Compressor and compression mechanism thereof

Abstract

The application discloses a real compressor and a compression mechanism thereof. The compression mechanism for the compressor comprises a cylinder, a rolling piston and a sliding vane. The cylinder is provided with an air suction passage; the rolling piston is arranged in the cylinder; and the sliding vane is matched with the rolling piston to form a low-pressure cavity and a high-pressure cavity in the cylinder. The air suction passage comprises a main passage and at least two branch passages, the at least two branch passages are communicated with the main passage and extend in opposite directions, the main passage is provided with an air inlet, and the at least two branch passages are communicated with the same low-pressure cavity. The compression mechanism for the compressor according to the embodiment of the application can weaken backflow.

Description

Technical Field

[0001] This invention relates to the field of compression technology, and in particular to a compression mechanism for a compressor and a compressor having the compression mechanism. Background Technology

[0002] As people pursue a comfortable life, the power consumption of air conditioners for cooling in summer and heating in winter has always been relatively high. Therefore, high-efficiency air conditioners are the pursuit of research institutes and HVAC companies. As the heart of the air conditioner, improving the efficiency of the compressor is the key to improving the overall efficiency of the air conditioner.

[0003] In compressors, backflow is a problem, especially in multi-stage compressors, where it is significant and greatly affects the compressor's operating efficiency, resulting in energy loss. Summary of the Invention

[0004] One object of the present invention is to provide a compression mechanism for a compressor that can reduce backflow.

[0005] Another object of the present invention is to provide a compressor.

[0006] A compression mechanism for a compressor according to an embodiment of the present invention includes: a cylinder, a rolling piston, and a sliding vane. The cylinder has an intake passage; the rolling piston is disposed within the cylinder; the sliding vane cooperates with the rolling piston to form a low-pressure chamber and a high-pressure chamber within the cylinder, wherein the intake passage includes a main passage and at least two branch passages, the at least two branch passages being connected to the main passage and extending in opposite directions, the main passage having an inlet, and the at least two branch passages being connected to the same low-pressure chamber.

[0007] The compression mechanism for a compressor according to an embodiment of the present invention can reduce backflow.

[0008] In addition, the compression mechanism for a compressor according to the above embodiments of the present invention may also have the following additional technical features:

[0009] In some embodiments, each of the diversion channels includes an inlet section and an outlet section that are interconnected, the inlet section connecting to the main channel and the outlet section connecting to the low-pressure chamber, the radial dimension of the outlet section being increased relative to the inlet section.

[0010] In some embodiments, an annular stepped structure is formed between the exit periphery of the inlet section and the inlet periphery of the outlet section.

[0011] In some embodiments, the outlet of the outlet section extends tangentially along the outlet section to communicate with the low-pressure chamber.

[0012] In some embodiments, the cylinder includes a cylinder body and an end cap, the cylinder body has a through hole extending in a vertical direction, the upper and lower ends of the cylinder body are closed by the end cap, the rolling piston is disposed in the through hole, and the intake channel is disposed on the wall of the cylinder body.

[0013] In some embodiments, the main channel of the intake channel extends along an axis perpendicular to the through hole, the intake channel includes two branch channels extending in a vertical direction, and the two branch channels and the main channel of the intake channel are configured to form a "T" shape that penetrates the outer peripheral surface, upper end surface and lower end surface of the cylinder body.

[0014] In some embodiments, the cylinder includes a plurality of cylinder bodies arranged vertically, and adjacent cylinder bodies share a common end cap.

[0015] In some embodiments, the outlet of the main channel is provided with a tapered hole that gradually narrows along the air intake direction.

[0016] In some embodiments, a groove is provided at a position opposite to the outlet of the main channel.

[0017] In some embodiments, the groove is gradually recessed from the periphery to the center.

[0018] In some embodiments, the slides include at least two spaced apart along the direction surrounding the rolling piston, and the two slides respectively cooperate with the rolling piston to form a set of low-pressure chambers and a set of high-pressure chambers, and the intake channel includes a plurality of chambers corresponding one-to-one with the low-pressure chambers.

[0019] According to an embodiment of the present invention, a compressor includes: a housing, a compression mechanism, and a motor. The compression mechanism is disposed within the housing and is a compression mechanism as described above. The motor is disposed within the housing and is used to drive the rolling piston.

