Compression assembly, compressor and heat pump system

Abstract

The invention discloses a compression assembly, a compressor and a heat pump system, and relates to the technical field of compressors, the compression assembly comprises a crankshaft, a balance structure, an upper bearing, a first cylinder, a second cylinder and a lower bearing, the crankshaft is provided with a first eccentric part located in the first air cylinder and a second eccentric part located in the second air cylinder, and the first eccentric part is located between the second eccentric part and the upper bearing. The balance structure is used for enabling the load borne by the first eccentric part when the compression assembly works to be larger than the load borne by the second eccentric part when the compression assembly works. According to the technical scheme, the balance structure is arranged, so that the load borne by the first eccentric part when the compression assembly works is larger than that borne by the second eccentric part when the compression assembly works, and therefore torque caused by the fact that the first eccentric part and the second eccentric part are located at different positions of the crankshaft is at least partially offset; therefore, the bearing reaction force or the bearing reaction torque borne by the upper bearing or the lower bearing is reduced.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a compression assembly, compressor, and heat pump system. Background Technology

[0002] In existing technologies, the main structures of a twin-rotor compressor, such as the two cylinders and the eccentric crankshaft, are the same. Since the two eccentric parts are located at different heights on the crankshaft, the crankshaft itself can only counteract centrifugal force but cannot counteract torque. Therefore, a balance block still needs to be placed on the motor rotor. Although the mass of the balance block is reduced compared to a single-rotor compressor, at high speeds, the crankshaft at the end where the motor rotor is located is still subjected to relatively large centrifugal force and centrifugal torque, which leads to an increase in radial displacement at the upper end of the motor rotor. This increases the risk of collision between the motor rotor and the motor stator. At the same time, the upper end of the crankshaft will also experience local bending deformation, and the support reaction force and support reaction torque of the upper and lower bearings are relatively large. Summary of the Invention

[0003] The main objective of this invention is to provide a compression assembly, compressor, and heat pump system designed to reduce the reaction force or reaction moment experienced by the upper or lower bearing.

[0004] To achieve the above objectives, the present invention provides a compression component comprising:

[0005] The upper bearing, the first cylinder, the second cylinder, and the lower bearing are arranged sequentially.

[0006] A crankshaft rotatably connected to the upper bearing and the lower bearing, the crankshaft having a first eccentric portion located within the first cylinder and a second eccentric portion located within the second cylinder, the first eccentric portion being located between the second eccentric portion and the upper bearing; the crankshaft having opposing first and second sides, the first eccentric portion being located on the first side and the second eccentric portion being located on the second side; and

[0007] A balancing structure is provided, wherein the load on the first eccentric part under the operation of the compression assembly is greater than the load on the second eccentric part under the operation of the compression assembly, and the fluctuation is allowed to be no greater than the load on the second eccentric part under the operation of the compression assembly.

[0008] In one embodiment, the compression assembly includes an upper bearing, a first cylinder, a second cylinder, and a lower bearing arranged sequentially; and a crankshaft rotatably connected to the upper bearing and the lower bearing. The crankshaft has a first eccentric portion located within the first cylinder and a second eccentric portion located within the second cylinder, the first eccentric portion being located between the second eccentric portion and the upper bearing; the crankshaft has a first side and a second side opposite to each other, the first eccentric portion being located on the first side and the second eccentric portion being located on the second side.

[0009] The eccentricity of the first eccentric part is different from that of the second eccentric part;

[0010] And / or, in the axial extension direction of the crankshaft, the cylinder height of the first cylinder and the cylinder height of the second cylinder are different;

[0011] And / or, the first cylinder is provided with a first intake port, the second cylinder is provided with a second intake port, and the first intake port and the second intake port are offset along the axial direction of the crankshaft.

[0012] In one embodiment, the cylinder height of the first cylinder is greater than the cylinder height of the second cylinder.

[0013] In one embodiment, the ratio of the cylinder height of the first cylinder to the cylinder height of the second cylinder is not less than 1.1 and not greater than 1.4.

[0014] In one embodiment, the eccentricity of the first eccentric portion is greater than the eccentricity of the second eccentric portion.

[0015] In one embodiment, the ratio of the eccentricity of the first eccentric portion to the eccentricity of the second eccentric portion is not less than 1.1 and not greater than 1.3.

[0016] In one embodiment, the misalignment angle between the first air intake and the second air intake is no greater than 60°.

[0017] In one embodiment, the compression assembly includes a first partition plate and a second partition plate sleeved on the crankshaft, and the upper bearing, the first cylinder, the first partition plate, the second partition plate, the second cylinder and the lower bearing are arranged sequentially along the axial direction of the crankshaft.

