Oil injection ring, screw compressor and refrigeration equipment

Abstract

This utility model discloses an oil injection ring, a screw compressor, and a refrigeration device. The oil injection ring includes: an oil injection ring body, an annular oil reservoir on the outer periphery of the oil injection ring body, and multiple oil injection holes distributed on at least one end face of the oil injection ring body. The oil injection end of the oil injection hole is located on the end face of the oil injection ring body, and the oil inlet end is connected to the annular oil reservoir. The oil injection holes on the same end face are inclined circumferentially, and the oil injection direction rotates clockwise or counterclockwise around the axis of the oil injection ring body. This utility model utilizes multiple oil injection holes to spray oil clockwise or counterclockwise, forming a protective oil film on the rotor end face, sealing the end face gap, and reducing inter-tooth leakage; at the bearing, oil droplets evenly cover the balls, fully lubricating and cooling the bearing, and reducing bearing oil churning power consumption.

Description

Technical Field

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

[0002] A screw compressor uses male and female rotors that mesh within a casing with intake and exhaust ports to achieve the intake, compression, and exhaust processes, thereby changing the thermodynamic state of the compressed working fluid. Compression efficiency, a key indicator of a unit's energy efficiency, is directly affected by leakage channels formed between critical components during rotor compression—the higher the leakage rate, the lower the compression efficiency.

[0003] To ensure operational reliability, a safety clearance (i.e., exhaust end face clearance) must be reserved between the male and female rotors and the exhaust end bearing housing to avoid frictional damage between moving and non-moving parts. However, the balance of this clearance is extremely fragile: too large a clearance will significantly reduce compression efficiency and increase energy consumption; too small a clearance will easily lead to reliability risks such as end face scratches and jamming of moving parts.

[0004] In oil-injected screw compressors, the gas force on the male and female rotors is balanced by bearings on both sides, and the lubrication method is oil injection cooling. Although current technology extends the life of the bearings by completely immersing them in a large amount of oil, it leads to excessive circulating oil in the refrigeration system, deteriorating economic efficiency. At the same time, the surge in power consumption from bearing oil churning further increases the overall energy consumption of the machine.

[0005] While existing oil injection ring structures can achieve basic lubrication (such as the design of oil injection holes connected to the end face of the annular oil reservoir), the traditional oil injection holes are set along the axial direction, which causes the lubricating oil to concentrate and cover a specific area, making it impossible to form a uniform oil film around the bearing. In order to compensate for insufficient coverage, the amount of oil injected is increased, which instead leads to a surge in oil churning losses.

[0006] Therefore, how to design an injection ring that can improve oil supply efficiency and reduce the amount of circulating oil in the compressor is a technical problem that the industry urgently needs to solve. Utility Model Content

[0007] To address the shortcomings of low oil supply efficiency in existing technologies, this invention proposes an oil injection ring, a screw compressor, and a refrigeration device. The oil injection ring body features inclined oil injection holes on its end face. Multiple injection holes spray oil clockwise or counterclockwise, forming a protective oil film on the rotor end face, sealing the end face gap, and reducing inter-tooth leakage. Oil droplets evenly cover the bearing balls at the bearing location, fully lubricating and cooling the bearing, and reducing bearing oil churning power consumption.

[0008] The technical solution adopted in this utility model is to design an injection ring, including: an injection ring body, an annular oil reservoir on the outer periphery of the injection ring body, and a plurality of injection holes distributed on at least one end face of the injection ring body. The injection end of the injection hole is located on the end face of the injection ring body, and the oil inlet end is connected to the annular oil reservoir. The injection holes on the same end face are inclined in the circumferential direction, and the injection direction rotates clockwise or counterclockwise around the axis of the injection ring body.

[0009] In some embodiments of this utility model, the cross-sectional area of ​​the annular oil reservoir is greater than or equal to the sum of the cross-sectional areas of all the oil injection holes.

[0010] In some embodiments of this utility model, the diameter of the oil injection hole is ≤3mm, and the number of oil injection holes on the same end face is ≥8.

[0011] In some embodiments of this utility model, the inclination angle between the fuel injection hole and the axis of the fuel injection ring body is 20° to 50°.

[0012] In some embodiments of this utility model, both end faces of the fuel injection ring body are provided with fuel injection holes, namely a first fuel injection hole located on one end face and a second fuel injection hole located on the other end face; wherein, viewed from the same end face, the fuel injection direction of the first fuel injection hole and the fuel injection direction of the second fuel injection hole rotate in the same direction around the axis of the fuel injection ring body.

