Pump body assembly, fluid machine and heat exchange equipment

Abstract

The invention provides a pump body assembly, a fluid machine and heat exchange equipment. The pump body assembly comprises a first cylinder; the volume V2 of the second air cylinder is smaller than or equal to 10% of the volume V1 of the first air cylinder; the crankshaft comprises a main body part and a reducing section, the outer periphery of the reducing section does not exceed the outer periphery of the main body part, and the reducing section and the main body part are eccentrically arranged in the axial direction of the main body part; wherein at least one part of the main body part is located in the first air cylinder, at least one part of the reducing section is located in the second air cylinder, and in the rotating process of the crankshaft, the part, located in the first air cylinder, of the main body part and the part, located in the second air cylinder, of the reducing section participate in the compression process. The invention solves the problem that the miniaturization design of small cylinders in fluid machinery in the prior art is limited.

Description

Technical Field

[0001] The present invention relates to the technical field of heat exchange equipment, and in particular to a pump body component, a fluid machine and a heat exchange equipment. Background Art

[0002] In the prior art, heat exchange equipment is already very common. The heat exchange of existing heat exchange equipment is realized by the pump body assembly in the fluid machinery. The conventional design is mostly multi-cylinder forms such as large and small cylinders, double cylinders, and three cylinders. The above design methods all place the cylinder between the upper and lower flange supports. Taking the large and small cylinders as an example, in order to ensure the assembly relationship of the pump body, the diameter of the small cylinder and the diameter of the eccentric part must be larger than the short shaft diameter (short shaft support position). In order to ensure the reliability of the pump body, the short shaft diameter cannot be very small. At this time, the diameter of the small cylinder and the diameter of the eccentric part cannot be adjusted accordingly according to the actual situation, that is, the eccentric part diameter cannot be reduced as the displacement demand decreases. In order to consider the assembly relationship and to avoid affecting the efficiency of the second cylinder or the third cylinder, other multi-cylinder forms also cannot adjust the volume of the small cylinder to achieve miniaturization and high efficiency.

[0003] As can be seen from the above, there is a problem in the prior art that the miniaturization design of small cylinders in fluid machinery is limited. Summary of the invention

[0004] The main purpose of the present invention is to provide a pump body assembly, a fluid machine and a heat exchange device to solve the problem of limited miniaturization design of small cylinders in the fluid machine in the prior art.

[0005] In order to achieve the above-mentioned purpose, according to one aspect of the present invention, a pump body assembly is provided, comprising: a first cylinder; a second cylinder, and the volume V2 of the second cylinder is less than or equal to 10% of the volume V1 of the first cylinder; a crankshaft, the crankshaft comprising a main body and a reduced diameter section, the outer periphery of the reduced diameter section does not exceed the outer periphery of the main body, and the reduced diameter section and the main body are eccentrically arranged in the axial direction of the main body; wherein at least a portion of the main body is located inside the first cylinder, and at least a portion of the reduced diameter section is located inside the second cylinder, and during the rotation of the crankshaft, the portion of the main body located in the first cylinder and the reduced diameter section located in the second cylinder respectively participate in the compression process.

[0006] Furthermore, the main body includes an expanded diameter section located inside the first cylinder and a non-expanded diameter section located outside the first cylinder, the outer periphery of the reduced diameter section does not exceed the outer periphery of the non-expanded diameter section, and the reduced diameter section and the expanded diameter section are eccentrically arranged relative to the non-expanded diameter section in the axial direction of the main body.

[0007] Further, the diameter expansion section and the diameter reduction section are eccentrically arranged in the same direction relative to the non-diameter expansion section; or the diameter expansion section and the diameter reduction section are eccentrically arranged in opposite directions relative to the non-diameter expansion section.

[0008] Further, at least a portion of the outer periphery of the diameter-reducing section is located inside the outer periphery of the non-diameter-expanding section; and / or the cross section of the diameter-reducing section is circular.

[0009] Further, the reduced diameter section is located at the end of the crankshaft; or the reduced diameter section is located in the middle of the crankshaft and above the expanded diameter section.

[0010] Furthermore, the crankshaft includes a first section and a second section which are axially separated and connected, the expanded diameter section and the reduced diameter section are both located on the second section, and the portion of the second section other than the expanded diameter section and the reduced diameter section and the first section are all non-expanded diameter sections.

[0011] Further, under the first load condition, the volume V1 of the first cylinder and the volume V2 of the second cylinder satisfy: 0.03≤V2 / V1≤0.06; and / or under the second load condition, the volume V1 of the first cylinder and the volume V2 of the second cylinder satisfy: 0.07≤V2 / V1≤0.1.

[0012] Further, the rotational speed of the crankshaft under the first load condition is less than the rotational speed of the crankshaft under the second load condition.

[0013] Furthermore, the pump body assembly also includes a second sliding vane, the second cylinder has a second sliding vane groove, and the second sliding vane is slidably arranged in the second sliding vane groove.

[0014] Furthermore, the pump body assembly also includes: a first flange and a second flange, the first cylinder is located between the first flange and the second flange; a cover plate, the second cylinder is located between the first flange and the cover plate or between the second flange and the cover plate.

[0015] According to another aspect of the present invention, a fluid machine is provided, comprising the above-mentioned pump body assembly.

[0016] According to another aspect of the present invention, a heat exchange device is provided, comprising the above-mentioned fluid machinery.

[0017] By applying the technical solution of the present invention, a pump body assembly includes a first cylinder, a second cylinder and a crankshaft, a volume V2 of the second cylinder is less than or equal to 10% of a volume V1 of the first cylinder, and the crankshaft includes a main body and a reduced diameter section, an outer periphery of the reduced diameter section does not exceed an outer periphery of the main body, and the reduced diameter section and the main body are eccentrically arranged in the axial direction of the main body, wherein at least a portion of the main body is located inside the first cylinder, and at least a portion of the reduced diameter section is located inside the second cylinder, and during the rotation of the crankshaft, the portion of the main body located in the first cylinder and the reduced diameter section located in the second cylinder respectively participate in the compression process, so that the pump body assembly is set as a large and small cylinder structure, and the reduced diameter section corresponding to the second cylinder is set within the outer periphery of the crankshaft, so that the second cylinder structure is compact, the volume of the second cylinder is greatly reduced, and the miniaturized design of the small cylinder in the large and small cylinder structure is realized, solving the problem of limited miniaturized design of small cylinders in fluid machinery in the prior art. In addition, since the second cylinder has a smaller volume, the power consumption generated by the friction pair inside the cylinder is greatly reduced, thereby improving energy efficiency, and achieving a miniaturized design while making the fluid machinery have higher energy efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0019] Figure 1 A schematic diagram of the structure of a fluid machine in Embodiment 1 of the present invention is shown;

