Compressor and refrigeration equipment
By setting up a boost structure at the upper end of the rotor to increase the negative pressure near the upper balance block, the problem of refrigerant countercurrent in the rotor compressor is solved, and the effect of reducing refrigerant refrigerant refrigerant refrigerant refrigerant, reducing influx and improving oil level is achieved.
Patent Information
- Application Number
- CN202422085255.4
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-08-26
- Publication Date
- 2025-06-27
- Estimated Expiration
- 2034-08-26
AI Technical Summary
Existing rotor compressors have problems with refrigerant countercurrent, resulting in increased risk of additional inflow and oil level.
A booster structure is provided at the upper end of the rotor, including an annular projection and an end plate, to increase the negative pressure near the upper balance block, thereby reducing refrigerant backflow and avoiding refrigerant backflow.
By increasing the negative pressure, the refrigerant reflux is reduced, the inflow is reduced, the oil level is improved, and the oil discharge rate of the compressor is reduced.
Smart Images
Figure CN223035254U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of compressors, and particularly to a compressor and a refrigeration device. Background Art
[0002] Rotary compressors are widely used due to their high efficiency, compact structure, small size and light weight, for example, inside household air conditioners. The rotor assembly is an important part of a rotary compressor. The traditional rotor assembly has two balance blocks of unequal sizes respectively placed at both ends of the rotor core to balance the unbalanced force caused by the eccentricity of the crankshaft.
[0003] In order to balance the unbalanced force caused by the eccentricity of the crankshaft, the mass and volume of the balance block on the side of the rotor core close to the eccentric shaft of the crankshaft are both larger than those of the balance block on the side far from the eccentric shaft of the crankshaft, resulting in a negative pressure formed by the balance block on the side close to the eccentric shaft being greater than that of the balance block on the side far from the eccentric shaft, forming a reverse flow of refrigerant, increasing the additional input force and the risk of oil liquid level. Summary of the Utility Model
[0004] The main purpose of the utility model is to propose a compressor and a refrigeration device, aiming to solve the problem of reverse flow of refrigerant existing in the existing rotary compressor.
[0005] To achieve the above purpose, the compressor proposed by the utility model includes:
[0006] A housing;
[0007] A motor, arranged inside the housing, the motor includes a rotor, and the rotor is provided with an installation hole for the crankshaft to pass through and a flow hole located outside the installation hole; and,
[0008] A balance structure, including an upper balance block eccentrically arranged at the upper end of the rotor, and the balance block is arranged outside the flow hole;
[0009] Wherein, a pressurizing structure concentric with the installation hole is further arranged at the upper end of the rotor.
[0010] In an embodiment, the pressurizing structure includes a first end plate located above the rotor and spaced from the rotor.
[0011] In an embodiment, the outer contour of the first end plate is set to be circular.
[0012] In an embodiment, the pressurizing structure further includes an annular convex portion arranged at the upper end of the rotor, and the annular convex portion is arranged at a position between the installation hole and the flow hole.
[0013] In one embodiment, the supercharging structure further includes a second end plate, the second end plate is mounted on the upper end surface of the rotor, and the second end plate is provided with a through hole corresponding to the through hole and a center hole corresponding to the mounting hole;
[0014] The central hole is configured as a flanged hole, and the hole wall of the flanged hole forms the annular convex portion.
[0015] In one embodiment, the supercharging structure further includes the first end plate disposed on a side of the annular protrusion away from the rotor, and the upper balancing block is disposed between the first end plate and the second end plate.
[0016] In one embodiment, the distance between the first end plate and the second end plate is h, the height of the annular protrusion is d, and d>h-2mm.
[0017] In one embodiment, the inner diameter of the annular protrusion is r, and a through hole corresponding to the flanging hole is formed on the first end plate, and the radius of the through hole is R, where Rr≤2 mm.
[0018] In one embodiment, the balancing structure further includes a lower balancing block disposed at the lower end of the rotor, and the lower balancing block is disposed offset from the center of the rotor.
