Compressor and air conditioner unit having the same

Abstract

The present application provides a compressor and an air-conditioning unit having the same, including a first cylinder assembly, a second cylinder assembly and a partition. The first cylinder assembly includes a fixed cylinder; the displacement of the fixed cylinder is V1; the second cylinder assembly includes a variable-displacement cylinder and a second roller, and the second roller is rotatably disposed in the variable-displacement cylinder; the displacement of the variable-displacement cylinder is V2; the partition is disposed between the first cylinder assembly and the second cylinder assembly, and the minimum sealing distance between the partition and the second roller is Lmin; wherein, V2 = V1; 2 mm < Lmin < 4 mm. According to the compressor and the air-conditioning unit having the same of the present application, the no-load power consumption of the variable-displacement cylinder can be reduced, and gas leakage can be reduced.

Description

Technical Field

[0001] This application belongs to the technical field of air-conditioning units, and particularly relates to a compressor and an air-conditioning unit having the same. Background Art

[0002] At present, most household multi-connected units operate in a low-load range for most of the time, and the energy efficiency level of the compressor in this range directly determines the energy efficiency of the household multi-connected unit. In order to improve the energy efficiency level in this range, variable displacement compressors have been developed in the industry. In the prior art, a variable displacement compressor structure and a single / double cylinder switching principle are adopted. At low load, the variable displacement compressor operates in a single-cylinder mode, and at high load, the variable displacement compressor operates in a double-cylinder mode. In this way, the energy efficiency of the household multi-connected unit at low load has been greatly improved. Therefore, the energy efficiency of the single cylinder of the variable displacement compressor is crucial for the overall energy efficiency of the variable displacement compressor. During the design process of the variable displacement compressor, in order to ensure the energy efficiency of the single cylinder of the variable displacement compressor, generally, the conventional cylinder adopts a flattened design idea, which can ensure the optimal design of the conventional cylinder. At the same time, in order to ensure the stable operation of the variable displacement compressor and reduce vibration and noise, the variable displacement compressor adopts an equal displacement design for the upper and lower cylinders during design.

[0003] However, due to the limited installation space on the unit, higher requirements are imposed on the shell diameter of the variable displacement compressor. When the variable displacement compressor is designed with a small shell diameter and a large displacement, the conventional cylinder can be designed according to the conventional compressor to maximize the displacement. However, for the variable displacement cylinder, a certain space is required to arrange the switching mechanism. Therefore, it is necessary to reduce the cylinder diameter and eccentricity of the variable displacement cylinder. Therefore, in order to ensure that the displacements of the conventional cylinder and the variable displacement cylinder are the same, only the cylinder height can be increased. When the variable displacement compressor operates in a single-cylinder mode, the variable displacement cylinder is in a low-pressure and no-load state, and the high-pressure gas will leak into the variable displacement cylinder through the gap between the partition plate and the roller, affecting the energy efficiency of the single cylinder of the variable displacement compressor. Moreover, since the variable displacement cylinder is in a no-load state, useless no-load power consumption will be generated. Therefore, to improve the energy efficiency of the single cylinder of the variable displacement compressor, mainly the sealing distance between the partition plate and the roller is increased and the no-load power consumption is reduced. However, the increase in cylinder height will increase the no-load power consumption during the single-cylinder operation of the variable displacement compressor and affect the energy efficiency of the single cylinder.

[0004] Therefore, how to provide a compressor and an air-conditioning unit having the same that can reduce the no-load power consumption of the variable displacement cylinder and reduce gas leakage has become an urgent problem to be solved by those skilled in the art. Summary of the Invention

[0005] Therefore, the technical problem to be solved by this application is to provide a compressor and an air-conditioning unit having the same that can reduce the no-load power consumption of the variable displacement cylinder and reduce gas leakage.