[0020] Figure 2 Shows Figure 1 A partial enlarged view of the middle A;

[0021] Figure 3 A relationship diagram between the volume ratio of the first cylinder and the second cylinder and the degree of energy efficiency improvement under a first load condition in the first embodiment of the present invention is shown;

[0022] Figure 4 A relationship diagram between the volume ratio of the first cylinder to the second cylinder and the degree of energy efficiency improvement under a second load condition in the first embodiment of the present invention is shown;

[0023] Figure 5 A schematic diagram showing the structure of the second sliding sheet in the first embodiment of the present invention is shown;

[0024] Figure 6 A schematic diagram showing a suction and exhaust mode of the pump assembly in the first embodiment of the present invention;

[0025] Figure 7 A schematic diagram showing another suction and exhaust method of the pump assembly in the first embodiment of the present invention;

[0026] Figure 8 A schematic diagram showing another suction and exhaust method of the pump assembly in the first embodiment of the present invention;

[0027] Fig. 9 A gas resistance moment curve diagram of the first compression part and the second compression part in the first embodiment of the present invention is shown;

[0028] Fig.10 A schematic structural diagram showing an angle when the diameter expansion section and the diameter reduction section in the first embodiment of the present invention are arranged opposite to each other;

[0029] Fig.11 A schematic structural diagram showing another angle when the diameter expansion section and the diameter reduction section in the first embodiment of the present invention are arranged opposite to each other;

[0030] Fig.12 A schematic diagram showing the positions of the first cylinder and the second cylinder when the diameter expansion section and the diameter reduction section are arranged opposite to each other in the first embodiment of the present invention;

[0031] Fig.13 A schematic diagram showing the positions of the first sliding vane groove and the second sliding vane groove when the diameter expansion section and the diameter reduction section are arranged opposite to each other in the first embodiment of the present invention;

[0032] Fig.14 A schematic structural diagram of an angle when the diameter expansion section and the diameter reduction section in the first embodiment of the present invention are arranged in the same direction is shown;

[0033] Fig.15 A structural schematic diagram showing another angle when the diameter expansion section and the diameter reduction section in the first embodiment of the present invention are arranged in the same direction;

[0034] Fig.16 A schematic diagram showing the positions of the first cylinder and the second cylinder when the diameter expansion section and the diameter reduction section in the first embodiment of the present invention are arranged in the same direction;

[0035] Fig.17 A schematic diagram showing the positions of the first sliding vane groove and the second sliding vane groove when the diameter expansion section and the diameter reduction section in the first embodiment of the present invention are arranged in the same direction;

[0036] Fig.18 A schematic diagram of the lubricating oil circuit of the pump assembly in the first embodiment of the present invention is shown;

[0037] Fig.19 A schematic diagram showing the structure of a fluid machine in a second embodiment of the present invention is shown;

[0038] Fig. 20 A schematic diagram of the lubricating oil circuit of the pump assembly in the second embodiment of the present invention is shown;

[0039] Fig.21 A schematic diagram of the structure of a fluid machine in a third embodiment of the present invention is shown;

[0040] Fig. 22 A schematic diagram of the lubricating oil circuit of the pump assembly in the third embodiment of the present invention is shown;

[0041] Fig.23 A structural schematic diagram showing a configuration of a fluid machine in a fourth embodiment of the present invention;

[0042] Fig.24 shows a pressure-enthalpy diagram of a fluid machine in the prior art;

[0043] Fig.25 shows a pressure-enthalpy diagram of a fluid machine in a fourth embodiment of the present invention;

[0044] Fig.26 A structural schematic diagram showing another arrangement of the fluid machinery according to the fourth embodiment of the present invention;

[0045] Fig. 27 A schematic diagram of the structure of the second flange in the fourth embodiment of the present invention is shown;

[0046] Fig.28 A structural schematic diagram showing a configuration of a fluid machine in a fifth embodiment of the present invention;

[0047] Fig.29 shows a pressure-enthalpy diagram of a fluid machine in a fifth embodiment of the present invention;

[0048] Fig.30 A structural schematic diagram showing another arrangement of the fluid machinery in the fifth embodiment of the present invention;

[0049] Fig.31 A schematic structural diagram of a fluid machine in a sixth embodiment of the present invention is shown.

[0050] The above drawings include the following reference numerals:

[0051] 10. First cylinder; 11. First vane slot; 12. First air intake port; 13. First air outlet port; 20. Second cylinder; 21. Second vane slot; 22. Second air intake port; 23. Second air outlet port; 24. Accommodation hole; 30. Crankshaft; 31. Reduced diameter section; 311. Second upper oil outlet port; 32. Expanded diameter section; 321. First upper oil outlet port; 322. Middle oil outlet port; 323. Lower oil outlet port; 33. Non-expanded diameter section; 34. Center oil hole; 40. First roller; 50. Second roller Sub; 60, first flange; 61, first lateral oil outlet hole; 70, second flange; 71, second lateral oil outlet hole; 80, cover plate; 90, second slide; 100, lateral oil outlet groove; 110, enthalpy increase port; 120, medium pressure air inlet pipe; 130, third cylinder; 131, third air intake port; 132, third air outlet port; 140, intermediate buffer chamber; 150, motor assembly; 151, bracket; 160, distributor; 170, first air inlet pipe; 180, second air inlet pipe; 190, shell. DETAILED DESCRIPTION

[0052] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0053] In order to solve the problem of limited miniaturization design of small cylinders in fluid machinery in the prior art, the present invention provides a pump body assembly, a fluid machinery and a heat exchange device. The fluid machinery described below includes the pump body assembly described below.