[0018] The present invention also proposes a compressor comprising the compression assembly described in any of the foregoing embodiments.

[0019] In one embodiment, the crankshaft has a first end and a second end opposite each other along its axial direction, and the first eccentric portion and the second eccentric portion are disposed at the first end;

[0020] The crankshaft is provided with a motor rotor at its second end, and a first balance block is provided on the second side of the crankshaft for the motor rotor, and a second balance block is provided on the first side of the crankshaft for the motor rotor;

[0021] The ratio of the first balancing block to the first eccentric part is not greater than 0.1, and the ratio of the second balancing block to the second eccentric part is not greater than 0.1.

[0022] The present invention also proposes a heat pump system comprising the compressor described in any of the foregoing embodiments.

[0023] In one embodiment, the heat pump system includes a first heat exchange component, a second heat exchange component, a third heat exchange component, and a fourth heat exchange component, wherein the first cylinder has a first exhaust port and a first intake port, and the second cylinder has a second exhaust port and a second intake port;

[0024] The first exhaust port, the first heat exchange component, the second heat exchange component, and the first intake port are sequentially connected to form a first refrigerant circulation heat exchange circuit; the second exhaust port, the third heat exchange component, the fourth heat exchange component, and the second intake port are sequentially connected to form a second refrigerant circulation heat exchange circuit.

[0025] The technical solution of the present invention sets up a balancing structure so that the load on the first eccentric part under the operation of the compression assembly is greater than the load on the second eccentric part under the operation of the compression assembly, thereby at least partially offsetting the torque caused by the first eccentric part and the second eccentric part being located at different positions on the crankshaft, thereby reducing the support reaction force or support reaction torque on the upper or lower bearing.

[0026] Furthermore, the balancing structure specifically includes different eccentricities between the first eccentric portion and the second eccentric portion; and / or, in the axial extension direction of the crankshaft, different cylinder heights between the first cylinder and the second cylinder; and / or, the first cylinder is provided with a first intake port, the second cylinder is provided with a second intake port, and the first intake port and the second intake port are offset along the axial direction of the crankshaft.

[0027] Thus, the technical solution of this invention can achieve self-balancing of the shaft system without the need for additional balance blocks. Furthermore, the absence of balance blocks significantly reduces the radial displacement at the top of the motor rotor at high speeds, lowering the risk of collision between the motor stator and rotor. Compared to the original compression assembly with equal upper and lower cylinders, the load amplitude and fluctuation of the upper or lower bearing in this invention are improved. The load fluctuation of the upper bearing is reduced to a maximum of 45% of its original value, reducing shaft vibration and facilitating bearing lubrication, preventing crankshaft and bearing wear at high speeds, and improving shaft system reliability. Attached Figure Description

[0028] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0029] Figure 1 This is a schematic diagram of the structure of an embodiment of the compression component provided by the present invention;

[0030] Figure 2 for Figure 1 A cross-sectional view from one perspective;

[0031] Figure 3 A schematic diagram of another embodiment of the compression component provided by the present invention;

[0032] Figure 4 A schematic diagram of the eccentric part of the first eccentric part;

[0033] Figure 5 A schematic diagram of the eccentric part of the second eccentric part;

[0034] Figure 6 A schematic diagram illustrating the arrangement of the intake ports of the first and second cylinders;

[0035] Figure 7-a The diagram shows the distribution of the support reaction force on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme ABC during crankshaft rotation.

[0036] Figure 7-b The distribution diagram of the support reaction force on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme ABC during crankshaft rotation.

[0037] Figure 7-c The diagram shows the distribution of the reaction torque on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme ABC during crankshaft rotation.

[0038] Figure 7-d The distribution diagram of the support reaction torque on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme ABC during crankshaft rotation.

[0039] Figure 8-a The diagram shows the distribution of the support reaction force on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme A during crankshaft rotation.

[0040] Figure 8-b The diagram shows the distribution of the support reaction force on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme A during crankshaft rotation.

[0041] Figure 8-c The diagram shows the distribution of the support reaction torque on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme A during crankshaft rotation.

[0042] Figure 8-d The diagram shows the distribution of the support reaction torque on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme A during crankshaft rotation.

[0043] Figure 9-a The diagram shows the distribution of the support reaction force on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme B during crankshaft rotation.

[0044] Figure 9-b The diagram shows the distribution of the support reaction force on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme B during crankshaft rotation.

[0045] Figure 9-c The diagram shows the distribution of the support reaction torque on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme B during crankshaft rotation.

[0046] Figure 9-d The diagram shows the distribution of the support reaction torque on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme B during crankshaft rotation.