[0006] To solve the above problems, this application provides a compressor, including:

[0007] The first cylinder assembly, the first cylinder assembly includes a fixed cylinder; the displacement of the fixed cylinder is V1;

[0008] The second cylinder assembly, the second cylinder assembly includes a variable displacement cylinder and a second roller, the second roller is rotatably arranged in the variable displacement cylinder; the displacement of the variable displacement cylinder is V2;

[0009] And a partition portion, the partition portion is arranged between the first cylinder assembly and the second cylinder assembly, and the minimum sealing distance between the partition portion and the second roller is Lmin; wherein, V2 = V1; 2mm < Lmin < 4mm.

[0010] Further, the compressor further includes a crankshaft, the crankshaft includes a first eccentric portion, a second eccentric portion, a long shaft and a short shaft, the first eccentric portion and the second eccentric portion are both arranged between the long shaft and the short shaft, the first cylinder assembly is arranged on the first eccentric portion, the second cylinder assembly is arranged on the second eccentric portion, the inner diameter of the long shaft is d1, the inner diameter of the short shaft is d2, wherein, d1 = d2.

[0011] Further, the inner diameter of the variable displacement cylinder is D2, the inner diameter of the fixed cylinder is D1; the eccentricity of the first eccentric portion is e1, the eccentricity of the second eccentric portion is e2; wherein, D1 > D2; and / or, e1 > e2.

[0012] Further, Lmin = (D2 - d2 - 6e2) / 2.

[0013] Further, the height of the fixed cylinder is H3, the height of the variable displacement cylinder is H4; wherein, H3 < H4; and / or,

[0014] Further, D2 = V2 / πH4e2 + e2 = H3e1(D1 - e1) / H4e2 + e2.

[0015] Further, the height of the first eccentric portion is H1, the height of the second eccentric portion is H2, wherein H1 < H2 < 1.5H1.

[0016] Further, the partition portion has a mounting hole, the mounting hole is used for mounting on the crankshaft, and the aperture of the mounting hole is D0; the inner diameter of the first eccentric portion is D3, the inner diameter of the second eccentric portion is D4; wherein, D0 > D4; and / or, D3 > D4.

[0017] Further, the first cylinder assembly further includes a first roller disposed in the fixed cylinder, and a first sliding vane groove is provided on the fixed cylinder; the gap between the first roller and the fixed cylinder is δfixed; a second sliding vane groove is provided on the variable displacement cylinder; the gap between the second roller and the variable displacement cylinder is δvariable; when the first roller rotates to a fixed position on the inner wall of the fixed cylinder, the central angle between the fixed position and the first sliding vane groove is a fixed angle; when the second roller rotates to a variable displacement position on the inner wall of the variable displacement cylinder, the central angle between the variable displacement position and the second sliding vane groove is a variable displacement angle; when the fixed angle is equal to the variable displacement angle, δfixed < δvariable.

[0018] Further, the fixed angle includes a first fixed angle α1, and the variable displacement angle includes a first variable displacement angle α5; wherein, 100° ≤ α1 = α5 ≤ 120°; δfixed < δvariable < 1.5δfixed.

[0019] According to another aspect of the present application, an air conditioner unit is provided, including a compressor, and the compressor is the compressor described above.

[0020] The compressor provided by the present application and the air conditioner unit having the same. The present application can reduce the no-load power consumption of the variable displacement cylinder and can reduce gas leakage. Description of the Drawings

[0021] Figure 1 It is a schematic structural diagram of the compressor according to the embodiment of the present application;

[0022] Figure 2 It is a schematic structural diagram of the second cylinder assembly according to the embodiment of the present application;

[0023] Figure 3 It is a schematic structural diagram of the crankshaft according to the embodiment of the present application;

[0024] Figure 4 It is a schematic installation structure diagram of the compressor according to the embodiment of the present application;

[0025] Figure 5 It is a schematic cooperation diagram of the fixed cylinder and the first roller according to the embodiment of the present application;

[0026] Figure 6 It is a schematic cooperation diagram of the variable displacement cylinder and the second roller according to the embodiment of the present application;

[0027] Figure 7 It is a schematic sealing structure diagram of the partition part and the second roller according to the embodiment of the present application;

[0028] Figure 8 It is a relationship diagram of the power consumption and leakage of the variable displacement cylinder according to the embodiment of the present application and L min of the relationship diagram.