[0054] Embodiment 1

[0055] like Figure 1 to Figure 2 As shown, the pump body assembly includes a first cylinder 10, a second cylinder 20 and a crankshaft 30. The volume V2 of the second cylinder 20 is smaller than the volume V1 of the first cylinder 10. The crankshaft 30 includes a main body and a reduced diameter section 31, the outer periphery of the reduced diameter section 31 does not exceed the outer periphery of the main body, and the reduced diameter section 31 and the main body are eccentrically arranged in the axial direction of the main body. Among them, at least a part of the main body is located inside the first cylinder 10, and at least a part of the reduced diameter section 31 is located inside the second cylinder 20. During the rotation of the crankshaft 30, the part of the main body located in the first cylinder 10 and the reduced diameter section 31 located in the second cylinder 20 respectively participate in the compression process.

[0056] In this embodiment, the volume V2 of the second cylinder 20 is less than or equal to 10% of the volume V1 of the first cylinder 10. That is, the volume ratio of the second cylinder 20 to the first cylinder 10 is less than 1 / 10. In this way, the pump body assembly is set as a large-small cylinder structure, and the reduced diameter section corresponding to the second cylinder 20 is set within the outer peripheral range of the crankshaft, so that the second cylinder 20 has a compact structure, greatly reducing the volume of the second cylinder 20, and realizing the miniaturization design of the small cylinder in the large-small cylinder structure. In addition, since the second cylinder 20 has a smaller volume, the power consumption generated by the friction pair inside the cylinder is greatly reduced, thereby improving energy efficiency, and realizing miniaturization design while making the fluid machinery have higher energy efficiency.

[0057] In this embodiment, the reduced diameter section 31 is located at the end of the crankshaft 30. That is, the reduced diameter section 31 in this embodiment is a short shaft at the end of the crankshaft 30.

[0058] like Figure 1 to Figure 2 As shown, the main body has an expanded diameter section 32 located inside the first cylinder 10 and a non-expanded diameter section 33 located outside the first cylinder 10, the outer periphery of the reduced diameter section 31 does not exceed the outer periphery of the non-expanded diameter section 33, and the reduced diameter section 31 and the non-expanded diameter section 33 are eccentrically arranged in the axial direction of the main body, and the non-expanded diameter section 33 is eccentrically arranged in the axial direction of the main body.

[0059] like Figure 1 to Figure 2 As shown, the pump assembly further includes a first roller 40 and a second roller 50. The first roller 40 and the second roller 50 are respectively accommodated in the first cylinder 10 and the second cylinder 20. The enlarged diameter section 32 drives the first roller 40 to move, and the reduced diameter section 31 drives the second roller 50 to move.

[0060] Specifically, when the crankshaft 30 rotates, the first roller 40 and the second roller 50 move in the first cylinder 10 and the second cylinder 20 respectively. The movement of the rollers in the cylinders is a surface-to-surface contact. Since the expansion section 32 and the reduction section 31 are eccentrically arranged, the first roller 40 and the second roller 50 do not rotate on their own, but the trajectory of contact with the cylinder is an eccentric circle. The eccentric circle trajectory makes a crescent-shaped compression chamber exist in the cylinder at all times. At this time, the volume of the compression chamber is maximized, which can improve the efficiency of compressing the gas.

[0061] like Figure 1 to Figure 2 As shown, the pump body assembly further includes a first flange 60, a second flange 70 and a cover plate 80. The first cylinder 10 is located between the first flange 60 and the second flange 70. The second cylinder 20 is located between the second flange 70 and the cover plate 80. In this embodiment, the cover plate 80 is located at the bottom of the pump body assembly, and correspondingly, the reduced diameter section 31 is located at the bottom end of the crankshaft 30.

[0062] In this embodiment, the reduced diameter section 31 is located at the bottom end of the crankshaft 30, the first flange 60 is located above the second flange 70, and the upper end surface of the first cylinder 10 is sealed and connected to the first flange 60, the lower end surface of the first cylinder 10 is sealed and connected to the second flange 70, the upper end surface of the second cylinder 20 is sealed and connected to the second flange 70, and the lower end surface of the second cylinder 20 is sealed and connected to the cover plate 80. The first flange 60 and the second flange 70 seal the first cylinder 10, and the second flange 70 and the cover plate 80 seal the second cylinder 20, so that the two cylinders are independent. At the same time, the crankshaft 30 passes through the first cylinder 10 and the second cylinder 20, and the enlarged diameter section 32 and the reduced diameter section 31 arranged on the crankshaft 30 respectively drive the first roller 40 arranged in the first cylinder 10 and the second roller 50 arranged in the second cylinder 20, so that the two cylinders are effectively compressed independently and in parallel.

[0063] like Figure 1 As shown, the fluid machinery in this embodiment is a double-cylinder compression structure, that is, it has a first compression part and a second compression part. The first compression part is composed of a first flange 60, a first cylinder 10, a first roller 40 and a second flange 70. One refrigerant goes from the heat exchange equipment system to the liquid distributor 160 to separate the lubricating oil, enters the first cylinder 10 through the first air inlet pipe 170 and the first air intake port 12 for compression, and is discharged into the inner cavity of the fluid machinery after one round of compression. The second compression part is composed of a second flange 70, a second cylinder 20, a second roller 50 and a cover plate 80. Another refrigerant goes from the air conditioning system to the second air inlet pipe 180, enters the second cylinder 20 through the second air intake port 22 for compression, and the compressed refrigerant is discharged into the inner cavity of the fluid machinery, mixed with the refrigerant compressed by the first compression part, and then discharged from the fluid machinery to the heat exchange equipment system.

[0064] In this embodiment, in order to achieve the design feasibility of the second cylinder 20, the diameter D2 of the reduced diameter section 31 is smaller than the diameter D1 of the non-expanded diameter section 33, that is, D2<D1; further, the reduced diameter section 31 is arranged within the axial diameter circle of the non-expanded diameter section 33, and the diameter D1 of the non-expanded diameter section 33, the diameter D2 of the reduced diameter section 31 and the eccentricity e2 of the reduced diameter section 31 satisfy: e2<D1 / 2-D2 / 2.

[0065] Furthermore, in order to ensure the sealing performance of the second cylinder 20, the end face sealing band formed between the outer diameter D3 of the second roller 50 and the diameter D1 of the non-expanded section 33 has a certain sealing distance. Specifically, the outer diameter D3 of the second roller 50, the diameter D1 of the non-expanded section 33 and the eccentricity e2 of the reduced diameter section 31 satisfy: D3 / 2-e2-D1 / 2>0.5mm.

