Pump components, compressors, air conditioners

Abstract

The present invention provides a pump body assembly, a compressor, and an air conditioner, wherein the pump body assembly includes a first compression part and a second compression part, the first compression part includes a first eccentric part and a first cylinder, the second compression part includes a second eccentric part and a second cylinder, the first eccentric part and the second eccentric part are both on a crankshaft, the first compression part is a variable capacity compression part, the second compression part is a non-variable capacity compression part, the displacement of the first compression part in a non-variable capacity state is V1, and the displacement of the second compression part is V2. According to the present invention, by optimizing the displacement ratio of the first compression part and the second compression part, the pump body assembly can meet the requirement of the smallest possible cooling capacity for single-cylinder operation and the largest possible cooling capacity for dual-cylinder operation, and at the same time, the no-load power consumption of the pump body assembly when the single-cylinder operation is small, thereby improving the energy efficiency when the single-cylinder operation is improved.

Description

Technical Field

[0001] The invention belongs to the technical field of compressor manufacturing, and in particular relates to a pump body assembly, a compressor, and an air conditioner. Background Art

[0002] In actual use, household multi-split units operate below 30% load for 60% of the time, especially when the load rate is below 20%, the operating time accounts for more than 40%. The operating time of a single indoor unit accounts for 60% of the total operating time, and the operating time of two or less indoor units accounts for 87% of the total operating time. Therefore, the minimum load rate of household multi-split units must be at least 5% of the rated cooling capacity to meet the demand range of its use. At present, the minimum cooling capacity of household multi-split units using conventional two-cylinder compressors on the market is more than 10% of the rated cooling capacity, but lower cooling capacity cannot be stably operated and can only be achieved through intermittent operation of the compressor stop-start, which consumes a lot of energy. In order to meet the low cooling capacity requirements of household multi-split units and improve the energy efficiency during low cooling capacity operation, the industry has proposed variable capacity compressors to solve this problem.

[0003] However, the current household multi-split units have put forward more stringent requirements on the cooling capacity range of the compressor, that is, smaller cooling capacity and larger cooling capacity. For the variable capacity compressors with conventional structures, it is impossible to meet the cooling capacity demand range of the household multi-split units by reducing the displacement of a single cylinder. Therefore, in order to meet the small cooling capacity requirements of the household multi-split units as much as possible, the commonly used method is to reduce the operating frequency of a single cylinder. However, the reduction in frequency will increase the difficulty of compressor control and seriously reduce energy efficiency. In order to solve the above problems, the present invention is proposed. Summary of the invention

[0004] Therefore, the present invention provides a pump body assembly, a compressor, and an air conditioner, which can overcome the shortcomings of the related art that in order to meet the small cooling capacity requirements of household multi-split units as much as possible, the single-cylinder operation frequency is reduced, resulting in increased difficulty in compressor control and serious energy efficiency degradation.

[0005] In order to solve the above problems, the present invention provides a pump body assembly, including a first compression part and a second compression part, the first compression part includes a first eccentric part and a first cylinder, the second compression part includes a second eccentric part and a second cylinder, the first eccentric part and the second eccentric part are both on the crankshaft, the first compression part is a variable capacity compression part, the second compression part is a non-variable capacity compression part, the displacement of the first compression part in the non-variable capacity state is V1, and the displacement of the second compression part is V2,

[0006] In some embodiments, the eccentricity of the first eccentric portion is e1, and the eccentricity of the second eccentric portion is e2.

[0007] In some embodiments, a driving motor is connected to the first end of the crankshaft, the second compression part is located at the second end of the crankshaft, and the first compression part is located between the second compression part and the driving motor.

[0008] In some embodiments, the crankshaft has an intermediate shaft section between the first eccentric portion and the second eccentric portion, and an intermediate bearing is mounted on an outer side of the intermediate shaft section.

[0009] In some embodiments, the diameter of the central through hole of the intermediate bearing is D1, and the outer diameter of the second eccentric portion is D3.

