Rotary compressor and refrigeration equipment
By setting the partition eccentric in the rotary compressor, the problem of leakage in the high-pressure zone caused by the small sealing distance between the roller and the partition is solved, the refrigeration capacity and efficiency are improved, and the lightweight and quiet design of the compressor is realized.
Patent Information
- Application Number
- CN202422800591.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-11-15
- Publication Date
- 2025-09-02
- Estimated Expiration
- 2034-11-15
AI Technical Summary
In rotary compressors, the sealing distance between the roller and the partition is small, which makes it easy to communicate with the gaps at the inner holes of the partition at the hinged connection between the slide plate and the roller, resulting in the high-pressure zone and the low-pressure zone, increasing suction return, and affecting the refrigeration capacity and efficiency.
By setting the partition eccentricity, the slide plate does not communicate with the hinge of the roller during reciprocating movement, and the geometric center of the inner hole is offset from the direction of the slide groove to reduce the possibility of refrigerant leaking to the low pressure zone in the high pressure zone.
It effectively reduces refrigerant leakage in high-pressure zones, improves the refrigeration capacity and efficiency of the compressor, reduces noise, and realizes the lightweight and miniaturized design of the compressor.
Smart Images
Figure CN223293896U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of compressors, in particular to a rotary compressor and refrigeration equipment. Background Art
[0002] In rotary compressors, the articulated vane and roller structure plays a vital role, especially for two-cylinder compressors. A cylinder partition is provided in the compressor to separate the upper and lower cylinders. Under conventional design, the cylinder partition is one-piece, and its inner diameter is slightly larger than the eccentric diameter of the crankshaft. At the same time, considering the overall lightweight of the compressor, the wall thickness of the roller is often not very large. For models with a sealing distance of only about 3mm between the roller and the partition, when the roller rotates 180° from the vane groove, the hinged connection between the vane and the roller is easily connected to the gap at the inner hole of the partition, resulting in high pressure at the partition leaking to the low-pressure suction cavity, resulting in increased suction reflux, affecting the cooling capacity and efficiency. Utility Model Content
[0003] The main purpose of the utility model is to provide a rotary compressor and refrigeration equipment, aiming to reduce the possibility of leakage at the partition of the rotary double-cylinder compressor.
[0004] In order to achieve the above-mentioned purpose, the rotary compressor proposed by the present invention comprises
[0005] case
[0006] Two cylinders, the two cylinders are fixedly arranged in the housing;
[0007] a partition plate, the partition plate being arranged between the two cylinders;
[0008] Among them, the cylinder group also includes a crankshaft, which has two rollers rotating in the two cylinders respectively, and the crankshaft has a rotation axis. The partition is provided with an inner hole for the crankshaft to pass through, and the geometric center of the inner hole deviates from the rotation axis of the crankshaft.
[0009] In one embodiment, the roller is hinged with a sliding vane, the cylinder is provided with a sliding vane groove, the sliding vane reciprocates in the sliding vane groove, and the geometric center of the inner hole deviates in a direction away from the sliding vane groove.
[0010] In one embodiment, the radius of the inner hole is not greater than the distance from the geometric center of the inner hole to the inner wall of the cylinder.
[0011] In one embodiment, assuming that the distance between the geometric center of the inner hole and the inner diameter center of the cylinder is a, and the diameter of the inner hole is d0, then:
[0012]
[0013] In one embodiment, assuming that the inner diameter of the cylinder is D and the eccentricity is e, then:
[0014]
[0015] In one embodiment, the diameter d0 of the inner hole is in the range of 25 mm ≤ d0 ≤ 40 mm.
[0016] In one embodiment, the inner diameter D of the cylinder is in the range of 40 mm ≤ D ≤ 65 mm.
[0017] In one embodiment, the eccentricity e is in the range of 3 mm ≤ e ≤ 6 mm.
[0018] In one embodiment, the projections of the geometric center of the sliding vane, the geometric center of the inner hole, and the center of the cylinder in the longitudinal direction of the crankshaft are located on the same straight line.
