Compression structure, compressor and air conditioner having the same

Abstract

The present application provides a compression structure, a compressor and an air conditioner having the same, a cylinder and a vane assembly, a vane groove is provided on the cylinder, the vane assembly includes a vane structure and a force-applying structure, the vane structure is movably provided in the vane groove, and the cylinder interior is divided into an intake side and an exhaust side, the vane structure includes a first vane and a second vane spliced ​​to each other; the force-applying structure can apply force to the first vane to drive the first vane and the second vane to move; in the circumferential direction of the cylinder, the force-applying direction of the force-applying structure on the first vane is located on the side where the center of gravity of the first vane is away from the exhaust side, and the head of the second vane is provided with a flexible hole. According to the compression structure, the compressor and the air conditioner having the same of the present application, the wear of the vane and both sides of the vane groove can be effectively solved.

Description

Technical Field

[0001] The present application belongs to the technical field of air conditioners, and in particular relates to a compression structure, a compressor, and an air conditioner having the same. Background Art

[0002] At present, the pump body structure of the traditional rolling rotor compressor is mainly composed of a cylinder, a rolling piston, a crankshaft, a vane, a spring, and bearings assembled at both ends of the cylinder. Under the action of the gas back pressure and the tail spring force, the vane head is in line contact and sealed with the outer surface of the rolling piston. However, when the compressor is running at a low frequency and the suction superheat is insufficient, it is easy for the suction to carry liquid and produce liquid hammer, causing the rolling piston and the vane to separate and the refrigerant to leak from the high-pressure chamber to the low-pressure chamber. The refrigeration capacity of the compressor is attenuated, but when the two are in contact again, a serious collision will occur, which is not conducive to the reliability of the compressor during operation. In the related technology, the hinge pin of the vane head is matched with the hinge groove of the rolling piston, and the vane head and the rolling piston hinge groove surface are contacted and sealed. This structure does not require the provision of a spring and a spring hole at the tail of the vane, which solves the reliability problem caused by the separation of the vane and the rolling piston in the traditional structure.

[0003] However, the pressure on the back of the vane, the extension line of its force line passes through the center of gravity of the vane. Since the vane is placed in the cylinder, the two sides of the vane will be subject to the pressure of the gas refrigerant in the suction chamber and the compression chamber, and the exhaust pressure is greater than the suction pressure. The combined force of the two will cause the vane to tilt at an angle toward the vane groove close to the suction side and contact with both sides of the vane groove to generate contact force, and the line of action of the force is perpendicular to the side of the vane, resulting in more severe wear on the vane and both sides of the vane groove, making the friction power consumption relatively high.

[0004] Therefore, how to provide a compression structure, a compressor and an air conditioner having the same which can effectively solve the wear of the sliding vane and both sides of the sliding vane groove 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 the present application is to provide a compression structure, a compressor and an air conditioner having the same, which can effectively solve the wear of the sliding vane and both sides of the sliding vane groove.

[0006] In order to solve the above problems, the present application provides a compression structure, including:

[0007] A cylinder, wherein a sliding plate groove is arranged on the cylinder;

[0008] The vane assembly includes a vane structure and a force-applying structure. The vane structure can be movably arranged in the vane groove to separate the interior of the cylinder into an intake side and an exhaust side. The vane structure includes a first vane and a second vane spliced ​​to each other. The force-applying structure can apply force to the first vane to drive the first vane and the second vane to move. In the circumferential direction of the cylinder, the force-applying direction of the force-applying structure on the first vane is located on the side where the center of gravity of the first vane is away from the exhaust side. A flexible hole is provided at the head of the second vane.

[0009] Further, the flexible hole penetrates the second sliding plate in the axial direction;

[0010] And / or, the flexible hole is provided at a joint position between the second sliding sheet and the first sliding sheet;

[0011] And / or, the cross-section of the flexible hole is semicircular.

[0012] Furthermore, the first slide vane includes a radial extension portion and a force-bearing portion which are connected to each other; the radial extension portion and the second slide vane are arranged sequentially in the circumferential direction of the cylinder, and the radial extension portion is located on the side of the second slide vane close to the exhaust side; the force-bearing portion is arranged at the end of the second slide vane, the force-bearing portion is located on the outer peripheral side of the second slide vane, and the force-bearing portion forms the slide vane tail portion of the slide vane structure, and the force-applying structure applies force to the force-bearing portion to drive the first slide vane and the second slide vane to move.

