Compression assembly, compressor and heat pump system

Abstract

The utility model 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 counteracted; 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] The utility model relates to the technical field of compressors, and particularly to a compression assembly, a compressor and a heat pump system. Background Art

[0002] In the related prior art, the main structures such as the two cylinders and the crankshaft eccentric parts of a twin-rotor compressor are the same. Since the two eccentric parts are located at different heights of the crankshaft, the crankshaft itself can only offset the centrifugal force and cannot offset the torque. A balance weight still needs to be arranged on the motor rotor. Although the mass of the balance weight is reduced compared with that of a single-rotor machine, at high speeds, the end of the crankshaft where the motor rotor is located still receives a relatively large centrifugal force and centrifugal torque, resulting in an increase in the radial displacement of the upper end of the motor rotor, thereby increasing the risk of collision between the motor rotor and the motor stator. At the same time, local bending deformation will also occur at the upper end of the crankshaft, and the reaction forces and reaction torques of the upper bearing and the lower bearing are relatively large. Summary of the Utility Model

[0003] The main purpose of the utility model is to propose a compression assembly, a compressor and a heat pump system, aiming to reduce the reaction force or reaction torque received by the upper bearing or the lower bearing.

[0004] To achieve the above object, the compression assembly proposed by the utility model includes:

[0005] An upper bearing, a first cylinder, a second cylinder and a lower bearing arranged in sequence;

[0006] A crankshaft rotatably connected to the upper bearing and the lower bearing. The crankshaft is provided with a first eccentric part located in the first cylinder and a second eccentric part located in the second cylinder. The first eccentric part is located between the second eccentric part and the upper bearing; the crankshaft has opposite first and second sides, the first eccentric part is arranged on the first side, and the second eccentric part is arranged on the second side; and

[0007] A balance structure for making the load received by the first eccentric part under the operation of the compression assembly greater than the load received by the second eccentric part under the operation of the compression assembly, and allowing a situation where the fluctuation does not exceed the load received by the second eccentric part under the operation of the compression assembly.

[0008] In an embodiment, the compression assembly includes an upper bearing, a first cylinder, a second cylinder and a lower bearing arranged in sequence; and a crankshaft rotatably connected to the upper bearing and the lower bearing. The crankshaft is provided with a first eccentric part located in the first cylinder and a second eccentric part located in the second cylinder. The first eccentric part is located between the second eccentric part and the upper bearing; the crankshaft has opposite first and second sides, the first eccentric part is arranged on the first side, and the second eccentric part is arranged 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 is different from that of the second cylinder;

[0011] And / or, the first cylinder is provided with a first air inlet, the second cylinder is provided with a second air inlet, and the first air inlet and the second air inlet are arranged axially misaligned along the crankshaft.

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

[0013] In one embodiment, the ratio of the cylinder height of the first cylinder to that 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 part is greater than that of the second eccentric part.

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

[0016] In one embodiment, the misalignment angle between the first air inlet and the second air inlet is not 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 in sequence along the axial direction of the crankshaft.

[0018] The present utility model further provides a compressor, and the compressor includes the compression assembly described in any one of the foregoing embodiments.

[0019] In one embodiment, the crankshaft has opposite first and second ends along its axial direction, and the first eccentric part and the second eccentric part are arranged at the first end;

[0020] A motor rotor is provided at the second end of the crankshaft, a first balance weight is provided on the second side of the crankshaft for the motor rotor, and a second balance weight is provided on the first side of the crankshaft for the motor rotor;

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

[0022] The present utility model also provides a heat pump system, which includes 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. The first cylinder has a first exhaust port and a first suction port, and the second cylinder has a second exhaust port and a second suction port.

[0024] The first exhaust port, the first heat exchange component, the second heat exchange component, and the first suction port 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 suction port are sequentially connected to form a second refrigerant circulation heat exchange loop.