[0013] This utility model also proposes a screw compressor, including: a compression chamber and a bearing housing, the compression chamber is provided with two meshing rotors, the bearing housing is provided with a bearing assembly for supporting the ends of the rotors, the aforementioned oil injection ring is provided between the rotors and the bearing assembly, and the bearing housing is provided with an oil passage for supplying oil to an annular oil reservoir.

[0014] Furthermore, the injection ring rotates in the same direction as its corresponding rotor.

[0015] Furthermore, the exhaust side of the compression chamber is provided with an exhaust end bearing seat, the exhaust end bearing seat is provided with an exhaust end bearing assembly, and an exhaust oil injection ring is provided between the rotor and its exhaust end bearing assembly. Both end faces of the exhaust oil injection ring are provided with oil injection holes.

[0016] Furthermore, the suction side of the compression chamber is provided with a suction end bearing seat, and a suction end bearing assembly is provided inside the suction end bearing seat. A suction oil injection ring is provided between the rotor and its suction end bearing assembly, and an oil injection hole is provided on one end face of the suction oil injection ring facing the suction end bearing assembly.

[0017] This utility model also proposes a refrigeration device, including the aforementioned screw compressor.

[0018] Compared with the prior art, this utility model designs multiple oil injection holes with circumferentially inclined distribution on the end face of the oil injection ring body, so that the lubricating oil forms a clockwise or counterclockwise directional swirling spray, forming a uniform oil film on the surface of the rotating parts, effectively improving the oil supply efficiency.

[0019] Based on this, the oil injection ring is applied in screw compressors, especially on the exhaust side of the screw compressor. The oil injection ring is installed between the rotor and the exhaust end bearing assembly. The oil injection ring has oil injection holes on both end faces, generating a continuous dynamic oil film on the exhaust end face of the rotor. This effectively seals the end face gap between the male and female rotors and the bearing housing, significantly reducing the leakage of the working fluid in the compression chamber. At the same time, it achieves uniform dispersion and coverage of oil droplets in the bearing lubrication area, forming a fully enclosed oil film on the surface of the ball bearings. While ensuring the cooling and lubrication effect of the bearing, it greatly reduces the energy dissipation caused by oil turbulence. Attached Figure Description

[0020] The present invention will now be described in detail with reference to the embodiments and accompanying drawings, wherein:

[0021] Figure 1 This is a three-dimensional schematic diagram of the bidirectional oil injection ring of this utility model;

[0022] Figure 2 This is an enlarged schematic diagram of the oil injection hole of this utility model;

[0023] Figure 3 This is a three-dimensional schematic diagram of the unidirectional oil injection ring of this utility model;

[0024] Figure 4 This is a cross-sectional schematic diagram of the screw compressor of this utility model;

[0025] Figure 5 This is a schematic diagram of the installation of the oil injection ring of this utility model; Attached image description:

[0027] 1. Fuel injection ring;

[0028] 11. Fuel injection ring body;

[0029] 12. Annular oil storage tank;

[0030] 13. Fuel injector hole;

[0031] 131. Fuel injection end;

[0032] 132. Oil inlet end;

[0033] 2. Screw compressor;

[0034] 21. Compression chamber;

[0035] 22. Bearing housing;

[0036] 221. Oil circuit;

[0037] 23. Rotor;

[0038] 24. Bearing assembly. Detailed Implementation

[0039] To make the technical problem to be solved, the technical solution, and the beneficial effects of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this utility model and are not intended to limit this utility model.

[0040] like Figures 1 to 3 As shown, the oil injection ring proposed in this utility model is applicable to compressors, including but not limited to screw compressors. Specifically, the oil injection ring 1 includes: an oil injection ring body 11, an annular oil reservoir 12, and a plurality of oil injection holes 13. The outer periphery of the oil injection ring body 11 is provided with a recessed portion to form an annular oil reservoir 12. The oil injection ring body 11 has a plurality of oil injection holes 13 distributed on at least one end face. One end of the oil injection hole 13 is an oil injection end 131, and the other end is an oil inlet end 132. The oil injection end 131 is located on the end face of the oil injection ring body 11, and the oil inlet end 132 is connected to the annular oil reservoir 12. The oil in the annular oil reservoir 12 enters the oil injection hole 13 from the oil inlet end 132, and then is sprayed outward from the oil injection end 131 of the oil injection hole 13.

