 310, second slide groove 320, partition assembly 400, connecting channel 401, first partition 410, second partition 420, first slide vane 510, second slide vane 520, first cavity 601, second cavity 602, lower bearing 610, lower muffler 620, upper bearing 630, upper muffler 640, housing 700, inner cavity 710, motor assembly 800, stator 810, rotor 820. DETAILED DESCRIPTION

[0040] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0041] In the description of the present invention, it should be understood that descriptions involving orientation, such as orientation or positional relationship indicated as up, down, etc., are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0042] In the description of the present invention, "a plurality" means more than two. If there is a description of "first" or "second", it is only used for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0043] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0044] In the related art, the pump assembly adopts multi-stage compression technology to evenly distribute the pressure ratio of each compression chamber, so that the compression chamber is within a reasonable pressure ratio range. However, in the process of multi-stage compression of refrigerant, the leakage of refrigerant is still large, resulting in insufficient volumetric efficiency of the compressor. It is understandable that the pressure ratio of a compressor is generally the ratio of the inlet and outlet pressures, but here there are pressure ratios of different compression chambers.

[0045] Reference Figure 1 , Figure 1 FIG. 1 is a cross-sectional schematic diagram of a pump assembly according to an embodiment of the present invention. Figure 1As shown, a pump body assembly of an embodiment of the present invention includes a crankshaft 100, a first cylinder 200, a second cylinder 300, an upper bearing 630, a lower bearing 610 and a partition assembly 400. The crankshaft 100 includes a first eccentric portion 110 and a second eccentric portion 120 spaced apart along the axial direction of the crankshaft 100. The first eccentric portion 110 is sleeved with a first piston 130, and the second eccentric portion 120 is sleeved with a second piston 140. The lower bearing 610, the first cylinder 200, the partition assembly 400, the second cylinder 300 and the upper bearing 630 are sequentially connected and arranged along the axial direction of the crankshaft 100, the first cylinder 200 is provided with a low-pressure compression chamber 210 and a first slide groove 220, the first slide groove 220 is communicated with the low-pressure compression chamber 210, a first slide plate 510 is slidably arranged in the first slide groove 220, the first piston 130 is rotatably arranged in the low-pressure compression chamber 210, the two ends of the first piston 130 are respectively abutted against the upper bearing 630 and the partition assembly 400, the first slide plate 510 is abutted against the outer peripheral surface of the first piston 130, the second cylinder 300 is provided with a high-pressure compression chamber 310 and a second slide groove 32 0, the second slide groove 320 is connected with the high-pressure compression chamber 310, a second slide plate 520 is slidably provided in the second slide groove 320, the second piston 140 is rotatably provided in the high-pressure compression chamber 310, the two ends of the second piston 140 are respectively abutted against the partition assembly 400 and the upper bearing 630, and the second slide plate 520 is abutted against the outer peripheral surface of the second piston 140, the partition assembly 400 is provided with a connecting passage 401, the exhaust port of the low-pressure compression chamber 210 is connected with the suction port of the high-pressure compression chamber 310 through the connecting passage 401, and when the pump body assembly is working, the pump body The refrigerant outside the component is sucked into the low-pressure compression chamber 210 from the air intake port of the low-pressure compression chamber 210, and the refrigerant completes the first-level compression in the low-pressure compression chamber 210. After that, the refrigerant is discharged into the connecting channel 401 through the exhaust port of the low-pressure compression chamber 210. The refrigerant in the connecting channel 401 is sucked into the high-pressure compression chamber 310 from the air intake port of the high-pressure compression chamber 310, and the refrigerant completes the second-level compression in the high-pressure compression chamber 310. 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.

[0046] Reference Figures 1 to 4 Combined with Figure 6 , Figure 2 A cross-sectional view of a pump assembly according to an embodiment of the present invention at another viewing angle. Figure 3 is a cross-sectional view of a compressor according to an embodiment of the present invention, Figure 4 for Figure 3 The cross-sectional view along the AA line. Figure 6 Schematic diagram of the first sliding plate 510 or the second sliding plate 520 of the embodiment of the present invention. As shown in the figure, in the embodiment of the present invention, the eccentricity of the first eccentric portion 110 is e 1 , the eccentricity of the second eccentric portion 120 is e 2The width of the end surface of the first piston 130 along the radial direction of the first piston 130 is L 1 The width of the end surface of the second piston 140 along the radial direction of the second piston 140 is L 2 , the height of the first cylinder 200 along the axial direction of the crankshaft 100 is H 1 , the diameter of the low pressure compression chamber 210 is D 1 , the working volume of the first cylinder 200 is V 1 , the height of the second cylinder 300 along the axial direction of the crankshaft 100 is H 2 , the diameter of the high pressure compression chamber 310 is D 2 , the working volume of the second cylinder 300 is V 2 , the thickness of the first sliding sheet 510 is T 1 , the thickness of the second sliding sheet 520 is T 2 , the above parameters satisfy the specified relationship U, U = (V 2 / V 1 )×(D i ×L i ×T i ) / (H i ×e i ), i=1 or i=2, satisfying: 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 usually refers to the residual volume between the compression chamber of the cylinder and the piston rotatably mounted inside the compression chamber. The unit of the working volume is cc, and the unit of the diameter of the compression chamber, the unit of the width of the end face, the unit of the thickness of the slide, the unit of the height of the cylinder, and the unit of the eccentricity are all mm, and this unit is used 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 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 assembly 400, or the surface of the second piston 140 abutting against the upper bearing 630; the eccentricity e of the first eccentric portion 110 1 It refers to the axis O of the crankshaft 100 1 The minimum distance between the axis of the first eccentric portion 110; the eccentricity of the second eccentric portion 120 2 It refers to the axis O of the crankshaft 100 1 The minimum distance between the axis of the second eccentric portion 120 .