[0066] In this embodiment, the pump body assembly includes a first sliding vane. Fig.12As shown, the first cylinder 10 has a first slide plate groove 11, and the first slide plate is slidably disposed at the first slide plate groove 11. In this embodiment, the top of the first slide plate is connected to the first roller 40, and the other end is connected to the elastic member, which is accommodated in the accommodation hole on the inner wall of the first cylinder 10 and abuts against the tail of the first slide plate, providing elastic force to the first slide plate so that the top of the first slide plate remains in contact with the first roller 40.

[0067] like Figure 5 As shown, the pump body assembly further includes a second slide plate 90. The second cylinder 20 has a second slide plate groove 21, and the second slide plate 90 is slidably disposed at the second slide plate groove 21. In this embodiment, one end of the second slide plate 90 is connected to the second roller 50, and the other end is connected to the elastic member, which is accommodated in the accommodation hole 24 on the inner wall of the second cylinder 20 and abuts against the tail of the second slide plate 90, providing elastic force to the second slide plate 90 so that the top of the second slide plate 90 remains in contact with the second roller 50.

[0068] In this embodiment, the width T of the second slide plate 90 satisfies: 1.5 mm ≤ T ≤ 5 mm. The arc diameter T4 of the head of the second slide plate 90 satisfies: 5 mm ≤ T4 ≤ 15 mm. Specifically, when the volume of the second cylinder 20 is small, after the exhaust port of the second compression part is closed, the triangular clearance volume formed by the second slide plate 90 and the second roller 50 accounts for a large proportion, affecting the volumetric efficiency. Through the above arrangement, the clearance volume can be greatly reduced.

[0069] In this embodiment, since the working volume of the second cylinder 20 is small, the parameters that affect the working chamber volume are similarly small. In order to ensure that the various components in the second cylinder 20 can work reasonably, the second roller 50 needs to keep in contact with the second sliding plate 90, and the outer radius of the second roller 50 needs to be greater than the eccentricity of the reduced diameter section 31 by a certain value. Specifically, the outer diameter D3 of the second roller 50 and the eccentricity e2 of the reduced diameter section 31 satisfy: D3 / 2-e2>2mm.

[0070] Through the above arrangement, the size of the second cylinder 20 can be significantly reduced, the diameter of the second roller 50 can be smaller than that of a conventional roller, and the end surface area and the relative movement speed of the end surface of the second roller 50 are reduced, so that the friction power consumption of the roller can be reduced. Furthermore, in order to take into account the sealing performance of the cylinder and the roller area, in this embodiment, the thickness of the second roller 50, that is, the difference between the inner and outer radii, ranges from 2 mm to 8 mm.

[0071] In this embodiment, the height of the reduced diameter section 31 in the axial direction of the crankshaft 30 is less than or equal to the height h of the second cylinder 20, and the height h of the second cylinder 20 satisfies: 3mm≤h≤20mm. Specifically, the second cylinder 20 in this embodiment is located below the first flange 60, and the force model of the crankshaft 30 is an outrigger beam model. The height of the reduced diameter section 31 corresponds to the height h of the second cylinder 20, and the height h has a certain influence on the force of the flange; at the same time, in the actual processing process, if the cylinder height is too small, some features will affect each other and deform. Therefore, under the premise that the second cylinder 20 is located within a suitable volume range, the height h of the second cylinder 20 is controlled within the above-mentioned numerical range, which minimizes the influence on the force of the crankshaft 30.

[0072] In this embodiment, if Figure 3 As shown, in order to achieve the best energy efficiency of the fluid machinery in each working state, when the fluid machinery achieves the best effect in the first load condition, the volume V1 of the first cylinder 10 and the volume V2 of the second cylinder 20 satisfy: 0.03≤V2 / V1≤0.06. Figure 4 As shown, when the fluid machinery achieves the best effect in the second load condition, the volume V1 of the first cylinder 10 and the volume V2 of the second cylinder 20 satisfy: 0.07≤V2 / V1≤0.1. Specifically, the first load condition in this embodiment is a low load condition, and the second load condition is a high load condition. The speed of the crankshaft 30 in the first load condition is less than the speed of the crankshaft 30 in the second load condition. Through the above settings, the pump body assembly in this embodiment can achieve the best working state under various conditions.

[0073] like Figure 6 As shown, the pump body assembly has a second air inlet 22 connected to the inner cavity of the second cylinder 20. When the height h of the second cylinder 20 is less than or equal to 7 mm, the second air inlet 22 is arranged on the second flange 70. The outer circle of the second flange 70 is equivalent to the inner circle of the housing 190. When the second air inlet pipe 180 is installed, the second flange 70 can be prevented from vibrating and deviating in the radial direction, thereby reducing the defective rate of the pump body assembly during the installation process.

[0074] like Figure 7 As shown, when the height h of the second cylinder 20 is less than or equal to 7 mm, the second air inlet 22 can also be set on the cover plate 80. The refrigerant of the second compression part enters the second cylinder 20 from the second air inlet 22 on the cover plate 80. Through the above arrangement, the second flange 70 can be thinned and the processing material can be reduced.

[0075] like Figure 8As shown, when the height h of the second cylinder 20 is greater than 7 mm, the second air inlet 22 is disposed on the second cylinder 20. That is, the second cylinder 20 has enough space to open an air intake passage, and the refrigerant is directly introduced into the second cylinder 20, thereby minimizing the volume of the pump body.

[0076] It should be noted that Figures 6 to 8 The arrow in the figure indicates the flow direction of the refrigerant.

[0077] In an optional embodiment, the second air intake port 22 may also be provided on the first cylinder 10. Specifically, the second air intake port 22 is staggered with the first air intake port 12, and the second flange is provided with a flow passage extending in the axial direction, and the second air intake port 22 is connected with the second cylinder 20 through the flow passage.

[0078] In this embodiment, the height of the second cylinder 20 is relatively small, so that the axial distance between the second compression part and the first compression part is relatively close, and the arrangement of the air intake port and the air intake channel is relatively compact. The close distance between the two air intake ports will lead to the first problem: insufficient space for the two air intake settings; the second problem is that the two independent air intake ports have the risk of refrigerant leakage and heat leakage. Under the condition that the volume of the second compression part is small, the resistance torque generated by the second compression part is small. The torque curve when the peak torque angle of the two compression parts is 180° is as follows Fig. 9 As shown, it is necessary to adjust the angle between the two cylinders based on the premise of minimizing the impact on the peak torque of the first compression part, so that the working torque of the second compression part affects the peak torque of the first compression part by less than 5%.

