A CO2 scroll compressor with atomized oil injection for large pressure difference

Abstract

The present invention discloses an atomizing oil-spraying CO2 scroll compressor for large pressure difference working conditions, which relates to the field of compressor technology and includes a cylinder, a lower end cover and a static scroll. The lower end cover is connected to the cylinder by bolts, and a first annular sealing groove is provided on the surface where the lower end cover and the cylinder contact each other. The static scroll is connected to the cylinder by bolts, and a second annular sealing groove is provided on the surface where the static scroll and the cylinder contact each other. The static scroll is located above the cylinder, and the lower end cover is located below the cylinder. The static scroll includes an end plate, an involute vortex body and a swirl cone straight nozzle. The involute vortex body consists of a sealing groove and a waist-shaped exhaust port, and nozzles are symmetrically provided on the end plate. The present invention adopts the above-mentioned atomizing oil-spraying CO2 scroll compressor for large pressure difference working conditions, which can not only reduce the superheat of the refrigerant and form an oil film in the leakage channel, but also reduce the amount of refrigerant leakage, thereby reducing the exhaust temperature and ensuring the reliable and efficient operation of the scroll compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, in particular to an atomizing oil-injection CO2 scroll compressor under large pressure difference working conditions. Background Art

[0002] High-efficiency refrigeration technology, refrigerant substitution, promotion of heat pump technology and utilization of renewable energy are the technical directions for my country's refrigeration industry to achieve high-quality development. HVAC systems consume a lot of energy during operation. The first three generations of refrigerants, CFCs, HCFCs and HFCs, which are currently widely used, will also cause two major environmental problems, ozone layer depletion and global warming, after leakage. After my country officially approved the Montreal Protocol (Kigali Amendment) in 2021, the fourth-generation refrigerants composed of HCs, HFOs and natural refrigerants have become a hot topic and application direction in the refrigeration industry. The natural refrigerant CO2 has an ozone depletion index (ODP) value and a global warming index (GWP) value of 0. It is safe and non-toxic, non-flammable, non-explosive, has a large cooling capacity per unit volume, low kinematic viscosity, and good heat transfer characteristics. It has unique advantages and may become the ultimate substitute for refrigerants.

[0003] Compared to compressors using refrigerants like R134a and R410A, CO2 compressors feature a lower pressure ratio, higher pressure differential, lower volumetric flow rate, and higher operating pressure. Their suction pressure is 3-5 MPa, their discharge pressure is 10-12 MPa, and their suction-discharge pressure differential is 5-9 MPa, reducing the compressor's volume by two-thirds. Due to the lower viscosity of CO2 in the supercritical state, leakage during compression increases significantly under the same clearance conditions. Therefore, for CO2 scroll compressors operating under high pressure differential conditions, the small dimensions make scroll profile machining difficult, and the large pressure differential across the leakage path makes dynamic sealing even more challenging. Reliable and efficient operation of scroll compressors requires significant consideration for leakage reduction. For these reasons, to address the technical challenges presented by refrigerant substitution while ensuring reliable and efficient operation of scroll compressors operating under high pressure differential conditions, an oil injection system must be developed. While ensuring adequate lubrication of the scroll compressor's internal friction pairs, an oil film forms within the leakage gap during compression, minimizing refrigerant leakage and ensuring reliable and efficient compressor operation. Summary of the Invention

[0004] The purpose of the present invention is to provide an atomized oil-injected CO2 scroll compressor operating under large pressure difference conditions, thereby reducing the exhaust temperature and ensuring reliable and efficient operation of the scroll compressor.

[0005] The present invention provides an atomizing oil-injected CO2 scroll compressor for large pressure difference working conditions, comprising a cylinder, a lower end cover and a static scroll, the lower end cover being connected to the cylinder by bolts, a first annular sealing groove being provided on the contact surface of the lower end cover and the cylinder, the static scroll being connected to the cylinder by bolts, a second annular sealing groove being provided on the contact surface of the static scroll and the cylinder, the static scroll being located above the cylinder, and the lower end cover being located below the cylinder, the static scroll comprising an end plate, an involute vortex body and a swirl cone straight nozzle, the involute vortex body being composed of a sealing groove and a waist-shaped exhaust port, and nozzles being symmetrically provided on the end plate.