[0047] It should be noted that if the diameter of the compression chamber is too large, the clearance volume of the cylinder (the clearance volume refers to the volume of gas remaining in the cylinder after compression is completed) will increase. The gas remaining in the clearance volume will expand again during the intake process, occupying part of the intake volume. The actual amount of gas inhaled by the compression chamber will be reduced, thereby reducing the volumetric efficiency of the compressor; if the diameter of the compression chamber is too small, the intake volume of the cylinder will be directly reduced, resulting in a decrease in the amount of gas inhaled by the compression chamber in each cycle, thereby reducing the volumetric efficiency of the compressor.

[0048] It should be noted that if the radial width of the piston end face is too large, the height clearance leakage of the piston will be aggravated; if the radial width of the piston end face is too small, the contact area of ​​the piston end face will be reduced, and the risk of gas leakage will increase, especially leakage from the high-pressure side to the low-pressure side of the compression chamber, thereby reducing the effective compressed gas volume and causing the volumetric efficiency of the compressor to decrease.

[0049] It should be noted that if the thickness of the sliding vane is too large, the gap between the sliding vane and the piston will be uneven. If the thickness of the sliding vane is too small, the strength of the sliding vane will be insufficient, and it will be easy to bend and deform, increasing the risk of gas leakage, thereby reducing the volumetric efficiency of the compressor.

[0050] It should be noted that the effect of the cylinder height on the volumetric efficiency of the compressor is similar to the effect of the diameter of the compression chamber on the volumetric efficiency of the compressor. If the cylinder height is too large, the clearance volume of the cylinder will increase. The residual gas in the clearance volume will re-expand during the intake process and occupy part of the intake volume. The actual amount of gas inhaled by the compression chamber is reduced, thereby reducing the volumetric efficiency of the compressor. If the cylinder height is too large, it will directly reduce the intake volume of the cylinder, resulting in a decrease in the amount of gas inhaled by the compression chamber in each cycle, thereby reducing the volumetric efficiency of the compressor.

[0051] It should be noted that if the eccentricity of the eccentric part is too large, the strength of the crankshaft will be weakened, the crankshaft will be prone to twisting and deformation, the wear of the piston will increase, the sealing performance of the compression chamber will decrease, the risk of gas leakage will increase, and the volumetric efficiency of the compressor will be reduced; if the eccentricity of the eccentric part is too small, the wall thickness of the piston will increase. During the operation of the compressor, the unbalanced inertia of the crankshaft will increase, making it prone to twisting and deformation, the wear of the piston will increase, the sealing performance of the compression chamber will decrease, and the risk of gas leakage will increase, resulting in a decrease in the volumetric efficiency of the compressor.

[0052] It can be understood that if the product of the diameter of the compression chamber, the radial width of the end face of the piston and the thickness of the vane is too large, the clearance volume of the cylinder will increase, and the gas remaining in the clearance volume will re-expand during the intake process, occupying part of the intake volume, and the actual amount of gas inhaled by the compression chamber will be reduced, thereby reducing the volumetric efficiency of the compressor; if the product of the diameter of the compression chamber, the radial width of the end face of the piston and the thickness of the vane is too small, the intake volume of the compression chamber will be reduced and the sealing performance of the compression chamber will be weakened, the risk of gas leakage will increase, and the volumetric efficiency of the compressor will be reduced.