[0013] Furthermore, the first sliding piece is an L-shaped structure, the short side of the L-shaped structure forms a force-bearing portion, and the long side of the L-shaped structure is spliced ​​with the second sliding piece.

[0014] Furthermore, the width of the short side of the L-shaped structure is a, the width of the long side of the L-shaped structure is b, and the length of the short side of the L-shaped structure is t, wherein a≥3; and / or 1 / 3≤(b / t)≤2 / 3.

[0015] Furthermore, the head of the first slide and the head of the second slide are assembled to form a slide head, a hinge groove is provided on the cylinder, the slide head is arranged in the hinge groove, and an oil guide channel is provided on the slide structure, and the oil guide channel can guide the lubricating oil into the hinge groove.

[0016] Further, the oil guide channel is provided on the first sliding plate, and the oil guide channel is located between the first sliding plate and the second sliding plate;

[0017] and / or, the oil guide channel penetrates the first sliding vane in the radial direction;

[0018] And / or, the number of the oil guide channels is set to at least one.

[0019] Furthermore, the oil guide channel includes an oil guide groove, and the maximum groove depth of the oil guide groove is e; when the first sliding plate is an L-shaped structure, the width of the long side of the L-shaped structure is b, and the length of the short side of the L-shaped structure is t, 0.1≤(e / (tb))≤0.3.

[0020] According to yet another aspect of the present application, a compressor is provided, comprising a compression structure, wherein the compression structure is the above-mentioned compression structure.

[0021] According to another aspect of the present application, an air conditioner is provided, comprising a compression structure, wherein the compression structure is the above-mentioned compression structure.

[0022] The compression structure, compressor and air conditioner provided by the present application, the vane in the present application is designed as a split structure, the gas back pressure Fb acts on the back of the first vane, but the extension of the line of action of the force passes through the geometric center G1 of the vane structure, that is, the center of gravity of the entire vane structure, and the distance d from the center of gravity G2 of the first vane in the present application is offset, therefore, the gas back pressure Fb will generate a moment that causes the first vane to deflect toward the exhaust side, and then the first vane contacts the second vane so that the entire vane structure deflects together, and this deflection angle will be greatly reduced to θ2 or even completely offset, thereby reducing the contact stress and friction power consumption between the vane and the vane slot, and at the same time reducing the vibration and noise of the compressor pump body. The present application can effectively solve the wear on both sides of the vane and the vane slot. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 A top view of the compression structure of an embodiment of the present application;

[0024] Figure 2 A schematic diagram of the structure of the compression structure of an embodiment of the present application;

[0025] Figure 3 A schematic diagram of the structure of the sliding plate structure of an embodiment of the present application;

[0026] Figure 4 A schematic diagram of the structure of the sliding plate structure of an embodiment of the present application;

[0027] Figure 5 This is a schematic structural diagram of a pump assembly according to an embodiment of the present application;

[0028] Figure 6 A schematic diagram of the force acting on the sliding plate structure of an embodiment of the present application;

[0029] Figure 7 It is a structural schematic diagram of an existing compression structure;

[0030] Figure 8 It is a force diagram of the sliding plate structure in the prior art;

[0031] Fig. 9 A comparison diagram of vibration acceleration between the compressor of the technical solution of the embodiment of the present application and the compressor of the prior art;

[0032] Fig.10This is a comparison chart of energy efficiency between the compressor of the technical solution of the embodiment of the present application and the compressor of the prior art.

[0033] The reference numerals are:

[0034] 1. Crankshaft; 2. Rolling piston; 3. Cylinder; 4. Sliding vane assembly; 5. Sliding vane groove bottom hole; 6. Main bearing; 7a. First sliding vane; 7b. Second sliding vane; 7c. Flexible hole; 8. Auxiliary bearing; 9. Sliding vane groove; 10. Oil guide channel. DETAILED DESCRIPTION