[0019] In one embodiment, the volume of the lower balancing weight is set to be larger than the volume of the upper balancing weight.
[0020] In one embodiment, the compressor comprises a carbon dioxide compressor.
[0021] The utility model also provides a refrigeration device, the refrigeration device comprises a compressor, the compressor comprises:
[0022] case;
[0023] A motor is disposed in the housing, the motor comprising a rotor, the rotor being provided with a mounting hole for a crankshaft to pass through, and a flow hole located outside the mounting hole; and,
[0024] A balancing structure, comprising an upper balancing block eccentrically arranged at the upper end of the rotor, wherein the balancing block is arranged at the periphery of the through hole;
[0025] Wherein, the upper end of the rotor is also provided with a boost structure which is arranged concentrically with the mounting hole.
[0026] In the technical solution of the present utility model, a pressurization structure concentric with the mounting hole is further provided at the upper end of the rotor, so that the negative pressure formed near the upper balance weight can be further increased, and the oil-gas mixture flowing out through the flow hole can be driven by the larger negative pressure generated near the upper balance weight, reducing the reflux of the refrigerant through the flow hole, avoiding the reverse flow of the refrigerant, reducing the input, and improving the oil level. Brief Description of the Drawings
[0027] 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 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.
[0028] Figure 1 Partial structural schematic diagram of an embodiment of a compressor provided by the present utility model;
[0029] Figure 2 is Figure 1 Top view schematic diagram of the upper rotor;
[0030] Figure 3 is Figure 1 Top view schematic diagram of the upper balance weight;
[0031] Figure 4 is Figure 1 Side view schematic diagram of the upper balance weight;
[0032] Figure 5 is Figure 1 Top view schematic diagram of the first end plate;
[0033] Figure 6 is Figure 1 Top view schematic diagram of the second end plate;
[0034] Figure 7 is Figure 1 Side view schematic diagram of the second end plate.
[0035] Explanation of the reference numerals in the drawings:
[0036] 1. Rotor; 1a. Mounting hole; 1b. Flow hole; 2. Upper balance weight; 3. Pressurization structure; 31. First end plate; 31a. Through hole; 32. Second end plate; 322. Annular convex part; 32a. Through hole; 32b. Central hole; 4. Lower balance weight.
[0037] The realization of the purpose, functional features and advantages of the present utility model will be further described with reference to the embodiments and the drawings. Detailed Embodiments
[0038] The technical solutions in the embodiments of the present utility model will be clearly and completely described below with reference to 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 the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present utility model without creative efforts shall fall within the protection scope of the present utility model.
[0039] 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 position relationship and movement conditions between components in a specific posture. If the specific posture changes, the directional indications will also change accordingly.
[0040] 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 where A and B are satisfied simultaneously. In addition, the technical solutions between various embodiments can be combined with each other, but it must be based on the ability of those of ordinary skill in the art to implement. When the combination of technical solutions results in contradictions or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the protection scope required by the present utility model.
[0041] Rotary compressors are widely used because of their high efficiency, compact structure, small size, and light weight, for example, inside household air conditioners. The rotor assembly is an important part of a rotary compressor. In traditional rotor assemblies, two balance weights of unequal sizes are respectively placed at both ends of the rotor core to balance the unbalanced force caused by the eccentricity of the crankshaft. To balance the unbalanced force caused by the eccentricity of the crankshaft, the mass and volume of the balance weight on the side of the rotor core close to the eccentric shaft of the crankshaft are both larger than those of the balance weight on the side far from the eccentric shaft of the crankshaft, resulting in a negative pressure formed by the balance weight on the side close to the eccentric shaft being greater than that of the balance weight on the side far from the eccentric shaft, forming a refrigerant countercurrent and increasing the risk of additional input and oil level.
[0042] The present utility model provides a compressor, aiming to solve the problem of refrigerant countercurrent existing in existing rotary compressors.