[0047] Figure 10-a The diagram shows the distribution of the support reaction force on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme C during crankshaft rotation.

[0048] Figure 10-b The diagram shows the distribution of the support reaction force on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme C during crankshaft rotation.

[0049] Figure 10-c The diagram shows the distribution of the reaction torque on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme C during crankshaft rotation.

[0050] Figure 10-d The diagram shows the distribution of the support reaction torque on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme C during crankshaft rotation.

[0051] Figure 11-a The diagram shows the distribution of the support reaction force on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme AB during crankshaft rotation.

[0052] Figure 11-b The diagram shows the distribution of the support reaction force on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme AB during crankshaft rotation.

[0053] Figure 11-c The diagram shows the distribution of the support reaction torque on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme AB during crankshaft rotation.

[0054] Figure 11-d The diagram shows the distribution of the support reaction torque on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme AB during crankshaft rotation.

[0055] Figure 12-a The diagram shows the distribution of the support reaction force on the upper bearing of the original upper and lower cylinder compression assembly and the AC compression assembly during crankshaft rotation.

[0056] Figure 12-b The diagram shows the distribution of the support reaction force on the lower bearing of the original upper and lower cylinder compression assembly and the AC compression assembly during crankshaft rotation.

[0057] Figure 12-c The diagram shows the distribution of the support reaction torque on the upper bearing of the original upper and lower cylinder compression assembly and the AC compression assembly during crankshaft rotation.

[0058] Figure 12-d The distribution diagram of the support reaction torque on the lower bearing of the original upper and lower cylinder compression assembly and the AC compression assembly during crankshaft rotation.

[0059] Figure 13-a The diagram shows the distribution of the support reaction force on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme BC during crankshaft rotation.

[0060] Figure 13-b The diagram shows the distribution of the support reaction force on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme BC during crankshaft rotation.

[0061] Figure 13-c The diagram shows the distribution of the reaction torque on the upper bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme BC during crankshaft rotation.

[0062] Figure 13-d This diagram shows the distribution of the reaction torque on the lower bearing of the original upper and lower cylinder compression assembly and the compression assembly of scheme BC during crankshaft rotation.

[0063] Explanation of icon numbers:

[0064] 10. Compression assembly; 100. Upper bearing; 200. Lower bearing; 300. First cylinder; 301. First intake port; 400. Second cylinder; 401. Second intake port; 500. Crankshaft; 510. First eccentric part; 520. Second eccentric part; 600. First partition plate; 700. Second partition plate;

[0065] 20. Motor rotor; 30. First balance block; 40. Second balance block.

[0066] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0067] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0068] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indications will also change accordingly.

[0069] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0070] This invention proposes a compression assembly that reduces the support reaction force on the upper or lower bearing, thereby improving the reliability of the compressor. For ease of understanding and explanation, details are attached to the specification of this invention. Figure 1 In section 7, the solid arrow indicates the air intake.

[0071] Please see Figure 1 In one embodiment of the present invention, the compression assembly 10 includes an upper bearing 100, a first cylinder 300, a second cylinder 400, a lower bearing 200, and a crankshaft 500 arranged sequentially. The crankshaft 500 is rotatably connected to the upper bearing 100 and the lower bearing 200. The crankshaft 500 has a first eccentric portion 510 located in the first cylinder 300 and a second eccentric portion 520 located in the second cylinder 400. The first eccentric portion 510 is located between the second eccentric portion 520 and the upper bearing 100. The crankshaft 500 has a first side and a second side opposite to each other. The first eccentric portion 510 is located on the first side, and the second eccentric portion 520 is located on the second side.

[0072] In an embodiment of the present invention, the compression assembly 10 is mainly used in a rolling roller compressor. The basic components of a rolling roller compressor typically include a motor assembly and a compression assembly 10. The compression assembly 10 typically includes a cylinder, rollers (rolling rotors), vanes, a crankshaft 500, an eccentric part, bearings, etc.

[0073] The cylinder has a compression chamber inside. The inner surface of the cylinder is a track for the movement of the vanes and rollers. It is equipped with an intake port and an exhaust port that are connected to the compression chamber. The intake port and the exhaust port are used for the intake and exhaust of gas, respectively. The intake port is located in the low-pressure area of ​​the compression chamber, and the exhaust port is located in the high-pressure area. When the rollers rotate, the low-pressure gas enters the compression chamber from the intake port and is discharged from the exhaust port after compression.