[0006] Preferably, a lower bearing seat and a main shaft are provided in the cylinder, an air intake port, an oil outlet pipe, and a main shaft oil return pipe are provided in the cavity formed between the lower bearing seat and the lower end cover, and the lower part of the main shaft oil return pipe is a lubricating oil pool;

[0007] The main shaft is respectively equipped with a main balance block and a secondary balance block, an oil supply passage is opened inside the main shaft, a motor rotor is arranged on the main shaft, a stator corresponding to the motor rotor is arranged in a cylinder, and a frame is fixed at the upper end of the stator in the cylinder.

[0008] Preferably, a lubricating oil pump that rotates with the rotation of the main shaft is concentrically mounted on the lower end of the lower bearing seat through a lubricating oil pump seat, and the lubricating oil pump is placed in a lubricating oil pool;

[0009] The ball anti-rotation mechanism and the movable scroll are installed in sequence along the axial direction in the space formed between the frame and the static scroll. A main bearing is provided between the main shaft and the frame, and a waist-shaped exhaust hole is opened on the top of the static scroll.

[0010] Preferably, the lubricating oil pressurized by the lubricating oil pump flows from the oil outlet pipe into the P1P2 pipeline of the fuel injection control system, and the lubricating oil is divided into two pipelines, P2P3 pipeline and P2P4 pipeline in the oil circuit block. The P2P3 pipeline is connected to the spindle oil return pipe, and the lubricating oil in the P2P4 pipeline is divided into two pipelines, P4P5 pipeline and P4P6 pipeline in the oil circuit block.

[0011] Preferably, eight bolt holes are provided on the static scroll end plate, and a positioning pin hole is also provided on the static scroll end plate.

[0012] Preferably, swirl chambers are symmetrically provided on the top surface of the static scroll end plate, and an annular sealing groove is also provided on the top surface of the static scroll end plate.

[0013] Preferably, the diameter D of the swirl chamber is 2 mm, the swirl core height l0 is 1 mm, the inner cone angle α is 120°, and the nozzle diameter d is 0.6 mm.

[0014] Therefore, the present invention adopts the above-mentioned atomized oil-spraying CO2 scroll compressor with a large pressure difference working condition, and divides the lubricating oil into two paths. One path lubricates the friction pairs (eccentric bearings, main bearings and auxiliary bearings) inside the compressor, and the other path is atomized by the swirl cone straight nozzle symmetrically opened on the static scroll disk and then sprayed into the suction chamber. The use of a spiral groove core makes it easier to achieve rapid atomization of the lubricating oil. The atomized lubricating oil is sprayed into the suction chamber and fully mixed with the refrigerant, which can not only reduce the superheat of the refrigerant and form an oil film in the leakage channel, but also reduce the amount of refrigerant leakage, thereby reducing the exhaust temperature and ensuring the reliable and efficient operation of the scroll compressor.

[0015] The technical solution of the present invention is further described in detail below through the accompanying drawings and embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 This is an overall longitudinal sectional view of an atomizing oil-injected CO2 scroll compressor operating under large pressure differential conditions according to the present invention;

[0017] Figure 2 The present invention provides an oil injection quantity control system for an atomized oil injection CO2 scroll compressor under large pressure difference working conditions;

[0018] Figure 3 A bottom view of the stationary scroll of an atomized oil-injected CO2 scroll compressor operating under large pressure differential conditions according to the present invention;

[0019] Figure 4 A top view of the stationary scroll of an atomized oil-injected CO2 scroll compressor operating under large pressure differential conditions according to the present invention;

[0020] Figure 5 A cross-sectional view and a partially enlarged view of the stationary scroll along the AA direction of an atomized oil-injected CO2 scroll compressor operating under large pressure differential conditions according to the present invention;

[0021] Figure 6 This is a schematic diagram of the core structure of an atomizing oil-injected CO2 scroll compressor operating under large pressure difference conditions according to the present invention.