[0010] In some embodiments, a conical section and a cylindrical section are included between the intermediate shaft section and the second eccentric portion, and a large-diameter bottom surface of the conical section is located on the intermediate bearing.

[0011] In some embodiments, the intermediate bearing is located between the first cylinder and the second cylinder, and a partition is further disposed between the intermediate bearing and the second cylinder, wherein the partition has a conical through hole matching the conical segment, and the diameter of the small diameter bottom surface of the conical through hole is D2, D 3 ≤D 2 .

[0012] In some embodiments, the diameter of the cylindrical section is d1, the crankshaft has a central oil passage, and in the direction from the first end to the second end of the crankshaft, the central oil passage sequentially includes a first section and a second section located on the second eccentric portion, wherein the flow diameter of the first section is d2, and the flow diameter of the second section is d3, and / or,

[0013] In some embodiments, the axial height of the second eccentric portion is H1, and the axial length of the second section is H, where H

[0014] The present invention also provides a compressor, comprising the above-mentioned pump body assembly.

[0015] The present invention also provides an air conditioner, comprising the above-mentioned compressor.

[0016] The present invention provides a pump body assembly, a compressor, and an air conditioner. By optimizing the design of the displacement ratio between the first compression part and the second compression part, the pump body assembly can meet the requirement of the smallest possible refrigeration capacity for single-cylinder operation and the requirement of the largest possible refrigeration capacity for dual-cylinder operation. At the same time, the no-load power consumption of the pump body assembly when the single-cylinder operation is in operation is small, thereby improving the energy efficiency when the single-cylinder operation is in operation. BRIEF DESCRIPTION OF THE DRAWINGS ​

[0017] Figure 1 A schematic diagram of the internal structure of a pump assembly according to an embodiment of the present invention;

[0018] Figure 2 for Figure 1 A schematic diagram of the local structure of the pump assembly from another perspective;

[0019] Figure 3 for Figure 1 A schematic diagram of the partial structure of the crankshaft;

[0020] Figure 4 It is a schematic diagram of a correlation curve between the displacement ratio of the second compression part to the first compression part and the minimum cooling capacity and the no-load power consumption ratio in the present invention.

[0021] The reference numerals are:

[0022] 11. first eccentric portion; 12. first cylinder; 13. first slide vane; 14. first roller; 21. second eccentric portion; 22. second cylinder; 221. air inlet; 23. second slide vane; 24. second roller; 3. crankshaft; 31. intermediate shaft section; 32. conical section; 33. cylindrical section; 41. intermediate bearing; 411. pin receiving hole; 412. connecting passage; 42. partition; 43. upper flange; 44. lower flange; 51. first section; 52. second section; 61. pin; 62. spring. DETAILED DESCRIPTION

[0023] See also Figures 1 to 4 As shown, according to an embodiment of the present invention, a pump body assembly is provided, including a first compression part and a second compression part, wherein the first compression part includes a first eccentric part 11 and a first cylinder 12, and the second compression part includes a second eccentric part 21 and a second cylinder 22, wherein the first eccentric part 11 and the second eccentric part 21 are both located on a crankshaft 3, and the first compression part is a variable capacity compression part, that is, the first compression part has two modes: a loaded mode (compression) and an unloaded mode (idling), and the second compression part is a non-variable capacity compression part, and the displacement of the first compression part in a non-variable capacity state is V1, and the displacement of the second compression part is V2, In this technical solution, by optimizing the displacement ratio of the first compression part and the second compression part, the pump body assembly can meet the requirement of the smallest possible refrigeration capacity in single-cylinder operation (that is, the second compression part is running alone) and the largest possible refrigeration capacity in double-cylinder operation, and at the same time, the no-load power consumption of the pump body assembly when the single-cylinder operation is small, and the energy efficiency when the single-cylinder operation is improved. It can be understood that in order to meet the large range of refrigeration requirements in household multi-split units, the difference between the displacements of the first compression part and the second compression part should be as large as possible, that is, the displacement of the first compression part should be as large as possible, and the displacement of the second compression part should be as small as possible, so that the minimum refrigeration capacity of the compressor when the single-cylinder operation is reduced and the maximum refrigeration capacity when the double-cylinder operation is increased. However, if the displacement difference between the two is too large, when the single-cylinder operation is in operation, the upper cylinder will generate a large no-load power consumption, reducing the energy efficiency when the single-cylinder operation is reduced. If the displacement difference between the two is too small, it is difficult to widen the refrigeration range of the compressor and cannot meet the use requirements well. The above-mentioned technical solution of the present invention can meet the above-mentioned use requirements.