[0074] In existing twin-rotor compressors, the two cylinders and the eccentric part of the crankshaft 500 are identical in their main structures. Because the two eccentric parts are located at different heights on the crankshaft 500, the crankshaft 500 itself can only counteract centrifugal force, not torque. Therefore, a balance block is still required on the motor rotor 20. Although the mass of the balance block is reduced compared to a single-rotor compressor, at high speeds, the end of the crankshaft 500 where the motor rotor 20 is located still experiences significant centrifugal force and torque. This leads to increased radial displacement at the upper end of the motor rotor 20, increasing the risk of collision between the motor rotor 20 and the motor stator. Simultaneously, localized bending deformation occurs at the upper end of the crankshaft 500, resulting in a large support reaction force and torque on the upper bearing 100. This affects the oil film thickness of the bearing, increases frictional power consumption at high speeds, and causes the upper bearing 100 to wear easily under heavy load and high-speed conditions, leading to low shaft system reliability.

[0075] Based on this, in an embodiment of the present invention, the compression assembly 10 is provided with a balancing structure, which is used to ensure that the load on the first eccentric part 510 under the operation of the compression assembly 10 is greater than the load on the second eccentric part 520 under the operation of the compression assembly 10, and allows for fluctuations that are not greater than the load on the second eccentric part 520 under the operation of the compression assembly.

[0076] It should be understood that, in the above-described balancing structure, during the operation of the compression assembly 10, the overall trend of the balancing structure is such that the load on the first eccentric part 510 under the operation of the compression assembly 10 is greater than the load on the second eccentric part 520 under the operation of the compression assembly 10. For example, within one working cycle of the compression assembly (1, 2, or 3 or more crankshaft rotations), for 70%, 80%, or 90% of the time, the balancing structure is such that the load on the first eccentric part 510 under the operation of the compression assembly 10 is greater than the load on the second eccentric part 520 under the operation of the compression assembly 10.

[0077] In this embodiment, the loads on the first eccentric portion 510 and the second eccentric portion 520 under the operation of the compression assembly 10 mainly consider the magnetic pull of the motor, the centrifugal force, and the gas force in the working chamber at the top of the crankshaft 500. Furthermore, the upper bearing 100 refers to the main bearing, and the lower bearing 200 refers to the auxiliary bearing; that is, the upper bearing 100 is the bearing closest to the side where the motor rotor 20 is located.

[0078] The technical solution of the present invention, by setting a balancing structure, ensures that during the operation of the compression assembly 10, the load on the first eccentric part 510 under the operation of the compression assembly 10 is greater than the load on the second eccentric part 520 under the operation of the compression assembly 10. This at least partially offsets the torque caused by the first eccentric part 510 and the second eccentric part 520 being located at different positions on the crankshaft 500, thereby reducing the support reaction force or support reaction torque on the upper bearing 100 or the lower bearing 200.

[0079] This can be achieved by reducing the support reaction force or support reaction moment on the upper or lower bearing. This can be achieved by reducing the support reaction force or support reaction moment on the upper bearing, reducing the support reaction force or support reaction moment on the lower bearing, or reducing the support reaction force or support reaction moment on both the upper and lower bearings simultaneously.

[0080] Further, the balancing structure specifically includes: the eccentricity of the first eccentric portion 510 and the eccentricity of the second eccentric portion 520 are different; and / or, in the axial extension direction of the crankshaft 500, the cylinder height of the first cylinder 300 and the cylinder height of the second cylinder 400 are different; and / or, the first cylinder 300 is provided with a first intake port 301, the second cylinder 400 is provided with a second intake port 401, and the first intake port 301 and the second intake port 401 are offset along the axial direction of the crankshaft 500.

[0081] The term "and / or" in the above context means that it includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, solution B, or a solution that satisfies both A and B. Therefore, the above embodiments include:

[0082] Example 1: The eccentricity of the first eccentric part 510 is different from that of the second eccentric part 520.

[0083] Example 2: In the axial extension direction of the crankshaft 500, the cylinder height of the first cylinder 300 and the cylinder height of the second cylinder 400 are different.

[0084] Example 3: The first cylinder 300 is provided with a first intake port 301, and the second cylinder 400 is provided with a second intake port 401. The first intake port 301 and the second intake port 401 are offset along the axial direction of the crankshaft 500.

[0085] Example 4: The eccentricity of the first eccentric part 510 is different from that of the second eccentric part 520, and the cylinder height of the first cylinder 300 is different from that of the second cylinder 400 in the axial extension direction of the crankshaft 500.

[0086] Example 5: The eccentricity of the first eccentric part 510 and the eccentricity of the second eccentric part 520 are different, and the first cylinder 300 is provided with a first intake port 301, and the second cylinder 400 is provided with a second intake port 401. The first intake port 301 and the second intake port 401 are offset along the axial direction of the crankshaft 500.

