Rotary compressor and refrigeration equipment

Abstract

The invention discloses a rotary compressor and refrigeration equipment, and relates to the technical field of compressors, and the rotary compressor comprises a shell; the two air cylinders are fixedly arranged in the shell; the partition plate is arranged between the two air cylinders; the rotary compressor further comprises a crankshaft, the crankshaft is provided with two rollers rotating in the two air cylinders respectively, the crankshaft is provided with a rotating axis, the partition plate is provided with an inner hole allowing the crankshaft to penetrate through, and the geometric center of the inner hole deviates from the rotating axis of the crankshaft. According to the technical scheme, the partition plate is eccentrically arranged, so that in the reciprocating motion process of the sliding piece, the hinged position of the sliding piece and the roller cannot communicate with a gap formed in an inner hole of the partition plate, a high-pressure area and a low-pressure area separated by the sliding piece cannot communicate, the possibility that a refrigerant in the high-pressure area leaks to the low-pressure area is reduced, and the service life of the sliding piece is prolonged. And the overall refrigerating capacity and efficiency of the compressor are improved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a rotary compressor and a refrigeration device. Background Art

[0002] In rotary compressors, the articulated vane and roller structure plays a vital role, especially for twin-cylinder compressors, in which a cylinder partition is provided 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. Considering the overall lightweight of the compressor, the wall thickness of the roller is often not very large. For models where the sealing distance between the roller and the partition is only about 3mm, 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 leakage at the partition to the low pressure suction chamber, resulting in increased suction reflux, affecting the cooling capacity and efficiency. Summary of the invention

[0003] The main purpose of the present invention is to provide a rotary compressor and a refrigeration device, aiming to reduce the possibility of leakage at the partition of the rotary double-cylinder compressor.

[0004] To achieve the above object, 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 is arranged between the two cylinders;

[0008] Wherein, 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 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.

[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 has a size range of 25 mm ≤ d0 ≤ 40 mm.

[0016] In one embodiment, the inner diameter D of the cylinder has a size 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 length direction of the crankshaft are located on the same straight line.

[0019] The present invention also provides a refrigeration device, comprising the above-mentioned rotary compressor.

[0020] The technical solution of the present invention sets 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 leakage from the high-pressure area 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 drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. 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 creative work.

[0022] Figure 1 A schematic cross-sectional view of the structure of a rotary compressor provided by the present invention;

[0023] Figure 2 It is a top view of the cylinder;

[0024] Figure 3 It 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 holes of the cylinder and the partition.

[0026] Description of Figure Numbers:

[0027] 1. Housing; 11. Liquid reservoir; 12. Oil pool; 2. Motor; 21. Stator; 22. Rotor; 3. Upper silencer; 4. Upper bearing; 5. Cylinder; 51. Upper cylinder; 52. Lower cylinder; 53. Slide slot; 54. Slide; 55. Cylinder center point O; 6. Partition; 61. Inner hole; 611. Inner hole geometric center A; 7. Lower bearing; 8. Lower silencer; 9. Crankshaft; 91. Roller; 92. Oil supply channel; 93. Oiling blade;

[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 described embodiments 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 creative work are 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 indication 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 used for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of technical features indicated. Therefore, the features limited to "first" and "second" may explicitly or implicitly include at least one of the features. In addition, if "and / or" or "and / or" appears in the full text, its meaning includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, solution B, or solutions that satisfy both A and B. 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 contradictory or cannot be implemented, it should be deemed that such 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 rotating 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 the articulated vane and roller structure play a vital role in the rotary compressor; the cylinder has an air inlet and an air outlet, the refrigerant enters the cylinder from the air inlet, and the rotation of the roller completes the compression process of the refrigerant, and the refrigerant is discharged through the air outlet after the compression is completed. 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 vane is needed to isolate the air inlet and the air outlet, that is, the vane 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 (i.e. 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 in which 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's isolation of 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 an increase in 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 double-cylinder compressor and ensure the refrigeration 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 arranged 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 housing 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 shell 1 is a vertically arranged columnar structure, and the shell 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 installed on the inner wall of the shell 1 by shrink fitting, that is, the iron core is fixedly connected to the inner wall of the shell 1. The middle of the stator 21 has an installation groove that passes through in the up and down directions. The rotor 22 is rotatably installed in the installation 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 are essentially different; in the present invention, an upper bearing 4 is provided at 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 at 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 surface of the partition 6. Correspondingly, along the extension direction of the crankshaft 9, a lower bearing 7 is also provided on the bottom surface 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 surface of the lower bearing 7. The lower muffler 8 is roughly in the shape of a cover and is arranged 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 the 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 the upper muffler 3, the upper bearing 4, the upper cylinder 515, the partition 6, the lower cylinder 525, the lower bearing 7 and the lower muffler 8. In the present invention, the upper bearing 4 is welded to the inner peripheral wall of the shell 1, and the upper cylinder 515 and the lower cylinder 525 are also welded to the peripheral wall of the shell 1, and the upper muffler 3, the upper bearing 4, the upper cylinder 515, the partition 6, the lower cylinder 525, the lower bearing 7 and the lower muffler 8 can be fixed as a whole by bolts, thereby improving the integrity of the compressor. It is convenient for the lightweight and miniaturized design of the compressor.