[0079] In this embodiment, if Figure 10 to Figure 11 As shown, the diameter expansion section 32 and the diameter reduction section 31 are eccentrically arranged in the same direction in opposite directions relative to the non-diameter expansion section 33 .

[0080] It should be noted that the same-direction eccentric setting means that the axes of the reduced diameter section 31, the expanded diameter section 32 and the non-expanded diameter section 33 are projected separately on the vertical projection plane of the crankshaft 30, and the axis projection of the non-expanded diameter section 33 is used as a reference. The axis projections of the reduced diameter section 31 and the expanded diameter section 32 are located on the same side of the axis projection of the non-expanded diameter section 33. The opposite-direction eccentric setting means that the axis projections of the reduced diameter section 31 and the expanded diameter section 32 are respectively located on both sides of the axis projection of the non-expanded diameter section 33.

[0081] In this embodiment, if Fig.10 As shown, at least a portion of the outer periphery of the reduced diameter section 31 overlaps with the outer periphery of the non-expanded diameter section 33, and at least another portion of the outer periphery of the reduced diameter section 31 is located inside the outer periphery of the non-expanded diameter section 33. The cross section of the reduced diameter section 31 is circular. Similarly, the cross sections of the expanded diameter section 32 and the non-expanded diameter section 33 are also circular.

[0082] like Figure 12 to Figure 13As shown, the first cylinder 10 has a first vane groove 11, the second cylinder 20 has a second vane groove 21, and when the diameter expansion section 32 and the diameter reduction section 31 are eccentrically arranged in opposite directions relative to the non-diameter expansion section 33, the angle θ between the first vane groove 11 and the second vane groove 21 satisfies: -90°<θ<90°. Specifically, the angle between the diameter reduction section 31 and the diameter expansion section 32 is 180°, and the working starting point of the first compression part is 0 degrees, and the working phase angle of the second cylinder 20 relative to the first cylinder 10 is in the range of 90° ahead to 90° behind.

[0083] like Figure 14 to Figure 15 As shown, the diameter-expanding section 32 and the diameter-reducing section 31 may also be eccentrically arranged in the same direction relative to the non-diameter-expanding section 33 .

[0084] like Figure 16 to Figure 17 As shown, when the diameter expansion section 32 and the diameter reduction section 31 are eccentrically arranged in the same direction relative to the non-diameter expansion section 33, the angle θ between the first vane groove 11 and the second vane groove 21 satisfies: 120°<θ<270°. Specifically, the angle between the diameter reduction section 31 and the diameter expansion section 32 is 0°, and the working starting point of the first compression part is 0 degrees. The working phase angle of the second cylinder 20 relative to the first cylinder 10 is in the range of 120° to 270°.

[0085] like Fig.18 As shown, in order to prevent the lubricating oil from transferring the heat of the friction pair between the two cylinders, the lubricating oil circuits of the two cylinders need to be separated, so the pump body assembly has a first lubricating oil circuit and a second lubricating oil circuit, which are used to lubricate and dissipate heat for the first compression part and the second compression part respectively. The lubricating oil in the first lubricating oil circuit enters the central oil hole 34 of the crankshaft 30 from the oil pool, and then flows out from the first upper oil outlet hole 321, the middle oil outlet hole 322 and the lower oil outlet hole 323 of the enlarged diameter section 32 of the crankshaft 30 respectively, to lubricate the first flange 60, the friction pair of the first roller 40 of the pump body assembly and the enlarged diameter section 32, and the friction pair of the second flange 70 and the crankshaft 30 respectively, and then flows back to the oil pool through the oil groove of the first flange 60 and the second lateral oil outlet hole 71 of the second flange 70 respectively. The lubricating oil in the second lubricating oil circuit enters the central oil hole 34 of the crankshaft 30 from the oil pool, then flows out from the second upper oil outlet hole 311 of the reduced diameter section 31 of the crankshaft 30 to lubricate the friction pair between the second roller 50 of the pump body assembly and the reduced diameter section 31, and then flows back to the oil pool through the lateral oil outlet groove 100 on the lower end surface of the crankshaft 30. Through the above arrangement, the two lubricating oil circuits of the two compression parts are separated to avoid the risk of overheating failure and thermal leakage of the lubricating oil caused by repeated lubrication of the two compression parts.

[0086] In this embodiment, the pump body assembly is assembled as follows: the crankshaft 30 and the first roller 40, the first slide, the first flange 60 and the second flange 70 are assembled based on the first cylinder 10, the gap of the first cylinder 10 is adjusted and locked; the second cylinder 20 is installed on the end face of the second flange 70 away from the first cylinder 10, the second roller 50 and the second slide 90 are installed, and finally the cover plate 80 is installed, the gap of the second cylinder 20 is adjusted and locked.

[0087] The present application also provides a fluid machine, comprising the above-mentioned pump body assembly. In this embodiment, the fluid machine is a compressor.

[0088] like Figure 1 As shown, the fluid machine further includes a motor assembly 150 , and the motor assembly 150 is used to drive the crankshaft 30 to move.

[0089] The present application also provides a heat exchange device, including the above-mentioned fluid machinery. In this embodiment, the heat exchange device is an air conditioner.

[0090] Embodiment 2

[0091] The difference between the second embodiment and the first embodiment is that the structure of the pump assembly is different from that of the first embodiment. Specifically, the reduced diameter section 31 is located in the middle of the crankshaft 30 and above the expanded diameter section 32. The cover plate 80 is located above the first flange 60, and the second cylinder 20 is located between the first flange 60 and the cover plate 80.

[0092] like Fig.19 As shown, the reduced diameter section 31 is located in the middle of the crankshaft 30, the first flange 60 is located above the second flange 70, and the upper end surface of the first cylinder 10 is sealedly connected to the first flange 60, the lower end surface of the first cylinder 10 is sealedly connected to the second flange 70, the upper end surface of the second cylinder 20 is sealedly connected to the cover plate 80, and the lower end surface of the second cylinder 20 is sealedly connected to the first flange 60.

[0093] In this embodiment, during installation, the crankshaft 30 and the first roller 40, the first slide, the first flange 60 and the second flange 70 are installed based on the first cylinder 10. The first cylinder 10 is locked first, and then the second cylinder 20 is locked, and finally assembled to the motor assembly 150. Specifically, the method of assembling the first cylinder 10 first to check the sealing and then assembling the second cylinder 20 is more likely to ensure the independence of each cylinder, and the order of large to small is also easier to assemble the pump body assembly.