[0087] Example 6: In the axial extension direction of the crankshaft 500, the cylinder height of the first cylinder 300 and the cylinder height of the second cylinder 400 are different, and the first cylinder 300 is provided with a first intake port 301, and the second cylinder 400 is provided with a second intake port 401. The first intake port 301 and the second intake port 401 are offset along the axial direction of the crankshaft 500.

[0088] Example 7: The eccentricity of the first eccentric part 510 and the eccentricity of the second eccentric part 520 are different. In the axial extension direction of the crankshaft 500, the cylinder height of the first cylinder 300 and the cylinder height of the second cylinder 400 are different. The first cylinder 300 is provided with a first intake port 301, and the second cylinder 400 is provided with a second intake port 401. The first intake port 301 and the second intake port 401 are offset along the axial direction of the crankshaft 500.

[0089] The different settings of these schemes must ultimately satisfy the following: the load on the first eccentric part under the operation of the compression component is greater than the load on the second eccentric part under the operation of the compression component, and fluctuations are allowed not to exceed the load on the second eccentric part under the operation of the compression component.

[0090] For example, the cylinder height of the first cylinder 300 can be referred to... Figure 2 h1, the cylinder height of the second cylinder 400, can be found in [reference]. Figure 2 h2 in the middle; the eccentricity of the first eccentric part 510 can be referred to. Figure 4 In the text, e1 refers to the eccentricity of the second eccentric part 520, which can be found in the reference. Figure 5 e2 in the text; the first intake port 301 and the second intake port 401 are offset along the axial direction of the crankshaft 500, as can be seen in the reference. Figure 1 As shown in Figure 7, the projections of the first intake port 301 and the second intake port 401 on the orthographic projection along the crankshaft 500 axis have non-overlapping portions.

[0091] Based on the above embodiment 1, in order to make the load on the first eccentric part 510 under the operation of the compression assembly 10 greater than the load on the second eccentric part 520 under the operation of the compression assembly 10, the cylinder height of the first cylinder 300 is greater than the cylinder height of the second cylinder 400.

[0092] Furthermore, the ratio of the cylinder height of the first cylinder 300 to the cylinder height of the second cylinder 400 is not less than 1.1 and not greater than 1.4. The ratio of the cylinder height of the first cylinder 300 to the cylinder height of the second cylinder 400 can be 1.1, 1.15, 1.2, 1.25, 1.3, 1.35, or 1.4, etc.

[0093] Based on the above embodiment 2, in order to ensure that the load on the first eccentric part 510 under the operation of the compression assembly 10 is greater than the load on the second eccentric part 520 under the operation of the compression assembly 10, the eccentricity of the first eccentric part 510 is greater than the eccentricity of the second eccentric part 520.

[0094] Furthermore, the ratio of the eccentricity of the first eccentric portion 510 to the eccentricity of the second eccentric portion 520 is not less than 1.1 and not greater than 1.3. The ratio of the eccentricity of the first eccentric portion 510 to the eccentricity of the second eccentric portion 520 can be 1.1, 1.15, 1.2, 1.25, or 1.3.

[0095] Based on the above embodiment three, the misalignment angle between the first air intake 301 and the second air intake 401 is no greater than 60°. Please refer to... Figure 6 That is Figure 6 shown ɑ The misalignment angle between the first intake port 301 and the second intake port 401 is determined based on the position where they begin to intake air, and the angle formed by the perpendicular line connecting this base point to the axis of the crankshaft 500. ɑ The values ​​include, but are not limited to, 5°, 10°, 15°, 20°, 25°, 30°, 35°, 40°, 45°, 50°, 55° or 60°.

[0096] In this way, when the compression assembly 10 is working, the pressure and reaction force generated by the compressed gas in the two cylinders can better cancel each other out, thereby reducing the torque generated by the compressed gas during the operation of the crankshaft 500 and improving the self-balancing of the shaft system.

[0097] Based on the above-described embodiment four, the eccentricity of the first eccentric portion 510 can be greater than the eccentricity of the second eccentric portion 520, and the cylinder height of the first cylinder 300 can be less than the cylinder height of the second cylinder 400; or the eccentricity of the first eccentric portion 510 can be less than the eccentricity of the second eccentric portion 520, and the cylinder height of the first cylinder 300 can be greater than the cylinder height of the second cylinder 400; or the eccentricity of the first eccentric portion 510 can be greater than the eccentricity of the second eccentric portion 520, and the cylinder height of the first cylinder 300 can be greater than the cylinder height of the second cylinder 400. In this case, it is necessary to ensure that the load on the first eccentric portion 510 under the operation of the compression assembly 10 is greater than the load on the second eccentric portion 520 under the operation of the compression assembly 10.