[0024] It should be noted that by reducing the displacement of a single cylinder, the frequency of the variable displacement compressor's single cylinder operation can be increased, the leakage of a single cylinder can be reduced, and the energy efficiency of a single cylinder operation can be improved. The increase in frequency can avoid the vibration of the compressor when a single cylinder is running, improve the reliability of the compressor, reduce the difficulty of compressor control, and improve the stability of compressor operation.

[0025] It can be understood that a partition 42 is sandwiched between the first eccentric portion 11 and the second eccentric portion 21, and the corresponding sealing distance between the first roller 14, the second roller 24 and the partition 42 reduces the leakage of the refrigerant. Preferably, the eccentricity of the first eccentric portion 11 is e1, and the eccentricity of the second eccentric portion is e2.

[0026] In some embodiments, the first end of the crankshaft 3 is connected to a drive motor (not shown in the figure), the second compression part is located at the second end of the crankshaft 3, and the first compression part is located between the second compression part and the drive motor. Figure 1 In the orientation shown, the first compression portion is above the second compression portion, and due to Therefore, the outer diameter of the corresponding second eccentric portion 21 will be smaller than the outer diameter of the first eccentric portion 11. In this way, the overall size of the crankshaft 3 can be designed as small as possible only at its lower end (free end), ensuring that the crankshaft 3 as a whole has sufficient structural strength.

[0027] In some embodiments, the crankshaft 3 has an intermediate shaft section 31 between the first eccentric portion 11 and the second eccentric portion 21. An intermediate bearing 41 is mounted on the outer side of the intermediate shaft section 31, which is specifically located between the first cylinder 12 and the partition plate 42. The intermediate bearing 41, together with the upper flange 43 and the lower flange 44 at its axial ends, forms a reliable support for the circumferential rotation of the crankshaft 3.

[0028] The diameter of the central through hole of the intermediate bearing 41 is D1, and the outer diameter of the second eccentric portion 21 is D3. In this way, the smooth assembly between the intermediate bearing 41 and the crankshaft 3 can be ensured. In some embodiments, a conical section 32 and a cylindrical section 33 are included between the intermediate shaft section 31 and the second eccentric portion 21, and the large-diameter bottom surface of the conical section 32 is located on the intermediate bearing 41. Through the design of the conical section 32, the outer diameter of the second eccentric portion 21 can be designed to be smaller, without designing the overall diameter to be larger in order to ensure the structural strength of the crankshaft 3.

[0029] The partition plate 42 has a conical through hole matching the conical section 32, and the diameter of the small diameter bottom surface of the conical through hole is D2, D 3 ≤D 2 In this way, the crankshaft 3 and the partition plate 42 can be smoothly assembled while increasing the sealing distance as much as possible to prevent refrigerant leakage.

[0030] In some embodiments, the diameter of the cylindrical section 33 is d1, and the crankshaft 3 has a central oil passage. In the direction from the first end to the second end of the crankshaft 3, the central oil passage sequentially includes a first section 51 and a second section 52 located on the second eccentric portion 21, wherein the flow diameter of the first section 51 is d2, and the flow diameter of the second section 52 is d3. and / or, The structural strength of the connection position between the intermediate shaft section 31 and the second eccentric portion 21 can be ensured. Based on the guarantee of the structural strength, further, the axial height of the second eccentric portion 21 is H1, and the axial length of the second section 52 is H, H