[0094] In order to realize the setting of the second cylinder 20 in the middle position of the pump body assembly, in this embodiment, the crankshaft 30 includes a first section and a second section that are axially split and connected, the expanded diameter section 32 and the reduced diameter section 31 are both located on the second section, and the parts of the second section other than the expanded diameter section 32 and the reduced diameter section 31 and the first section are all non-expanded diameter sections 33. The second cylinder 20 is located at the connection between the second section and the first section. Since the reduced diameter section 31 meets the diameter requirements in this embodiment, in this embodiment, the crankshaft 30 needs to be set as a split structure between the motor assembly 150 and the second compression part, the large shaft (first section) is the crankshaft motor section, and the small shaft (second section) is the crankshaft pump body section, and the two parts can be connected and fixed by different methods such as pin connection and interference fit.

[0095] In this embodiment, the second air intake port 22 is disposed on the first flange 60 .

[0096] like Fig. 20 As shown, when the reduced diameter section 31 is located in the middle of the crankshaft 30, the lubricating oil in the first lubricating oil circuit enters the central oil hole 34 of the crankshaft 30 from the oil pool, and then flows out from the first upper oil outlet hole 321, the middle oil outlet hole 322 and the lower oil outlet hole 323 of the expanded diameter section 32 of the crankshaft 30 respectively, so as to lubricate the first flange 60, the friction pair between the first roller 40 of the pump body assembly and the expanded diameter section 32, and the friction pair between the second flange 70 and the crankshaft 30 respectively, and the lubricating oil flowing through the first flange 60 flows back to the oil pool through the first lateral oil outlet hole 61 of the first flange 60, and the lubricating oil flowing through the friction pair between the second flange 70 and the crankshaft 30 flows downwardly back to the oil pool. The lubricating oil in the second lubricating oil circuit enters the central oil hole 34 of the crankshaft 30 from the oil pool, and then flows out from the second upper oil outlet hole 311 of the reduced diameter section 31 of the crankshaft 30 to lubricate the friction pair between the second roller 50 of the pump body assembly and the reduced diameter section 31, and then flows back to the oil pool through the first lateral oil outlet hole 61 of the first flange 60.

[0097] Embodiment 3

[0098] The difference between the third embodiment and the first embodiment is that the structural form of the pump body assembly is different from that of the first embodiment. Specifically, the second cylinder 20 is arranged above the motor assembly 150. The lower part of the motor assembly 150 is the first compression part, and the upper part of the motor assembly 150 is the second compression part. The reduced diameter section 31 is located at the top of the crankshaft 30, the bracket 151 is fixed to the motor stator or on the housing 190, and the second cylinder 20 is mounted on the bracket 151. Further, the second air intake port 22 is arranged on the bracket 151.

[0099] like Fig.21As shown, the reduced diameter section 31 is located at the top end of the crankshaft 30, the first flange 60 is located above the second flange 70, and the upper end surface of the first cylinder 10 is sealedly connected to the first flange 60, the lower end surface of the first cylinder 10 is sealedly connected to the second flange 70, the upper end surface of the second cylinder 20 is sealedly connected to the cover plate 80, and the lower end surface of the second cylinder 20 is used to be sealedly connected to the bracket 151 of the motor assembly 150.

[0100] In this embodiment, during installation, the crankshaft 30 and the first roller 40, the first slide, the first flange 60 and the second flange 70 are assembled based on the first cylinder 10, the gap of the first cylinder 10 is adjusted and locked to form the first component; the first component and the stator and rotor of the motor are installed on the housing 190, the bracket 151 is fixed on the stator of the motor or fixed on the housing 190, the second cylinder 20 is installed on the upper end surface of the bracket 151, the second roller 50 and the second slide 90 are installed, and finally the cover plate 80 is installed, the gap of the second cylinder 20 is adjusted and locked, and the oil plug is installed on the center hole of the cover plate 80.

[0101] like Fig. 22 As shown, when the reduced diameter section 31 is located at the top of the crankshaft 30, the lubricating oil in the first lubricating oil circuit enters the central oil hole 34 of the crankshaft 30 from the oil pool, and then flows out from the first upper oil outlet hole 321, the middle oil outlet hole 322 and the lower oil outlet hole 323 of the enlarged diameter section 32 of the crankshaft 30 respectively, so as to lubricate the first flange 60, the friction pair between the first roller 40 of the pump body assembly and the enlarged diameter section 32, and the friction pair between the second flange 70 and the crankshaft 30 respectively, and flows through the first flange 6 0 returns to the oil pool through the oil groove of the first flange 60, and the lubricating oil flowing through the friction pair of the second flange 70 and the crankshaft 30 returns downward to the oil pool; the lubricating oil in the second lubricating oil circuit enters the central oil hole 34 of the crankshaft 30 from the oil pool, and then flows out from the second upper oil outlet hole 311 of the reduced diameter section 31 of the crankshaft 30 to lubricate the friction pair of the second roller 50 of the pump body assembly and the reduced diameter section 31, and then returns to the oil pool through the lateral oil outlet hole of the motor assembly 150.

[0102] Embodiment 4

[0103] The difference between the fourth embodiment and the first embodiment is that the compression method of the fluid machinery is different from that of the first embodiment.

[0104] Specifically, Fig.23 As shown, the pump body assembly also has an enthalpy increase port 110 connected to the inner cavity of the first cylinder 10 and a medium-pressure intake pipe 120 for connecting to the enthalpy increase assembly. The enthalpy increase port 110 and the second air intake port 22 are respectively connected in parallel to the medium-pressure intake pipe 120.