[0029] The reference numerals are shown as:

[0030] 1. First cylinder assembly; 11. Fixed cylinder; 12. First roller; 13. First sliding vane groove; 2. Second cylinder assembly; 21. Variable displacement cylinder; 22. Second roller; 23. Second sliding vane; 24. Second sliding vane groove; 3. Partition; 4. Crankshaft; 41. Long shaft; 42. Short shaft; 43. First eccentric part; 44. Second eccentric part; 5. Lower flange; 61. Pin; 62. Pin spring. Detailed implementation mode

[0031] Refer to in combination Figure 1-8 As shown in the figure, a compressor includes a first cylinder assembly 1, a second cylinder assembly 2 and a partition 3. The first cylinder assembly 1 includes a fixed cylinder 11; the displacement of the fixed cylinder 11 is V1; the second cylinder assembly 2 includes a variable displacement cylinder 21 and a second roller 22, and the second roller 22 is rotatably arranged in the variable displacement cylinder 21; the displacement of the variable displacement cylinder 21 is V2; the partition 3 is arranged between the first cylinder assembly 1 and the second cylinder assembly 2, and the minimum sealing distance between the partition 3 and the second roller 22 is Lmin; wherein, V2 = V1; 2mm < Lmin < 4mm. The compressor of the present application is a variable displacement compressor. When the variable displacement compressor has a small shell diameter and a large displacement design, the inner diameter of the variable displacement cylinder 21 decreases. To ensure that the displacement of the upper variable displacement cylinder 21 is equal, it is necessary to increase the cylinder height of the variable displacement cylinder 21. When the cylinder diameter decreases, the sealing distance between the roller and the partition can be increased. However, when the cylinder height increases, it will cause an increase in no-load power consumption during single-cylinder operation. Through reasonable design of the pump body structure, the present application realizes an increase in the sealing distance between the partition and the roller without significantly increasing the power consumption, reduces leakage, and improves energy efficiency. By increasing the clearance fit clearance between the variable displacement cylinder 21 and the roller, the no-load power consumption of the variable displacement cylinder 21 during single-cylinder operation is reduced, and the energy efficiency of the variable displacement compressor during single-cylinder operation is improved. The minimum sealing distance Lmin between the partition 3 and the second roller 22 refers to the minimum distance between the outer circle of the roller of the second roller and the central hole of the partition.

[0032] The present application also discloses some embodiments. The compressor further includes a crankshaft 4, which includes a first eccentric portion 43, a second eccentric portion 44, a long shaft 41 and a short shaft 42. The first eccentric portion 43 and the second eccentric portion 44 are both disposed between the long shaft 41 and the short shaft 42. The first cylinder assembly 1 is disposed on the first eccentric portion 43, and the second cylinder assembly 2 is disposed on the second eccentric portion 44. The inner diameter of the long shaft 41 is d1, and the inner diameter of the short shaft 42 is d2, where d1 = d2. The variable displacement compressor mainly consists of components such as the crankshaft 4, the first roller 12, the fixed cylinder 11, the partition portion 3, the second roller 22, the variable displacement cylinder 21, the second flange, the pin spring 62, the pin 61, and the second sliding vane 23. When the pin 61 locks the second sliding vane 23, the variable displacement compressor operates with a single cylinder, and the variable displacement cylinder 21 does not compress the gas. At this time, the variable displacement cylinder 21 is in a low-pressure no-load state. When the pin 61 disengages from the second sliding vane 23 and the second sliding vane 23 contacts the second roller 22, the variable displacement compressor operates with two cylinders. When the variable displacement compressor operates with a single cylinder, high-pressure gas leaks to the variable displacement cylinder 21. At the same time, the no-load of the variable displacement cylinder 21 will generate a certain no-load power consumption. The displacement of the fixed cylinder 11 is equivalent to that of the variable displacement cylinder 21, and the diameter d1 of the long shaft 41 of the crankshaft 4 is equivalent to the diameter d2 of the short shaft 42.