[0053] Understandably, V 2 / V 1 If the working volume V of the first cylinder 200 is too small, 1 If the capacity is too large, the high-pressure compression chamber 310 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 210, resulting in excess performance and reduced volumetric efficiency of the compressor; V 2 / V 1 When the working volume V of the second cylinder 300 is too large, for low temperature heating conditions, the working volume V 2 Too large, equivalent to the working volume V of the first cylinder 200 1 If it is too small, the air intake 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=(V 2 / V 1 )×(D 1 ×L 1 ×T 1 ) / (H 1 ×e 1 ). The ratio V of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 is 2 / V 1 The diameter D of the constant, low-pressure compression chamber 210 1 The width L of the end surface of the first piston 130 along the radial direction of the first piston 130 is unchanged. 1 The thickness T of the first sliding sheet 510 is constant. 1 For example, when U is less than 1, the height H of the first cylinder 200 1 The eccentricity e of the first eccentric portion 110 1 The product of is too large, the height H of the first cylinder 200 1 If the crankshaft 100 is too long, the eccentricity e of the first eccentric portion 110 will be too large. 1 If the height H of the first cylinder 200 is too large, the strength of the crankshaft 100 will be weakened. 1 The eccentricity e of the first eccentric portion 110 is too large. 1Under the combined effect of , during the operation of the compressor, the deflection of the crankshaft 100 increases, the crankshaft 100 is prone to distortion and deformation, the wear of the first piston 130 increases, the sealing performance of the low-pressure compression chamber 210 decreases, and the leakage of the refrigerant in the low-pressure compression chamber 210 increases, resulting in a decrease in the volumetric efficiency of the compressor; when U is greater than 51, the height H of the first cylinder 200 1 The eccentricity e of the first eccentric portion 110 1 The product of is too small, the height H of the first cylinder 200 1 If the volume of the low-pressure compression chamber 210 is too small, the eccentricity of the first eccentric portion 110 is too small. 1 If the height of the first cylinder 200 is too small, the wall thickness of the first piston 130 will increase. During the operation of the compressor, the unbalanced inertia of the crankshaft 100 will increase, the crankshaft 100 will be easily twisted and deformed, the wear of the first piston 130 will increase, the sealing performance of the low-pressure compression chamber 210 will decrease, and the leakage of the refrigerant in the low-pressure compression chamber 210 will increase. Under the combined effect of the small height of the first cylinder 200 and the small eccentricity of the first eccentric part 110, the volumetric efficiency of the compressor will decrease. Therefore, it is reasonable to design the ratio V of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 2 / V 1 , the diameter D of the low pressure compression chamber 210 1 , the width L of the end surface of the first piston 130 along the radial direction of the first piston 130 1 , the thickness T of the first sliding sheet 510 1 , the height H of the first cylinder 200 1 and the eccentricity e of the first eccentric portion 110 1 The relationship between can improve the sealing performance of the low-pressure compression chamber 210 to reduce the leakage of the refrigerant in the low-pressure compression chamber 210, thereby improving the volumetric efficiency of the compressor.

[0055] As another embodiment, when i=2, U=(V 2 / V 1 )×(D 2 ×L 2 ×T 2 ) / (H 2 ×e 2 ). The ratio V of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 is 2 / V 1 The diameter D of the constant, high pressure compression chamber 310 2 The width L of the end surface of the second piston 140 along the radial direction of the second piston 140 is unchanged. 2 The thickness T of the second sliding sheet 520 is unchanged. 2 For example, when U is less than 1, the height H of the second cylinder 300 2The eccentricity e of the second eccentric portion 120 2 The product of is too large, the height H of the second cylinder 300 2 If the crankshaft 100 is too long, the eccentricity of the second eccentric portion 120 will be too large. 2 If the height H of the second cylinder 300 is too large, the strength of the crankshaft 100 will be weakened. 2 The eccentricity e of the second eccentric portion 120 is too large. 2 Under the combined effect of , during the operation of the compressor, the deflection of the crankshaft 100 increases, the crankshaft 100 is prone to distortion and deformation, the wear of the second piston 140 increases, the sealing performance of the high-pressure compression chamber 310 decreases, and the leakage of the refrigerant in the high-pressure compression chamber 310 increases, resulting in a decrease in the volumetric efficiency of the compressor; when U is greater than 51, the height H of the second cylinder 300 2 The eccentricity e of the second eccentric portion 120 2 The product of is too small, the height H of the second cylinder 300 2 If the volume of the low-pressure compression chamber 210 is too small, the eccentricity of the second eccentric portion 120 is too small. 2 If the height H of the second piston 140 is too small, the wall thickness of the second piston 140 will increase. During the operation of the compressor, the unbalanced inertia of the crankshaft 100 will increase, the crankshaft 100 will be easily twisted and deformed, the wear of the second piston 140 will increase, the sealing performance of the high-pressure compression chamber 310 will decrease, the leakage of the refrigerant in the high-pressure compression chamber 310 will increase, and the height H of the second cylinder 300 will increase. 2 The eccentricity e of the second eccentric portion 120 is too small. 2 Under the combined effect of too small, the volumetric efficiency of the compressor is reduced. Therefore, the ratio V of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 is reasonably designed. 2 / V 1 , the diameter D of the high pressure compression chamber 310 2 , the width L of the end surface of the second piston 140 along the radial direction of the second piston 140 2 , the thickness T of the second sliding sheet 520 2 , the height H of the second cylinder 300 2 and the eccentricity e of the second eccentric portion 120 2 The relationship between the high-pressure compression chamber 310 and the high-pressure compression chamber 310 can improve the sealing performance of the high-pressure compression chamber 310 to reduce the leakage of the refrigerant in the high-pressure compression chamber 310, thereby improving the volumetric efficiency of the compressor.