[0025] By providing a balance structure in the technical solution of the present utility model, the load received by the first eccentric part under the operation of the compression component is greater than the load received by the second eccentric part under the operation of the compression component, so as to at least partially offset the torque caused by the first eccentric part and the second eccentric part being located at different positions on the crankshaft, thereby reducing the reaction force or reaction torque received by the upper bearing or the lower bearing.

[0026] Further, the balance structure is specifically that the eccentricity of the first eccentric part is different from the eccentricity of the second eccentric part; and / or, in the axial extension direction of the crankshaft, the cylinder height of the first cylinder is different from the cylinder height of the second cylinder; and / or, the first cylinder is provided with a first suction port, the second cylinder is provided with a second suction port, and the first suction port and the second suction port are axially offset along the crankshaft.

[0027] In this way, the technical solution of the present utility model can achieve the self - balance of the shafting without the need to additionally provide a balance weight. In addition, the absence of a balance weight can significantly reduce the radial displacement at the top of the motor rotor at high speeds and reduce the risk of collision between the stator and rotor of the motor. Compared with the original compression component with equal upper and lower cylinders, both the amplitude and fluctuation of the load received by the upper bearing or the lower bearing in the solution of the present utility model are improved. Among them, the load fluctuation of the upper bearing drops to at most 45% of the original value, reducing the vibration of the shafting, being beneficial to bearing lubrication, avoiding wear of the crankshaft and bearings at high speeds, and improving the reliability of the shafting. Description of the Drawings

[0028] In order to more clearly illustrate the technical solutions in the embodiments of the present utility model or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present utility model. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on the structures shown in these drawings.

[0029] Figure 1 Schematic diagram of a structure of an embodiment of the compression assembly provided by the present utility model;

[0030] Figure 2 is Figure 1 Cross-sectional view from one perspective;

[0031] Figure 3 Schematic diagram of a structure of another embodiment of the compression assembly provided by the present utility model;

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

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

[0034] Figure 6 Schematic diagram of a structure of an implementation of the arrangement of the suction ports of the first cylinder and the second cylinder;

[0035] Figure 7-a Distribution diagram of the reaction forces received by the upper bearings of the compression assembly with the original upper and lower equal-cylinder design and the compression assembly of Scheme ABC during the rotation of the crankshaft;

[0036] Figure 7-b Distribution diagram of the reaction forces received by the lower bearings of the compression assembly with the original upper and lower equal-cylinder design and the compression assembly of Scheme ABC during the rotation of the crankshaft;

[0037] Figure 7-c Distribution diagram of the reaction moments received by the upper bearings of the compression assembly with the original upper and lower equal-cylinder design and the compression assembly of Scheme ABC during the rotation of the crankshaft;

[0038] Figure 7-d Distribution diagram of the reaction moments received by the lower bearings of the compression assembly with the original upper and lower equal-cylinder design and the compression assembly of Scheme ABC during the rotation of the crankshaft;

[0039] Figure 8-a Distribution diagram of the reaction forces received by the upper bearings of the compression assembly with the original upper and lower equal-cylinder design and the compression assembly of Scheme A during the rotation of the crankshaft;

[0040] Figure 8-b Distribution diagram of the reaction forces received by the lower bearings of the compression assembly with the original upper and lower equal-cylinder design and the compression assembly of Scheme A during the rotation of the crankshaft;

[0041] Figure 8-cThe distribution diagrams of the reaction moments received by the upper bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan A during the rotation of the crankshaft;

[0042] Figure 8-d The distribution diagrams of the reaction moments received by the lower bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan A during the rotation of the crankshaft;

[0043] Figure 9-a The distribution diagrams of the reaction forces received by the upper bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan B during the rotation of the crankshaft;

[0044] Figure 9-b The distribution diagrams of the reaction forces received by the lower bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan B during the rotation of the crankshaft;

[0045] Figure 9-c The distribution diagrams of the reaction moments received by the upper bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan B during the rotation of the crankshaft;

[0046] Figure 9-d The distribution diagrams of the reaction moments received by the lower bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan B during the rotation of the crankshaft;

[0047] Figure 10-a The distribution diagrams of the reaction forces received by the upper bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan C during the rotation of the crankshaft;