[0019] The utility model also provides a refrigeration device, comprising the above-mentioned rotary compressor.
[0020] The technical solution of the present invention is to set the partition eccentrically so that during the reciprocating motion of the sliding vane, the hinge between the sliding vane and the roller will not be connected with the gap of the inner hole of the partition, so that the high-pressure area and the low-pressure area separated by the sliding vane will not be connected, thereby reducing the possibility of refrigerant in the high-pressure area leaking to the low-pressure area, and improving the overall cooling capacity and efficiency of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS
[0021] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.
[0022] Figure 1 A schematic cross-sectional view of the structure of the rotary compressor provided by the present invention;
[0023] Figure 2 It is a top view of the cylinder;
[0024] Figure 3 This is the relative position diagram of the cylinder and the inner hole of the partition;
[0025] Figure 4 This is a simplified diagram of the inner hole of the cylinder and the partition.
[0026] Description of Figure Numbers:
[0027] 1. Housing; 11. Reservoir; 12. Oil sump; 2. Motor; 21. Stator; 22. Rotor; 3. Upper muffler; 4. Upper bearing; 5. Cylinder; 51. Upper cylinder; 52. Lower cylinder; 53. Slide vane groove; 54. Slide vane; 55. Cylinder center point O; 6. Partition plate; 61. Inner hole; 611. Inner hole geometric center A; 7. Lower bearing; 8. Lower muffler; 9. Crankshaft; 91. Roller; 92. Oil supply channel; 93. Oiling vane
[0028] The realization of the purpose, functional features and advantages of the present invention will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION
[0029] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts shall fall within the scope of protection of the present invention.
[0030] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement status, etc. between the components in a certain specific posture. If the specific posture changes, the directional indications will also change accordingly.
[0031] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present invention, 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 number of the indicated technical features. Therefore, the features limited to "first" and "second" may explicitly or implicitly include at least one of such features. In addition, if "and / or" or "and / or" appears in the full text, its meaning includes three parallel schemes. Taking "A and / or B" as an example, it includes scheme A, or scheme B, or a scheme in which A and B are satisfied at the same time. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in this field to implement. When the combination of technical solutions is mutually contradictory or cannot be implemented, it should be deemed that such a combination of technical solutions does not exist and is not within the scope of protection required by the present invention.
[0032] A rotary compressor is a type of compressor that is currently commonly used in refrigeration equipment such as refrigerators, air conditioners, or water dispensers. Its motor does not need to convert the rotational motion of the rotor into the reciprocating motion of the piston, but directly drives the rotary piston (also called roller) to rotate to complete the compression of the refrigerant vapor.
[0033] At present, the most widely used rotary compressors are single-cylinder rotary compressors and double-cylinder rotary compressors, that is, single-cylinder rotary compressors and double-cylinder rotary compressors; and in rotary compressors, the articulated slide and roller structure plays a vital role; the cylinder has an air inlet and an air outlet, and the refrigerant enters the cylinder from the air inlet, and the rotation of the roller completes the compression process of the refrigerant, and after the compression is completed, it is discharged through the air outlet. It can be simply understood that the part of the cylinder that is connected to the air inlet is a low-pressure area, and the part that is connected to the air outlet is a high-pressure area; and the air inlet and the air outlet are both on the cylinder, so a slide is needed to isolate the air inlet and the air outlet, that is, a slide is needed to isolate the low-pressure area and the high-pressure area to avoid direct connection between the air inlet and the air outlet, which causes compression failure.
[0034] The vane is hinged to the outer circumference of the roller, and the inner wall of the cylinder is provided with a vane groove for the vane to be inserted. The vane will continuously reciprocate in the vane groove as the roller moves, thereby isolating the direct connection between the air inlet and the air outlet; in a two-cylinder rotary compressor, a cylinder partition is also provided, which is used to separate the two cylinders to avoid direct connection between the two cylinders; generally speaking, the cylinder partition is one-piece, and in order to facilitate assembly and rotation of the crankshaft, an inner hole is provided on the partition for the crankshaft to pass through, and the diameter of the inner hole is slightly larger than the eccentric diameter of the crankshaft (that is, the diameter of the roller); with the trend of lightweight design of compressors, in order to reduce the overall weight of the compressor, the wall thickness of the roller is often designed to be thinner, thereby reducing the weight of the roller and thus reducing the weight of the compressor.