[0056] Reference Figure 7 , Figure 7 For an embodiment of the present invention (V 2 / V 1 )×(D i ×L i ×T i ) / (Hi ×e i ) and the volumetric efficiency of the compressor. The cylinder 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, within 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 V of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 2 / V 1 , the diameter D of the low pressure compression chamber 210 1 , the diameter D of the high pressure compression chamber 310 2 , the width L of the end surface of the first piston 130 along the radial direction of the first piston 130 1 , the width L of the end surface of the second piston 140 along the radial direction of the second piston 140 2 , the thickness T of the first sliding sheet 510 1 , the thickness T of the second sliding sheet 520 2 , the height H of the first cylinder 200 1 , the height H of the second cylinder 300 2 , the eccentricity e of the first eccentric portion 110 1 and the eccentricity e of the second eccentric portion 120 2 The relationship between the low-pressure compression chamber 210 and the high-pressure compression chamber 310 can improve the sealing performance to reduce the leakage of the refrigerant in the compression chamber, thereby improving the volumetric efficiency of the compressor.

[0057] For example Figure 2 As shown, in the embodiment of the present invention, the height H of the first cylinder 200 along the axial direction of the crankshaft 100 is 1 The diameter D of the low pressure compression chamber 210 1 The ratio is W 1 , W 1 =H 1 / D 1 , satisfying: 0.25≤W 1 ≤0.5, e.g. W 1 The height H of the first cylinder 200 along the axial direction of the crankshaft 100 can be 0.25, 0.3, 0.35, 0.4, 0.45, 0.5. 1 The diameter D of the low pressure compression chamber 210 1 , when designing the first cylinder 200 with any working volume, the compressor can have better performance, ensuring that the first cylinder 200 has better scalability.

[0058] For example, the diameter D of the compression chamber 210 is reduced by a low pressure. 1 For example, when W1 When it is less than 0.25, the height H of the first cylinder 200 along the axial direction of the crankshaft 100 1 If W is too small, the working volume of the first cylinder 200 is insufficient, resulting in a decrease in the volumetric efficiency of the compressor. 1 When it is greater than 0.5, the height H of the first cylinder 200 along the axial direction of the crankshaft 100 1 If the height H of the first piston 130 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, resulting in a decrease in the performance of the compressor. 1 The diameter D of the low pressure compression chamber 210 1 , when designing the first cylinder 200 with any working volume, the compressor can have better performance, ensuring that the first cylinder 200 has better scalability.

[0059] Similarly, the height H of the second cylinder 300 along the axial direction of the crankshaft 100 is 2 The diameter D of the high pressure compression chamber 310 2 The ratio is W 2 , W 2 =H 2 / D 2 , satisfying: 0.25≤W 2 ≤0.5, e.g. W 2 It can be 0.25, 0.3, 0.35, 0.4, 0.45, 0.5, by reasonably restricting the height H of the second cylinder 300 along the axial direction of the crankshaft 100 2 The diameter D of the high pressure compression chamber 310 2 , when designing the second cylinder 300 of any working volume, the compressor can have better performance, ensuring that the second cylinder 300 has better scalability.

[0060] For example, the diameter D of the high pressure compression chamber 310 is 2 For example, when W 2 When it is less than 0.25, the height H of the second cylinder 300 along the axial direction of the crankshaft 100 2 If the working volume V of the second cylinder 300 is too small, 2 Insufficient, resulting in a decrease in the volumetric efficiency of the compressor; when W 2 When it is greater than 0.5, the height H of the second cylinder 300 along the axial direction of the crankshaft 100 2If the height H of the second piston 300 along the axial direction of the crankshaft 100 is too large, the contact area between the second piston 140 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 decreases and the energy consumption increases, resulting in a decrease in the performance of the compressor. 2 The diameter D of the high pressure compression chamber 310 2 , when designing the second cylinder 300 of any working volume, the compressor can have better performance, ensuring that the second cylinder 300 has better scalability.

[0061] For example Figure 1 As shown, in the embodiment of the present invention, the eccentricity e of the first eccentric portion 110 is 1 The diameter D of the low pressure compression chamber 210 1 The ratio is X 1 , X 1 =e 1 / D 1， Satisfy: 0.08≤X 1 ≤0.11, for example, X 1 It can be 0.08, 0.09, 0.10, 0.11. By properly designing the eccentricity e of the first eccentric part 110 1 The diameter D of the low pressure compression chamber 210 1 The relationship between them can improve the service life and performance of the compressor.

[0062] For example, the diameter D of the compression chamber 210 is reduced by a low pressure. 1 For example, when X 1 When the eccentricity e of the first eccentric portion 110 is less than 0.08, 1 If the X is too small, the wall thickness of the first piston 130 increases, the width of the end surface of the first piston 130 along the radial direction of the first piston 130 increases, the friction between the first piston 130 and the partition assembly 400 increases, or the friction between the first piston 130 and the lower bearing 610 increases, resulting in a decrease in the performance of the compressor; when X 1 When the eccentricity e of the first eccentric portion 110 is greater than 0.11, 1 If the eccentricity of the first eccentric portion 110 is too large, the strength of the crankshaft 100 will be weakened, and the crankshaft 100 will be easily twisted and deformed, which will affect the service life of the compressor. 1 The diameter D of the low pressure compression chamber 210 1 The relationship between them can improve the service life and performance of the compressor.