[0020] In some embodiments, the housing is provided with a plurality of compression mechanisms arranged along the axial direction of the drive shaft of the motor. Attached Figure Description

[0021] Figure 1 This is a longitudinal cross-sectional view of the compression mechanism of a rotary compressor in Embodiment 1 of the present invention.

[0022] Figure 2 This is a longitudinal cross-sectional view of the low-pressure gas circuit in the cylinder of implementation state 1.

[0023] Figure 3 This is a longitudinal cross-sectional view showing the details of the low-pressure gas circuit and the co-current gas in implementation state 1.

[0024] Figure 4 This is a plan view of the compression chamber and fluid elements in implementation state 1.

[0025] Figure 5 This is a plan view showing the details of the high-pressure gas flow and vortex grooves leaking into the low-pressure gas in implementation state 1.

[0026] Figure 6 This represents a longitudinal cross-sectional view of the gas flow recirculating in the low-pressure gas circuit in implementation state 1.

[0027] Figure 7 This is a longitudinal cross-sectional view showing the details of the low-pressure gas circuit and the countercurrent gas in implementation state 1.

[0028] Figure 8 This is a longitudinal cross-sectional view of the low-pressure gas circuit in embodiment 2 of the present invention.

[0029] Figure 9 This is a longitudinal cross-sectional view of the low-pressure gas circuit in implementation state 2.

[0030] Figure 10 This is a plan view of the compression mechanism of the cylinder compression chamber in embodiment 3 of the present invention.

[0031] Figure 11 This is a longitudinal cross-sectional view showing the details of the cylinder in the same implementation state 3.

[0032] Reference numerals: Motor 4, Compression mechanism 5, Rolling piston 14, Sliding vane 13, Groove 36c, Housing 2, Conical bore 37, Low-pressure chamber 11a, High-pressure chamber 11b, Crankshaft 8, Cylinder block 10, Compression chamber 11, Intake pipe 12, (Vortex type) Fluid element 33A, Inlet / outlet groove 33a, Rotating groove 34a, (Vortex type) Fluid element 33B, Inlet / outlet groove 33b, Rotating groove 34b, Cylindrical bore 36, Main bearing 40, Secondary bearing 45. Detailed Implementation

[0033] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0034] Combination Figures 1 to 11 According to an embodiment of the present invention, the compression mechanism 5 for a compressor includes: a cylinder, a rolling piston 14, and a sliding vane 13.

[0035] Specifically, the cylinder has an intake channel for introducing fluid into the cylinder. A rolling piston 14 is disposed inside the cylinder. A sliding vane 13 cooperates with the rolling piston 14 to form a low-pressure chamber 11a and a high-pressure chamber 11b inside the cylinder. The combination of the sliding vane 13 and the rolling piston 14 forms the low-pressure chamber 11a and the high-pressure chamber 11b. After the fluid enters the low-pressure chamber 11a, it is pressurized by the rolling piston 14 and then sent to the high-pressure chamber 11b.

[0036] The intake passage may include a main passage and at least two branch passages. The main passage is the passage connecting to external components. In the compressor, the main passage connects to the compressor inlet. The at least two branch passages are connected to the main passage and extend in opposite directions. The main passage has an air inlet, and the at least two branch passages are connected to the same low-pressure chamber 11a.

[0037] The compression mechanism 5 for the compressor according to an embodiment of the present invention can reduce backflow. When backflow occurs, the fluid will flow from the branch channel to the main channel. Since there are multiple branch channels, and the multiple branch channels eventually converge in the main channel, the kinetic energy of the fluid flowing back from the branch channels will cancel each other out, thereby reducing the intensity of backflow. In addition, the suction action of the compressor further reduces backflow, thereby reducing or even eliminating the problem of fluid backflow.

[0038] In some embodiments, to further reduce backflow, each diversion channel includes an inlet section and an outlet section that are interconnected, with the inlet section connecting to the main channel and the outlet section connecting to the low-pressure chamber 11a, and the radial dimension of the outlet section relative to the inlet section being increased.

[0039] In the embodiments described below, for ease of description, the outlet section is described as a rotating channel because if backflow occurs, the backflowing fluid will swirl in the outlet section, thereby reducing the energy of the backflowing fluid. Additionally, in the following embodiments, the outlet of the outlet section may be described as an inlet / outlet channel; that is, the rotating channel described below is the outlet section, and the inlet / outlet channel described below is the outlet of the outlet section.