[0043] Please refer to Figure 1 、 Figure 2 、 Figure 5 andFigure 6 , in an embodiment of the present utility model, the compressor includes a housing (not shown in the figure), a motor, and a balancing structure. The motor is disposed within the housing. The motor includes a rotor 1, and a mounting hole 1a for the crankshaft to pass through and a flow hole 1b located on the periphery of the mounting hole 1a are provided through the rotor 1. The balancing structure includes an upper balancing block 2 eccentrically disposed at the upper end of the rotor 1, and the balancing block is disposed outside the flow hole 1b. Wherein, a boosting structure 3 concentric with the mounting hole 1a is further provided at the upper end of the rotor 1.
[0044] It should be noted that the housing is the outer shell of the compressor for accommodating internal components such as the motor, cylinder, etc. The motor is the power source of the compressor for driving the rotor 1 to rotate. The rotor 1 is one of the core components of the motor for transmitting the torque generated by the motor. The mounting hole 1a is a hole penetrating the center of the rotor 1 for the crankshaft to pass through. The flow hole 1b is a hole located on the periphery of the mounting hole 1a for gas flow. The balancing structure is a structure for balancing the unbalanced torque generated during the rotation of the rotor 1. The upper balancing block 2 is a balancing block disposed at the upper end of the rotor 1 and located outside the flow hole 1b.
[0045] It should also be noted that when the rotor rotates at a high speed, the eccentrically disposed balancing block will disturb the surrounding fluid, causing the fluid to accelerate near the balancing block. Due to the presence of the balancing block, the fluid is forced to change its direction and speed near the balancing block, which causes the fluid to accelerate. According to Bernoulli's principle, the pressure of the fluid in the acceleration region will decrease, thus forming a negative pressure region near the balancing block. When the rotor rotates at a high speed, the fluid near the balancing block will be affected by the centrifugal force. The centrifugal force will cause the fluid to move towards the outside, thus forming a low-pressure region near the balancing block. The centrifugal force effect will also promote the formation of the negative pressure. The combined action of the two effects results in the formation of a low-pressure region near the balancing block. When the properties of the fluid (such as viscosity, density) and the speed of the rotor are certain, the shape, position, and size of the balancing block will all affect its ability to disturb the flow field, and thus affect the magnitude of the negative pressure.
[0046] It should be noted that the purpose of setting the pressurizing structure 3 is to form a greater negative pressure at the upper end of the rotor 1. The way to increase the negative pressure can be to increase the volume of the upper balance weight 2, or to arrange components around the upper balance weight 2. When the rotor 1 rotates, a low-pressure area corresponding to the through-flow hole 1b is enclosed between the components and the upper balance weight 2. The pressurizing structure 3 can be in various forms. For example, it can be an end plate arranged at intervals above the rotor 1 and corresponding to the through-flow hole 1b, or a component arranged at intervals with the balance weight and at least partially staggered with the through-flow hole 1b on the upper end surface of the rotor 1. Of course, the pressurizing structure 3 is not limited to the above examples. Those skilled in the art may make other changes under the inspiration of the technical essence of the embodiments of this specification. However, as long as the functions and effects achieved are the same as or similar to those of the embodiments of this specification, they should all be covered within the protection scope of the embodiments of this specification.
[0047] It can be understood that during the operation of the compressor, when the oil-gas mixture formed by the high-pressure refrigerant gas and lubricating oil sprays upward from the air outlet of the cylinder and passes through the through-flow hole on the rotor, it needs to continue to spray upward to the exhaust port of the compressor. Therefore, during the upward movement of the oil-gas mixture, there is a relatively large demand for upward power.
[0048] Since the refrigerant exhaust of the compressor is constant, the total refrigerant flow rate in the motor channel is constant. The refrigerant volume flowing back through the rotor needs to be supplemented by other channels. Therefore, the reflux of the refrigerant and refrigerating oil at the stator cutting edge is enhanced, and thus the oil spitting rate of the compressor can be reduced.
