Rotary compressor and refrigeration apparatus

Abstract

The utility model discloses a rotary compressor and refrigeration plant relates to compressor technical field, and the rotary compressor includes motor and pump body component, and the pump body component includes crankshaft, first bearing, cylinder and second bearing, and one end of crankshaft is linked with the rotor of motor, and the other end of crankshaft is in order to wear in first bearing, cylinder and second bearing and is linked with eccentric member in the cylinder, and the cylinder is equipped with the suction hole that opens to the outside along its radial direction, and the communication hole that is communicated with the suction hole and extends along the axial direction of cylinder, and the pump body component is equipped with buffer groove also, and buffer groove is communicated with the suction hole through the communication hole, wherein, along the circumferential direction of cylinder, the center line of buffer groove and the center line of suction hole are staggered arrangement. Improve the suction volume, and can strengthen the upper end surface pressure of cylinder suction hole, reduce the risk of leakage, avoid high pressure refrigerant to the suction cavity leakage, improve the energy efficiency of rotary compressor, thereby guarantee the stability in the whole system operation process.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to rotary compressors and refrigeration equipment. Background Technology

[0002] As a core component of refrigeration systems, the energy efficiency of rotary compressors directly impacts the overall energy consumption of air conditioning and refrigeration equipment. During compressor operation, the suction port structure is a key factor determining refrigerant intake efficiency. Its size design requires a precise balance between intake volume, airflow resistance, sealing performance, and compression phase. The size of the suction port affects the intake volume, ultimately impacting energy consumption. Limited by cylinder height and cylinder slide grooves, the cross-sectional area of ​​the cylinder's suction port is constrained. Increasing the intake port size to increase intake volume would increase the suction closing angle, leading to leakage and backflow, resulting in reduced compressor cooling capacity and efficiency. Utility Model Content

[0003] The main purpose of this invention is to provide a rotary compressor and refrigeration equipment that can store a portion of the recirculated refrigerant during the intake and recirculation process, and play a supplementary role during intake, thereby increasing the intake volume, increasing the unit intake volume, and improving the compressor's energy efficiency.

[0004] To achieve the above objectives, this utility model proposes a rotary compressor, including a motor and a pump body component. The pump body component includes a crankshaft, a first bearing, a cylinder, and a second bearing. One end of the crankshaft is connected to the rotor of the motor, and the other end of the crankshaft passes sequentially through the first bearing, the cylinder, and the second bearing and is connected to an eccentric component inside the cylinder. The cylinder is provided with an air intake hole that opens radially outward and a connecting hole that communicates with the air intake hole and extends along the axial direction of the cylinder. The pump body component is also provided with a buffer groove, which communicates with the air intake hole through the connecting hole. In particular, along the circumferential direction of the cylinder, the center line of the buffer groove is offset from the center line of the air intake hole.

[0005] In one embodiment, the buffer groove is located on the end face of the cylinder near the first bearing; or, the end face of the cylinder and the end face of the first bearing together define the buffer groove.

[0006] In one embodiment, the distance between the buffer groove and the outer edge of the cylinder is a, where a ≥ 2 mm.

[0007] In one embodiment, the distance between the buffer groove and the cavity wall of the cylinder is b, where b ≥ 1 mm.

[0008] In one embodiment, the intake port is formed with a chamfered section and a straight section along the radial direction of the cylinder, and the chamfered section communicates with the inner cavity of the cylinder; The connecting hole is connected to the straight segment and is located close to the cavity wall of the cylinder.

[0009] In one embodiment, the center line of the buffer groove is offset from the center line of the connecting hole along the circumferential direction of the cylinder.

[0010] In one embodiment, screw holes and sliding plate grooves are provided on opposite sides of the air intake hole; The distance between the buffer groove and the sliding groove is greater than the distance between the buffer groove and the screw hole.

[0011] In one embodiment, the distance between the buffer groove and the screw hole is c, where c ≥ 1 mm.

[0012] In one embodiment, the angle between the central axis of the connecting hole and the end face of the cylinder is α, the total volume of the buffer groove is Vc, and the displacement of the rotary compressor is Ve, satisfying: 45°≤α≤90°. .