[0105] The fluid machinery in this embodiment is a "single-stage enthalpy increase compression + independent compression" mode. Specifically, the fluid machinery also includes an enthalpy increase component. The single-machine enthalpy increase compression is that after the fluid machinery compresses the low-pressure refrigerant to a certain extent, the medium-pressure refrigerant is added to the compression chamber of the first cylinder 10 through the enthalpy increase port 110 for mixed compression. The mixed refrigerant is discharged to high pressure to achieve the enthalpy increase effect. By mixing the medium-pressure and low-pressure refrigerants and compressing them to high pressure, a single compressor is compressed in two stages, which increases the enthalpy difference in the circuit and improves the compression efficiency. On the basis of the original single-cylinder enthalpy increase compression, the pump body assembly also has the above-mentioned second compression part, which adds a medium-pressure refrigerant flow path to the medium-pressure intake pipe 120 originally acting on the first cylinder 10, and introduces it into the second cylinder 20 from the outside of the shell 190. That is to say, in this embodiment, the first cylinder 10 (large cylinder) is used as a single-stage enthalpy increase compression cylinder, and the second cylinder 20 (small cylinder) is used as an independent compression combination. Since the pressure in the cylinder of a single-cylinder enthalpy-added compression system builds up too quickly under light working conditions and the enthalpy-added refrigerant cannot be replenished, refrigerant backflow may occur. By adding a second cylinder 20 as a second compression cylinder, the enthalpy-added refrigerant that cannot be replenished into the first cylinder 10 can be introduced into the second cylinder 20 for compression.

[0106] like Figure 24 to Figure 25 As shown, the power consumption in the single-stage refrigeration cycle is (m1+m2)*(h2-h1). In the refrigeration cycle of this embodiment, m1 is used as the flow rate of the single-cylinder enthalpy increase process, and m2 is used as the flow rate of the parallel independent compression process. The power consumption in the cycle is m1*(h2'-h1')+m2*(h4-h3). From the relationship on the pressure diagram, it can be seen that compared with the single-stage cycle, the refrigeration cycle in this embodiment can effectively increase the enthalpy difference "h1-h8" on the evaporation side, increase the cooling capacity, and reduce the power consumption in the cycle. In the figure, "(h4-h3)<(h2'-h1')<(h2-h1)". Among them, h represents the enthalpy value, m represents the mass flow rate, and p represents the pressure.

[0107] This embodiment can improve the problem of insufficient single-cylinder enthalpy increase effect under the first load condition. The structural principle of the single-cylinder enthalpy increase is to connect the enthalpy increase channel after the compressor crankshaft rotates to a certain angle, and spray the enthalpy increase pressure refrigerant into the compression chamber. When the single-cylinder enthalpy increase compressor is under the first load condition, the intermediate pressure in the compression chamber is formed quickly, but due to mechanical structural limitations, when the crankshaft rotates to a certain angle, the enthalpy increase port 110 will definitely open. At this time, the refrigerant pressure in the compression chamber is higher than the enthalpy increase pressure, and the air replenishment effect cannot be formed. After adding the second compression section, all the intermediate-pressure gas that cannot be replenished by the single-cylinder enthalpy increase under the first load condition can be introduced into the second compression section, thereby improving the refrigeration effect of the single-cylinder enthalpy increase structure under the first load condition. Fig.26As shown, the enthalpy increase port 110 can also be connected in parallel with the second air intake port 22 and then connected to the medium-pressure air intake pipe 120. In other words, the air replenishment enthalpy increase channel and the air intake port of the second compression part are combined into one medium-pressure channel, and only one medium-pressure air intake pipe 120 is introduced outside the shell 190 to realize the function of two medium-pressure refrigerant channels. Fig. 27 As shown, the medium-pressure channel is arranged on the second flange 70 between the first cylinder 10 and the second cylinder 20, and the upper end surface of the second flange 70 has an enthalpy increase port 110 connected to the medium-pressure channel, and the lower end surface of the second flange 70 is connected to the second air intake port 22. Through the above arrangement, the structure of the pipeline outside the shell 190 is simplified, the length of the pipeline is reduced, and the cost is saved. Of course, according to different structural forms of the pump body assembly, the enthalpy increase port 110 can also be opened on the first flange 60, which can be selected according to actual needs.

[0108] Embodiment 5

[0109] The difference between the fifth embodiment and the first embodiment is that the compression method of the fluid machinery is different from that of the first embodiment.

[0110] Specifically, Fig.28 As shown, the pump body assembly also includes a third cylinder 130, which is connected to the first cylinder 10 through an intermediate buffer chamber 140 to form a multi-stage compression structure. The pump body assembly has a second intake port 22 connected to the inner cavity of the second cylinder 20 and a medium-pressure intake pipe 120 for connecting to the enthalpy increase assembly.

[0111] The fluid machinery in this embodiment is a "two-stage enthalpy increase compression + independent compression" mode. Specifically, the first cylinder 10 and the third cylinder 130 are a two-stage enthalpy increase compression structure, that is, the first cylinder 10 is a first-stage compression cylinder, and the third cylinder 130 is a second-stage compression cylinder. The volume ratio of the two compression cylinders is 0.6 to 0.8. There is an intermediate buffer chamber 140 between the two compression cylinders, and its function is to mix the refrigerant after the first-stage compression with the refrigerant sucked into the medium-pressure channel, and then flow into the second-stage compression cylinder for compression to achieve the enthalpy increase effect. On the basis of the two-stage enthalpy increase compression, the pump body assembly also has the above-mentioned second compression part. In this embodiment, the second compression part is arranged under the second flange 70 of the two-stage cylinder, and a medium-pressure refrigerant flow path is added to the medium-pressure intake pipe 120, which is introduced from the outside of the shell 190 into the second cylinder 20.

[0112] like Fig.29As shown, in the refrigeration cycle of this embodiment, m1 is used as the flow rate of the first-stage compression process, m2 is used as the flow rate of the medium-pressure refrigerant, and m3 is used as the flow rate of the parallel independent compression process. The power consumption in the cycle is "m1*(h1'-h1)+m3*(h4-h3)+(m1+m2-m3)*(h2'-h3')". From the relationship on the pressure diagram, it can be seen that compared with the single-stage cycle, the refrigeration cycle in this embodiment can effectively increase the enthalpy difference "h1-h8" on the evaporation side, increase the cooling capacity, and reduce the power consumption in the cycle. In the figure, (h4-h3)<(h2'-h3')<(h2-h1). Among them, h represents enthalpy value, m represents mass flow rate, and p represents pressure.

[0113] In this embodiment, if Fig.28 As shown, after parallel connection, the intermediate buffer chamber 140 is connected with the third air inlet 131 of the third cylinder 130, and the compressed refrigerant in the first cylinder 10 is mixed with the refrigerant entering the intermediate buffer chamber 140 from the medium-pressure air inlet pipe 120 and then enters the third cylinder 130 through the third air inlet 131 for further compression. Then it is discharged through the third air outlet 132. Another part of the refrigerant in the medium-pressure air inlet pipe 120 enters the second cylinder 20 through the second air inlet 22.