[0063] Similarly, the eccentricity e of the second eccentric portion 120 is 2 The diameter D of the high pressure compression chamber 310 2 The ratio is X2 , X 2 =e 2 / D 2， Satisfies: 0.08≤X2≤0.11, for example, X 2 It can be 0.08, 0.09, 0.10, 0.11. By properly designing the eccentricity e of the second eccentric portion 120 2 The diameter D of the high pressure compression chamber 310 2 The relationship between them can improve the service life and performance of the compressor.

[0064] For example, the diameter D of the high pressure compression chamber 310 is 2 For example, when X 2 When the eccentricity e of the second eccentric portion 120 is less than 0.08, 2 If the value of X is too small, the wall thickness of the second piston 140 increases, the width of the end surface of the second piston 140 along the radial direction of the second piston 140 increases, the friction between the second piston 140 and the partition assembly 400 increases, or the friction between the second piston 140 and the upper bearing 630 increases, resulting in a decrease in the performance of the compressor. 2 When the eccentricity e of the second eccentric portion 120 is greater than 0.11, 2 If the eccentricity of the second eccentric portion 120 is too large, the strength of the crankshaft 100 will be weakened, and the crankshaft 100 will be easily twisted and deformed, which will affect the service life of the compressor. 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] Reference Figure 5 , Figure 5 The cross-sectional view of the first piston 130, the first sliding plate 510, the second piston 140 and the second sliding plate 520 of one embodiment of the invention is shown. Figure 5 As shown, in the embodiment of the present invention, along the sliding direction of the first sliding sheet 510, the maximum length of the first sliding sheet 510 is L 3 The height of the first sliding vane 510 along the axial direction of the crankshaft 100 is H 3 , satisfying: 0.8≤L 3 / H 3 ≤1.4, for example, L 3 / H 3 It can be 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4. By properly designing the maximum length L of the first sliding sheet 510 along the sliding direction of the first sliding sheet 510 3 The height H of the first sliding vane 510 in the axial direction of the crankshaft 100 3 The relationship between can reduce the leakage of refrigerant in the low-pressure compression chamber 210, thereby improving the volumetric efficiency of the compressor.

[0066] Understandably, L 3 / H 3 Characterizes the relationship between the height clearance leakage and radial leakage of the low-pressure compression chamber 210. 3 / H 3 When L is less than 0.8, the height gap leakage increases rapidly; 3 / H 3 When it is greater than 1.4, the radial sealing distance is reduced, and the radial leakage is significantly deteriorated, resulting in a significant decrease in the volumetric efficiency of the compressor. Therefore, by reasonably designing the maximum length L of the first sliding vane 510 along the sliding direction of the first sliding vane 510 3 The height H of the first sliding vane 510 in the axial direction of the crankshaft 100 3 The relationship between can reduce the leakage of refrigerant in the low-pressure compression chamber 210, thereby improving the volumetric efficiency of the compressor.

[0067] In the embodiment of the present invention, the thickness T of the first sliding sheet 510 is 1 The height H of the first sliding vane 510 in the axial direction of the crankshaft 100 3 The ratio is T 1 / H 3 , satisfying: 0.1≤T 1 / H 3 ≤0.28, for example, T 1 / H 3 The thickness T of the first sliding sheet 510 can be 0.1, 0.12, 0.14, 0.16, 0.18, 0.2, 0.22, 0.24, 0.26, or 0.28. 1 The height H of the first sliding vane 510 in the axial direction of the crankshaft 100 3 The relationship between them can increase the volumetric efficiency of the compressor and improve the performance of the compressor.

[0068] Understandably, T 1 / H 3 The relationship between the front end leakage of the first sliding plate 510 and the contact force of the front end of the first sliding plate 510 is characterized. The front end of the first sliding plate 510 refers to the end of the first sliding plate 510 that contacts the outer peripheral surface of the first piston 130. 1 For example, when T 1 / H 3 When T is less than 0.1, the contact force at the front end of the first sliding vane 510 decreases, and the leakage of the refrigerant in the low-pressure compression chamber 210 increases, resulting in a decrease in the volumetric efficiency of the compressor. 1 / H 3When the thickness T of the first sliding vane 510 is greater than 0.28, the contact force at the front end of the first sliding vane 510 increases, resulting in increased wear between the first sliding vane 510 and the first piston 130, and reduced performance of the compressor. 1 The height H of the first sliding vane 510 in the axial direction of the crankshaft 100 3 The relationship between them can increase the volumetric efficiency of the compressor and improve the performance of the compressor.

[0069] Similarly, along the sliding direction of the second sliding sheet 520, the maximum length of the second sliding sheet 520 is L 4 The height of the second sliding vane 520 along the axial direction of the crankshaft 100 is H 4 , satisfying: 0.8≤L 4 / H 4 ≤1.4, for example, L 4 / H 4 It can be 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4. By properly designing the maximum length L of the second sliding sheet 520 along the sliding direction of the second sliding sheet 520 4 The height H of the second sliding vane 520 along the axial direction of the crankshaft 100 4 The relationship between the refrigerant and the high-pressure compression chamber 310 can reduce the leakage of the refrigerant in the high-pressure compression chamber 310, thereby improving the volumetric efficiency of the compressor.