[0041] The oil injection holes 13 on the same end face are inclined around the circumference of the oil injection ring body 11. The oil injection direction of the oil injection holes 13 rotates clockwise around the axis of the oil injection ring body 11, that is, the oil injection rotation direction of the oil injection holes 13 is clockwise, or the oil injection direction of the oil injection holes 13 rotates counterclockwise around the oil injection ring body 11, that is, the oil injection rotation direction of the oil injection holes 13 is counterclockwise, so that the lubricating oil forms a directional swirling spray and forms a uniform oil film on the surface of the rotating parts to improve the oil supply efficiency.

[0042] For example, if there is working fluid leakage on one end face of the oil injection ring 1, an oil injection hole 13 is designed on that end face. The lubricating oil injected by directional swirl is used to generate a continuous dynamic oil film on the rotor end face, which effectively seals the end face gap between the male and female rotors and the bearing housing, and significantly reduces the working fluid leakage in the compression chamber.

[0043] For example, if there is a bearing lubrication requirement on one side of the oil injection ring 1, an oil injection hole 13 is designed on this side. The lubricating oil is sprayed in a directional swirling manner to achieve uniform dispersion and coverage of oil droplets in the bearing lubrication area, so that a fully wrapped oil film is formed on the surface of the ball. Under the premise of ensuring the cooling and lubrication effect of the bearing, the energy dissipation caused by the turbulent flow of oil is greatly reduced.

[0044] For example, if there is working fluid leakage on one end face of the oil injection ring 1 and bearing lubrication needs on the other end face, then oil injection holes 13 are designed on both end faces of the oil injection ring 1. The oil injection ring 1 sprays oil in both directions, which can effectively seal the end face gap between the male and female rotors and the bearing housing, significantly reduce the working fluid leakage in the compression chamber, and achieve uniform dispersion and coverage of oil droplets in the bearing lubrication area, reducing the energy dissipation caused by oil turbulence.

[0045] In some embodiments of this utility model, the cross-sectional area of ​​the annular oil reservoir 12 is greater than or equal to the sum of the cross-sectional areas of all the oil injection holes 13. External lubricating oil continuously enters the annular oil reservoir 12 and then flows from the annular oil reservoir 12 to each oil injection hole 13. If the cross-sectional area of ​​the annular oil reservoir 12 is less than the sum of the cross-sectional areas of all the oil injection holes 13, a throttling effect is likely to occur—the oil forms turbulence in the flow channel, resulting in a decrease in the oil supply of the end oil injection hole and a reduction in the injection velocity, which in turn causes uneven distribution or even rupture of the oil film on the surface of the rotating component, affecting the oil supply efficiency of the oil injection ring 1. Conversely, if the cross-sectional area of ​​the annular oil reservoir 12 is greater than or equal to the sum of the cross-sectional areas of all the oil injection holes 13, it can ensure that the oil is transported smoothly in a laminar flow state, so that the oil volume of the oil injection hole 13 is sufficient, the flow rate of the oil injection hole 13 spraying outward is fast, forming a uniform and dense protective oil film, and the oil supply efficiency of the oil injection ring 1 is high.

[0046] Based on this, the preferred solution is that the diameter of the injection hole 13 is ≤3mm, the number of injection holes 13 on the same end face is ≥8, the smaller the diameter of the injection hole 13, the faster the outward flow rate of the oil, and the more injection holes 13 there are, the more uniform the oil is sprayed outward by the injection ring 1.

[0047] The injection performance is further enhanced through the coordinated design of the 13 injection holes' diameter and number. The reduced hole diameter significantly improves the injection kinetic energy, resulting in a substantial increase in lubricant penetration distance and a significant improvement in uniformity. Meanwhile, the multi-hole layout (≥8 holes per end face) achieves circumferential coverage without dead angles, significantly improving the oil film coverage on the bearing ball surface. The combination of these two features creates a "micro-droplet matrix" effect, achieving full ball lubrication under high-speed rotation conditions while reducing the intensity of oil turbulence.

[0048] In some embodiments of this invention, the inclination angle between the oil injection hole 13 and the axis of the oil injection ring body 11 is 20° to 50°. This design optimizes the lubricating oil injection trajectory through fluid dynamics principles, solving problems such as uneven coverage, high leakage rate, and low energy efficiency in traditional oil injection structures. The design of the inclined oil injection hole 13 essentially adjusts the lubricating oil injection path from axial (parallel to the axis) to a circumferential swirling flow mode.