[0048] Figure 10-b The distribution diagrams of the reaction forces received by the lower bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan C during the rotation of the crankshaft;

[0049] Figure 10-c The distribution diagrams of the reaction moments received by the upper bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan C during the rotation of the crankshaft;

[0050] Figure 10-d The distribution diagrams of the reaction moments received by the lower bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan C during the rotation of the crankshaft;

[0051] Figure 11-a The distribution diagrams of the reaction forces received by the upper bearings of the compression components of the original upper and lower equal-cylinder design and the compression components of Plan AB during the rotation of the crankshaft;

[0052] Figure 11-bThe distribution diagrams of the reaction forces received by the lower bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme AB during the rotation of the crankshaft;

[0053] Figure 11-c The distribution diagrams of the reaction moments received by the upper bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme AB during the rotation of the crankshaft;

[0054] Figure 11-d The distribution diagrams of the reaction moments received by the lower bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme AB during the rotation of the crankshaft;

[0055] Figure 12-a The distribution diagrams of the reaction forces received by the upper bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme AC during the rotation of the crankshaft;

[0056] Figure 12-b The distribution diagrams of the reaction forces received by the lower bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme AC during the rotation of the crankshaft;

[0057] Figure 12-c The distribution diagrams of the reaction moments received by the upper bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme AC during the rotation of the crankshaft;

[0058] Figure 12-d The distribution diagrams of the reaction moments received by the lower bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme AC during the rotation of the crankshaft;

[0059] Figure 13-a The distribution diagrams of the reaction forces received by the upper bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme BC during the rotation of the crankshaft;

[0060] Figure 13-b The distribution diagrams of the reaction forces received by the lower bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme BC during the rotation of the crankshaft;

[0061] Figure 13-c The distribution diagrams of the reaction moments received by the upper bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme BC during the rotation of the crankshaft;

[0062] Figure 13-d The distribution diagrams of the reaction moments received by the lower bearings of the compression components with the original upper and lower equal-cylinder design and the compression components of Scheme BC during the rotation of the crankshaft.

[0063] Explanation of the reference numerals in the attached drawings:

[0064] 10. Compression assembly; 100. Upper bearing; 200. Lower bearing; 300. First cylinder; 301. First suction port; 400. Second cylinder; 401. Second suction 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 weight; 40. Second balance weight.

[0066] The realization, functional features and advantages of the purpose of the present utility model will be further described in conjunction with the embodiments and with reference to the accompanying drawings. Detailed implementation manners

[0067] Next, the technical solutions in the embodiments of the present utility model will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all of the embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without making creative efforts belong to the scope of protection of the present utility model.

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

[0069] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present utility model, the descriptions of "first", "second", etc. are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In addition, if "and / or" or "and / or" appears throughout the text, its meaning 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 at the same time. In addition, the technical solutions between the embodiments can be combined with each other, but it must be based on the fact that those of ordinary skill in the art can implement them. When the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection required by the present utility model.

[0070] The present utility model proposes a compression assembly to reduce the reaction force borne by the upper bearing or the lower bearing, thereby improving the reliability of the compressor. For the convenience of understanding and description, in the attached drawings of the specification of the present utility model Figure 1Among 0 to 7, the intake port is indicated by the solid arrow.

[0071] Please refer to Figure 1 In an 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 in sequence; the crankshaft 500 is rotatably connected to the upper bearing 100 and the lower bearing 200, and the crankshaft 500 is provided with a first eccentric portion 510 located in the first cylinder 300 and a second eccentric portion 520 located in the second cylinder 400, and the first eccentric portion 510 is located between the second eccentric portion 520 and the upper bearing 100; the crankshaft 500 has opposite first and second sides, the first eccentric portion 510 is provided on the first side, and the second eccentric portion 520 is provided on the second side.

[0072] In an embodiment of the present invention, the compression assembly 10 is mainly applied to a rolling roller compressor. The basic components of a rolling roller compressor usually include a motor assembly and a compression assembly 10. The compression assembly 10 usually includes a cylinder, a roller (rolling rotor), a sliding vane, a crankshaft 500, an eccentric portion, a bearing, etc.