[0040] In some embodiments, the inlet section is located at the center of the outlet section in the projection along the direction from the inlet section to the outlet section. During the backflow process, the backflowing fluid will form vortices in the outlet section, further reducing the backflow.

[0041] In other words, there is a ring-shaped stepped structure between the exit perimeter of the inlet section and the inlet perimeter of the outlet section, or the connection between the inlet section and the outlet section forms a ring-shaped stepped structure. That is to say, there is a gap between each point of the exit perimeter of the inlet section and the inlet perimeter of the outlet section.

[0042] In some embodiments, the outlet of the outlet section extends tangentially along the outlet section to connect to the low-pressure chamber 11a.

[0043] In some embodiments, the cylinder includes a cylinder body 10 and an end cap. The cylinder body 10 has a through hole extending in the vertical direction. The upper and lower ends of the cylinder body 10 are closed by the end cap. A rolling piston 14 is disposed in the through hole, and an air intake passage is disposed on the wall of the cylinder body 10.

[0044] In fact, the term "end cap" in this invention is a general term, and the main bearing and secondary bearing described below are both considered as end caps.

[0045] In some embodiments, the main channel of the intake channel extends along the axis perpendicular to the through hole, and the intake channel includes two branch channels extending in the vertical direction. The two branch channels and the main channel in the intake channel are configured to form a "T" shape that penetrates the outer peripheral surface, upper end surface and lower end surface of the cylinder body 10.

[0046] Among them, reference Figure 7 The cylindrical hole 36 is constructed from two flow channels, wherein the two sections of the cylindrical hole 36 located above and below the conical hole 3737 are each a flow channel.

[0047] In some embodiments, the cylinder includes a plurality of cylinder bodies 10 arranged vertically, and adjacent cylinder bodies 10 share a common end cap.

[0048] In some embodiments, the outlet of the main channel is provided with a tapered hole 37 that gradually decreases in the direction of air intake.

[0049] In some embodiments, a groove 36c is provided at a position opposite to the outlet of the main channel. When fluid enters from the main channel, it flows to the groove 36c, and under the guiding effect of the groove 36c, the fluid will be dispersed into the diversion channel.

[0050] In some embodiments, the groove 36c is gradually recessed in the direction from the periphery to the center.

[0051] In some embodiments, the slide 13 includes at least two slides spaced apart along the direction surrounding the rolling piston 14, and the two slides 13 cooperate with the rolling piston 14 to form a set of low-pressure chambers 11a and high-pressure chambers 11b, respectively, and the intake passage includes a plurality of chambers corresponding one-to-one with the low-pressure chambers 11a.

[0052] According to an embodiment of the present invention, the compressor includes: a housing 2, a compression mechanism 5 and a motor 4. The compression mechanism 5 is disposed inside the housing 2 and is the compression mechanism 5 described above. The motor 4 is disposed inside the housing 2 and is connected to a rolling piston 14. Specifically, the rolling piston 14 of the compression mechanism 5 is connected to a crankshaft, and the motor 4 is connected to the crankshaft. The power of the motor 4 is transmitted to the rolling piston 14 through the crankshaft.

[0053] In some embodiments, the housing 2 is provided with a plurality of compression mechanisms 5 arranged along the axial direction of the drive shaft of the motor 4.

[0054] Some specific embodiments of the present invention are described below with reference to the accompanying drawings.

[0055] In the compressor of the present invention, a motor and a compression mechanism driven by the motor are built into a sealed housing; a cylindrical compression chamber on the cylinder of the compression mechanism is connected to an intake passage; and the compressor is a rotary compressor having a fluid control element that increases the resistance of gas flowing back from the compression chamber to the intake passage relative to the resistance of gas flowing from the intake passage to the compression chamber.

[0056] The aforementioned fluid control element comprises a vortex-type fluid element consisting of a rotating groove with openings on both sides of the cylinder, an inlet / outlet groove with openings on these rotating grooves and the aforementioned compression chamber, and a bifurcated channel with an opening from the aforementioned intake channel to the center of the aforementioned rotating groove.

[0057] The aforementioned inlet / outlet slot is positioned adjacent to the sliding plate on the aforementioned cylinder.