[0098] The above embodiments five, six and seven can be described with reference to the situation in embodiment four, and will not be described in detail here.

[0099] To verify the technical effect of the present invention, one embodiment from each of the above embodiments one to seven will be selected below, and the experimental data is recorded below.

[0100] Option A: The cylinder height of the first cylinder 300 is different from that of the second cylinder 400;

[0101] Option B: The eccentricity of the first eccentric part 510 is different from that of the second eccentric part 520;

[0102] Option C: The intake port of the first cylinder 300 and the intake port of the second cylinder 400 have different intake phase angles;

[0103] Option AB: The cylinder height of the first cylinder 300 is different from that of the second cylinder 400, and the eccentricity of the first eccentric part 510 is different from that of the second eccentric part 520.

[0104] Solution AC: The cylinder height of the first cylinder 300 is different from that of the second cylinder 400, and the intake phase angles of the intake ports of the first cylinder 300 and the second cylinder 400 are different.

[0105] Scheme BC: The eccentricity of the first eccentric part 510 is different from that of the second eccentric part 520, and the intake phase angles of the intake port of the first cylinder 300 and the intake port of the second cylinder 400 are different.

[0106] Scheme ABC: The cylinder height of the first cylinder 300 is different from that of the second cylinder 400; the eccentricity of the first eccentric part 510 is different from that of the second eccentric part 520; and the intake phase angles of the intake ports of the first cylinder 300 and the second cylinder 400 are different.

[0107] Table 1: Parameters of one specific embodiment of the above seven schemes.

[0108]

[0109]

[0110] In this embodiment, during the design, the loads on the first eccentric part 510 and the second eccentric part 520 under the operation of the compression assembly 10 are mainly considered to be the magnetic pull force of the motor, the centrifugal force and the gas force in the working chamber on the top of the crankshaft 500. The main parameters are shown in Table 1.

[0111] The original compression assembly with upper and lower cylinders consists mainly of a first cylinder (hereinafter referred to as the upper cylinder) and a second cylinder (hereinafter referred to as the lower cylinder) with identical structures. The intake ports of the upper and lower cylinders are distributed with the same phase angle (no phase angle difference), along with a first vane, a second vane, a first piston, a second piston, a first eccentric part, a second eccentric part, an upper bearing, a lower bearing, a crankshaft, and a partition. The eccentric parts of the crankshaft are symmetrically arranged with a 180-degree phase angle difference. During operation, with the first vane fully in its slot (0 degrees), and because the upper and lower cylinders are distributed with the same phase angle, and the first and second eccentric parts are symmetrically arranged with a 180-degree phase angle difference, when the upper cylinder begins intake, the lower cylinder is in the compression process. The gas loads on the two eccentric parts have a 180-degree phase angle difference, and the load on the crankshaft cycles in 180-degree increments.

[0112] The above seven schemes also take the first slider being completely in the slider groove as the crankshaft 0-degree angle.

[0113] Table 2 shows the load variation trends of the upper and lower bearings for the seven schemes mentioned above.

[0114]

[0115] In the compression assembly 10 provided by the technical solution of this embodiment and the original compression assembly 10 with upper and lower cylinders, the upper bearing 100 and lower bearing 200 of both are subjected to loads as follows: Figures 7-a to 1 As shown in 3c. Under the same working conditions, the specific ratio of the fluctuation value and maximum value of the support reaction force and support reaction moment of the upper bearing 100 and the lower bearing 200 of the compression assembly 10 of the present invention and the original compression assembly 10 with upper and lower equal cylinders is shown in Table 2. The fluctuation value is characterized by the discrete standard deviation std of the curve.

[0116] Depend on Figures 7-a to 1 As can be seen from the data in 3c and Table 2, compared with the original compression assembly 10 with upper and lower cylinders, the compression assembly 10 provided by the present invention has significantly reduced the maximum value and fluctuation of the support reaction force and support reaction torque on the upper bearing 100 and the lower bearing 200.

[0117] The experimental data above show that the compressor using the compression assembly 10 provided by this invention can achieve self-balancing of the shaft system without the need for a balance block. This self-balancing of the shaft system includes force balance and torque balance under the action of motor magnetic pull, centrifugal load, and working chamber gas load. In addition, the absence of a balance block can significantly reduce the radial displacement of the top of the motor rotor 20 at high speeds, reducing the risk of collision between the motor stator and rotor. Compared with the traditional two-cylinder compression assembly 10, the bearing load amplitude and fluctuation in the present invention are improved. The load fluctuation of the upper bearing 100 is reduced to a maximum of 45% of the original value, reducing shaft vibration and facilitating bearing lubrication, preventing wear of the crankshaft 500 and bearings at high speeds, and improving shaft system reliability.