[0042] Reference Figure 1Specifically, in the present invention, a liquid reservoir 11 is further provided outside the shell 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 shell 1, that is, the top of the motor 2 and the top of the shell 1 are enclosed together to form an exhaust cavity, and the compressed refrigerant will enter the exhaust cavity and be discharged from the shell 1; in the interior of the shell 1, an oil pool 12 is formed between the lower muffler 8 and the bottom of the shell 1, and the oil pool 12 contains 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 invention, 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 surfaces 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, and after the cooling oil is output from the upper end of the oil supply channel 92, under the action of gravity, it flows back to the oil pool 12 through the gaps between the components in the shell 1, and circulates in this way, so as to provide lubrication and heat dissipation for the moving parts in the shell 1.

[0043] Reference Figures 2 to 4 The above is a specific arrangement of the present invention. To solve the problem that after the roller 91 starts to rotate 180° from the vane groove 53, the hinged connection between the vane 54 and the roller 91 is easily connected with the gap in the inner hole 61 of the partition 6, resulting in the failure of the vane 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 vane groove 53. It can be simply understood that the partition 6 is offset in the direction away from the vane 54 along the extension direction of the vane 54, thereby greatly reducing the probability of the hinge of the roller 91 being connected with the gap in the inner hole 61 of the partition 6, thereby reducing the possibility of refrigerant leakage from the high-pressure area 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 the inner hole 61 also needs to be controlled within a certain range to ensure that the partition 6 isolates the upper and lower cylinders 525; in the present invention, the distance from the inner hole 61 to the vane groove 53 is greater than the length of the vane 54, and the radius of the inner hole 61 is not greater than the distance from the geometric center of the inner hole 61 to the inner wall of the cylinder 5; in other words, when the roller 91 starts to run 180° from the vane groove 53, the position of the inner hole 61 is located between the hinge of the vane 54 and the roller 91 and the inner wall of the cylinder 5, and within this range, it belongs to the position where the inner hole 61 can be set. The offset setting of the inner hole 61 greatly reduces the probability of the hinge of the roller 91 and the gap of the inner hole 61 of the partition 6 being connected, 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 larger the distance between the geometric center of the inner hole 61 and the inner diameter center of the cylinder 5, that is, the geometric center of the inner hole 61 needs to be farther away from the center point of the cylinder 5 to avoid the hinge of the roller 91 being connected to the gap of the inner hole 61 of the partition 6, thereby causing the high-pressure area to be connected with the low-pressure area; accordingly, in order to limit the offset of the inner hole 61 to be too large and 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 between the geometric center of the inner hole 61 and the inner diameter center of the cylinder 5 is limited to a range, that is, the range within 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, 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, which means that the position where 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, 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, which means that the position where 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 the 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 of this size range is relatively easy to manufacture, and the cost is relatively reasonable, and it is neither as Unlike the small cylinder 5, which is difficult to process and has high costs, it does not require more materials and production equipment like the large cylinder 5, thus controlling the cost. In addition, within this size range, the cylinder 5 can better balance the compression ratio, exhaust volume and efficiency. Although the smaller cylinder 5 can obtain a higher compression ratio, the exhaust volume is limited; while the larger cylinder 5 has a large exhaust volume, but the compression ratio may be relatively low. The size of 40mm to 65mm can strike a balance between these factors. Furthermore, the weight and volume of the cylinder 5 in this size range are moderate, which is convenient for the overall design and installation of the compressor, especially suitable for occasions with limited space or need to be moved. According to the inner diameter size range of the cylinder 5, the size range of the diameter d0 of the inner hole 61 and the range of the eccentricity e are obtained, and then the range of the distance a between the geometric center of the inner hole 61 and the inner diameter center of the cylinder 5 is obtained.

[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 vane groove 53; in the present invention, since the vane 54 reciprocates in the vane groove 53, the extension direction of the vane groove 53 actually passes through the center of the cylinder 5. In a more rigorous sense, the projections of the geometric center of the vane 54, the geometric center of the inner hole 61 and 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 failure of the partition 6 to isolate the upper cylinder 515 and the lower cylinder 525 due to incorrect offset direction of the inner hole 61.

[0052] The present invention 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 refrigeration device adopts all the technical solutions of all the above-mentioned embodiments, it at least has all the beneficial effects brought by the technical solutions of the above-mentioned embodiments, which will not be repeated here one by one.

[0053] The above description is only an exemplary embodiment of the present invention, and does not limit the patent scope of the present invention. All equivalent structural changes made by using the contents of the present invention specification and drawings under the technical concept of the present invention, or directly / indirectly applied 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 is 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, characterized in that 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, characterized in that: 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, characterized in 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:

5. The rotary compressor according to claim 4, characterized in that 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, characterized in that: The projections of the geometric center of the slide, 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 a rotary compressor as claimed in any one of claims 1 to 9.

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