[0033] The present application also discloses some embodiments. The inner diameter of the variable displacement cylinder 21 is D2, and the inner diameter of the fixed cylinder 11 is D1; the eccentricity of the first eccentric portion 43 is e1, and the eccentricity of the second eccentric portion 44 is e2; where D1 > D2; and / or, e1 > e2.

[0034] The present application also discloses some embodiments, where Lmin = (D2 - d2 - 6e2) / 2.

[0035] According to the formula: Although the inner diameter D2 of the variable displacement cylinder 21 decreases, Lmin, that is, the minimum sealing distance between the partition portion 3 and the second roller 22, is more susceptible to the influence of the eccentricity. Therefore, the decrease in the eccentricity will cause an increase in Lmin. And when the eccentricity decreases, according to the formula When the eccentricity decreases, the cylinder height increases. According to the theoretical leakage formula, the theoretical leakage amount of the hollowed-out part is:

[0036]

[0037] The hollowed-out part refers to the position between the outer circle of the second roller 22 and the central hole of the partition portion 3, that is, Figure 7 the position corresponding to the wider shaded area in Figure 7At the corresponding positions of the denser shadows. There are also hollow parts and annular parts between the variable displacement cylinder 21 and the partition part 3 in the static state. The overall contact area is the sum of the two, but the positions of the hollow parts and the annular parts will change with the rotation of the roller.

[0038] Theoretical leakage of the annular part:

[0039] p d : Exhaust pressure; p s : Suction pressure;: p s Axial clearance between the roller and the partition, R: Outer radius of the roller, R1: Inner radius of the roller.

[0040] According to the above formula, it can be known that the leakage of the hollow part is inversely proportional to the partition seal distance Lα. When Lα increases, the leakage decreases.

[0041] Viscous friction torque between the outer circle of the roller and the inner wall of the cylinder:

[0042] In the formula, αF is the oil film arc angle; δ is the clearance between the outer circle of the roller and the inner wall of the cylinder, and R2 is the inner radius of the cylinder. According to the formula, it can be known that when the inner diameter of the cylinder decreases, the friction torque decreases. However, when the inner diameter of the cylinder decreases, as described above, when the cylinder diameter decreases, the cylinder height increases, which will increase the friction torque. And according to the formula, the influence of the cylinder height change on the friction torque is greater than the influence of the cylinder diameter change on the friction torque. Therefore, in a variable displacement compressor, when the cylinder height increases, the friction power consumption will increase. When the shortest seal distance between the partition part 3 and the second roller 22 satisfies: 2 < L min <4mm; It can increase the seal distance between the partition part 3 and the second roller 22 without significantly increasing the friction power consumption.

[0043] Some embodiments of the present application are also disclosed. The height of the fixed cylinder is H3, and the height of the variable displacement cylinder is H4; wherein, H3 < H4; and / or, When implementing the design of a variable displacement compressor with a small shell diameter and a large displacement, due to the existence of the variable displacement mechanism, it is necessary to reduce the inner diameter of the variable displacement cylinder 21 and the eccentricity of the eccentric part of the corresponding crankshaft 4. However, in order to facilitate the control of the compressor and reduce noise, it is necessary to ensure that the displacements of the fixed cylinder 11 and the variable displacement cylinder 21 are equal. At this time, only the cylinder height of the variable displacement cylinder 21 can be increased.

[0044] Some embodiments of the present application are also disclosed. D2 = V2 / πH4e2 + e2 = H3e1(D1 - e1) / H4e2 + e2. Through the above structural parameter design, the seal distance between the partition part 3 and the second roller 22 can be increased, the leakage of high-pressure gas into the variable displacement cylinder 21 can be reduced, and at the same time, the friction power consumption between the partition part 3 and the second roller 22 will not increase significantly, thereby achieving the effect of improving energy efficiency.