[0118] In addition, in this invention, the different volumes of the first cylinder 300 and the second cylinder 400 can meet different power requirements. At the same time, it can be combined with a dual-intake and dual-exhaust heat pump system. The first cylinder 300 and the second cylinder 400 with different volumes can be designed according to the heat exchange of high pressure and medium pressure, so that the overall system energy efficiency is optimal.

[0119] In one embodiment, the compression assembly 10 includes a first partition plate 600 and a second partition plate 700 sleeved on the crankshaft 500, and the upper bearing 100, the first cylinder 300, the first partition plate 600, the second partition plate 700, the second cylinder 400 and the lower bearing 200 are arranged sequentially along the axial direction of the crankshaft 500.

[0120] In this embodiment, a double-diaphragm configuration effectively isolates the two compression zones of the compression assembly 10, preventing the mixing or leakage of gas, liquid, or lubricating oil between different parts, thus giving the compression assembly better sealing performance. Furthermore, compared to a single-diaphragm, the double-diaphragm configuration better absorbs and disperses vibrations and stresses generated during operation, further reducing the load on the crankshaft.

[0121] The present invention also proposes a compressor, which includes a compression assembly 10. The specific structure of the compression assembly 10 is as described in the above embodiments. Since the compressor adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0122] In one embodiment, please refer to Figure 3 The crankshaft 500 has a first end and a second end opposite to each other along its axial direction. The first eccentric portion 510 and the second eccentric portion 520 are disposed at the first end. The second end of the crankshaft 500 is provided with a motor rotor 20. In this embodiment, in order to further achieve dynamic balance of the crankshaft 500, the motor rotor 20 is provided with a first balance block 30 on the second side of the crankshaft 500, and the motor rotor 20 is provided with a second balance block 40 on the first side of the crankshaft 500. The ratio of the first balance block 30 to the first eccentric portion 510 is not greater than 0.10, and the ratio of the second balance block 40 to the second eccentric portion 520 is not greater than 0.10.

[0123] The ratio of the first balancing block 30 to the first eccentric part 510 can be 0.01, 0.02, 0.03, 0.04, 0.05, 0.06, 0.07, 0.08, 0.09, or 0.10, and the ratio of the second balancing block 40 to the second eccentric part 520 can be 0.01, 0.02, 0.03, 0.04, 0.05, 0.06, 0.07, 0.08, 0.09, or 0.10.

[0124] This embodiment, by setting a first balance block 30 and a second balance block 40 at both ends of the motor rotor 20, can further improve the dynamic balance of the crankshaft 500, thereby enhancing the stability of the compressor. Furthermore, by limiting the ratio of the first balance block 30 to the first eccentric portion 510 and the second balance block 40 to the second eccentric portion 520 to no more than 0.10, the weight of the balance blocks is kept within a reasonable range. This further improves the dynamic balance of the crankshaft 500 while avoiding other problems caused by excessive weight.

[0125] The present invention also proposes a heat pump system, characterized in that the heat pump system includes the aforementioned compressor, the specific structure of which is as described in the above embodiments. Since the compressor adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0126] In one embodiment, the heat pump system includes a first heat exchange component, a second heat exchange component, a third heat exchange component, and a fourth heat exchange component. The first cylinder 300 has a first exhaust port and a first intake port 301, and the second cylinder 400 has a second exhaust port and a second intake port 401. The first exhaust port, the first heat exchange component, the second heat exchange component, and the first intake port 301 are sequentially connected to form a first refrigerant circulation heat exchange loop. The second exhaust port, the third heat exchange component, the fourth heat exchange component, and the second intake port 401 are sequentially connected to form a second refrigerant circulation heat exchange loop.

[0127] Thus, since the volumes of the first cylinder 300 and the second cylinder 400 are different, this can meet the needs of different power requirements. In this embodiment, combined with the dual intake and dual exhaust heat pump system, the first cylinder 300 and the second cylinder 400 with different volumes are designed according to the heat exchange of high pressure and medium pressure, so that the overall system energy efficiency is optimal.

[0128] The first exhaust port, the first heat exchange component, the second heat exchange component, and the first intake port 301 are sequentially connected to form a first refrigerant circulation heat exchange circuit. Through switching components such as reversing valves, the first exhaust port, the second heat exchange component, the first heat exchange component, and the first intake port 301 can be sequentially connected to form a first refrigerant circulation heat exchange circuit.

[0129] The second exhaust port, the third heat exchange component, the fourth heat exchange component, and the second intake port 401 are sequentially connected to form a second refrigerant circulation heat exchange circuit. Through switching components such as reversing valves, the second exhaust port, the fourth heat exchange component, the third heat exchange component, and the second intake port 401 can be sequentially connected to form a second refrigerant circulation heat exchange circuit.