[0049] When the tilt angle is controlled between 20° and 50°, the oil acquires a tangential velocity component, forming a spiral oil jet around the axis. Under centrifugal force, the oil accelerates, increasing the kinetic energy of the jet (according to Bernoulli's equation, the increase in kinetic energy is proportional to the square of the velocity), significantly increasing the penetration distance. For example, at an angle of 30°, the oil jet can cover a large radius bearing area; when the angle is less than 20°, the swirling flow is insufficient, resulting in weak oil jet penetration; when the angle exceeds 50°, the oil jet becomes excessively dispersed, leading to increased fluctuations in oil film thickness. The 20°–50° range ensures that the Reynolds number (Re) remains stable within the laminar flow range (Re < 2300), avoiding oil splashing and pressure fluctuations caused by turbulence, thereby maintaining the stability of the injection pressure.

[0050] Specifically applied to screw compressors, especially on the exhaust side, the swirling oil jet generated by the inclined oil injection hole 13 forms a continuous dynamic oil film on the exhaust end face of the male and female rotors, actively sealing the end face gap and suppressing the leakage of the working fluid in the compression chamber. The oil jet is evenly sprayed onto the surface of the bearing balls in a swirling manner, and the 20° to 50° inclination makes the oil mist distribution wider, increasing the oil film coverage of the bearing balls, eliminating dry friction points, and the swirling oil mist forms a vortex ring cooling zone, expanding the heat exchange area and extending the bearing life. Precise oil injection significantly reduces the amount of lubricating oil used and improves the energy efficiency (COP) of the refrigeration equipment.

[0051] The fuel injection ring 1 can be designed with fuel injection holes 13 on two end faces or one end face, depending on the application requirements. A ring with fuel injection holes 13 on two end faces is a bidirectional fuel injection ring, while a ring with fuel injection holes 13 on one end face is a unidirectional fuel injection ring. The structure of the two types of fuel injection rings 1 will be described in detail below.

[0052] The bidirectional fuel injection ring has a structure in which fuel injection holes 13 are provided on both end faces of the fuel injection ring body. These are a first fuel injection hole 13_1 located on one end face and a second fuel injection hole 13_2 located on the other end face. Viewed from the same end face, the fuel injection direction of the first fuel injection hole 13_1 and the fuel injection direction of the second fuel injection hole 13_2 rotate in the same direction around the axis of the fuel injection ring body 11. Figure 1 For example, a first oil injection hole 13_1 is opened on the right end face of the oil injection ring 1, rotating clockwise (viewed from the right end face). The first oil injection hole 13_1 ejects small oil mist particles to the right, forming a clockwise spray through the oil path of the clockwise distributed first oil injection hole 13_1. A second oil injection hole 13_2 is opened on the left end face of the oil injection ring 1, rotating clockwise (viewed from the right end face). The second oil injection hole 13_2 ejects small oil mist particles to the left, forming a clockwise spray through the oil path of the clockwise distributed second oil injection hole 13_2. By designing oil injection holes 13 on both sides of the oil injection ring 1, bidirectional oil injection is achieved, meeting the lubrication needs in both the left and right directions.

[0053] The one-way injection ring has an injection hole 13 on one end face of the injection ring body 11. Figure 3For example, a ring of injection holes 13, which rotate clockwise (viewed from the right side), are opened on the right end face of the injection ring 1. Small oil mist particles are ejected from the injection holes 13 to the right, forming a clockwise injection through the oil path of the clockwise distributed injection holes 13.

[0054] like Figure 4 , 5 As shown, this utility model also proposes a screw compressor 2 with the above-mentioned oil injection ring, including: a compression chamber 21 and a bearing housing 22. The compression chamber 21 is provided with two meshing rotors 23. The bearing housing 22 is provided with a bearing assembly 24 for supporting the ends of the rotors 23. The above-mentioned oil injection ring 1 is provided between the rotors 23 and the bearing assembly 24. The oil injection ring 1 is installed on the shaft section of the rotor end face. The bearing housing 22 is provided with an oil passage 221 for supplying oil to the annular oil reservoir. High-pressure lubricating oil is supplied into the annular oil reservoir 12 of the oil injection ring 1 through the oil passage 221 in the bearing housing 22, and then sprayed outward through the oil injection hole 13 to form a uniform oil film on the surface of the rotating parts, effectively improving the oil supply efficiency.