[0035] However, as the wall thickness of the roller gradually decreases, especially for compressors where the sealing distance between the roller and the partition is only about 3mm, after the roller rotates 180° from the vane groove, the hinged connection between the vane and the roller is likely to connect with the gap in the inner hole of the partition, resulting in the failure of the vane to isolate the air inlet and outlet, that is, the high-pressure area in the cylinder is connected to the low-pressure area, which in turn leads to increased suction reflux, affecting the cooling capacity and compressor efficiency.
[0036] Reference Figure 1In order to solve the above problems, the present invention proposes a rotary compressor, which aims to reduce the possibility of leakage at the partition 6 of the rotary twin-cylinder compressor and ensure the cooling capacity and efficiency of the compressor; specifically, the rotary compressor proposed by the present invention includes a shell 1, two cylinders 5 and a partition 6, the two cylinders 5 are fixedly arranged in the shell 1, and the partition 6 is fixedly arranged between the two cylinders 5. The partition 6 is used to separate the two cylinders 5 to ensure that the two cylinders 5 can operate independently without affecting each other; wherein, a motor 2 is also provided in the shell 1, and the output end of the motor 2 is a crankshaft 9. In the present invention, two rollers 91 are integrally formed on the crankshaft 9, both of which are eccentrically arranged, and the two rollers 91 rotate in the two cylinders 5 respectively, thereby completing the compression process of the refrigerant (refrigerant); the motor 2 has a rotor 22 and a stator 21, the stator 21 is fixed in the shell 1, and the rotor 22 rotates in the stator 21. The rotor 22 has an output end, that is, the output end of the motor 2, that is, the crankshaft 9, and the crankshaft 9 faces downward, so that when the rotor 22 rotates, the crankshaft 9 will rotate with the rotation of the rotor 22, so that the roller 91 rotates eccentrically in the cylinder 5 to complete the compression of the refrigerant.
[0037] Reference Figure 1 Specifically, the housing 1 is a vertically arranged columnar structure, and the housing 1 has a cavity. The stator 21 consists of an iron core and a coil wound around the iron core. The stator 21 is fixedly mounted on the inner wall of the housing 1 by shrink fitting, that is, the iron core is fixedly connected to the inner wall of the housing 1. The middle of the stator 21 has a mounting groove that passes through in the up and down directions. The rotor 22 is rotatably mounted in the mounting groove of the stator 21, and the motor 2 is assembled.
[0038] Furthermore, the two cylinders 5 are both arranged below the motor 2, and the two cylinders 5 are arranged along the length direction of the crankshaft 9; for the convenience of description, according to the relative positions of the two cylinders 5, the cylinder 5 relatively close to the motor 2 is called the upper cylinder 515, and the cylinder 5 relatively far away from the motor 2 is called the lower cylinder 525. Here, the upper cylinder 515 and the lower cylinder 525 are merely nicknames based on the relative positions of the two cylinders 5, and do not represent that the two cylinders 5 have an essential difference; in the present utility model, an upper bearing 4 is provided on the top of the upper cylinder 515, and the upper bearing 4 is rotatably connected to the crankshaft 9; and an upper muffler 3 is also provided on the top of the upper bearing 4. The upper muffler 3 is roughly in the shape of a cover and is provided on the top of the upper bearing 4. The setting of the upper muffler 3 can utilize its shape to suppress the noise generated by the compressor during operation, thereby reducing the decibel level during operation of the compressor and improving the quietness of the compressor.