[0022] Reference numerals

[0023] 1. Lower end cover; 2. Cylinder; 2a. First annular sealing groove; 2b. Second annular sealing groove; 3a. Motor stator; 3b. Motor rotor; 4. Frame; 5. Ball anti-rotation mechanism; 6. Main shaft; 7. Eccentric bearing; 8. Main bearing; 9. Auxiliary bearing; 10. Main balance block; 11. Auxiliary balance block; 12. Orbiting scroll; 13. Stationary scroll; 14. Lower bearing seat; 15. Lubricating oil pump; 16. Lubricating oil pump seat; 17. Lubricating oil reservoir; 18. Inlet port; 19. Key; 20. Oil outlet pipe; 21. Main shaft oil return pipe; 22. Fuel injection control system; 221. Oil manifold block; 222. Needle valve; 223. Sight glass; 224. Ball valve; 225. High-pressure pressure gauge; 226. Temperature gauge ; 227, heat exchanger; 228, flow meter; 229, swirl core; 229a, first straight groove; 229b, second straight groove; 229c, first spiral groove; 229d, second spiral groove; 131, static vortex end plate; 132, involute vortex body; 133, involute sealing groove; 134, waist-shaped exhaust hole; 135, bolt hole; 136a, first positioning pin hole; 136b, second positioning pin hole; 137, exhaust pipe annular sealing groove; 138a, first swirl chamber; 138b, second swirl chamber; 139a, first nozzle; 139b, second nozzle; 14a, refrigerant gas flow through hole; 14b, first axial oil return through hole; 16a, second axial oil return through hole. DETAILED DESCRIPTION

[0024] The technical solution of the present invention is further described below with reference to the accompanying drawings and embodiments.

[0025] Unless otherwise defined, technical or scientific terms used in the present invention shall have the same meaning as commonly understood by one of ordinary skill in the art to which the present invention belongs.

[0026] The words "first", "second" and similar terms used in the present invention do not indicate any order, quantity or importance, but are only used to distinguish different components. Words such as "include" or "comprise" mean that the elements or objects preceding the word include the elements or objects listed after the word and their equivalents, without excluding other elements or objects. Words such as "connect" or "connected" are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "Up", "down", "left", "right" and the like are only used to indicate relative position relationships. When the absolute position of the object being described changes, the relative position relationship may also change accordingly.

[0027] Example 1

[0028] like Figure 1-6As shown, the present invention discloses an atomized oil-injected CO2 scroll compressor for high-pressure differential operation, comprising a cylinder 2, a lower end cover 1, and a stationary scroll 13. The lower end cover 1 is bolted to the cylinder 2, and a first annular sealing groove 2a is provided on the contact surface between the lower end cover 1 and the cylinder 2. The stationary scroll 13 is also bolted to the cylinder 2, and a second annular sealing groove 2b is provided on the contact surface between the stationary scroll 13 and the cylinder 2 to prevent compressor suction and lubricating oil from leaking into the atmosphere. The stationary scroll 13 is located above the cylinder 2, and the lower end cover 1 is located below the cylinder 2.

[0029] The cavity formed between the lower bearing seat 14 and the lower end cover 1 is equipped with an air intake 18, an oil outlet pipe 20, and a main shaft oil return pipe 21. The lower portion of the cavity contains a lubricating oil pool 17. A lubricating oil pump 15, which rotates with the main shaft 6, is concentrically mounted at the lower end of the lower bearing seat 14 via a lubricating oil pump seat 16. The lubricating oil pump 15 is housed in the lubricating oil pool 17. The ball anti-rotation mechanism 5 and the orbiting scroll 12 are sequentially mounted along the axis in the space formed between the frame 4 and the stationary scroll 13. A main bearing 8 is disposed between the main shaft 6 and the frame 4. A waist-shaped exhaust hole 134 is provided at the top of the stationary scroll 13.