[0035] See also Figure 1-10 As shown, a compression structure includes a cylinder 3 and a vane assembly 4, and a vane groove 9 is provided on the cylinder 3; the vane assembly 4 includes a vane structure and a force-applying structure, the vane structure is movably arranged in the vane groove 9, and the interior of the cylinder 3 is divided into an intake side and an exhaust side, and the vane structure includes a first vane 7a and a second vane 7b spliced ​​to each other; the force-applying structure can apply force to the first vane 7a to drive the first vane 7a and the second vane 7b to move; in the circumferential direction of the cylinder 3, the force-applying direction of the force-applying structure on the first vane 7a is located on the side where the center of gravity of the first vane 7a is away from the exhaust side; the head of the second vane 7b is provided with a flexible hole 7c. The present application solves the problem that the vane is deflected toward the intake side due to the gas force on both sides of the vane, so that the normal contact force between the vane and the vane groove 9 increases sharply, resulting in high friction power consumption of the compressor. Improve the problem of excessive contact stress and excessive friction wear between the hinge pin at the vane head and the hinge groove of the rolling piston 2. The problem that the contact stress between the hinge pin of the vane head and the hinge groove of the rolling piston 2 increases sharply during the process of the rolling piston 2 returning from the highest point to the lowest point due to the existence of the vane deflection angle is solved. In addition, the present application provides a flexible hole 7c on the air intake side of the hinge pin of the vane head, thereby improving the contact stress between the hinge pin of the vane head and the hinge groove of the rolling piston 2 without reducing the strength of the entire vane head, thereby reducing the friction, wear and vibration noise between the two.

[0036] The vane assembly 4 of the present application can generate a torque that causes the vane to deflect toward the exhaust side under the action of gas back pressure, greatly reducing or even offsetting the deflection angle θ of the vane, thereby reducing the contact stress and friction power consumption between the vane and the vane groove 9. The vane assembly 4 reduces the deflection angle of the vane, thereby solving the problem of a sharp increase in contact stress between the hinge pin on the vane head and the hinge groove of the rolling piston 2 during the process of the rolling piston 2 returning from the highest point to the lowest point, thereby improving the friction and wear between the two and improving the reliability of the compressor operation.

[0037] The compression structure of the present application includes components such as a crankshaft 1, a main bearing 6, a cylinder 3, a secondary bearing 8, a rolling piston 2, and a vane assembly 4. The force-applying structure applies force to the vane structure along the radial direction of the cylinder 3 at the tail of the vane structure, and only the first structure applies force, and its force-applying point is located at the center of the entire vane structure in the circumferential direction.

[0038] In the related technical solution, the pressure on the back of the vane is Fb and the extension of its line of action passes through the center of gravity G1 of the vane. Since the vane is placed in the cylinder 3, the two sides of the vane will be subject to the pressure of the gas refrigerant in the suction chamber and the compression chamber, and the exhaust pressure is greater than the suction pressure. The combined force of the two is Fp. The vane will tilt toward the vane slot 9 close to the suction side at an angle θ and contact the two sides of the vane slot 9 to generate contact forces Fn1 and Fn2 respectively, and the line of action of the force is perpendicular to the side of the vane, which leads to more serious wear of the vane and the two sides of the vane slot 9, making the friction power consumption relatively high. The vane slot 9 in the related technology has a bottom hole 5 of the vane slot.

[0039] In the present application, the vane is designed as a split structure, and the gas back pressure Fb acts on the back of the first vane 7a, but the extension of the line of action of the force passes through the geometric center G1 of the vane structure, that is, the center of gravity of the entire vane structure, and the distance d from the center of gravity G2 of the first vane 7a in the present application is offset. Therefore, the gas back pressure Fb will generate a torque that causes the first vane 7a to deflect toward the exhaust side, and then the first vane 7a and the second vane 7b contact to cause the entire vane structure to deflect together, and this deflection angle will be greatly reduced to θ2 or even completely offset, thereby reducing the contact stress and friction power consumption between the vane and the vane groove 9, and reducing the vibration and noise of the compressor. Obviously, in the present application, the vane assembly 4 reduces the deflection angle of the vane, thereby solving the problem of the sharp increase in contact stress between the vane head hinge pin and the rolling piston 2 hinge groove during the process of the rolling piston 2 returning from the highest point to the lowest point, improving the friction and wear between the two, and improving the reliability of the compressor operation. The present application solves the problem that the normal contact force between the sliding plate and the sliding plate groove 9 increases sharply due to the sliding plate being deflected toward the suction side by the gas force on both sides of the sliding plate, resulting in high friction power consumption of the compressor. It also solves the problem that the contact stress between the hinge pin of the sliding plate head and the hinge groove of the rolling piston 2 increases sharply during the process of the rolling piston 2 returning from the highest point to the lowest point due to the existence of the sliding plate deflection angle.