[0049] In the technical solution of the present utility model, by further providing a pressurizing structure 3 concentric with the mounting hole 1a at the upper end of the rotor 1, the negative pressure formed near the upper balance weight 2 can be further increased, so that the oil-gas mixture flowing out through the through-flow hole 1b can be driven by the relatively large negative pressure generated near the upper balance weight 2, reducing the reflux of the refrigerant through the through-flow hole 1b, avoiding the reverse flow of the refrigerant, reducing the input, improving the oil level surface, and reducing the oil spitting rate of the compressor.
[0050] Specifically, please refer to Figure 1 and Figure 6 , the pressurizing structure 3 includes a first end plate 31 located above the rotor 1 and spaced from the rotor 1.
[0051] The first end plate 31 is an end plate located above the rotor 1; the annular convex portion 322 is an annular structure arranged between the mounting hole 1a and the through-flow hole 1b; through the arrangement of the above structures, a low-pressure area is formed in the area corresponding to the through-flow hole 1b at the upper end of the rotor 1.
[0052] An upper balance weight 2 is eccentrically arranged at the upper end of the rotor 1. When a first end plate 31 is arranged above the upper balance weight 2, the first end plate 31 can guide the flow direction of the fluid, making it more concentrated near the upper balance weight 2, increasing the degree of fluid disturbance. The area between the first end plate 31 and the top of the rotor 1 can further restrict the fluid flow, change the fluid flow path, promote the acceleration and turbulence of the fluid, so that a greater negative pressure can be generated near the balance weight.
[0053] It can be understood that the first end plate 31 is concentrically arranged with the rotor 1, and the first end plate 31 does not affect the magnitude of the torque generated by the balance structure. When the rotor 1 rotates, due to the action of centrifugal force, the oil-gas mixture will be thrown out towards the circumferential side of the rotor 1 at the upper end of the through-hole 1b, and the movement path of the oil-gas mixture is obliquely upward. Therefore, the interval between the first end plate 31 and the upper end surface of the rotor 1 only needs to be set above the highest height that can ensure the oil-gas mixture can be emitted.
[0054] Furthermore, the outer contour of the first end plate 31 is set to be circular. The first end plate 31 is set as a circular end plate, which can provide a smoother fluid flow path, reduce fluid turbulence, help form a more uniform negative pressure distribution, and at the same time can reduce the eddy current generated at the edge of the first end plate 31, reduce fluid resistance, and help the fluid flow more smoothly.
[0055] In this embodiment, please refer to Figure 1 and Figure 7 , the boosting structure 3 further includes an annular convex portion 322 arranged at the upper end of the rotor 1, and the annular convex portion 322 is arranged at a position between the mounting hole 1a and the through-hole 1b.
[0056] Since the crankshaft passes through the mounting hole 1a, there is a gap between the mounting hole 1a and the crankshaft. The gas in the bottom area of the rotor 1 will move upward through the gap between the mounting hole 1a and the crankshaft. When a negative pressure is generated near the upper balance weight 2, this part of the gas will be supplemented to near the balance weight, so that the negative pressure near the upper balance weight 2 is instead reduced. By arranging the annular convex portion 322 between the mounting hole 1a and the through-hole 1b, the gas passing through the gap between the mounting hole 1a and the crankshaft is blocked by the annular convex portion 322, so that the negative pressure near the upper balance weight 2 can be further increased.
[0057] Furthermore, please refer to Figure 1 and Figure 6, in this embodiment, the supercharging structure 3 further includes a second end plate 32, which is installed on the upper end face of the rotor 1. A through hole 32a corresponding to the flow-through hole 1b and a central hole 32b corresponding to the mounting hole 1a are provided on the second end plate 32; the central hole 32b is set as a flanged hole, and the hole wall of the flanged hole forms the annular convex portion 322.
[0058] By directly connecting the second end plate 32 to the upper end face of the rotor 1, it is convenient to fix the annular convex portion 322 at the top of the rotor 1. The second end plate 32 can be screwed, riveted, welded, etc. to the upper balance weight 2 to form an integral body.
[0059] Furthermore, please refer to Figure 1 and Figure 7 , in this embodiment, the supercharging structure 3 further includes a first end plate 31 disposed on the side of the annular convex portion 322 away from the rotor 1, and the upper balance weight 2 is disposed between the first end plate 31 and the second end plate 32.