[0070] For example, L 4 / H 4 Characterizes the relationship between the height clearance leakage and radial leakage of the high pressure compression chamber 310. When L 4 / H 4 When L is less than 0.8, the height gap leakage increases rapidly; 4 / H 4 When it is greater than 1.4, the radial sealing distance is reduced, and the radial leakage is significantly worsened, resulting in a significant decrease in the volumetric efficiency of the compressor. Therefore, by reasonably designing the maximum length L of the second sliding vane 520 along the sliding direction of the second sliding vane 520 4 The height H of the second sliding vane 520 along the axial direction of the crankshaft 100 4 The relationship between the refrigerant and the high-pressure compression chamber 310 can reduce the leakage of the refrigerant in the high-pressure compression chamber 310, thereby improving the volumetric efficiency of the compressor.

[0071] Understandably, T 2 / H 4 The relationship between the front end leakage of the second sliding plate 520 and the contact force of the front end of the second sliding plate 520 is characterized. The front end of the second sliding plate 520 refers to the end of the second sliding plate 520 that contacts the outer peripheral surface of the second piston 140. 2 For example, when T 2 / H 4When T is less than 0.1, the contact force at the front end of the second sliding vane 520 decreases, and the leakage of the refrigerant in the high-pressure compressor increases, resulting in a decrease in the volumetric efficiency of the compressor. 2 / H 4 If the thickness T of the second sliding vane 520 is greater than 0.28, the contact force at the front end of the second sliding vane 520 increases, resulting in increased wear between the second sliding vane 520 and the second piston 140, and reduced performance of the compressor. 2 The relationship between the height H4 of the second sliding vane 520 in the axial direction of the crankshaft 100 can increase the volumetric efficiency of the compressor and improve the performance of the compressor.

[0072] In the embodiment of the present invention, the working volume V of the second cylinder 300 is 2 and the working volume V of the first cylinder 200 1 The ratio is V P , V P =V 2 / V 1 Satisfy: 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, V P =0.8. Taking the working volume of the second cylinder 300 as an example, when V P When V is less than 0.4, the working volume of the first cylinder 200 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 excess performance, which leads to a decrease in the volumetric efficiency of the compressor. P When it is greater than 0.8, for low-temperature heating conditions, the working volume of the first cylinder 200 is too small, the suction volume 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 exhaust pulsation can be reduced, the vibration and noise can be reduced, and the volumetric efficiency of the compressor can be improved.

[0073] In an embodiment of the present invention, the exhaust pressure of the connecting channel 401 is greater than the exhaust pressure of the low-pressure compression chamber 210, and the exhaust pressure of the connecting channel 401 is less than the exhaust pressure of the high-pressure compression chamber 310. The connecting channel has a petal-shaped structure, and the connecting channel 401 can buffer the refrigerant discharged from the low-pressure compression chamber 210. When the pump body assembly is running, the refrigerant discharged from the exhaust port of the low-pressure compression chamber 210 enters the connecting channel 401, which is beneficial to reduce exhaust pulsation and improve the performance of the compressor.

[0074] As another embodiment, the communication channel 401 may also be a through hole, and a plurality of through holes are provided, and the plurality of through holes surround the axis of the crankshaft 100. 1 The two ends of each through hole are respectively connected to the first cavity 601 and the air intake 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 an embodiment of the present invention, the pump body assembly also includes a lower muffler 620, which 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 are enclosed to form a first cavity 601, and the exhaust port of the low-pressure compression chamber 210 is connected to the connecting channel 401 through the first cavity 601, which is beneficial to reduce exhaust noise, thereby improving the user experience.

[0076] It is understandable 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 present invention, 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 connecting channel 401 respectively through two valve seats. That is, the low-pressure compression chamber 210 adopts a double exhaust solution, which can effectively reduce exhaust loss and improve the performance of the compressor.

[0077] 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 arranged opposite to each other along the axial direction of the crankshaft 100. The first partition 410 is located below the second partition 420. The first partition 410 and the second partition 420 enclose a connecting passage 401. The first partition 410 is connected to the upper end surface of the first cylinder 200, and the second partition 420 is connected to the lower end surface of the second cylinder 300. The first partition 410 and the second partition 420 can be processed separately, which is conducive to processing and manufacturing the connecting passage 401 on the partition assembly 400, and can reduce the processing and manufacturing cost of the partition assembly 400.

[0078] It should be noted that a connection structure is provided between the first partition 410 and the second partition 420, and 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 connection member, and the connection member is a screw or a bolt, and the connection member includes a rod and a head at one end of the rod of the connection member, the rod is passed through the second partition 420 and is threadedly connected to the first partition 410, and the head is installed in the second partition 420, which can facilitate the connection and fixation of the first partition 410 and the second partition 420. As another embodiment, the connection member is a pin, one end of the connection member is fixedly connected to the first partition 410, and the other end of the connection member is fixedly connected to the second partition 420, which can also facilitate the connection and fixation of the first partition 410 and the second partition 420, which will not be repeated here.

[0079] It should be noted that there are multiple connecting members, and the multiple connecting members surround the axis O of the crankshaft 100. 1 The arrangement can increase the connection stability between the first partition plate 410 and the second partition plate 420, which will not be described in detail here.