[0058] In the aforementioned compression mechanism, the component parts connected to the two side planes of the aforementioned cylinder each have the aforementioned vortex-type fluid element.

[0059] The aforementioned component is either a bearing that slides with the crankshaft of the aforementioned compression mechanism or an intermediate plate that is connected to the plane of the aforementioned cylinder.

[0060] The intake passages of the two compression chambers, which are divided by a rolling piston and two sliding vane areas, formed by the cylinder described above, are respectively equipped with the aforementioned vortex-type fluid element.

[0061] A tapered hole with a smaller inner diameter is made at the outlet of the aforementioned intake channel, which is opened at the center of the aforementioned bifurcation channel, and a hole is made on the aforementioned bifurcation channel.

[0062] The aforementioned compression mechanism has at least two of the aforementioned cylinders.

[0063] Due to the re-expansion of the gaseous refrigerant leaking from the high-pressure chamber 11b to the low-pressure chamber 11a, the low-pressure gas will flow back from the low-pressure chamber 11a to the suction pipe 12, thus reducing the cooling capacity. Therefore, this application mentions a solution that can reduce the backflow.

[0064] The cylinder has cylindrical holes 36 branching off from the intake pipe 12 to both sides of the cylinder, and vortex-type fluid elements 33A and vortex-type fluid elements 33B with openings at the outlets of these cylindrical holes into the compression chamber 11. Due to the backflow prevention effect of these two fluid elements, the backflow of low-pressure gas generated from the inlet / outlet channels 33a and 33b connected to the low-pressure chamber 11a is greatly reduced.

[0065] This invention relates to improving the cooling capacity loss caused by the re-expansion of high-pressure gas leaking into the low-pressure side of the compression chamber by using a fluid control element (fluid element) provided in the low-pressure gas passage through an opening in the cylinder compression chamber of a rotary compressor to prevent backflow. The method involves equipping the low-pressure gas passage with a two-stage fluid element.

[0066] To address the shortcomings in the related technology, the United States experimented with adding a suction valve to the outlet of the suction port between 1968 and 1983. On the one hand, recent tests have reported an approximately 4% increase in cooling capacity by adding the suction valve.

[0067] However, there are two reasons why the suction valve on rotary compressors has not been put into practical use so far: (1) the reciprocating motion of the suction valve increases noise; (2) the long-term operation and absorption of liquid refrigerant will cause reliability problems such as damage to the suction valve.

[0068] The present invention is characterized by the fact that, in order to improve the weaknesses of the above-mentioned rotary compressor, it does not use an intake valve, but introduces fluid control (Fluidics System) through the application of two fluid elements.

[0069] In this invention:

[0070] 1. By incorporating fluid control in the intake circuit, freezing capacity can be improved by approximately 4%.

[0071] 2. Because fluid control uses fluid components with no moving parts, there are no reliability issues. Furthermore, it does not cause noise degradation.

[0072] 3. The selected fluid components are easy to manufacture and can be added to existing parts. Moreover, the cost of adding them is low.

[0073] 4. This invention can be widely applied to multi-cylinder rotary compressors, multi-stage rotary compressors, capacity-controlled rotary compressors, CO2 rotary compressors, etc.

[0074] The following describes some specific embodiments of the present invention with reference to the accompanying drawings.

[0075] Implementation Status 1:

[0076] Figure 1 The rotary cylinder compressor 1 represents the motor 4 and compression mechanism 5 fixed to the inner circumference of the sealed housing 2. The lubricating oil sealed into the bottom of the housing 2 is omitted.

[0077] The compression mechanism 5 includes a cylinder with a cylindrical compression chamber 11 welded to the inner circumference of the housing 2, a main bearing 40 and a secondary bearing 45 connected to its upper and lower planes, a crankshaft 8 that slides with these bearings, a rolling piston 14 driven by an eccentric shaft 8a to revolve around the inner circumference of the compression chamber 11, a sliding plate 13 that reciprocates against the rolling piston 14, and a sliding plate spring 13a that presses against the sliding plate 13. The main bearing 40 has an exhaust port 41 and an exhaust valve 41a, and the exhaust muffler 44 that discharges high-pressure gas has a muffler exhaust port 44a.