[0073] Among them, a compression cavity is formed inside the cylinder. The inner surface of the cylinder is the track for the movement of the sliding vane and the roller, and is provided with an intake port and an exhaust port communicating with the compression cavity. The intake port and the exhaust port are respectively used for the intake and exhaust of gas. The intake port is located in the low-pressure area of the compression cavity, and the exhaust port is located in the high-pressure area. When the roller rotates, low-pressure gas enters the compression cavity from the intake port and is discharged from the exhaust port after compression.

[0074] In existing twin-rotor compressors, the main structures such as the two cylinders and the eccentric portions of the crankshaft 500 are the same. Since the two eccentric portions are located at different heights of the crankshaft 500, the crankshaft 500 itself can only offset the centrifugal force and cannot offset the torque. It is still necessary to arrange balance weights on the motor rotor 20. Although the mass of the balance weights has decreased compared to that of a single-rotor machine, at high speeds, the end of the crankshaft 500 where the motor rotor 20 is located still receives a relatively large centrifugal force and centrifugal torque, resulting in an increase in the radial displacement of the upper end of the motor rotor 20, thereby increasing the risk of collision between the motor rotor 20 and the motor stator. At the same time, the upper end of the crankshaft 500 will also be locally bent and deformed, and the reaction force and reaction torque of the upper bearing 100 are relatively large, affecting the oil film thickness of the bearing and increasing the friction power consumption at high speeds. Under heavy-load and high-speed working conditions, the upper bearing 100 is prone to wear and the reliability of the low shafting is reduced.

[0075] Based on this, in the embodiments of the present utility model, a balancing structure is provided inside the compression assembly 10. The balancing structure is configured to make the load received by the first eccentric part 510 under the operation of the compression assembly 10 greater than the load received by the second eccentric part 520 under the operation of the compression assembly 10, and it is allowed that there are fluctuations not greater than the load received by the second eccentric part 520 under the operation of the compression assembly.

[0076] It should be understood that in the above-mentioned balancing structure, during the operation of the compression assembly 10, overall, the balancing structure is configured to make the load received by the first eccentric part 510 under the operation of the compression assembly 10 greater than the load received by the second eccentric part 520 under the operation of the compression assembly 10. For example, within one working cycle of a compression assembly (the crankshaft rotates 1 circle, 2 circles, 3 circles or more than 3 circles), it can be 70%, 80% or 90% of the time that the balancing structure is configured to make the load received by the first eccentric part 510 under the operation of the compression assembly 10 greater than the load received by the second eccentric part 520 under the operation of the compression assembly 10.

[0077] In this embodiment, the loads received by the first eccentric part 510 and the second eccentric part 520 under the operation of the compression assembly 10 mainly consider the magnetic pulling force of the motor, the centrifugal force, and the gas force in the working chamber at the top of the crankshaft 500. In addition, 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 closer to the side where the motor rotor 20 is located.

[0078] The technical solution of the present utility model, by providing a balancing structure, makes it so that during the operation of the compression assembly 10, overall, the load received by the first eccentric part 510 under the operation of the compression assembly 10 is greater than the load received by the second eccentric part 520 under the operation of the compression assembly 10, thereby at least partially offsetting the torque caused by the first eccentric part 510 and the second eccentric part 520 being located at different positions on the crankshaft 500, and further reducing the reaction force or reaction torque received by the upper bearing 100 or the lower bearing 200, reducing the reaction force or reaction torque received by the upper bearing 100 or the lower bearing 200.

[0079] Among them, reducing the reaction force or reaction torque received by the upper bearing or the lower bearing can be reducing the reaction force or reaction torque received by the upper bearing, or reducing the reaction force or reaction torque received by the lower bearing, or simultaneously reducing the reaction force or reaction torque received by the upper bearing and the lower bearing.