[0030] The lubricating oil pressurized by the lubricating oil pump 15 flows from the oil outlet pipe 20 into the P1P2 pipeline of the oil injection control system 22. The lubricating oil is divided into two pipelines, P2P3 and P2P4, in the oil circuit block 221a. The P2P3 pipeline is connected to the main shaft return oil pipe 21. This part of the lubricating oil is mainly used to lubricate the friction pair eccentric bearings, main bearings and auxiliary bearings inside the scroll compressor. The lubricating oil in the P2P4 pipeline is divided into two pipelines, P4P5 and P4P6, in the oil circuit block 221b. This part of the lubricating oil is atomized by the nozzle opened on the fixed scroll 13 and then sprayed into the suction chamber of the scroll compressor. During the compression process, the lubricating oil can form an oil film in the leakage channel between the movable scroll 12 and the fixed scroll 13 to reduce the amount of refrigerant leakage. In order to accurately measure and control the amount of oil injection, a regulating valve 222a and a flow meter 228 are installed in the P2P4 pipeline. To accurately measure and control the injection temperature, a heat exchanger 227 is installed in the P2P4 line, and a temperature gauge 226 is installed in the P4P5 line. When ball valve 224 is fully closed, the suction chamber injection passage P2P4 is completely disconnected. By adjusting the opening of regulating valve 222b, the minimum oil supply to the friction pair inside the compressor is maintained.

[0031] In order to make the fuel injection control system 22 reflect the state of the lubricating oil more clearly, some auxiliary equipment has been added. Sight glasses 223a and 223b are used to observe the flow state of the lubricating oil. The ball valve 224 is in the fully open and fully closed states. The high-pressure pressure gauge 225a is used to measure the inlet pressure of the lubricating oil pipeline. The high-pressure pressure gauges 225b, 225c and 225d are used to measure the pressure of the lubricating oil branch. The pressure difference between the high-pressure pressure gauges 225a and 225d is used to determine whether there is a blockage in the fuel injection control system 22 pipeline. The air intake 18 is installed on the cylinder 2 and is located in the annular space formed by the lower bearing seat 14 and the lower end cover 1. The lower bearing seat 14 is installed on the lower end of the cylinder 2 and is provided with a refrigerant gas flow through hole 14a and an axial oil return through hole 14b. The auxiliary bearing 9 is installed concentrically with the lower bearing seat 14. Reference numeral 15 denotes a lubricating oil pump, which is placed in the lubricating oil pool 17. The main shaft of the oil pump is connected to the main shaft 6 via a key 9. The rotation of the main shaft 6 drives the rotation of the lubricating oil pump 15, providing power for the forced circulation of the lubricating oil. The motor 3 is composed of a stator 3a and a rotor 3b. The stator 3a is pressed into the cylinder 2 through a shrink-fit process. The rotor 3b is interference-fitted with the main shaft 6 and is installed in the middle of the main shaft 6. The main balance block 10 and the secondary balance block 11, which have undergone secondary balancing design for the dynamics of the scroll compressor, are respectively installed on the main shaft 6 and are located on both sides of the rotor 3b. The main bearing 21 is installed between the frame 4 and the main shaft 6 and is located at the bottom of the frame 4. 6b is the eccentric part of the upper part of the main shaft 6, i.e., the crank pin, with an eccentric bearing 7 installed on its outer side. A ball anti-rotation mechanism 5 is installed between the frame 4 and the movable scroll 12, which enables the horizontal rotation of the movable scroll. The involute scroll of the orbiting scroll meshes with the involute scroll 132 of the stationary scroll, forming multiple pairs of crescent-shaped suction, compression, and exhaust cavities. Waist-shaped exhaust holes 134 not only increase the structural strength of the tooth tips and maximize exhaust space utilization, but also minimize exhaust losses and airflow pulsation. High-temperature, high-pressure refrigerant gas flows through the waist-shaped exhaust holes into the refrigeration system cycle.