[0055] Based on this, as a preferred embodiment, the injection rotation direction of the injection ring 1 is the same as the rotation direction of its corresponding bearing assembly 24, so that the small oil mist ejected from the injection hole 13 can more smoothly cover the rotating parts and form a uniform and dense oil film. It should be understood that the two rotors are a male rotor and a female rotor, respectively. A main injection ring is provided between the male rotor and its bearing assembly, and a secondary injection ring is provided between the female rotor and its bearing assembly. Since the rotation directions of the male rotor and the female rotor are opposite, the injection rotation directions of the main injection ring and the secondary injection ring are opposite.

[0056] Specifically, the exhaust side of the compression chamber 21 is provided with an exhaust end bearing housing, and an exhaust end bearing assembly is provided inside the exhaust end bearing housing. The exhaust side shaft section of the rotor 23 is supported within the exhaust end bearing assembly. The intake side of the compression chamber 21 is provided with an intake end bearing housing, and an intake end bearing assembly is provided inside the intake end bearing housing. The intake side shaft section of the rotor 23 is supported within the intake end bearing assembly.

[0057] Because the male and female rotors mesh with each other, the two adjacent tooth slots represent two independent intake, compression, and exhaust processes, resulting in a certain pressure difference. For operational reliability, a certain gap is usually left between the rotor and the end face of the exhaust end bearing housing, called the exhaust end face gap (generally designed as...).

[0058] (0.04~0.10mm) Due to the presence of the exhaust end face gap, the working gas with a pressure difference between two adjacent tooth grooves leaks through the end face gap. Furthermore, screw compressors typically use oil immersion to lubricate and cool the bearings, preventing insufficient or uneven oil supply from causing bearing ball lubrication and cooling failure, thus reducing lifespan. While refrigeration oil provides viscous resistance to the bearing balls, the immersion method, while greatly ensuring reliable bearing operation, also further increases bearing power consumption.

[0059] For the exhaust side of the screw compressor 2, due to the defects of end face gap leakage and insufficient bearing oil supply efficiency, this utility model sets an exhaust oil injection ring between the rotor 23 and its exhaust end bearing assembly, and the two end faces of the exhaust oil injection ring are provided with oil injection holes 13.

[0060] by Figure 1 , 5 For example, high-pressure lubricating oil is supplied into the annular oil reservoir 12 of the oil injection ring 1 through the oil passage 221 inside the bearing housing 22. A second oil injection hole 13_2 is opened on the left end face of the oil injection ring 1, which rotates counterclockwise (viewed from the left end face). The second oil injection hole 13_2 ejects small oil mist particles to the left. Through the counterclockwise distributed oil passage of the second oil injection hole 13_2, a counterclockwise spray is formed, which is the same as the rotation direction of the male rotor. This allows for smoother entry into the gap of the exhaust end face, forming a small molecule oil film that fills the gap of the exhaust end face. This not only ensures reliable operation but also solves the leakage problem between adjacent tooth grooves and improves the compression insulation efficiency of the screw compressor 2.

[0061] A first oil injection hole 13_1 is opened on the right end face of the oil injection ring 1, pointing clockwise (viewed from the right end face). The first oil injection hole 13_1 ejects small oil mist particles to the right. The oil path of the clockwise distributed first oil injection hole 13_1 forms a clockwise spray, which is the same as the rotation direction of the male rotor and the same as the rotation direction of the exhaust end bearing assembly. The spray direction is directly aimed at the ball. The oil injection holes 13 on the oil injection ring 1 are evenly distributed around the circumference, which ensures that the oil distribution of the bearing ball is uniform, so that each ball can contact the lubricating oil, which greatly reduces the amount of lubricating oil supplied in the bearing cavity.

[0062] For the suction side of the screw compressor 2, when there is no end face leakage problem on the suction side, the only defect on the suction side is insufficient bearing oil supply efficiency. In this invention, a suction oil injection ring is set between the rotor 23 and its suction end bearing assembly, and the suction oil injection ring is provided with an oil injection hole 13 on one end face facing the suction end bearing assembly.