[0045] The present application also discloses some embodiments. The height of the first eccentric part is H1, and the height of the second eccentric part is H2, where H1 < H2 < 1.5H1. The size of the effective width of the crankshaft affects the frictional losses between the crankshaft and the roller and between the sliding vane and the roller. When the effective width is designed to be larger, the friction between the crankshaft and the roller is reduced, and the friction between the sliding vane and the roller is increased. Therefore, making the crankshaft eccentric part corresponding to the variable displacement cylinder 21 of the variable displacement compressor larger can reduce the no-load power consumption during single-cylinder operation. However, if it is too large, the frictional power consumption between the sliding vane and the roller during double-cylinder operation will increase significantly, reducing the energy efficiency during double-cylinder operation.

[0046] The present application also discloses some embodiments. The separating part has a mounting hole for mounting on the crankshaft, and the aperture of the mounting hole is D0; the inner diameter of the first eccentric part is D3, and the inner diameter of the second eccentric part is D4; wherein, D0 > D4; and / or, D3 > D4. The lower concentricity method can be adopted to ensure smooth assembly.

[0047] The present application also discloses some embodiments. The first cylinder assembly 1 further includes a first roller 12 disposed in the fixed cylinder 11, and a first sliding vane groove 13 is provided on the fixed cylinder 11; the gap between the first roller 12 and the fixed cylinder 11 is δfix; a second sliding vane groove 24 is provided on the variable displacement cylinder 21; the gap between the second roller 22 and the variable displacement cylinder 21 is δvar; when the first roller 12 rotates to a fixed position on the inner wall of the fixed cylinder 11, the central angle between the fixed position and the first sliding vane groove 13 is the fixed angle; when the second roller 22 rotates to a variable displacement position on the inner wall of the variable displacement cylinder 21, the central angle between the variable displacement position and the second sliding vane groove 24 is the variable displacement angle; when the fixed angle is equal to the variable displacement angle, δfix < δvar.

[0048] The present application also discloses some embodiments. The fixed angle includes a first fixed angle α1, and the variable displacement angle includes a first variable displacement angle α5; wherein, 100° ≤ α1 = α5 ≤ 120°; δfix < δvar < 1.5δfix. α1 + α2 = 180°; 10° ≤ α3 = α4 ≤ 20°. In the present application, the fixed angle and the variable displacement angle are respectively referenced to the first sliding vane groove 13 and the second sliding vane groove 24. Rotating from the sliding vane groove towards the exhaust port, if the exhaust port is on the right side of the sliding vane groove, it is clockwise, and if the exhaust port is on the left side of the sliding vane groove, it is counterclockwise. Only when the roller runs to the α1 angle, a smaller numerical range requirement is made for the gap between the solid cylinder and the roller, and at the same time, the gap between the variable displacement cylinder and the roller should not be too large. Therefore, it is necessary to limit the maximum gap between the variable displacement cylinder and the roller, and only the remaining angles need to satisfy that the gap between the fixed cylinder and the roller is less than that between the variable displacement cylinder. For example, α2 < α6; α3 < α7; α4 < α8.

[0049] When operating with a single cylinder, it is possible to further reduce the no-load power consumption of the variable-displacement cylinder 21. According to the frictional torque formula, increasing the clearance between the outer circle of the roller and the inner wall of the cylinder can effectively reduce the frictional torque between the roller and the cylinder. Therefore, in this application, the radial mating clearance between the variable-displacement cylinder 21 and the second roller 22 is increased to reduce the frictional power consumption. However, when operating with two cylinders, if the mating clearance between the variable-displacement cylinder 21 and the second roller 22 is too large, it will increase the internal leakage of the variable-displacement cylinder 21 during two-cylinder operation and reduce the energy efficiency of the two cylinders. Therefore, this application can reduce the no-load power consumption during single-cylinder operation and will not significantly increase the internal leakage of the variable-displacement cylinder 21 during two-cylinder operation.

[0050] According to an embodiment of the present application, an air-conditioning unit is provided, including a compressor, and the compressor is the compressor described above.