[0080] Further, the balance structure is specifically as follows: the eccentricity of the first eccentric part 510 is different from the eccentricity of the second eccentric part 520; and / or, in the axial extension direction of the crankshaft 500, the cylinder height of the first cylinder 300 is different from the cylinder height of the second cylinder 400; and / or, the first cylinder 300 is provided with a first air inlet 301, the second cylinder 400 is provided with a second air inlet 401, and the first air inlet 301 and the second air inlet 401 are arranged in an axial dislocation along the crankshaft 500.

[0081] Among them, the meaning of "and / or" mentioned above is that it includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, or solution B, or the solution where both A and B are satisfied. Thus, the above embodiments include:

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

[0083] Embodiment 2: In the axial extension direction of the crankshaft 500, the cylinder height of the first cylinder 300 is different from the cylinder height of the second cylinder 400.

[0084] Embodiment 3: The first cylinder 300 is provided with a first air inlet 301, the second cylinder 400 is provided with a second air inlet 401, and the first air inlet 301 and the second air inlet 401 are arranged in an axial dislocation along the crankshaft 500.

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

[0086] Embodiment 5: The eccentricity of the first eccentric part 510 is different from the eccentricity of the second eccentric part 520, and the first cylinder 300 is provided with a first air inlet 301, the second cylinder 400 is provided with a second air inlet 401, and the first air inlet 301 and the second air inlet 401 are arranged in an axial dislocation along the crankshaft 500.

[0087] Embodiment 6: In the axial extension direction of the crankshaft 500, the cylinder height of the first cylinder 300 is different from the cylinder height of the second cylinder 400, and the first cylinder 300 is provided with a first air inlet 301, the second cylinder 400 is provided with a second air inlet 401, and the first air inlet 301 and the second air inlet 401 are arranged in an axial dislocation along the crankshaft 500.

[0088] Embodiment Seven: The eccentricity of the first eccentric part 510 is different from that of the second eccentric part 520. In the axial extension direction of the crankshaft 500, the cylinder height of the first cylinder 300 is different from that of the second cylinder 400. The first cylinder 300 is provided with a first air inlet 301, and the second cylinder 400 is provided with a second air inlet 401. The first air inlet 301 and the second air inlet 401 are arranged axially offset along the crankshaft 500.

[0089] Due to the differences in the above arrangements, finally, it is necessary to satisfy that the load received by the first eccentric part under the operation of the compression assembly is greater than the load received by the second eccentric part under the operation of the compression assembly, and a situation where the fluctuation is not greater than the load received by the second eccentric part under the operation of the compression assembly is allowed.

[0090] Exemplarily, for the cylinder height of the first cylinder 300, reference can be made to Figure 2 h1 in Figure 2 For the cylinder height of the second cylinder 400, reference can be made to Figure 4 h2 in Figure 5 For the eccentricity of the first eccentric part 510, reference can be made to Figure 1 e1 in

[0091] Based on the above Embodiment One, in order to make the load received by the first eccentric part 510 under the operation of the compression assembly 10 greater than the load received by the second eccentric part 520 under the operation of the compression assembly 10, the cylinder height of the first cylinder 300 is greater than that 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. Among them, 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 Two, in order to achieve that the load received by the first eccentric part 510 under the operation of the compression assembly 10 is greater than the load received by the second eccentric part 520 under the operation of the compression assembly 10, the eccentricity of the first eccentric part 510 is greater than that of the second eccentric part 520.

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

[0095] Based on the above Embodiment 3, the misalignment angle between the first air inlet 301 and the second air inlet 401 is not greater than 60°. Please refer to Figure 6 , that is Figure 6 shown in ɑ . Wherein, the misalignment angle between the first air inlet 301 and the second air inlet 401 is determined based on the positions where both start to inhale air, and is the included angle formed by the vertical connection line between this base point and the axis of the crankshaft 500. ɑ The values of 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 works, the pressures and reaction forces generated by compressing the gas in the two cylinders can better cancel each other out, so as to reduce the torque generated by the compressed gas during the operation of the crankshaft 500, thereby improving the self - balance of the shafting.