[0013] This utility model also proposes a refrigeration device, characterized in that it includes the above-mentioned rotary compressor, the rotary compressor including at least a motor and a pump body component, the pump body component including a crankshaft, a first bearing, a cylinder and a second bearing, one end of the crankshaft being connected to the rotor of the motor, the other end of the crankshaft being sequentially passed through the first bearing, the cylinder and the second bearing and connected to an eccentric component inside the cylinder, the cylinder having an air intake hole that opens radially outward and a connecting hole that communicates with the air intake hole and extends along the axial direction of the cylinder, and the pump body component also having a buffer groove, the buffer groove communicating with the air intake hole through the connecting hole; In particular, along the circumferential direction of the cylinder, the center line of the buffer groove is offset from the center line of the air intake hole.

[0014] In the technical solution of this utility model, the compression assembly can store a portion of the recirculated refrigerant in the buffer groove during the suction return process. When the suction port begins to draw air, this stored gas is introduced into the suction port, thereby supplementing the air supply, increasing the suction volume, and thus increasing the unit suction volume and improving the compressor's energy efficiency. Since the surface pressure directly above the suction port is low, and the buffer groove reduces the sealing distance, there is a risk of leakage. By staggering the centerline of the buffer groove from the centerline of the suction port, the surface pressure at the upper end of the cylinder's suction port is strengthened, reducing the risk of leakage, preventing high-pressure refrigerant from leaking into the suction chamber, improving the energy efficiency of the rotary compressor, and ensuring the stability of the entire system during operation. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0016] Figure 1 A schematic diagram of a structural embodiment of the rotary compressor provided by this utility model; Figure 2 for Figure 1 Top view of the middle cylinder; Figure 3 for Figure 1 Cross-sectional schematic diagram of the middle cylinder.

[0017] Explanation of icon numbers: 1. Cylinder; 10. Intake port; 10a. Straight section; 10b. Chamfered section; 11. Buffer groove; 12. Connecting hole; 20. Screw hole; 30. Sliding vane groove; 3. First bearing; 4. Second bearing; 5. Crankshaft.

[0018] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0019] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0020] It should be noted that if the embodiments of this utility model involve directional indication, the directional indication is only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indication will also change accordingly.

[0021] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of indicated technical features. Therefore, features defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. If the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0022] As a core component of refrigeration systems, the energy efficiency of rotary compressors directly affects the overall energy consumption of air conditioning, refrigeration, and other equipment. A rotary compressor mainly consists of a housing, motor, crankshaft, piston, cylinder, and vanes. The piston is located inside the cylinder; as the crankshaft rotates around its center of rotation, the piston rotates in close contact with the inner surface of the cylinder. This creates a crescent-shaped space between the outer surface of the piston and the inner surface of the cylinder. The reciprocating vanes divide this space into two independent parts: an intake chamber and a compression chamber.

[0023] During compressor operation, the structure of the suction port is one of the key factors determining refrigerant intake efficiency. Its size design requires a precise balance between intake volume, airflow resistance, sealing performance, and compression phase. The size of the suction port affects the intake volume, ultimately impacting energy consumption. Limited by cylinder height and cylinder slide grooves, the cross-sectional area of ​​the cylinder's suction port is constrained. Increasing the intake port size to increase intake volume would increase the suction closing angle, leading to leakage and backflow, resulting in reduced compressor cooling capacity and efficiency.

[0024] When the compressor finishes intake, there will be a backflow of intake gas. In the existing technology, some of the backflowed gas will enter the liquid receiver from the cylinder. This process has a long flow path and large gas loss, which affects the intake volume of the compressor and thus the energy efficiency of the compressor. On the other hand, the backflow of intake gas will increase pressure pulsation, which will cause noise degradation. There is room for improvement.

[0025] This invention proposes a rotary compressor that can store a portion of the refrigerant during the intake and recirculation process, and play a supplementary role when intake begins, thereby increasing the intake volume, increasing the unit intake volume, and improving the compressor's energy efficiency.