[0060] In this way, when the rotor 1 rotates, a low-pressure area enclosed by the first end plate 31, the second end plate 32 and the upper balance weight 2 is correspondingly arranged with the flow-through hole 1b. The first end plate 31 blocks the air above from supplementing into the low-pressure area, and the annular convex portion 322 blocks the air on the side and the air in the mounting hole 1a from supplementing into the low-pressure area, so that a greater negative pressure is generated in the area corresponding to the flow-through hole 1b.
[0061] Specifically, please refer to Figure 4 and Figure 7 , in this embodiment, the distance between the first end plate 31 and the second end plate 32 is h, and the height of the annular convex portion 322 is d, where d > h - 2mm.
[0062] It should be noted that since there is an oil sump for storing lubricating oil at the bottom of the compressor, the lubricating oil is recycled in the shell. The normal circulation path of the lubricating oil is as follows: the lubricating oil in the oil sump enters the pump body compressor cavity through the oil supply hole at the bottom of the crankshaft to participate in the lubrication and sealing of the rotating components. Part of the lubricating oil will enter the compression cavity in the compression pump and be discharged through the muffler along with the high-pressure gas; at this time, the gas-liquid mixture enters the upper space of the stator assembly through the rotor flow-through hole; the gas-liquid mixture in the upper space of the stator assembly is separated under the action of gravity separation, centrifugal separation, impact separation, etc., and the liquid oil droplets are separated; the separated lubricating oil flows back to the compressor bottom oil sump through the trimming gap reserved inside the stator and the shell to participate in the subsequent oil supply. This is the complete lubricating oil circulation process inside the compressor.
[0063] Therefore, the higher the oil level in the oil sump, the better the oil return effect. The closer the height of the annular convex portion 322 is set to the first end plate 31, the greater the negative pressure formed near the flow hole 1b. Then, the pressure difference between the negative pressure generated near the upper balance weight 2 at the upper end of the rotor 1 and the negative pressure generated near the lower balance weight 4 at the lower end of the rotor 1 is smaller. As a result, the lubricating oil can return from the lower end to the upper end more smoothly, thereby improving the oil return efficiency, ensuring sufficient lubrication inside the compressor, and maintaining a relatively high oil level at the bottom of the oil sump.
[0064] Further, please refer to Figure 5 and Figure 6 In this embodiment, the inner diameter of the annular convex portion 322 is r, and a through hole 31a corresponding to the flanging hole is formed in the first end plate 31. The radius of the through hole 31a is R, and R - r ≤ 2 mm. The crankshaft passes through the through hole 31a. The smaller the difference between the radius of the through hole 31a and the inner diameter of the annular convex portion 322, the smaller the gap between the through hole 31a and the annular convex portion 322. In the radial direction, the pressure difference between the negative pressure generated near the upper balance weight 2 at the upper end of the rotor 1 and the negative pressure generated near the lower balance weight 4 at the lower end of the rotor 1 is smaller, and the lubricating oil can return from the lower end to the upper end more easily, thereby improving the oil return effect.
[0065] Specifically, in this embodiment, the balance structure further includes a lower balance weight 4 disposed at the lower end of the rotor 1, and the lower balance weight 4 is offset from the center of the rotor 1.
[0066] It should be noted that the unbalanced torque is caused by the uneven mass distribution of each part of the rotor 1. By providing an upper balance weight 2 at the upper end of the rotor 1 and a lower balance weight 4 at the lower end of the rotor 1, these unbalanced torques can be better balanced.
[0067] By providing the lower balance weight 4 at the lower end of the rotor 1, the lower balance weight 4 and the upper balance weight 2 can achieve symmetric balance, that is, equal but opposite torques are applied at both ends of the rotor 1, thereby canceling the unbalanced torque.
[0068] Further, please refer to Figure 1 In this embodiment, the volume of the lower balance weight 4 is set to be larger than the volume of the upper balance weight 2.