[0097] Based on the above Embodiment 4, it can be that the eccentricity of the first eccentric part 510 is greater than the eccentricity of the second eccentric part 520, and the cylinder height of the first cylinder 300 is less than the cylinder height of the second cylinder 400; it can be that the eccentricity of the first eccentric part 510 is less than the eccentricity of the second eccentric part 520, and the cylinder height of the first cylinder 300 is greater than the cylinder height of the second cylinder 400; it can also be that the eccentricity of the first eccentric part 510 is greater than the eccentricity of the second eccentric part 520, and the cylinder height of the first cylinder 300 is greater than the cylinder height of the second cylinder 400. At this time, it is necessary to make the load received by the first eccentric part 510 under the operation of the compression assembly 10 greater than the load received by the second eccentric part 520 under the operation of the compression assembly 10.

[0098] For the above Embodiment 5, Embodiment 6 and Embodiment 7, the situation of Embodiment 4 can be referred to, and no further elaboration will be given here one by one.

[0099] In order to verify the technical effects of the technical solution of the present invention, one embodiment will be selected from each of the above Embodiments 1 to 7 for the following, and the following is the experimental process data record.

[0100] Solution A: The cylinder heights of the first cylinder 300 and the second cylinder 400 are different;

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

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

[0103] Solution 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 ports of the first cylinder 300 and the second cylinder 400 have different intake phase angles;

[0105] Solution BC: The eccentricity of the first eccentric part 510 is different from that of the second eccentric part 520, and the intake ports of the first cylinder 300 and the second cylinder 400 have different intake phase angles;

[0106] Solution 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 ports of the first cylinder 300 and the second cylinder 400 have different intake phase angles.

[0107] Table 1: Parameters of each of the above seven solutions in one specific embodiment.

[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 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. The main parameters are shown in Table 1.

[0111] Compression assembly with original upper and lower equal-cylinder setting: It mainly consists of a first cylinder (hereinafter referred to as the upper cylinder) and a second cylinder (hereinafter referred to as the lower cylinder) with the same structure, and the suction ports of the upper and lower cylinders are distributed with the same phase angle (no phase angle difference), a first sliding vane, a second sliding 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, when the first sliding vane is completely in the vane slot, it is defined as the 0-degree angle of the crankshaft. Since the upper cylinder and the lower cylinder have the same phase distribution, and the first eccentric part and the second eccentric part are symmetrically distributed with a 180-degree phase angle difference, when the upper cylinder starts to inhale, the lower cylinder is in the compression process, and the phase angles of the gas loads received by the two eccentric parts differ by 180 degrees. The load on the crankshaft has a cycle of 180 degrees.

[0112] For the above seven schemes, it is also defined that when the first sliding vane is completely in the vane slot, it is the 0-degree angle of the crankshaft.

[0113] Table 2, the changing trends of the loads on the upper bearing and the lower bearing corresponding to the above seven schemes

[0114]

[0115] In the compression assembly 10 provided by the technical solution of this embodiment and the compression assembly 10 with the original upper and lower equal-cylinder setting, for the upper bearing 100 and the lower bearing 200 of both, the loads are as Figures 7-a to 1 shown in Fig. 3c. Under the same working conditions, for the compression assembly 10 of the present utility model and the compression assembly 10 with the original upper and lower equal-cylinder setting, the specific ratios of the fluctuation values and the maximum values of the reaction forces and reaction moments received by the upper bearing 100 and the lower bearing 200 of both are shown in Table 2, where the fluctuation value is characterized by the discrete standard deviation std of the curve.

[0116] From Figures 7-a to 1 the data in Fig. 3c and Table 2, it can be seen that compared with the compression assembly 10 with the original upper and lower equal-cylinder setting, for the compression assembly 10 provided by the present utility model, the maximum amplitudes and fluctuations of the reaction forces and reaction moments received by the upper bearing 100 and the lower bearing 200 are significantly decreased.