[0078] Figure 2 This indicates the intake passage for the gas refrigerant in the low-pressure chamber 11a that connects the cylinder and the compression chamber 11. Figure 3 This is a detailed diagram of the aforementioned intake channel, showing the absorption airflow. Figure 4 It means Figure 2 Plan view of the x-section.

[0079] exist Figure 2 and Figure 3 In the cylinder, the low-pressure gas flows into the intake pipe 12, which is connected between the reservoir 48 and the side of the cylinder, through the rolling piston that revolves due to the rotation of the crankshaft 8. The gas is evenly split in the upper and lower directions of the cylindrical hole 36, flowing into the rotating groove 34a from the cylindrical hole end 36a and into the rotating groove 34b from the cylindrical hole end 36b, and finally flowing into the low-pressure chamber 11a equally from the inlet and outlet grooves 33a and 33b.

[0080] Figure 3 In the intake pipe 12, the groove 36c (also called a disc groove) machined at the front end reduces the resistance loss of the high-speed gas discharged from the conical hole 37, ensuring accurate flow splitting to the cylindrical hole ends 36a and 36b. The conical hole 37 machined at the front end of the intake pipe 12 is a simple fluid element that reduces the flow rate of low-pressure gas returning from the low-pressure chamber 11a.

[0081] Figure 4 In the process, the low-pressure gas flowing from the intake pipe 12 to the low-pressure chamber 11a is compressed into high-pressure gas by the clockwise rotating rolling piston 14, and discharged from the exhaust port 41 to the exhaust muffler 44. Then, it passes through the muffler exhaust port 44a (… Figure 2 The fluid flows into the housing 2. Therefore, the pressure in the housing 2 and the pressure on the inner diameter of the rolling piston 14 are both high pressure.

[0082] Figure 4The upper right figure is a planar enlarged view of a vortex-type fluid element (Vortex Diode) with backflow prevention function, showing the rotating groove 34b constituting the vortex-type fluid element 33B and the cylindrical end 36b with a central opening therein. The width (W) of the side of the inlet / outlet groove 33b adjacent to the side of the slide 13 is approximately half that of a conventional circular low-pressure gas orifice.

[0083] Furthermore, in Embodiment 1, the cylinder has inlet / outlet grooves 33a and 33b on both sides, so its total opening area remains unchanged compared to the past. The above describes the stroke of the low-pressure airflow from the intake pipe 12 into the low-pressure chamber 11a. Additionally, in the following text, the vortex-type fluid element will be referred to as a fluid element.

[0084] Figure 5 This describes the flow of high-pressure gas leaking into the low-pressure chamber during the operation of a rotary compressor, illustrating the characteristics of Embodiment 1 and the necessity of the fluid element. Symbol A represents high-pressure gas leaking from the gap between the outer circumference of the rolling piston 14 and the inner circumference of the cylinder. Symbol B represents high-pressure gas leaking from the inner diameter of the high-pressure rolling piston 14 through its upper and lower sliding surfaces. Symbol C represents high-pressure gas leaking from the line contact surface between the front end of the vane 13 and the outer circumference of the rolling piston 14.

[0085] In other aspects, high-pressure gas also leaks out from the gaps between the main bearing 40 and the secondary bearing 45, which are connected to the side sliding surface of the slide vane 13 and the two side planes of the cylinder. The amount of this leaked gas is proportional to the pressure difference between the high-pressure gas (Pd) and the low-pressure gas (Ps), and the amount of re-expanded gas that expands into low-pressure gas in the low-pressure chamber 11a increases proportionally to the compression ratio of the high-pressure gas (Pd) and the low-pressure gas (Ps).

[0086] For example, the high and low pressure difference of R410A, a commonly used refrigerant in air conditioners, is 3 MPa, and its compression ratio is 3.0. In contrast, the high and low pressure difference of CO2 used in water heaters is 7 MPa. Compared to a compression ratio of 3.3, the leakage of high-pressure CO2 is greater, and the re-expansion loss of CO2 increases by approximately 10%. This re-expansion loss reduces the amount of gas drawn into the low-pressure chamber 11a. Because the temperature of the low-pressure gas rises significantly, the compressor's cooling capacity is reduced, thus lowering the compressor's coefficient of performance (COP).