[0026] Please refer to Figures 1 to 2The rotary compressor includes a motor and a pump body component. The pump body component includes a crankshaft 5, a first bearing 3, a cylinder 1, and a second bearing 4. One end of the crankshaft 5 is connected to the rotor of the motor, and the other end of the crankshaft 5 passes through the first bearing 3, the cylinder 1, and the second bearing 4 in sequence and is connected to an eccentric component inside the cylinder 1. The cylinder 1 is provided with an air intake hole 10 that opens outward along its radial direction and a connecting hole 12 that communicates with the air intake hole 10 and extends along the axial direction of the cylinder 1. The pump body component is also provided with a buffer groove 11, which communicates with the air intake hole 10 through the connecting hole 12. The center line of the buffer groove 11 is offset from the center line of the air intake hole 10 along the circumferential direction of the cylinder 1.

[0027] In the technical solution of this utility model, during the suction and recirculation process, the buffer groove 11 can store a portion of the recirculated refrigerant. When the suction port 10 begins to draw air, this stored gas is introduced into the suction port 10, thereby supplementing the air supply, increasing the suction volume, and thus increasing the unit suction volume and improving the compressor's energy efficiency. Since the surface pressure directly above the suction port 10 is low, and the buffer groove 11 reduces the sealing distance, there is a risk of leakage. By ensuring that the centerline of the buffer groove 11 is offset from the centerline of the suction port 10, the surface pressure at the upper end of the cylinder 1 suction port 10 is strengthened, reducing the risk of leakage, preventing high-pressure refrigerant from leaking into the suction chamber, improving the energy efficiency of the rotary compressor, and thus ensuring the stability of the entire system during operation.

[0028] On the end face of cylinder 1, the line connecting the center line of buffer groove 11 and the center of cylinder 1, and the center line of suction port 10 form an angle θ, where θ > 0. Setting buffer groove 11 and suction port 10 offset is beneficial to increase surface pressure and improve the leakage problem caused by the inward deformation of suction port 10 of cylinder 1 under low pressure and high pressure.

[0029] Specifically, at the end of the intake of the rotary compressor, a portion of the gas enters the buffer tank 11 from the intake port 10 through the connecting port 12, thereby shortening the flow path of the gas returning from the intake, reducing gas flow loss, and thus improving the intake efficiency of the rotary compressor, increasing the intake volume, and improving the efficiency of the rotary compressor. Moreover, shortening the gas flow path helps to reduce turbulence, which reduces pressure pulsation and thus reduces noise.

[0030] When cylinder 1 draws in air again, the gas stored in buffer tank 11 can enter the intake port 10 through connecting hole 12 and enter the cylinder 1 together with low-pressure gas, thereby increasing the intake volume and forming an air circulation.

[0031] By reasonably setting the volume of the buffer tank 11, the intake volume of the rotary compressor can be effectively increased, thereby effectively improving the efficiency of the rotary compressor. Furthermore, it allows designers to flexibly set the volume of the buffer tank 11 according to actual needs, so as to maximize the efficiency of the rotary compressor.

[0032] According to the embodiment of the present invention, the rotary compressor provides driving force to the crankshaft 5 by setting a motor, so that the crankshaft 5 can drive the eccentric part to move to compress the gas, thereby realizing the compression function of the rotary compressor. At the same time, a first bearing 3 and a second bearing 4 are sleeved on the outside of the crankshaft 5. The cylinder 1 can be sealed by the first bearing 3 and the second bearing 4 to improve the reliability of gas compression. The crankshaft 5 can also be supported by the first bearing 3 and the second bearing 4 to reduce the vibration of the crankshaft 5. In addition, the intake volume of the rotary compressor can be increased by setting a buffer groove 11 to reduce noise. Furthermore, the efficiency of the rotary compressor can be effectively improved by reasonably setting the volume of the buffer groove 11.

[0033] In some embodiments, the buffer groove 11 is provided on the end face of the cylinder 1 near the first bearing 3. Specifically, the buffer groove 11 is provided on the upper end face of the cylinder 1 so that the gas flows upward into the buffer groove 11 while flowing outward from the suction hole 10. The gas can be stored in the buffer groove 11 to shorten the gas flow path, reduce flow loss, and avoid liquid accumulation. In other embodiments, the end face of the cylinder 1 and the end face of the first bearing 3 together define the buffer groove 11. Specifically, the first bearing 3 is disposed above the cylinder 1, and the buffer groove 11 can be disposed between the first bearing 3 and the cylinder 1, so that the upper end face of the cylinder 1 and the lower end face of the first bearing 3 together define the buffer groove 11. This reduces the number of steps required to process the buffer groove 11 and facilitates the production of the rotary compressor.