[0051] It is easily understood by those skilled in the art that, on the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0052] The above are only the preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present application shall be included in the protection scope of the present application. The above is only the preferred implementation manner of the present application. It should be noted that for those of ordinary skill in the art, without departing from the technical principle of the present application, several improvements and modifications can still be made, and these improvements and modifications should also be regarded as the protection scope of the present application.

Claims

1. A compressor, the compressor being a variable displacement compressor, characterized in that, Comprising: A first cylinder assembly (1), the first cylinder assembly (1) includes a fixed cylinder (11), and the displacement of the fixed cylinder (11) is V1; A second cylinder assembly (2), the second cylinder assembly (2) includes a variable-displacement cylinder (21) and a second roller (22), and the second roller (22) is rotatably arranged in the variable-displacement cylinder (21); the displacement of the variable-displacement cylinder (21) is V2; And a partition (3), the partition (3) is arranged between the first cylinder assembly (1) and the second cylinder assembly (2), and the minimum sealing distance between the partition (3) and the second roller (22) is Lmin; wherein, V2 = V1; 2mm < Lmin < 4mm; The first cylinder assembly (1) further includes a first roller (12) arranged in the fixed cylinder (11), and a first sliding vane groove (13) is arranged on the fixed cylinder (11); the gap between the first roller (12) and the fixed cylinder (11) is δsolid; a second sliding vane groove (24) is arranged on the variable-displacement cylinder (21); the gap between the second roller (22) and the variable-displacement cylinder (21) is δvariable; when the first roller (12) rotates to a fixed position on the inner wall of the fixed cylinder (11), the central angle between the fixed position and the first sliding vane groove (13) is a fixed angle; when the second roller (22) rotates to a variable-displacement position on the inner wall of the variable-displacement cylinder (21), the central angle between the variable-displacement position and the second sliding vane groove (24) is a variable-displacement angle; when the fixed angle is equal to the variable-displacement angle, δsolid < δvariable; the fixed angle includes a first fixed angle α1, and the variable-displacement angle includes a first variable-displacement angle α5; wherein, 100° ≤ α1 = α5 ≤ 120°; δsolid < δvariable < 1.5δsolid.

2. The compressor according to claim 1, characterized in that, The compressor further includes a crankshaft (4), the crankshaft (4) includes a first eccentric portion (43), a second eccentric portion (44), a long shaft (41) and a short shaft (42), both the first eccentric portion (43) and the second eccentric portion (44) are arranged between the long shaft (41) and the short shaft (42), the first cylinder assembly (1) is arranged on the first eccentric portion (43), the second cylinder assembly (2) is arranged on the second eccentric portion (44), the inner diameter of the long shaft (41) is d1, and the inner diameter of the short shaft (42) is d2, wherein, d1 = d2.

3. The compressor according to claim 2, wherein, The inner diameter of the variable-displacement cylinder (21) is D2, and the inner diameter of the fixed cylinder (11) is D1; the eccentricity of the first eccentric portion (43) is e1, and the eccentricity of the second eccentric portion (44) is e2; wherein, D1 > D2; and / or, e1 > e2.

4. The compressor according to claim 3, characterized in that, Lmin = (D2 - d2 - 6e2) / 2.

5. The compressor according to claim 3, wherein The height of the fixed cylinder (11) is H3, and the height of the variable-displacement cylinder (21) is H4; wherein, H3 < H4; and / or, 6. The compressor according to claim 5, wherein D2 = V2 / (πH4e2) + e2 = H3e1(D1 - e1) / (H4e2) + e2。 7. The compressor according to claim 2, characterized in that, The height of the first eccentric part (43) is H1, and the height of the second eccentric part (44) is H2, where H1 < H2 < 1.5H1.

8. The compressor according to claim 2, wherein The partition part (3) has a mounting hole for mounting the crankshaft (4), and the aperture of the mounting hole is D0; the inner diameter of the first eccentric part (43) is D3, and the inner diameter of the second eccentric part (44) is D4; wherein, D0 > D4; and / or, D3 > D4.

9. An air conditioning unit, comprising a compressor, characterized in that, The compressor is the compressor according to any one of claims 1 - 8.

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