[0080] In an embodiment of the present invention, the pump body assembly also includes an upper muffler 640, which 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 chamber 310 is connected to the second cavity 602. The refrigerant discharged from the high-pressure compression chamber 310 can enter the third cavity and then be discharged to the inner cavity 710 of the compressor shell 700, which is beneficial to reduce exhaust noise and improve user experience.

[0081] For example Figure 3 As shown, the compressor of the second embodiment of the present invention includes a housing 700 and a pump body assembly of the above embodiment, wherein the housing 700 has an inner cavity 710, and the pump body assembly is installed in the inner cavity 710. The compressor adopts the pump body assembly of the above embodiment. When the pump body assembly is working, the refrigerant outside the pump body assembly is sucked into the low-pressure compression chamber 210 from the air intake port of the low-pressure compression chamber 210, and the refrigerant completes the first-stage compression in the low-pressure compression chamber 210. After that, the refrigerant is discharged into the connecting channel 401 through the exhaust port of the low-pressure compression chamber 210, and the refrigerant in the connecting channel 401 is sucked into the high-pressure compression chamber 310 from the air intake port of the high-pressure compression chamber 310, and the refrigerant completes the second-stage compression in the high-pressure compression chamber 310. 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 eccentricity of the first eccentric portion 110 is e 1 , the eccentricity of the second eccentric portion 120 is e 2 The width of the end surface of the first piston 130 along the radial direction of the first piston 130 is L 1 The width of the end surface of the second piston 140 along the radial direction of the second piston 140 is L 2, the height of the first cylinder 200 along the axial direction of the crankshaft 100 is H 1 , the diameter of the low pressure compression chamber 210 is D 1 , the working volume of the first cylinder 200 is V 1 , the height of the second cylinder 300 along the axial direction of the crankshaft 100 is H 2 , the diameter of the high pressure compression chamber 310 is D 2 , the working volume of the second cylinder 300 is V 2 , the thickness of the first sliding sheet 510 is T 1 , the thickness of the second sliding sheet 520 is T 2 , the above parameters satisfy the specified relationship U, U = (V 2 / V 1 )×(D i ×L i ×T i ) / (H i ×e i ), i=1 or i=2, satisfying: 1≤U≤51. When i=1 and U is less than 1, the height H of the first cylinder 200 1 The eccentricity e of the first eccentric portion 110 1 The product of is too large, the height H of the first cylinder 200 1 If the crankshaft 100 is too long, the eccentricity e of the first eccentric portion 110 will be too large. 1 When the height H of the first cylinder 200 is too large, the strength of the crankshaft 100 is weakened. During the operation of the compressor, the deflection of the crankshaft 100 increases, the sealing performance of the low-pressure compression chamber 210 decreases, and the leakage of the refrigerant in the low-pressure compression chamber 210 increases, resulting in a decrease in the volumetric efficiency of the compressor. When i=1 and U is greater than 51, the height H of the first cylinder 200 is 1 The eccentricity e of the first eccentric portion 110 1 The product of is too small, the height H1 of the first cylinder 200 is too small, resulting in a too small volume of the low-pressure compression chamber 210, and the eccentricity e of the first eccentric portion 110 is too small. 1 If the height H of the first piston 130 is too small, the wall thickness of the first piston 130 will increase. During the operation of the compressor, the unbalanced inertia of the crankshaft 100 will increase, the crankshaft 100 will be easily twisted and deformed, the leakage of the refrigerant in the low-pressure compression chamber 210 will increase, and the volumetric efficiency of the compressor will decrease. When i=2 and U is less than 1, the height H of the second cylinder 300 is 2 The eccentricity e of the second eccentric portion 120 2 The product of is too large, the height H of the second cylinder 300 2 If the crankshaft 100 is too long, the eccentricity of the second eccentric portion 120 will be too large. 2When the height H of the second cylinder 300 is too large, the strength of the crankshaft 100 is weakened. During the operation of the compressor, the deflection of the crankshaft 100 increases, the sealing performance of the high-pressure compression chamber 310 decreases, and the leakage of the refrigerant in the high-pressure compression chamber 310 increases, resulting in a decrease in the volumetric efficiency of the compressor. When i=2 and U is greater than 51, the height H of the second cylinder 300 is 2 The eccentricity e of the second eccentric portion 120 2 The product of is too small, the height H of the second cylinder 300 2 If the volume of the high-pressure compression chamber 310 is too small, the eccentricity of the second eccentric portion 120 is too small. 2 If the working volume of the second cylinder 300 is too small, the wall thickness of the second piston 140 will increase. During the operation of the compressor, the unbalanced inertia of the crankshaft 100 will increase, the crankshaft 100 will be easily twisted and deformed, the leakage of the refrigerant in the low-pressure compression chamber 210 will increase, and the volumetric efficiency of the compressor will decrease. Therefore, the ratio V of the working volume of the second cylinder 300 to the working volume of the first cylinder 200 should be reasonably designed. 2 / V 1 , the diameter D of the low pressure compression chamber 210 1 , the diameter D2 of the high-pressure compression chamber 310 , the width L of the end surface of the first piston 130 along the radial direction of the first piston 130 1 , the width L of the end surface of the second piston 140 along the radial direction of the second piston 140 2 , the thickness T of the first sliding sheet 510 1 , the thickness T of the second sliding sheet 520 2 , the height H of the first cylinder 200 1 , the height H of the second cylinder 300 2 , the eccentricity e of the first eccentric portion 110 = and the eccentricity e of the second eccentric portion 120 2 The relationship between the low-pressure compression chamber 210 and the high-pressure compression chamber 310 can improve the sealing performance to reduce the leakage of the refrigerant in the compression chamber, thereby improving the volumetric efficiency of the compressor.