[0034] The distance between the buffer groove 11 and the outer edge of the cylinder 1 is a, where a ≥ 2 mm. That is, the outer edge of the buffer groove 11 is spaced from the outer edge of the first bearing 3, which can prevent external high-pressure gas from directly entering the buffer groove 11 due to the inward deformation of the air intake hole 10 of the cylinder 1 under high pressure and low pressure.

[0035] Furthermore, the distance between the buffer groove 11 and the cavity wall of the cylinder 1 is b, where b ≥ 1 mm. The inner edge of the buffer groove 11 does not exceed the inner diameter of the cylinder 1. This is because if the inner edge of the buffer groove 11 exceeds the inner diameter of the cylinder 1, it will cause the buffer groove 11 and the compression chamber of the cylinder 1 to be directly connected, which will cause the compressed gas to enter the buffer groove 11, resulting in direct communication with the outside.

[0036] For existing mass-produced compressor cylinders 1, most have a large chamfer at the location where the intake port 10 connects to the inner wall of cylinder 1. Please refer to... Figure 3The intake port 10 has a chamfered section 10b and a straight section 10a along the radial direction of the cylinder 1. The chamfered section 10b communicates with the inner cavity of the cylinder 1. The connecting hole 12 communicates with the straight section 10a and is located close to the cavity wall of the cylinder 1. This is because if the connecting hole 12 were located in the chamfered section 10b, it would be detrimental to the formation of pressure differential, and the outward-facing port of the straight section 10a is usually used to insert a pipe. Therefore, the connecting hole 12 is positioned closer to the chamfered section 10b.

[0037] Please refer to Figure 2 In this embodiment, the centerline of the buffer groove 11 coincides with the centerline of the connecting hole 12. In some embodiments, the centerline of the buffer groove 11 and the centerline of the connecting hole 12 are offset along the circumferential direction of the cylinder 1. That is, the centerline of the connecting hole 12 is located between the centerline of the buffer groove 11 and the centerline of the suction hole 10. This is because, depending on the offset setting of the buffer groove 11, the buffer groove 11 and the suction hole 10 may be axially offset from each other in the cylinder 1, while the connecting hole 12 still needs to maintain the connection relationship with the corresponding segment of the suction hole 10. Therefore, the two can be structurally set to be eccentric, which will not affect the realization of the functions of the buffer groove 11 and the connecting hole 12.

[0038] Screw holes 20 and sliding plate grooves 30 are provided on opposite sides of the air intake hole 10; buffer groove 11 can be provided between the center line of screw hole 20 and air intake hole 10, and buffer groove 11 can also be provided between the center line of sliding plate groove 30 and air intake hole 10.

[0039] In some implementations, the distance between the buffer groove 11 and the sliding plate groove 30 is greater than the distance between the buffer groove 11 and the screw hole 20. This is because a sliding plate needs to be installed at the sliding plate groove 30. If the distance between the buffer groove 11 and the sliding plate is small, it will reduce the rigidity near the sliding plate groove 30, leading to increased deformation of the sliding plate groove 30. The further the buffer groove 11 is from the sliding plate groove 30, the better the structural effect. However, there is a screw hole 20 on the other side of the buffer groove 11, so it is necessary to ensure that the buffer groove 11 and the screw hole 20 have a certain distance to avoid interference.

[0040] Specifically, the distance between the buffer groove 11 and the screw hole 20 is c, where c ≥ 1 mm. This ensures structural strength. In this embodiment, the angle between the central axis of the connecting hole 12 and the end face of the cylinder 1 is α, the total volume of the buffer groove 11 is Vc, and the displacement of the rotary compressor is Ve, and the following conditions are met: 45°≤α≤90°. .