[0087] Furthermore, if the rotation speed of motor 4 is 60 rpm, the low-pressure gas will alternate between forward and reverse flow 60 times per second, resulting in a high flow rate. Reverse flow reduces the amount of low-pressure gas generated from suction pipe 12, causing a loss of compressor cooling capacity. In Embodiment 1, as a means to prevent reverse flow, the aforementioned fluid element 33A and fluid element 33B are arranged on the upper and lower planes of the cylinder.

[0088] Figure 5In the process, the high-pressure gas leaking from the low-pressure chamber 11a undergoes re-expansion, increasing the pressure and temperature of the low-pressure gas, which then flows back into the inlet / outlet grooves 33b and 33a machined on both sides of the cylinder, and flows into the fluid elements 33B and 33A. At this time, because the returning low-pressure gas rotates at high speed along the inner circumference of the rotating groove 34b, the amount of gas that can flow from the cylindrical hole end 36a with the central opening to the cylindrical hole 36 is very small due to the centrifugal force effect.

[0089] Figure 6 This indicates the low-pressure airflow returning from the low-pressure chamber 11a to the intake pipe 12. Figure 7 Here is a detailed diagram. A portion (approximately 10%) of the low-pressure gas returning from the low-pressure chamber 11a to fluid elements 33A and 33B flows into the cylindrical bore 36 from the opposing cylindrical bore ends 36a and 36b. Because the same amount of returning gas impacts each other in the cylindrical bore 36, the velocity of the returning gas is greatly reduced.

[0090] Therefore, only a small portion (approximately 4%) of the low-pressure gas can flow back into the intake pipe 12 from the opening end, thus establishing a fluid control element with backflow prevention function. Furthermore, the cylindrical orifice 36 becomes an opposing fluid element with a second backflow prevention function.

[0091] In other words, the synergistic effect of the scroll-type fluid element (first fluid element) and the opposing fluid element (second fluid element) is similar to the suction valve on a reciprocating piston compressor, thus preventing backflow. Furthermore, although the suction pipe 12 is connected to the outer peripheral side of the cylinder in embodiment 1, it would not be obstructed if it were connected to the side of the main bearing 40 or the secondary bearing 45, or even if it were connected indirectly to the cylindrical bore 36 of the cylinder.

[0092] Implementation Status 2:

[0093] Implementation state 2 relates to the configuration and capacity expansion of fluid elements 33A and 33B. For example... Figure 8 As shown, in a design with a thin single cylinder, such as a single-cylinder rotary compressor or a multi-cylinder rotary compressor, these fluid elements can be configured on the main bearing 40 and the secondary bearing 45.

[0094] Figure 9 This is a means of increasing the volume of fluid elements 33A and 33B, and even expanding the low-pressure flow path from the intake pipe 12 to the low-pressure chamber 11a, thereby reducing the resistance to downstream gas flow. Because fluid elements 33A and 33B, which are respectively added to the main bearing 40 and the auxiliary bearing 45, are connected to the rotating grooves 34a and 34b on the cylinder, the volume of fluid elements 33A and 33B and the opening area of ​​the inlet / outlet grooves 33a and 33b are approximately doubled.

[0095] On the one hand, if the inner diameters of the cylindrical bore 30 and the suction pipe 12 are enlarged, the low-pressure gas flow path is expanded, which may allow its application in rotary compressors equipped with high-speed variable frequency motors such as 120 rpm. Furthermore, in Embodiment 2, the front ends of the inlet / outlet slots 33a and 33b cannot have openings in the inner diameter of the rolling piston 14. Moreover, in multi-cylinder rotary compressors, because an intermediate plate is provided between the two cylinders, one or both of the main bearing 40 and the auxiliary bearing 45 are equipped with fluid elements 33A and 33B on the intermediate plate.

[0096] Implementation Status 3:

[0097] Figure 10 This is a plan view of the compression mechanism 6 of a rotary compressor with 1 cylinder and 2 compression chambers. Figure 11 yes Figure 10 The x-section view. In Figure 10 In the cylinder 20, the central cylindrical cavity 21 is divided into compression chamber A 21a and compression chamber B 21b with equal displacement by a rolling piston 14 that revolves clockwise and opposing sliding vanes A 23 and B 24.

[0098] Similar to implementation state 1, fluid elements 33A and 33B, which have anti-backflow functions and are adjacent to the sides of slide A 23 and slide B 24 respectively, are connected to suction pipe A 22a and suction pipe B 22b. Furthermore, exhaust ports 43a and 43b, which are openings in the main bearing 40, are respectively located in compression chamber A 21a and compression chamber B 21b.