[0040] The present application also discloses some embodiments, in which the flexible hole 7c penetrates the second slide 7b in the axial direction; it can better improve the contact stress between the hinge pin of the slide head and the hinge groove of the rolling piston 2 without reducing the strength of the entire slide head, and reduce the friction, wear and vibration noise between the two.

[0041] The present application also discloses some embodiments, in which the flexible hole 7c is arranged at the joint position between the second sliding sheet 7b and the first sliding sheet 7a.

[0042] The present application also discloses some embodiments, in which the cross section of the flexible hole 7c is semicircular. The flexible hole 7c is opened on the suction side, i.e., the low-pressure side, wherein the cross-sectional shape of the flexible hole 7c is semicircular, and can also be designed into other shapes. According to the literature, the hinge pin of the vane head is in clearance with the hinge groove of the rolling piston 2, and the contact point T is always located on the suction side, that is, the suction side of the vane head is the main force-bearing part, that is, the contact force and friction force here are the largest. Therefore, the present technical solution is to provide a flexible hole 7c that runs through the entire vane on the suction side of the hinge pin of the vane head, without reducing the strength of the entire vane head, to improve the contact stress between the hinge pin of the vane head and the hinge groove of the rolling piston 2, and reduce the friction, wear and vibration noise between the two.

[0043] The present application also discloses some embodiments, wherein the first slide 7a includes a radial extension portion and a force-bearing portion connected to each other; the radial extension portion and the second slide 7b are arranged in sequence in the circumferential direction of the cylinder 3, and the radial extension portion is located on the side of the second slide 7b close to the exhaust side; the force-bearing portion is arranged at the end of the second slide 7b, the force-bearing portion is located on the outer peripheral side of the second slide 7b, and the force-bearing portion forms the slide tail of the slide structure, and the force-applying structure applies force to the force-bearing portion to drive the first slide 7a and the second slide 7b to move. The radial extension portion has the same structure as the second slide 7b and is assembled with each other. Obviously, the center of gravity of the first slide 7a is biased toward the exhaust side of the cylinder 3 relative to the force-applying direction. At this time, the gas back pressure Fb will generate a torque that causes the first slide 7a to deflect toward the exhaust side, and then the first slide 7a and the second slide 7b contact to cause the entire slide assembly 4 to deflect together, and this deflection angle will be greatly reduced to θ2 or even completely offset.

[0044] The present application also discloses some embodiments, the first vane 7a is an L-shaped structure, the short side of the L-shaped structure forms a force-bearing portion, and the long side of the L-shaped structure is spliced ​​with the second vane 7b. In the present application, the vane is designed as a split structure and the cross section of the first vane 7a is L-shaped. The gas back pressure Fb acts on the back of the first vane 7a, but the extension of the line of action of the force passes through the geometric center G1 of the vane assembly 4, that is, the center of gravity of the vane structure, and the distance from the center of gravity G2 of the first vane 7a of the present application is d. Therefore, the gas back pressure Fb will generate a moment that causes the first vane 7a to deflect toward the exhaust side, and then the first vane 7a contacts the second vane 7b to cause the entire vane assembly 4 to deflect together, and this deflection angle will be greatly reduced to θ2 or even completely offset, thereby reducing the contact stress and friction power consumption between the vane and the vane slot 9, and at the same time reducing the pump body vibration and noise of the compressor. In addition, in the present application, the vane assembly 4 reduces the deflection angle of the vane, thereby solving the problem of a sharp increase in contact stress between the hinge pin on the vane head and the hinge groove of the rolling piston 2 during the process of the rolling piston 2 returning from the highest point to the lowest point, thereby improving the friction and wear between the two and improving the reliability of the compressor operation.

[0045] The present application also discloses some embodiments, wherein the width of the short side of the L-shaped structure is a, the width of the long side of the L-shaped structure is b, and the length of the short side of the L-shaped structure is t, wherein a≥3; and / or 1 / 3≤(b / t)≤2 / 3.