[0041] The end face can be either an upper or lower end face, meaning the buffer groove 11 can be positioned above or below the intake port 10, with α between 45° and 90°. The connecting hole 12 can be inclined relative to the end face of the cylinder 1, and can be tilted towards the center of the cylinder 1, so that gas can enter the connecting hole 12 from the intake port 10 during the recirculation process. The total volume of the buffer groove 11 is Vc, and the displacement of the rotary compressor 100 is Ve, where the size of Vc determines... The amount of gas that the buffer tank 11 can store determines the compression capacity of the rotary compressor 100. When Vc / Ve is too large, that is, the volume of the buffer tank 11 is larger, which means that the buffer tank 11 occupies more space on the cylinder 1, which will lead to a decrease in the structural strength of the cylinder 1. When Vc / Ve is too small, that is, the volume of the buffer tank 11 is smaller, which reduces the amount of gas stored in the buffer tank 11, which is not conducive to increasing the intake volume of the rotary compressor. Vc / Ve can be kept between 0.1 and 0.4. At this time, the intake volume of the rotary compressor can be increased while ensuring the structural strength of the cylinder 1, which is conducive to improving the efficiency of the rotary compressor. Specifically, the rotary compressor can have one or more cylinders 1. Increasing the number of cylinders 1 can improve the flow rate and compression capacity of the rotary compressor. The number of rotor poles affects the rotational speed of the rotary compressor, which in turn affects the flow rate and compression capacity. The ratio of the number of rotor poles to the number of cylinders 1 should be greater than or equal to the value of cylinders 1. For example, when the number of cylinders 1 is 1, the number of rotor poles can be 10, 12, or 16, etc. When the number of cylinders 1 is 2, the number of rotor poles can be 20, 24, or 28, etc. This way, the number of rotor poles can be increased while increasing the number of cylinders 1, so as to ensure the driving capacity of the motor and the compression capacity of the rotary compressor, thereby ensuring the reliable operation of the rotary compressor.

[0042] This utility model also proposes a refrigeration device, which includes a rotary compressor. The specific structure of the rotary compressor is as described in the above embodiments. Since this refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0043] The above are merely preferred embodiments of this utility model and do not limit the patent scope of this utility model. Any equivalent structural transformations made based on the inventive concept of this utility model and the contents of this utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of this utility model.

Claims

1. A rotary compressor, characterized in that, The device includes a motor and a pump body assembly. The pump body assembly includes a crankshaft, a first bearing, a cylinder, and a second bearing. One end of the crankshaft is connected to the rotor of the motor, and the other end of the crankshaft passes sequentially through the first bearing, the cylinder, and the second bearing and is connected to an eccentric component inside the cylinder. The cylinder has an air intake hole that opens radially outward and a connecting hole that communicates with the air intake hole and extends axially along the cylinder. The pump body assembly also has a buffer groove that communicates with the air intake hole through the connecting hole. In particular, along the circumferential direction of the cylinder, the center line of the buffer groove is offset from the center line of the air intake hole.

2. The rotary compressor as described in claim 1, characterized in that, The buffer groove is located on the end face of the cylinder near the first bearing; or, the end face of the cylinder and the end face of the first bearing together define the buffer groove.

3. The rotary compressor as described in claim 2, characterized in that, The distance between the buffer groove and the outer edge of the cylinder is a, where a ≥ 2 mm.

4. The rotary compressor as described in claim 1, characterized in that, The distance between the buffer groove and the cavity wall of the cylinder is b, where b ≥ 1 mm.

5. The rotary compressor as described in claim 1, characterized in that, The intake port has a chamfered section and a straight section along the radial direction of the cylinder, and the chamfered section communicates with the inner cavity of the cylinder; The connecting hole is connected to the straight segment and is located close to the cavity wall of the cylinder.

6. The rotary compressor as described in claim 1, characterized in that, Along the circumferential direction of the cylinder, the center line of the buffer groove is offset from the center line of the connecting hole.

7. The rotary compressor as described in claim 1, characterized in that, Screw holes and sliding plate grooves are provided on opposite sides of the air intake hole; The distance between the buffer groove and the sliding groove is greater than the distance between the buffer groove and the screw hole.

8. The compressor according to claim 7, characterized in that, The distance between the buffer groove and the screw hole is c, where c ≥ 1 mm.

9. The rotary compressor as described in claim 1, characterized in that, The angle between the central axis of the connecting hole and the end face of the cylinder is α, the total volume of the buffer groove is Vc, and the displacement of the rotary compressor is Ve, all satisfying: 45°≤α≤90°. .

10. A refrigeration device, characterized in that, Including the rotary compressor as described in any one of claims 1 to 9.

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