[0069] It should be noted that in the rotating system, the position of the center of gravity of the rotor 1 affects the distribution of the centrifugal force. A relatively large centrifugal force will be generated on the side close to the crankshaft due to the rotation of the rotor 1. Therefore, it is necessary to increase the mass to balance the generated centrifugal force. Therefore, the volume of the lower balance weight 4 is set to be larger than the volume of the upper balance weight 2.
[0070] However, when the volume of the lower balance weight 4 is greater than that of the upper balance weight 2, the negative pressure formed near the lower balance weight 4 is greater than the negative pressure generated near the upper balance weight 2. To prevent affecting the flow of the refrigerant and avoid reverse flow of the refrigerant, by providing the pressurizing structure 3, the negative pressure above the rotor 1 is increased, so that the lubricating oil can more easily return from the lower end to the upper end.
[0071] Specifically, in this embodiment, the compressor includes a carbon dioxide compressor. A carbon dioxide compressor is a special compressor that uses carbon dioxide as the working medium and is usually used in a refrigeration system called "carbon dioxide transcritical cycle". It has no destructive effect on the ozone layer. In some application scenarios, the carbon dioxide system can achieve higher energy efficiency than traditional refrigeration systems, operate within a wide temperature range, and is suitable for various refrigeration and air conditioning applications.
[0072] The present utility model also provides a refrigeration device, which includes an air conditioner, a refrigerator, etc. The refrigeration device includes a compressor and a heat exchanger. The specific structure of the compressor refers to the above embodiment. Since this refrigeration device 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, which will not be elaborated one by one here.
[0073] The above description is only an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformation made under the technical concept of the present utility model by using the content of the specification and drawings of the present utility model, or direct / indirect application in other related technical fields is included in the patent protection scope of the present utility model.
Claims
1. A compressor, characterized in that: include: case; A motor is disposed in the housing, the motor comprising a rotor, the rotor being provided with a mounting hole for a crankshaft to pass through, and a flow hole located outside the mounting hole; and, A balancing structure, comprising an upper balancing block eccentrically arranged at the upper end of the rotor, wherein the balancing block is arranged at the periphery of the through hole; Wherein, the upper end of the rotor is also provided with a boost structure which is arranged concentrically with the mounting hole.
2. The compressor according to claim 1, characterized in that The supercharging structure includes a first end plate located above the rotor and spaced apart from the rotor.
3. The compressor according to claim 2, characterized in that The outer contour of the first end plate is set to be circular.
4. The compressor according to claim 2, characterized in that The supercharging structure further includes an annular protrusion arranged at the upper end of the rotor, and the annular protrusion is arranged at a position between the mounting hole and the through-flow hole.
5. The compressor according to claim 4, characterized in that The supercharging structure further includes a second end plate, the second end plate is mounted on the upper end surface of the rotor, and the second end plate is provided with a through hole corresponding to the through hole and a center hole corresponding to the mounting hole; The central hole is configured as a flanged hole, and the hole wall of the flanged hole forms the annular convex portion.
6. The compressor according to claim 5, characterized in that The supercharging structure further includes the first end plate which is arranged on a side of the annular protrusion away from the rotor, and the upper balancing block is arranged between the first end plate and the second end plate.
7. The compressor according to claim 6, characterized in that The distance between the first end plate and the second end plate is h, and the height of the annular protrusion is d, where d>h-2mm.
8. The compressor according to claim 6, characterized in that The inner diameter of the annular protrusion is r, and a through hole corresponding to the flanging hole is formed on the first end plate, and the radius of the through hole is R, where Rr≤2mm.
9. The compressor according to claim 1, characterized in that The balancing structure further comprises a lower balancing block arranged at the lower end of the rotor, wherein the lower balancing block is arranged offset from the center of the rotor.
10. The compressor according to claim 9, characterized in that The volume of the lower balancing weight is set to be larger than the volume of the upper balancing weight.
11. The compressor according to any one of claims 1 to 10, characterized in that The compressor comprises a carbon dioxide compressor.
12. A refrigeration device, characterized in that: Comprising the compressor according to any one of claims 1 to 11.