[0039] Reference Figure 1, the partition 6 is arranged at the bottom of the upper cylinder 515, and the two sides of the partition 6 are actually tightly fitted with the upper cylinder 515 and the lower cylinder 525, so that the partition 6 can meet the design requirements of isolating the upper cylinder 515 and the lower cylinder 525 while ensuring the airtightness of the upper cylinder 515 and the lower cylinder 525; it should be noted that during the assembly process of the compressor, the roller 91 on the crankshaft 9 away from the motor 2 needs to pass through the upper cylinder 515 and the partition 6 in turn before entering the lower cylinder 525, and in order to avoid the partition 6 from interfering with the operation of the crankshaft 9, an inner hole 61 is also opened on the partition 6, and the diameter of the inner hole 61 is slightly larger than the diameter of the roller 91, that is, the diameter of the inner hole 61 needs to be larger than the eccentric diameter of the crankshaft 9 to meet the assembly requirements and operation requirements.
[0040] The top of the lower cylinder 525 fits tightly against the bottom of the partition 6. Accordingly, along the extension direction of the crankshaft 9, a lower bearing 7 is also provided on the bottom of the lower cylinder 525. The lower bearing 7 is the same as the upper bearing 4, that is, the lower bearing 7 is also rotatably connected to the crankshaft 9. A lower muffler 8 is also provided on the bottom of the lower bearing 7. The lower muffler 8 is the same as the upper muffler 3. The lower muffler 8 is also roughly in the shape of a cover and is provided at the bottom of the lower bearing 7. The setting of the lower muffler 8 can also utilize its shape to suppress the noise generated by the compressor during operation, thereby reducing the decibel level during operation of the compressor and improving the quietness of the compressor.
[0041] Reference Figure 1 It should be noted that, from top to bottom, they are, in order, the upper muffler 3, upper bearing 4, upper cylinder 515, partition 6, lower cylinder 525, lower bearing 7, and lower muffler 8. In the present invention, the upper bearing 4 is welded to the inner circumferential wall of the housing 1, and the upper cylinder 515 and lower cylinder 525 are also welded to the circumferential wall of the housing 1. The upper muffler 3, upper bearing 4, upper cylinder 515, partition 6, lower cylinder 525, lower bearing 7, and lower muffler 8 can be fixed as a whole by bolts, thereby improving the integrity of the compressor and facilitating lightweight and miniaturized design of the compressor.
[0042] Reference Figure 1Specifically, in the present invention, a liquid reservoir 11 is further provided outside the casing 1 of the compressor. The liquid reservoir 11 is used to store the refrigerant to be compressed. The interior of the liquid reservoir 11 is respectively communicated with the air inlets of the two cylinders 5, so that the refrigerant to be compressed can directly enter the cylinder 5 through the liquid reservoir 11 for compression; and an exhaust cavity is formed at the top of the casing 1, that is, the top of the motor 2 and the top of the casing 1 together form an exhaust cavity, and the compressed refrigerant will enter the exhaust cavity and be discharged from the casing 1; in the interior of the casing 1, an oil pool 12 is formed between the lower muffler 8 and the bottom of the casing 1, and the oil pool 12 is filled with cooling oil, and the end of the crankshaft 9 extends out of the lower muffler 8 and extends into the oil pool. 12; it should be noted that, in the present utility model, the crankshaft 9 is hollow, that is, an oil supply channel 92 is also provided in the center of the crankshaft 9, and the oil supply channel 92 passes through the upper and lower end faces of the crankshaft 9 in the up and down directions, and the lower end of the oil supply channel 92 is connected to the oil pool 12, and the upper end is connected to the exhaust chamber; the inner circumferential wall of the lower end of the oil supply channel 92 is provided with an oiling blade 93. When the crankshaft 9 rotates, the oiling blade 93 can drive the cooling oil in the oil pool 12 to be transported upward through the oil supply channel 92. After the cooling oil is output from the upper end of the oil supply channel 92, it flows back to the oil pool 12 through the gaps between the components in the shell 1 under the action of gravity, and circulates like this to provide lubrication and heat dissipation for the moving parts in the shell 1.