[0063] by Figure 3 , 5For example, high-pressure lubricating oil is supplied into the annular oil reservoir 12 of the oil injection ring 1 through the oil passage 221 inside the bearing housing 22. A ring of clockwise pointing (viewed from the right end face) oil injection holes 13 are opened on the right end face of the oil injection ring 1. Small oil mist particles are ejected from the oil injection holes 13 to the right. The clockwise distribution of the oil passages through the oil injection holes 13 forms a clockwise spray, which is the same as the rotation direction of the male rotor and the same as the rotation direction of the intake bearing assembly. The spray direction is directly aimed at the ball. The oil injection holes on the oil injection ring 1 are evenly distributed around the circumference, which ensures that the oil distribution of the bearing balls is uniform, so that each ball can contact the lubricating oil, which greatly reduces the amount of lubricating oil supplied in the bearing cavity.

[0064] This utility model also proposes a refrigeration device, including the aforementioned screw compressor 2. From the perspective of overall machine use, due to the high oil supply efficiency of the oil injection ring 1, the amount of lubricating oil used in the system operation can be significantly reduced, improving the economic efficiency and environmental friendliness of the refrigeration device. At the same time, it reduces the power consumption of bearing oil churning, further improving the energy efficiency of the refrigeration device and making its operation more energy-saving.

[0065] It should be noted that the terminology used above is for describing specific embodiments only and is not intended to limit the exemplary embodiments according to this utility model. When the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof. The order of execution of actions, steps, etc., in the apparatus and methods shown in the specification and drawings can be implemented in any order unless a specific express order is specified, and as long as the output of the preceding process is not used in the subsequent process. Similar sequential terms used for ease of description do not imply that such an order must be followed.

[0066] Techniques, methods, and apparatus known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and apparatus should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0067] The above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. An oil spray ring comprising: The fuel injection ring body comprises an annular oil reservoir on the outer periphery of the fuel injection ring body and a plurality of fuel injection holes distributed on at least one end face of the fuel injection ring body, wherein the fuel injection end of the fuel injection hole is located on the end face of the fuel injection ring body and the fuel inlet end is connected to the annular oil reservoir; characterized in that the fuel injection holes on the same end face are inclined in the circumferential direction and the fuel injection direction rotates clockwise or counterclockwise around the axis of the fuel injection ring body.

2. The oil control ring of claim 1, wherein The cross-sectional area of ​​the annular oil reservoir is greater than or equal to the sum of the cross-sectional areas of all the oil injection holes.

3. The oil control ring of claim 2, wherein The diameter of the injection hole is ≤ 3mm, and the number of oil injection holes on the same end face is ≥8.

4. The oil control ring of claim 1, wherein The inclination angle between the injection hole and the axis of the injection ring body is 20° to 50°.

5. The fuel injection ring according to any one of claims 1 to 4, characterized in that, The two end faces of the oil injection ring body are provided with the oil injection holes, namely a first oil injection hole located on one end face and a second oil injection hole located on the other end face; Viewed from the same end face, the injection direction of the first injection hole and the injection direction of the second injection hole rotate in the same direction around the axis of the injection ring body.

6. Screw compressor comprising: The compression chamber and bearing housing are provided. The compression chamber is provided with two meshing rotors, and the bearing housing is provided with a bearing assembly for supporting the ends of the rotors. The characteristic feature is that an oil injection ring as described in any one of claims 1 to 5 is provided between the rotors and the bearing assembly, and an oil passage for supplying oil to the annular oil reservoir is provided in the bearing housing.

7. Screw compressor according to claim 6, characterized in that The direction of the oil injection ring's rotation is the same as the direction of its corresponding rotor's rotation.

8. Screw compressor according to claim 6, characterized in that The exhaust side of the compression chamber is provided with an exhaust end bearing seat, and an exhaust end bearing assembly is provided inside the exhaust end bearing seat. An exhaust oil injection ring is provided between the rotor and its exhaust end bearing assembly, and the two end faces of the exhaust oil injection ring are provided with the oil injection holes.

9. Screw compressor according to claim 6, characterized in that The suction side of the compression chamber is provided with a suction end bearing seat, and a suction end bearing assembly is provided inside the suction end bearing seat. A suction oil injection ring is provided between the rotor and its suction end bearing assembly, and the suction oil injection ring is provided with an oil injection hole on one end face facing the suction end bearing assembly.

10. A refrigeration appliance characterised in that, The refrigeration equipment includes the screw compressor as described in any one of claims 6 to 9.

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