[0032] The flow process of the refrigerant inside the compressor is as follows: First, the low-temperature and low-pressure refrigerant gas from the evaporator enters the lower area of ​​the cylinder 2 through the intake port 18. Secondly, it passes through the axial through hole 14a opened on the lower bearing seat 14 and the annular channel formed by the inner side of the stator 3a and the outer side of the rotor 3b. Thirdly, after the cooling motor, it enters the intake cavity formed by the frame 4 and the static scroll 13 through the axial air inlet channel opened on the frame 4. The movable scroll 12 and the static scroll 13 engage with each other to form multiple pairs of compression chambers. As the movable scroll 12 rotates horizontally, the refrigerant completes the intake, compression and exhaust processes in sequence. Finally, the compressed high-temperature and high-pressure refrigerant gas is discharged from the waist-shaped exhaust hole 134 and flows into the refrigeration cycle.

[0033] The flow process of lubricating oil inside the compressor is as follows: As the main shaft 6 rotates, the lubricating oil in the lubricating oil pool 17 is sucked into the lubricating oil pump 15, and the pressurized lubricating oil enters the oil injection control system 22 through the oil outlet pipe 20. After the flow distribution of the oil quantity control system 22, the lubricating oil passes through the main shaft return oil pipe 21 and enters the oil supply passage 6a inside the main shaft. After the lubricating oil reaches the top of the main shaft 6, it lubricates the eccentric bearing 7 and the main bearing 8 in turn. After the lubricating oil passes downward through the annular channel formed by the inner side of the stator 3a and the outer side of the rotor 3b, it continues to lubricate the secondary bearing 9 downward and then passes through the axial through hole 14b opened on the lower bearing seat 14 and returns to the lubricating oil pool 17, completing the circulation of the lubricating oil inside the compressor.

[0034] like Figure 2 As shown in the figure, the oil injection control system is designed to flexibly regulate and precisely control the mass flow and oil temperature of the lubricating oil injected into the suction chamber while ensuring proper lubrication of the scroll compressor's internal moving parts. Lubricating oil, pressurized by the lubricating oil pump 15, flows from the oil outlet pipe 20 into the P1P2 pipeline of the oil injection control system 22. The lubricating oil is then divided into two paths, P2P3 and P2P4, within the oil block 221a. The P2P3 pipeline is connected to the main shaft oil return pipe 21, and this portion of lubricating oil is primarily used to lubricate the friction pairs within the scroll compressor. The lubricating oil in the P2P4 pipeline is then divided into two paths, P4P5 and P4P6, within the oil block 221b. This lubricating oil is atomized by nozzles on the fixed scroll 13 and then injected into the scroll compressor's suction chamber. During the compression process, the lubricating oil forms an oil film within the leakage path between the orbiting and fixed scrolls, minimizing refrigerant leakage. To accurately measure and control the injection quantity, a regulating valve 222a and flowmeter 228 are installed in the P2P4 pipeline. To precisely measure and control the injection temperature, a heat exchanger 227 is installed in the P2P4 pipeline, and a thermometer 226 is installed in the P4P5 pipeline. When ball valve 224 is fully closed, the suction chamber injection passage P2P4 is completely disconnected. By adjusting the opening of regulating valve 222b, the minimum oil supply to the friction pair within the compressor is maintained.

[0035] The advantages of the fuel injection quantity control system are: 1. By switching the ball valve of the fuel injection branch, the fuel injection and non-fuel injection states can be switched; 2. By changing the opening of the regulating valve, the optimal fuel injection quantity can be obtained quickly and flexibly; 3. After the lubricating oil is cooled by the external heat exchanger, it is beneficial to reduce the intake superheat and the exhaust temperature; 4. The fuel injection pressure, lubricating oil temperature and mass flow rate are displayed in real time.