[0046] The present application also discloses some embodiments, the head of the first slide 7a and the head of the second slide 7b are assembled to form a slide head, a hinge groove is provided on the cylinder 3, the slide head is arranged in the hinge groove, and an oil guide channel 10 is provided on the slide structure, and the oil guide channel 10 can guide the lubricating oil into the hinge groove. A plurality of oil guide channels 10 are provided on the side of the first slide 7a of the slide assembly 4, and the high-pressure lubricating oil on the back pressure side of the slide guides the refrigeration oil to the hinge groove of the slide head hinge pin and the rolling piston 2, that is, the low-pressure side, through the oil guide channel 10, thereby improving the lubrication state between the two and reducing friction power consumption. The vane assembly 4 is formed by splicing the first vane 7a and the second vane 7b and is arranged in the vane groove 9 of the cylinder 3, and can reciprocate along the vane groove 9; the crankshaft 1 is provided with a long axis, a short axis and an eccentric portion, and the long axis and the short axis are respectively located on both sides of the eccentric portion; the rolling piston 2 is sleeved on the eccentric portion of the crankshaft 1, arranged in the cylinder 3 and hinged with the vane assembly 4, the hinge pin at the head of the vane assembly 4 and the hinge groove of the rolling piston 2 are clearance-matched, and the hinge pin at the head of the vane and the hinge groove of the rolling piston 2 are surface contact seals. The present application can improve the problem of excessive contact stress and excessive friction and wear between the hinge pin at the head of the vane and the hinge groove of the rolling piston 2. A plurality of oil inlet holes and oil outlet holes are provided on the vane assembly 4. The lubricating oil on the back pressure side of the vane column leads the refrigeration oil to the hinge groove between the hinge pin of the vane head and the rolling piston 2 and the upper and lower end surfaces of the vane assembly 4 through the oil inlet hole, thereby improving the lubrication state between the friction pairs and reducing the friction power consumption.

[0047] The present application also discloses some embodiments, in which the oil guide channel 10 is arranged on the first sliding plate 7a, and the oil guide channel 10 is located between the first sliding plate 7a and the second sliding plate 7b, so that the lubricating oil forms an oil film between the first sliding plate 7a and the second sliding plate 7b to prevent the two from separating.

[0048] The present application also discloses some embodiments, in which the oil guide channel 10 penetrates the first sliding vane 7 a in the radial direction.

[0049] The present application also discloses some embodiments, in which the number of oil guide channels 10 is set to at least one. The side of the first slide 7a is provided with a plurality of oil guide grooves evenly distributed along the axial direction, the starting point of the oil guide groove is the back pressure side of the first surface of the first slide 7a, extending along the second surface of the first slide 7a to the third surface of the first slide 7a, and finally reaching the head of the first slide 7a. A plurality of oil guide channels 10 are provided on the side of the first slide 7a, and the lubricating oil on the back pressure side of the slide leads the refrigeration oil to the hinge pin of the slide head and the hinge groove of the rolling piston 2 through the oil guide channel 10, thereby improving the lubrication state between the two and reducing the friction power consumption.

[0050] The present application also discloses some embodiments, the oil guide channel 10 includes an oil guide groove, the maximum groove depth of the oil guide groove is e; when the first slide 7a is an L-shaped structure, the width of the long side of the L-shaped structure is b, and the length of the short side of the L-shaped structure is t, 0.1≤(e / (tb))≤0.3. The number and total flow area of ​​the oil guide channels 10 need to be designed accordingly according to the oil supply required by the articulated pin and the articulated groove of the rolling piston 2 in the actual operating conditions of the compressor. In addition, considering the structural strength requirements of the slide, the maximum depth of the oil groove should be numerically limited in combination with the cross-sectional dimensions of the slide.

[0051] The comparison chart of the vibration acceleration and energy efficiency of the compressor of the present application and the compressor of the prior art shows that the vibration acceleration of the compressor of the present application is significantly lower than that of the compressor of the prior art and is reduced by an average of 5m / s2. On the other hand, compared with the prior art, the energy efficiency of the whole machine is improved by about 5% due to the reduction of the friction power consumption of the pump body in the present technology.