[0043] Reference Figures 2 to 4 The above is the specific arrangement of the present invention. In order to solve the problem that when the roller 91 starts to rotate 180° from the slide groove 53, the hinged connection between the slide 54 and the roller 91 is easily connected with the gap provided at the inner hole 61 of the partition 6, resulting in the failure of the slide 54 to isolate the air inlet and the air outlet. In the present invention, the crankshaft 9 has a rotation axis, and the geometric center of the inner hole 61 of the partition 6 deviates from the rotation axis of the crankshaft 9, that is, the geometric center of the inner hole 61 is offset in the direction away from the slide groove 53. It can be simply understood that the partition 6 is offset in the direction away from the slide 54 along the extension direction of the slide 54, thereby greatly reducing the probability of the hinged connection between the roller 91 and the gap provided at the inner hole 61 of the partition 6, thereby reducing the possibility of the refrigerant in the high-pressure area leaking to the low-pressure area, and improving the overall cooling capacity and efficiency of the compressor.
[0044] Reference Figures 2 to 4Specifically, the offset of the geometric center of inner hole 61 must also be controlled within a certain range to ensure that partition 6 isolates upper and lower cylinders 525. In the present invention, the distance from inner hole 61 to vane slot 53 is greater than the length of vane 54, and the radius of inner hole 61 is no greater than the distance from the geometric center of inner hole 61 to the inner wall of cylinder 5. To put it another way, when roller 91 rotates 180° from vane slot 53, the position of inner hole 61 is between the hinge of vane 54 and roller 91 and the inner wall of cylinder 5, falling within the range of possible positions for inner hole 61. The offset setting of inner hole 61 greatly reduces the probability of communication between the hinge of roller 91 and the gap between inner hole 61 of partition 6, thereby ensuring the efficiency of the compressor.
[0045] In the present invention, if expressed mathematically, assuming that the distance between the geometric center of the inner hole 61 and the inner diameter center of the cylinder 5 is a, and the diameter of the inner hole 61 is d0, then:
[0046]
[0047] It can be seen that, within a reasonable design range, the larger the diameter of the inner hole 61, the greater the distance between the geometric center of the inner hole 61 and the center of the inner diameter of the cylinder 5. That is, the geometric center of the inner hole 61 needs to be further away from the center point of the cylinder 5 to avoid the hinge of the roller 91 from being connected to the gap in the inner hole 61 of the partition 6, thereby causing the high-pressure area to be connected to the low-pressure area. Accordingly, in order to limit the offset of the inner hole 61 from being too large, which would cause the partition 6 to fail to isolate the upper cylinder 515 and the lower cylinder 525, assuming that the inner diameter of the cylinder 5 is D and the eccentricity is e, then:
[0048]
[0049] Therefore, the distance a between the geometric center of the inner hole 61 and the inner diameter center of the cylinder 5 is limited to a range, which is to say, the range in which the inner hole 61 can deviate is limited; it can be seen from the above inequality that when the eccentricity and the diameter of the inner hole 61 are constant, the larger the diameter of the cylinder 5 is, the larger the range of the distance between the geometric center of the inner hole 61 and the inner diameter center of the cylinder 5 is, which means that the position in which the inner hole 61 can be set is more free; and if the inner diameter of the cylinder 5 is constant and the eccentricity is constant, the larger the diameter of the inner hole 61 is, the smaller the range of the distance between the geometric center of the inner hole 61 and the inner diameter center of the cylinder 5 is, which means that the position in which the inner hole 61 can be set is more restricted.
[0050] Reference Figures 2 to 4Furthermore, considering the actual design size of the compressor, the size range of the diameter d0 of the inner hole 61 is 25mm≤d0≤40mm, the size range of the inner diameter D of the cylinder 5 is 40mm≤D≤65mm, and the range of the eccentricity e is 3mm≤e≤6mm; wherein, the inner diameter range of the cylinder 5 provides flexibility and the possibility of optimizing performance for the design and application of the compressor, while also considering cost and production efficiency; specifically, this size range can cover a variety of compressor design requirements from small to medium-sized, and has good adaptability; and the cylinder 5 in this size range is relatively easy to manufacture, and the cost is relatively reasonable, and it is neither extremely Unlike small cylinders 5, which are difficult and expensive to manufacture, small cylinders 5 do not require the same amount of materials and production equipment as large cylinders 5, thus controlling costs. Furthermore, within this size range, cylinders 5 can achieve a good balance between compression ratio, displacement, and efficiency. While smaller cylinders 5 can achieve a higher compression ratio, their displacement is limited; larger cylinders 5 have a larger displacement but may have a relatively lower compression ratio. A size of 40mm to 65mm strikes a balance between these factors. Furthermore, cylinders 5 within this size range have a moderate weight and volume, facilitating the overall design and installation of the compressor, making them particularly suitable for applications with limited space or requiring mobility. Based on the inner diameter range of cylinder 5, the range of the diameter d0 of inner bore 61 and the range of the eccentricity e are derived, which in turn derives the range of the distance a between the geometric center of inner bore 61 and the inner diameter center of cylinder 5.