[0036] The static vortex includes an end plate 131, an involute vortex body 132 and a swirl cone straight nozzle. The involute vortex body 132 is composed of a sealing groove 133 and a waist-shaped exhaust port 134. The end plate 131 is symmetrically provided with a first nozzle 139a and a second nozzle 139b. Figure 3As shown, the static vortex 13 is composed of an end plate 131, an involute vortex body 132, a sealing groove 133 provided on the top surface of the vortex body 132, and a waist-shaped exhaust port 134. Nozzles 139a and 139b are symmetrically provided on the static vortex end plate 131. The angle between the nozzle 139b and the outer end surface of the involute vortex body 132 is 41°, mainly considering that the atomized lubricating oil can fill the suction channel and does not block the refrigerant from entering the suction chamber. Eight bolt holes 135 are provided on the static vortex end plate 131 for fixing the static vortex 13 and the cylinder 2. The strength of the bolts should meet the axial gas force generated during the compression process of the refrigerant gas. Bolt holes 135, a first positioning pin hole 136a and a second positioning pin hole 136b are also provided on the static vortex end plate 131 to facilitate the installation of the static disk. See Figure 4 This figure is a bottom view of the fixed scroll. It shows that the top surface of the fixed scroll end plate 131 is symmetrically defined with a first swirl chamber 138a and a second swirl chamber 138b. To connect to the compressor exhaust pipe, an annular sealing groove 137 is also defined on the top surface of the fixed scroll end plate 131 for sealing the exhaust pipe.

[0037] like Figure 5 As shown in FIG. 1 , this figure is a cross-sectional view of the static scroll 13 along the AA direction. As can be seen from the figure, compared with the R134a scroll compressor with the same cooling capacity, the tooth height of the static scroll involute vortex body 132 is very short, only 7 mm, and the straight-line distance between the center lines of the two nozzles is less than 60 mm, which increases the processing and assembly difficulty of the nozzle. As can be seen from the partial enlarged view I, a sealing groove 133 is provided on the top surface of the vortex body 132. As can be seen from the partial enlarged view II, the swirl cone straight nozzle consists of three parts: a swirl core 229, a swirl chamber 138 and a nozzle 139, and its function is to achieve rapid atomization of the lubricating oil. The upper part of the nozzle is the lubricating oil inlet, and the lower part is connected to the suction chamber. The lubricating oil is guided by the swirl core and generates tangential rotation in the second swirl chamber 138b. As the diameter of the swirl chamber decreases, the tangential velocity of the lubricating oil gradually increases, and the radial velocity gradually decreases. After being ejected through the nozzle, rapid atomization of the lubricating oil is achieved. After structural analysis and flow field simulation, the nozzle structure dimensions adopted in the present invention are: swirl chamber diameter D is 2 mm, swirl core height l0 is 1 mm, inner cone angle α is 120°, and nozzle diameter d is 0.6 mm.

[0038] like Figure 6As shown in the figure, this is a schematic diagram of the rotary core structure. It can be seen from the figure that the rotary core is a channel for the flow of lubricating oil machined on a cylinder, and the shape of the flow cross section is two symmetrical fan rings with an angle of 60°. When the shape and position of the flow cross section remain consistent from top to bottom, it is the first straight groove 229a and the second straight groove 229b. When the shape of the flow cross section remains unchanged from top to bottom and the position rotates along the central axis, it is the first spiral groove 229c and the second spiral groove 229d. The straight groove processing is relatively simple, and the local resistance loss is small. The spiral groove rotary core processing is more complicated. During the movement of the lubricating oil, the rotational tangential speed is gradually increased, which can make it easier to achieve lubricating oil atomization, and the local resistance loss is large.

[0039] The advantages of the swirl cone straight nozzle are: 1. It consists of three parts: the swirl core, the cone straight nozzle and the nozzle; 2. In order to achieve rapid atomization of the lubricating oil, a spiral groove swirl core design is adopted; 3. The suction chamber oil injection design can reduce the processing accuracy of the swirl disk and the assembly accuracy of the whole machine when the leakage rate is the same, thereby reducing manufacturing costs.

[0040] The oil supply passage 6a opened inside the main shaft 6, the refrigerant gas flow hole 14a and the first axial oil return hole 14b on the frame 4 and the lower bearing seat 14 are based on the principle of ensuring the smooth flow of refrigerant gas and lubricating oil liquid. The welding parts of the air intake 18, oil outlet pipe 20 and main shaft oil return pipe 21 connected to the cylinder 2 by welding should ensure good welding quality. The regulating valve, high-pressure pressure gauge and temperature gauge set in the injection quantity control system 22 should ensure that the model selection is reasonable. If used in intelligent air conditioning, they can be replaced with electric regulating valves, pressure sensors and temperature sensors. The diameter of the connecting pipeline should meet the maximum flow rate of the lubricating oil, and the pipeline connection should reduce the along-the-line resistance loss and local resistance loss generated during the flow of the lubricating oil.