[0052] According to an embodiment of the present application, a compressor is provided, including a compression structure, the compression structure being the above-mentioned compression structure. The compressor is a rotary compressor, and may also be a rotary fluid machine with a similar structure, such as a rotary expander, a vane compressor, a vane expander, and the like.

[0053] According to an embodiment of the present application, an air conditioner is provided, comprising a compression structure, wherein the compression structure is the above-mentioned compression structure.

[0054] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0055] The above are only 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 principles of the present application shall be included in the protection scope of the present application. The above are only preferred implementations of the present application. 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 application, and these improvements and variations should also be regarded as the protection scope of the present application.

Claims

1. A compression structure, It is characterized in that include: A cylinder (3), wherein a slide plate groove (9) is provided on the cylinder (3); A vane assembly (4), the vane assembly (4) comprising a vane structure and a force-applying structure, the vane structure being movably arranged in the vane groove (9) to separate the interior of the cylinder (3) into an intake side and an exhaust side, the vane structure comprising a first vane (7a) and a second vane (7b) spliced ​​to each other; the force-applying structure being capable of applying force to the first vane (7a) to drive the first vane (7a) and the second vane (7b) to move; in the circumferential direction of the cylinder (3), the force-applying direction of the force-applying structure on the first vane (7a) is located on a side of the center of gravity of the first vane (7a) away from the exhaust side; a flexible hole (7c) is provided at the head of the second vane (7b); The vane assembly (4) can generate a moment causing the vane to deflect toward the exhaust side under the action of gas back pressure.

2. The compression structure according to claim 1, It is characterized in that The flexible hole (7c) penetrates the second sliding sheet (7b) in the axial direction; And / or, the flexible hole (7c) is arranged at a joint position between the second sliding sheet (7b) and the first sliding sheet (7a); And / or, the cross section of the flexible hole (7c) is semicircular.

3. The compression structure according to claim 1, It is characterized in that The first slide vane (7a) includes a radial extension portion and a force-bearing portion which are interconnected; the radial extension portion and the second slide vane (7b) are arranged in sequence in the circumferential direction of the cylinder (3), and the radial extension portion is located on the side of the second slide vane (7b) close to the exhaust side; the force-bearing portion is arranged at the end of the second slide vane (7b), the force-bearing portion is located on the outer peripheral side of the second slide vane (7b), and the force-bearing portion forms the slide vane tail of the slide vane structure, and the force-applying structure applies force to the force-bearing portion to drive the first slide vane (7a) and the second slide vane (7b) to move.

4. The compression structure according to claim 3, It is characterized in that The first sliding piece (7a) is an L-shaped structure, the short side of the L-shaped structure forms the force-bearing portion, and the long side of the L-shaped structure is spliced ​​with the second sliding piece (7b).

5. The compression structure according to claim 4, It is characterized in that The width of the long side of the L-shaped structure is b, the length of the short side of the L-shaped structure is t, and 1 / 3≤(b / t)≤2 / 3.

6. The compression structure according to claim 1, It is characterized in that The head of the first slide (7a) and the head of the second slide (7b) are assembled to form a slide head. The cylinder (3) is provided with a hinge groove, and the slide head is arranged in the hinge groove. The slide structure is provided with an oil guide channel (10), and the oil guide channel (10) can guide lubricating oil into the hinge groove.

7. The compression structure according to claim 6, It is characterized in that The oil guide channel (10) is arranged on the first sliding plate (7a), and the oil guide channel (10) is located between the first sliding plate (7a) and the second sliding plate (7b); And / or, the oil guide channel (10) penetrates the first sliding vane (7a) in the radial direction; And / or, the number of the oil guide channel (10) is set to at least one.

8. The compression structure according to any one of claims 1 to 7, It is characterized in that The oil guide channel (10) comprises an oil guide groove, the maximum groove depth of the oil guide groove is e; when the first sliding plate (7a) is an L-shaped structure, the width of the long side of the L-shaped structure is b, and the length of the short side of the L-shaped structure is t, 0.1≤(e / (tb))≤0.

3.

9. A compressor comprising a compression structure, It is characterized in that The compression structure is the compression structure according to any one of claims 1 to 8.

10. An air conditioner comprising a compression structure, It is characterized in that The compression structure is the compression structure according to any one of claims 1 to 8.

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