[0082] In this embodiment, the upper bearing 630 of the pump body assembly is fixedly connected to the inner circumference of the inner cavity 710, or the first cylinder 200 and / or the second cylinder 300 are fixedly connected to the inner circumference of the inner cavity 710. The fixed connection method can be welding or interference fit, where the welding method includes but is not limited to resistance welding and laser welding.

[0083] In this embodiment, the compressor also includes a motor assembly 800, which includes a stator 810 and a rotor 820 rotatably disposed in the stator 810, wherein the outer circumferential surface of the rotor 820 abuts against the inner circumferential surface of the shell 700, and the rotor 820 is fixedly connected to 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 embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment, which will not be described in detail here.

[0085] The refrigeration equipment of the third embodiment of the present invention comprises the compressor of the above embodiment. The refrigeration equipment can be a central air conditioner, a package air conditioner, a split air conditioner, a duct air conditioner, a window air conditioner or the like.

[0086] The embodiments of the present invention are described in detail above with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A pump assembly, characterized in that: include: A crankshaft, comprising a first eccentric portion and a second eccentric portion spaced apart in the axial direction of the crankshaft, wherein the eccentricity of the first eccentric portion is e1, and the eccentricity of the second eccentric portion is e2; a first piston is sleeved on the first eccentric portion, and the width of the end surface of the first piston along the radial direction of the first piston is L1; a second piston is sleeved on the second eccentric portion, and the width of the end surface of the first piston along the radial direction of the second piston is L2; A first cylinder is provided with a low-pressure compression chamber and a first slide groove communicating with the low-pressure compression chamber, the first piston is rotatably disposed 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 slide groove communicating with the high-pressure compression chamber, the second piston is rotatably disposed 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; a partition assembly connected between the first cylinder and the second cylinder, the partition assembly being provided with a communication passage, the exhaust port of the low-pressure compression chamber being communicated with the suction port of the high-pressure compression chamber through the communication passage; a first sliding plate and a second sliding plate, wherein the first sliding plate is slidably disposed in the first sliding groove, the first sliding plate abuts against the outer peripheral surface of the first piston, and the thickness of the first sliding plate is T1; and the second sliding plate is slidably disposed in the second sliding groove, the second sliding plate abuts against the outer peripheral surface of the second piston, and the thickness of the second sliding plate is T2; Where, U = (V2 / V1) × (D i ×L i ×T i ) / (H i ×e i ), i=1 or i=2, satisfying: 1≤U≤51.

2. The pump assembly according to claim 1, characterized in that: 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, which satisfies: 0.25≤W1≤0.5; 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, which satisfies: 0.25≤W2≤0.

5.

3. The pump assembly according to claim 1, characterized in that: The ratio of the eccentricity of the first eccentric portion to the diameter of the low-pressure compression chamber is X1, which satisfies: 0.08≤X1≤0.11; and / or, The ratio of the eccentricity of the second eccentric portion to the diameter of the high-pressure compression chamber is X2, which satisfies: 0.08≤X2≤0.

11.

4. The pump assembly according to claim 1, characterized in that: The maximum length of the first sliding plate along the sliding direction of the first sliding plate is L3, and the height of the first sliding plate along the axial direction of the crankshaft is H3, which satisfies: 0.8≤L3 / H3≤1.4; and / or, The maximum 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, which satisfies: 0.8≤L4 / H4≤1.

4.

5. The pump assembly according to claim 1, characterized in that: The height of the first sliding vane along the axial direction of the crankshaft is H3, which satisfies: 0.1≤T1 / H3≤0.28; and / or, The height of the second sliding vane along the axial direction of the crankshaft is H4, which satisfies: 0.1≤T2 / H4≤0.

28.

6. The pump assembly according to claim 1, characterized in that: 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.

7. The pump assembly according to claim 1, characterized in that: 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.

8. The pump assembly according to claim 7, characterized in that: The partition assembly includes a first partition and a second partition that are arranged opposite to each other along the axial direction of the crankshaft. The first partition and the second partition form the connecting passage. The first partition is connected to the first cylinder, and the second partition is connected to the second cylinder.

9. The pump assembly according to claim 1, characterized in that: The pump body assembly also includes a lower bearing and a lower muffler, both of which are connected to the first cylinder. The lower bearing and the lower muffler are enclosed to form a first cavity, and the exhaust port of the low-pressure compression chamber is connected to the connecting channel through the first cavity.

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

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

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