[0117] As can be seen from the above experimental data, the compressor adopting the compression assembly 10 provided by the present utility model can achieve the self - balance of the shafting without the need for a balance weight. The self - balance of the shafting includes the force balance and moment balance under the action of the motor magnetic pull force, centrifugal load, and working - chamber gas load. In addition, the absence of a balance weight can significantly reduce the radial displacement at the top of the motor rotor 20 at high speeds, reducing the risk of collision between the stator and rotor of the motor. Compared with the traditional compression assembly 10 with two equal - cylinder settings, both the amplitude and fluctuation of the load on the bearings in the solution of the present utility model are improved. Among them, the load fluctuation of the upper bearing 100 drops to at most 45% of the original value, reducing the vibration of the shafting, facilitating bearing lubrication, avoiding wear of the crankshaft 500 and bearings at high speeds, and improving the reliability of the shafting.

[0118] In addition, in the present utility model, the different volumes in the first cylinder 300 and the second cylinder 400 can meet the scenarios with different power requirements. At the same time, it can be combined with a double - suction and double - discharge heat - pump system. According to the heat exchange amounts of high - pressure and medium - pressure, the first cylinder 300 and the second cylinder 400 with different volumes are designed to optimize the overall system energy efficiency.

[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. 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 in sequence along the axial direction of the crankshaft 500.

[0120] In this embodiment, the double - partition plate setting can effectively isolate the two compression regions of the compression assembly 10, preventing the mixing or leakage of gas, liquid, or lubricating oil between different parts, so that the compression assembly has good sealing performance. In addition, compared with a single partition plate, the double - partition plate can better absorb and disperse the vibration and stress generated during operation, and can further reduce the load borne by the crankshaft.

[0121] The present utility model also proposes a compressor, which includes a compression assembly 10. The specific structure of the compression assembly 10 refers to the above - mentioned embodiment. Since this compressor adopts all the technical solutions of the above - mentioned embodiments, it has at least all the beneficial effects brought by the technical solutions of the above - mentioned embodiments, which will not be elaborated here one by one.

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

[0123] Among them, the ratio of the first balance weight 30 to the first eccentric portion 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 balance weight 40 to the second eccentric portion 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] In this embodiment, by providing the first balance weight 30 and the second balance weight 40 at both ends of the motor rotor 20, the dynamic balance of the crankshaft 500 can be further improved, thereby enhancing the stability of the compressor. In addition, limiting the ratios of the first balance weight 30 to the first eccentric portion 510 and the second balance weight 40 to the second eccentric portion 520 to be not greater than 0.10 makes the weights of the balance weights within a reasonable range, and while further improving the dynamic balance of the crankshaft 500, other problems caused by excessive weight can be avoided.

[0125] The present utility model further provides a heat pump system, characterized in that the heat pump system includes the compressor described above, and the specific structure of the compressor refers to the above embodiment. Since this compressor adopts all the technical solutions of the above embodiments, it at least has all the beneficial effects brought by the technical solutions of the above embodiments, and will not be elaborated one by one 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 suction port 301, and the second cylinder 400 has a second exhaust port and a second suction port 401; the first exhaust port, the first heat exchange component, the second heat exchange component and the first suction port 301 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 suction port 401 are sequentially connected to form a second refrigerant circulation heat exchange circuit.

[0127] Thus, due to the different volumes in the first cylinder 300 and the second cylinder 400, this can meet the scenarios with different power requirements. In this embodiment, in combination with a double-suction and double-exhaust heat pump system, the first cylinder 300 and the second cylinder 400 with different volumes are designed according to the heat exchange amounts of high pressure and medium pressure, so as to optimize the overall system energy efficiency.

[0128] Wherein, the first exhaust port, the first heat exchange component, the second heat exchange component, and the first suction port 301 are sequentially connected to form a first refrigerant circulation heat exchange loop. Through switching components such as a reversing valve, it can be made that the first exhaust port, the second heat exchange component, the first heat exchange component, and the first suction port 301 are sequentially connected to form a first refrigerant circulation heat exchange loop;

[0129] The second exhaust port, the third heat exchange component, the fourth heat exchange component, and the second suction port 401 are sequentially connected to form a second refrigerant circulation heat exchange loop. Through switching components such as a reversing valve, it can be made that the second exhaust port, the fourth heat exchange component, the third heat exchange component, and the second suction port 401 are sequentially connected to form a second refrigerant circulation heat exchange loop.