[0031] ​A pin accommodating hole 411 is constructed on the intermediate bearing 41, and a pin assembly is arranged in the pin accommodating hole 411. The pin assembly can lock or unlock the first slide plate 13 in the first compression part. The pin assembly specifically includes a pin 61 and a spring 62, wherein the head of the pin 61 faces the tail of the first slide plate 13, and the spring 62 is located between the tail of the pin 61 and the partition 42. Under the elastic force of the spring 62, the pin 61 has a tendency to move toward one side of the pin 61, and the movement direction of the pin 61 can be controlled and adjusted by connecting control fluids of different pressures between the head and the tail of the pin 61. In some embodiments, the pin accommodating hole 411 is connected to the intake port 221 on the second cylinder 22 through a connecting channel 412.

[0032] Depend on Figure 4 It can be seen that when When cooling, the pump assembly can simultaneously meet the requirements of minimum cooling capacity and minimum no-load power consumption.

[0033] According to an embodiment of the present invention, there is also provided a compressor, comprising the above-mentioned pump body assembly.

[0034] According to an embodiment of the present invention, there is also provided an air conditioner, in particular a household multi-split air conditioner, comprising the above-mentioned compressor.

[0035] It is easy for those skilled in the art to understand that the above-mentioned advantageous methods can be freely combined and superimposed without conflict.

[0036] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention shall be included in the protection scope of the present invention. The above are only preferred embodiments of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present invention, and these improvements and variations should also be regarded as the protection scope of the present invention.

Claims

1. A pump assembly, It is characterized in that The invention comprises a first compression part and a second compression part, wherein the first compression part comprises a first eccentric part (11) and a first cylinder (12), and the second compression part comprises a second eccentric part (21) and a second cylinder (22). The first eccentric part (11) and the second eccentric part (21) are both located on a crankshaft (3). The first compression part is a variable capacity compression part, and the second compression part is a non-variable capacity compression part. The displacement of the first compression part in a non-variable capacity state is V1, and the displacement of the second compression part is V2. The first end of the crankshaft (3) is connected to a drive motor, the second compression part is located at the second end of the crankshaft (3), and the first compression part is located between the second compression part and the drive motor; the crankshaft (3) has an intermediate shaft section (31) located between the first eccentric part (11) and the second eccentric part (21); a conical section (32) and a cylindrical section (33) are included between the intermediate shaft section (31) and the second eccentric part (21), and the large-diameter bottom surface of the conical section (32) is located on the intermediate shaft section (31); an intermediate bearing (41) is sleeved on the outer side of the intermediate shaft section (31), and a pin receiving hole (411) is constructed on the intermediate bearing (41).

2. The pump assembly according to claim 1, It is characterized in that The eccentricity of the first eccentric portion (11) is e1, and the eccentricity of the second eccentric portion is e2.

3. The pump assembly according to claim 1, It is characterized in that The diameter of the central through hole of the intermediate bearing (41) is D1, and the outer diameter of the second eccentric portion (21) is D3.

4. The pump assembly according to claim 1, It is characterized in that The intermediate bearing (41) is located between the first cylinder (12) and the second cylinder (22), and a partition plate (42) is sandwiched between the intermediate bearing (41) and the second cylinder (22), wherein the partition plate (42) has a conical through hole matching the conical section (32), and the diameter of the small diameter bottom surface of the conical through hole is D2, D 3 ≤D 2 .

5. The pump assembly according to claim 4, It is characterized in that The diameter of the cylindrical section (33) is d1, and the crankshaft (3) has a central oil passage. In the direction from the first end to the second end of the crankshaft (3), the central oil passage sequentially includes a first section (51) and a second section (52) located on the second eccentric portion (21), wherein the flow diameter of the first section (51) is d2, and the flow diameter of the second section (52) is d3. and / or, 6. The pump assembly according to claim 5, It is characterized in that The axial height of the second eccentric portion (21) is H1, and the axial length of the second section (52) is H, where H<H1.

7. A compressor, It is characterized in that A pump body assembly comprising any one of claims 1 to 6.

8. An air conditioner, It is characterized in that Comprising the compressor as claimed in claim 7.

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