[0114] like Fig.30 As shown, the intermediate buffer chamber 140 can also be connected to the medium-pressure air inlet pipe 120 and the second air intake port 22 respectively. In other words, the second cylinder 20 is directly connected to the intermediate buffer chamber 140. The refrigerant in the medium-pressure air inlet pipe 120 first enters the intermediate buffer chamber 140 and then enters the second cylinder 20 through the second air intake port 22. Through the above arrangement, only one medium-pressure air inlet pipe 120 needs to be introduced from the outside of the shell 190 to the intermediate buffer chamber 140, and the intermediate pressure is introduced into the second cylinder 20 in the pump body, so that the two medium-pressure refrigerant channels can be merged without adding parts and processes. The structure of the pipeline outside the shell 190 is simplified, the length of the pipeline is reduced, and the cost is saved.

[0115] Embodiment 6

[0116] The difference between the sixth embodiment and the first embodiment is that the compression method of the fluid machinery is different from that of the first embodiment.

[0117] Specifically, Fig.31 As shown, the pump body assembly has a first air outlet 13 connected to the inner cavity of the first cylinder 10, a second air intake 22 connected to the inner cavity of the second cylinder 20, and a medium-pressure air intake pipe 120 for connecting to the enthalpy increase assembly. The first air outlet 13 is connected in parallel with the medium-pressure air intake pipe 120 and then connected to the second air intake 22.

[0118] The fluid machinery in this embodiment is a two-stage compression method with large and small cylinders. That is, the first cylinder 10 is used as a low-pressure compression cylinder, and the second cylinder 20 is used as a high-pressure compression cylinder. After the low-pressure side refrigerant is compressed by the first cylinder 10, it is mixed with the medium-pressure intake pipe 120 and enters the second cylinder 20. The second cylinder 20 has a small volume, which can improve the mechanical efficiency of the two-stage compression, thereby improving the efficiency of the fluid machinery.

[0119] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0120] Unless otherwise specifically stated, the relative arrangement of the parts and steps described in these embodiments, numerical expressions and numerical values ​​do not limit the scope of the present invention. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to the actual proportional relationship. The technology, method and equipment known to ordinary technicians in the relevant field may not be discussed in detail, but in appropriate cases, the technology, method and equipment should be regarded as a part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once a certain item is defined in an accompanying drawing, it does not need to be further discussed in subsequent drawings.

[0121] In the description of the present invention, it is necessary to understand that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the devices or elements referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention. The directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

[0122] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0123] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. If not otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

[0124] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0125] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the numbers used in this way can be interchanged where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein.

[0126] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A pump assembly, characterized in that: include: A first cylinder (10); a second cylinder (20), wherein a volume V2 of the second cylinder (20) is less than or equal to 10% of a volume V1 of the first cylinder (10); A crankshaft (30), the crankshaft (30) comprising a main body and a reduced diameter section (31), the outer periphery of the reduced diameter section (31) does not exceed the outer periphery of the main body, and the reduced diameter section (31) and the main body are eccentrically arranged in the axial direction of the main body; At least a portion of the main body is located inside the first cylinder (10), and at least a portion of the reduced diameter section (31) is located inside the second cylinder (20). During the rotation of the crankshaft (30), the portion of the main body located inside the first cylinder (10) and the portion of the reduced diameter section (31) located inside the second cylinder (20) respectively participate in the compression process.

2. The pump assembly according to claim 1, characterized in that: The main body portion comprises an expanded diameter section (32) located inside the first cylinder (10) and a non-expanded diameter section (33) located outside the first cylinder (10); the outer periphery of the reduced diameter section (31) does not exceed the outer periphery of the non-expanded diameter section (33); and the reduced diameter section (31) and the expanded diameter section (32) are eccentrically arranged relative to the non-expanded diameter section (33) in the axial direction of the main body portion.

3. The pump assembly according to claim 2, characterized in that: The diameter-expanding section (32) and the diameter-reducing section (31) are eccentrically arranged in the same direction relative to the non-diameter-expanding section (33); or The diameter-expanding section (32) and the diameter-reducing section (31) are eccentrically arranged in opposite directions relative to the non-diameter-expanding section (33).

4. The pump assembly according to claim 2, characterized in that: At least a portion of the outer periphery of the reduced diameter section (31) is located inside the outer periphery of the non-expanded diameter section (33); and / or The cross section of the reduced diameter section (31) is circular.

5. The pump assembly according to claim 2, characterized in that: The reduced diameter section (31) is located at the end of the crankshaft (30); or The reduced diameter section (31) is located in the middle of the crankshaft (30) and above the expanded diameter section (32).

6. The pump assembly according to claim 2, characterized in that: The crankshaft (30) comprises a first section and a second section which are axially separated and connected, the expanded diameter section (32) and the reduced diameter section (31) are both located on the second section, and the portion of the second section other than the expanded diameter section (32) and the reduced diameter section (31) and the first section are all the non-expanded diameter sections (33).

7. The pump assembly according to claim 1, characterized in that: Under a first load condition, the volume V1 of the first cylinder (10) and the volume V2 of the second cylinder (20) satisfy the following relationship: 0.03≤V2 / V1≤0.06; and / or Under the second load condition, the volume V1 of the first cylinder (10) and the volume V2 of the second cylinder (20) are equal to V2 satisfies: 0.07≤V2 / V1≤0.

1.

8. The pump assembly according to claim 7, characterized in that: The rotation speed of the crankshaft (30) under the first load condition is lower than the rotation speed of the crankshaft (30) under the second load condition.

9. The pump assembly according to claim 1, characterized in that: The pump body assembly further comprises a second sliding plate (90), the second cylinder (20) has a second sliding plate groove (21), and the second sliding plate (90) is slidably disposed at the second sliding plate groove (21).

10. The pump assembly according to any one of claims 1 to 9, characterized in that: The pump assembly also includes: a first flange (60) and a second flange (70), wherein the first cylinder (10) is located between the first flange (60) and the second flange (70); A cover plate (80), wherein the second cylinder (20) is located between the first flange (60) and the cover plate (80) or between the second flange (70) and the cover plate (80).

11. A fluid machine, characterized in that: A pump body assembly comprising any one of claims 1 to 10.

12. A heat exchange device, characterized in that: A fluid machine including the one described in claim 11.

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