[0130] In an exemplary embodiment, taking the first refrigerant circulation heat exchange loop where the first cylinder 300 is located as the heat exchange loop of an air conditioner and the second refrigerant circulation heat exchange loop where the second cylinder 400 is located as the heat exchange loop of a water heater as an example, the double-suction and double-exhaust heat pump system has the best energy efficiency when applied to high-end residential places such as high-class hotels.

[0131] The above is only the exemplary implementation manner of the present invention, and does not thus limit the patent scope of the present invention. All equivalent structural transformations made under the technical concept of the present invention by using the content of the specification and drawings of the present invention, or directly / indirectly applied in other related technical fields are included in the patent protection scope of the present invention.

Claims

1. A compression assembly, applied to a compressor, characterized in that: include: An upper bearing, a first cylinder, a second cylinder and a lower bearing are sequentially arranged; 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 a first side and a second side opposite to each other, 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 is different from the eccentricity of the second eccentric portion; and / or, in the axial extension direction of the crankshaft, the cylinder height of the first cylinder is different from the cylinder height of 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 staggered along the axial direction of the crankshaft.

2. A compression assembly, applied to a compressor, characterized in that: include: An upper bearing, a first cylinder, a second cylinder and a lower bearing are sequentially arranged; 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 a first side and a second side opposite to each other, the first eccentric portion being provided on the first side, and the second eccentric portion being provided on the second side; as well as A balancing structure is provided, wherein the balancing structure is used to ensure that the load borne by the first eccentric part when the compression assembly is in operation is greater than the load borne by the second eccentric part when the compression assembly is in operation, and to allow for fluctuations not greater than the load borne by the second eccentric part when the compression assembly is in operation.

3. The compression assembly according to claim 1 or 2, characterized in that A cylinder height of the first cylinder is greater than a cylinder height of the second cylinder.

4. The compression assembly according to claim 3, characterized in that A ratio of a cylinder height of the first cylinder to a cylinder height of the second cylinder is not less than 1.1 and not more than 1.

4.

5. The compression assembly according to claim 3, characterized in that The eccentricity of the first eccentric portion is greater than the eccentricity of the second eccentric portion.

6. The compression assembly according to claim 5, characterized in that A 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 more than 1.

3.

7. The compression assembly according to claim 5, characterized in that The misalignment angle between the first air inlet and the second air inlet is not greater than 60°.

8. The compression assembly according to claim 5, characterized in that 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 in sequence along the axial direction of the crankshaft.

9. A compressor, characterized in that: Comprising a compression assembly as claimed in any one of claims 1 to 8.

10. The compressor according to claim 9, characterized in that The crankshaft has a first end and a second end opposite to each other along its axial direction, and the first eccentric portion and the second eccentric portion are arranged at the first end; A motor rotor is disposed at the second end of the crankshaft, a first balancing block is disposed at the second side of the crankshaft, and a second balancing block is disposed at the first side of the crankshaft; The ratio of the first balancing mass to the first eccentric portion is not greater than 0.1, and the ratio of the second balancing mass to the second eccentric portion is not greater than 0.

1.

11. A heat pump system, characterized in that: Comprising a compressor as claimed in claim 9 or 10.

12. The heat pump system according to claim 11, characterized in that: The heat pump system comprises a first heat exchange component, a second heat exchange component, a third heat exchange component and a fourth heat exchange component, the first cylinder has a first exhaust port and a first air intake port, the second cylinder has a second exhaust port and a second air intake port; The first exhaust port, the first heat exchange component, the second heat exchange component and the first air intake port are connected in sequence 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 air intake port are connected in sequence to form a second refrigerant circulation heat exchange circuit.

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