[0130] In one exemplary embodiment, the first refrigerant circulation heat exchange circuit where the first cylinder 300 is located is the heat exchange circuit of an air conditioner, and the second refrigerant circulation heat exchange circuit where the second cylinder 400 is located is the heat exchange circuit of a water heater. This dual-intake and dual-exhaust heat pump system is most energy efficient when applied to high-end residences such as luxury hotels.

[0131] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention specification and drawings under the technical concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A compression assembly, used in a compressor, characterized in that, Comprising: an upper bearing, a first cylinder, a second cylinder and a lower bearing arranged in sequence; a crankshaft rotatably connected to the upper bearing and the lower bearing, the crankshaft being provided with a first eccentric portion located in the first cylinder and a second eccentric portion located in the second cylinder, the first eccentric portion being located between the second eccentric portion and the upper bearing; the crankshaft having opposite first and second sides, the first eccentric portion being provided on the first side and the second eccentric portion being provided on the second side; and the eccentricity of the first eccentric portion and the eccentricity of the second eccentric portion are different; and / or, the cylinder height of the first cylinder and the cylinder height of the second cylinder are different in the axial extension direction of the crankshaft; and / or, the first cylinder is provided with a first air inlet and the second cylinder is provided with a second air inlet, the first air inlet and the second air inlet being arranged in axial offset with respect to the crankshaft.

2. A compression assembly for use in a compressor, the compression assembly comprising: Comprising: an upper bearing, a first cylinder, a second cylinder and a lower bearing arranged in sequence; a crankshaft rotatably connected to the upper bearing and the lower bearing, the crankshaft being provided with a first eccentric portion located in the first cylinder and a second eccentric portion located in the second cylinder, the first eccentric portion being located between the second eccentric portion and the upper bearing; the crankshaft having opposite first and second sides, the first eccentric portion being provided on the first side and the second eccentric portion being provided on the second side; and a balance structure for making the load received by the first eccentric portion under the operation of the compression assembly greater than the load received by the second eccentric portion under the operation of the compression assembly, and allowing the fluctuation to be not greater than the load received by the second eccentric portion under the operation of the compression assembly. The cylinder height of the first cylinder is greater than the cylinder height of the second cylinder.

3. The compression assembly of claim 1 or 2, wherein, The ratio of the cylinder height of the first cylinder to the cylinder height of the second cylinder is not less than 1.1 and not greater than 1.

4.

4. The compression assembly of claim 3, wherein, The eccentricity of the first eccentric portion is greater than the eccentricity of the second eccentric portion.

5. The compression assembly of claim 3, wherein, The ratio of the eccentricity of the first eccentric portion to the eccentricity of the second eccentric portion is not less than 1.1 and not greater than 1.

3.

6. The compression assembly of claim 5, wherein, The offset angle between the first air inlet and the second air inlet is not greater than 60°.

7. The compression assembly of claim 5, wherein, The compression assembly comprises a first partition plate and a second partition plate sleeved on the crankshaft, the upper bearing, the first cylinder, the first partition plate, the second partition plate, the second cylinder and the lower bearing are arranged in sequence along the axial direction of the crankshaft.

8. The compression assembly of claim 5, wherein, The compression assembly comprises the compression assembly according to any one of claims 1 to 8.

9. A compressor characterized by, The crankshaft has opposite first and second ends in its axial direction, the first eccentric portion and the second eccentric portion are provided on the first end; 10. The compressor of claim 9, wherein, The second end of the crankshaft is provided with a motor rotor, the motor rotor is provided with a first balance block on the second side of the crankshaft, and the motor rotor is provided with a second balance block on the first side of the crankshaft; The ratio of the first balance block to the first eccentric portion is not greater than 0.1, and the ratio of the second balance block to the second eccentric portion is not greater than 0.

1. The compressor comprises the compressor according to claim 9 or 10.

11. A heat pump system, characterized by, ​ 12. The heat pump system of claim 11, wherein, The heat pump system comprises a first heat exchange assembly, a second heat exchange assembly, a third heat exchange assembly and a fourth heat exchange assembly, the first cylinder has a first exhaust port and a first suction port, the second cylinder has a second exhaust port and a second suction port; The first exhaust port, the first heat exchange assembly, the second heat exchange assembly and the first suction port are sequentially communicated to form a first refrigerant circulating heat exchange loop; the second exhaust port, the third heat exchange assembly, the fourth heat exchange assembly and the second suction port are sequentially communicated to form a second refrigerant circulating heat exchange loop.

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