[0051] Reference Figures 2 to 4 It should be noted that, although the inner hole 61 is eccentrically arranged, the center of the inner hole 61 is still located in the extension direction of the slide groove 53; in the present utility model, since the slide 54 reciprocates in the slide groove 53, the extension direction of the slide groove 53 actually passes through the center of the cylinder 5. To be more rigorous, the geometric center of the slide 54, the geometric center of the inner hole 61 and the projection of the center of the cylinder 5 on the plane perpendicular to the length direction of the crankshaft 9 are located on the same straight line, thereby limiting the offset range of the inner hole 61, thereby reducing the possibility of the partition 6 failing to isolate the upper cylinder 515 and the lower cylinder 525 due to the incorrect offset direction of the inner hole 61.
[0052] The present utility model also proposes a refrigeration device, which includes the above-mentioned rotary compressor. The specific structure of the rotary compressor refers to the above-mentioned embodiment. Since the present refrigeration device adopts all the technical solutions of all the above-mentioned embodiments, it has at least all the beneficial effects brought by the technical solutions of the above-mentioned embodiments, which will not be described one by one here.
[0053] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. All equivalent structural transformations made using the contents of the present invention specification and drawings under the technical concept of the present invention, or direct / indirect application in other related technical fields are included in the patent protection scope of the present invention.
Claims
1. A rotary compressor, characterized in that: include case; Two cylinders, the two cylinders are fixedly arranged in the housing; a partition plate, the partition plate being arranged between the two cylinders; Wherein, the rotary compressor also includes a crankshaft, which has two rollers rotating in the two cylinders respectively, and the crankshaft has a rotation axis. The partition is provided with an inner hole for the crankshaft to pass through, and the geometric center of the inner hole deviates from the rotation axis of the crankshaft.
2. The rotary compressor according to claim 1, wherein The roller is hinged with a sliding plate, the cylinder is provided with a sliding plate groove, the sliding plate reciprocates in the sliding plate groove, and the geometric center of the inner hole deviates in a direction away from the sliding plate groove.
3. The rotary compressor according to claim 2, wherein The radius of the inner hole is not greater than the distance from the geometric center of the inner hole to the inner wall of the cylinder.
4. The rotary compressor according to claim 3, wherein The distance between the geometric center of the inner hole and the inner diameter center of the cylinder is a, and the diameter of the inner hole is d0, then:
5. The rotary compressor according to claim 4, wherein The inner diameter of the cylinder is D, and the eccentricity is e, then:
6. The rotary compressor according to any one of claims 4 to 5, characterized in that The diameter d0 of the inner hole has a size range of 25 mm ≤ d0 ≤ 40 mm.
7. The rotary compressor according to any one of claims 4 to 5, characterized in that The inner diameter D of the cylinder has a size range of 40 mm ≤ D ≤ 65 mm.
8. The rotary compressor according to any one of claims 4 to 5, characterized in that The range of the eccentricity e is 3mm≤e≤6mm.
9. The rotary compressor according to claim 5, wherein The projections of the geometric center of the sliding vane, the geometric center of the inner hole, and the center of the cylinder in the length direction of the crankshaft are located on the same straight line.
10. A refrigeration device, characterized in that: It comprises the rotary compressor according to any one of claims 1 to 9.