[0041] Therefore, the present invention adopts the above-mentioned atomized oil-spraying CO2 scroll compressor with a large pressure difference working condition, and divides the lubricating oil into two paths. One path lubricates the friction pairs (eccentric bearings, main bearings and auxiliary bearings) inside the compressor, and the other path is atomized by the swirl cone straight nozzle symmetrically opened on the static scroll disk and then sprayed into the suction chamber. The use of a spiral groove core makes it easier to achieve rapid atomization of the lubricating oil. The atomized lubricating oil is sprayed into the suction chamber and fully mixed with the refrigerant, which can not only reduce the superheat of the refrigerant and form an oil film in the leakage channel, but also reduce the amount of refrigerant leakage, thereby reducing the exhaust temperature and ensuring the reliable and efficient operation of the scroll compressor.

[0042] The above embodiments are only used to illustrate the technical solutions of the present invention rather than to limit the same. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solutions of the present invention can still be modified or replaced by equivalents, and these modifications or equivalent replacements cannot cause the modified technical solutions to deviate from the spirit and scope of the technical solutions of the present invention.

Claims

1. A CO2 scroll compressor with atomized oil injection under large pressure difference working conditions, characterized in that: The vortex comprises a cylinder, a lower end cover and a static scroll, wherein the lower end cover is connected to the cylinder by bolts, and a first annular sealing groove is provided on the contact surface of the lower end cover and the cylinder, and the static scroll is connected to the cylinder by bolts, and a second annular sealing groove is provided on the contact surface of the static scroll and the cylinder, the static scroll is located above the cylinder, and the lower end cover is located below the cylinder, and the static scroll comprises an end plate, an involute vortex body and a swirl cone straight nozzle, the involute vortex body consists of a sealing groove and a waist-shaped exhaust port, and nozzles are symmetrically opened on the end plate; The lower bearing seat and the main shaft are arranged in the cylinder. The cavity formed between the lower bearing seat and the lower end cover is provided with an air intake port, an oil outlet pipe, and a main shaft oil return pipe. The lower part of the main shaft oil return pipe is a lubricating oil pool. The main shaft is equipped with a main balance block and a secondary balance block. An oil supply passage is provided inside the main shaft. The motor rotor is provided on the main shaft. The stator corresponding to the motor rotor is provided in the cylinder. A frame is fixed at the upper end of the stator in the cylinder. The lower end of the lower bearing seat is concentrically mounted with a lubricating oil pump seat, which rotates with the rotation of the main shaft, and the lubricating oil pump is placed in the lubricating oil pool; The space formed between the frame and the static scroll is equipped with a ball anti-rotation mechanism and a movable scroll in sequence along the axial direction. A main bearing is provided between the main shaft and the frame. A waist-shaped exhaust hole is provided on the top of the static scroll. The lubricating oil pressurized by the lubricating oil pump flows from the oil outlet pipe into the P1P2 pipeline of the fuel injection control system. The lubricating oil is divided into two pipelines, P2P3 and P2P4, in the oil block. The P2P3 pipeline is connected to the spindle oil return pipe. The lubricating oil in the P2P4 pipeline is divided into two pipelines, P4P5 and P4P6, in the oil block. The top surface of the static vortex disc end plate is symmetrically provided with a swirl chamber, and the top surface of the static vortex disc end plate is also provided with an annular sealing groove; The diameter D of the swirl chamber is 2 mm, the swirl core height l0 is 1 mm, the inner cone angle α is 120°, and the nozzle diameter d is 0.6 mm.

2. The atomized oil-injected CO2 scroll compressor for large pressure difference working conditions according to claim 1 is characterized in that: Eight bolt holes are provided on the static vortex disc end plate, and a positioning pin hole is also provided on the static vortex disc end plate.

Images