[0099] The low-pressure gas intake circuit in implementation state 3 is the same design as that in implementation state 1. However, since the total displacement of the two compression chambers mentioned above is almost equal to that in implementation state 1, the internal volume of the low-pressure gas intake circuit is designed to be smaller than that in implementation state 1.

[0100] As the rolling piston 14 rotates, low-pressure gas is drawn in, compressed, and discharged in compression chamber A 21a, and the same process occurs in compression chamber B 21b. Similar to embodiment 1, the expanding low-pressure gas leaking into the low-pressure chambers of each compression chamber improves the problem of low cooling capacity by preventing backflow through fluid elements 33B and 33A and the cylindrical orifice 36. Furthermore, compared to conventional suction ports, the cooling capacity is further improved because the opening width W of the inlet / outlet slots 33a and 33b is shorter.

[0101] As illustrated in embodiments 1, 2, and 3, the design that improves refrigeration capacity by arranging fluid elements in the suction circuit and re-expanding the high-pressure gas leaking into the low-pressure chamber is a common technology across rotary compressors. For example, it can be widely applied to rotary multi-cylinder compressors, multi-stage compressors, low-pressure compressors, and even cryogenic freezers or CO2 compressors.

[0102] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0103] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0104] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0105] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0106] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0107] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A compression mechanism for a compressor, characterized by, include: A cylinder having an air intake passage; A rolling piston, wherein the rolling piston is disposed inside the cylinder; A sliding vane, which cooperates with the rolling piston to form a low-pressure chamber and a high-pressure chamber within the cylinder. The intake channel includes a main channel and at least two branch channels. The at least two branch channels are connected to the main channel and extend in opposite directions. The main channel has an air inlet. The at least two branch channels are connected to the same low-pressure chamber. A groove is provided at a position opposite to the outlet of the main channel. The outlet of the main channel is provided with a tapered hole that gradually narrows along the intake direction.

2. The compression mechanism for a compressor according to claim 1, characterized by, Each of the diversion channels includes an inlet section and an outlet section that are interconnected, the inlet section connecting to the main channel and the outlet section connecting to the low-pressure chamber, the radial dimension of the outlet section being increased relative to the inlet section.

3. The compression mechanism for a compressor according to claim 2, characterized by, A ring-shaped stepped structure is formed between the periphery of the inlet section and the periphery of the outlet section.

4. The compression mechanism for a compressor according to claim 3, characterized by, The outlet of the outlet section extends tangentially along the outlet section and connects to the low-pressure chamber.

5. The compression mechanism for a compressor according to any one of claims 1 to 4, characterized in that, The cylinder includes a cylinder body and an end cap. The cylinder body has a through hole extending in the vertical direction. The upper and lower ends of the cylinder body are closed by the end cap. The rolling piston is disposed in the through hole, and the intake channel is disposed on the wall of the cylinder body.

6. The compression mechanism for a compressor according to claim 5, wherein The main channel of the intake channel extends along the axis perpendicular to the through hole. The intake channel includes two branch channels extending in the vertical direction. The two branch channels and the main channel of the intake channel are configured to form a "T" shape that penetrates the outer peripheral surface, upper end surface and lower end surface of the cylinder body.

7. The compression mechanism for a compressor according to claim 5, wherein The cylinder includes a plurality of cylinder bodies arranged vertically, and two adjacent cylinder bodies share a common end cap.

8. The compression mechanism for a compressor of claim 1, wherein, The groove gradually indents from the periphery to the center.

9. The compression mechanism for a compressor of claim 1, wherein, The sliding vanes include at least two arranged at intervals along the direction surrounding the rolling piston, and the two sliding vanes respectively cooperate with the rolling piston to form a set of low-pressure chambers and a set of high-pressure chambers, and the intake channel includes a plurality of chambers corresponding one-to-one with the low-pressure chambers.

10. A compressor characterized by, include: case; A compression mechanism, wherein the compression mechanism is disposed within the housing, and the compression mechanism is the compression mechanism according to any one of claims 1-9; An electric motor is disposed within the housing and is used to drive the rolling piston.

11. The compressor of claim 10, wherein, The housing contains a plurality of compression mechanisms arranged along the axial direction of the drive shaft of the motor.

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