Atomization oil injection CO2 scroll compressor under large pressure difference working condition

Abstract

The invention discloses an atomization oil injection CO2 scroll compressor under a large pressure difference working condition, and relates to the technical field of compressors, the atomization oil injection CO2 scroll compressor comprises a cylinder body, a lower end cover and a static scroll plate, the lower end cover is connected with the cylinder body through a bolt, a first annular sealing groove is formed in the contact surface of the lower end cover and the cylinder body, and the static scroll plate is connected with the cylinder body through a bolt; a second annular sealing groove is formed in the face, making contact with the barrel, of the static vortex disc, the static vortex disc is located above the barrel, the lower end cover is located below the barrel, the static vortex disc comprises an end plate, an involute type vortex body and a rotational flow cone straight nozzle, the involute type vortex body is composed of the sealing groove and a kidney-shaped exhaust port, and nozzles are symmetrically formed in the end plate. According to the atomization oil injection CO2 scroll compressor under the large pressure difference working condition, the superheat degree of a refrigerant can be reduced, an oil film is formed in a leakage channel, the leakage amount of the refrigerant can be reduced, and therefore the exhaust temperature is reduced, and reliable and efficient operation of the scroll compressor is guaranteed.

Description

Technical Field

[0001] The invention relates to the technical field of compressors, and in particular to an atomizing oil-injected 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. A large amount of energy is consumed during the operation of HVAC systems. The first three generations of refrigerants, CFCs, HCFCs and HFCs, which are currently widely used, will also cause 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 working fluids have become a hot topic and application direction in the refrigeration industry. The natural working fluid 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. Unique advantages, such as good heat transfer characteristics, may make it the ultimate substitute for refrigerants.

[0003] Compared with compressors using refrigerants such as R134a and R410A, CO2 compressors have the characteristics of small pressure ratio, large pressure difference, small volume flow rate and high working pressure. The suction pressure is 3-5MPa, the exhaust pressure is 10-12MPa, the suction and exhaust pressure difference is 5-9MPa, and the volume of the compressor is reduced by 2 / 3. Since CO2 has a lower viscosity in the supercritical state, under the same gap conditions, the leakage during the compression process will increase significantly. Therefore, for CO2 scroll compressors with large pressure difference conditions, the structural size is small, the scroll profile is difficult to process, the pressure difference on both sides of the leakage channel is large, and it becomes more difficult to achieve dynamic sealing. In order for the scroll compressor to operate reliably and efficiently, it is necessary to focus on reducing the leakage. Based on the above reasons, in order to cope with the technical difficulties caused by refrigerant substitution and ensure the reliable and efficient operation of scroll compressors under large pressure difference conditions, a set of oil injection system must be developed. On the basis of ensuring that the internal friction pairs of the scroll compressor are fully lubricated, the lubricating oil forms an oil film in the leakage gap during the compression process, which can reduce the refrigerant leakage and ensure that the compressor can operate reliably and efficiently. Summary of the invention

[0004] The purpose of the present invention is to provide an atomized oil-injected CO2 scroll compressor under large pressure difference working conditions, reduce the exhaust temperature, and ensure the 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 disk, the lower end cover being connected to the cylinder by bolts, a first annular sealing groove being provided on the contact surface between the lower end cover and the cylinder, the static scroll disk being connected to the cylinder by bolts, a second annular sealing groove being provided on the contact surface between the static scroll disk and the cylinder, the static scroll disk being located above the cylinder, the lower end cover being located below the cylinder, the static scroll disk 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 arranged in the cylinder, and 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] A main balance block and a secondary balance block are respectively installed on the main shaft, 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 coaxially mounted at 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] A ball anti-rotation mechanism and a 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 arranged between the main shaft and the frame. 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 injection CO2 scroll compressor with a large pressure difference working condition, and divides the lubricating oil into two paths, one path lubricates the friction pair (eccentric bearing, main bearing and auxiliary bearing) inside the compressor, and the other path is sprayed into the suction chamber after being atomized by the swirl cone straight nozzle symmetrically opened on the static scroll. The use of a spiral groove vortex 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 leakage of the refrigerant, thereby reducing the exhaust temperature, 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 It is an overall longitudinal section view of an atomizing oil-injected CO2 scroll compressor under large pressure difference working condition of the present invention;

[0017] Figure 2 The invention discloses 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 a stationary scroll of an atomized oil-injected CO2 scroll compressor under a large pressure difference working condition according to the present invention;

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

[0020] Figure 5 It is a cross-sectional view and a partial enlarged view of a stationary scroll along the AA direction of an atomized oil-injected CO2 scroll compressor under large pressure difference working conditions of the present invention;

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

[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. Moving scroll; 13. Stationary scroll; 14. Lower bearing seat; 15. Lubricating oil pump; 16. Lubricating oil pump seat; 17. Lubricating oil pool; 18. Air intake; 19. Key; 20. Oil outlet pipe; 21. Main shaft oil return pipe; 22. Oil injection control system; 221. Oil block; 222. Needle valve; 223. Sight glass; 224. Ball valve; 225. High 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 through the accompanying drawings and embodiments.

[0025] Unless otherwise defined, technical or scientific terms used in the present invention shall have the common meanings understood by one having ordinary skills in the field 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 "comprises" and similar terms mean that the elements or objects appearing before 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" and similar terms 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 positional relationships. When the absolute position of the object being described changes, the relative positional relationship may also change accordingly.

[0027] Embodiment 1

[0028] like Figure 1-6As shown, the present invention is an atomized oil-injected CO2 scroll compressor for large pressure difference working conditions, including a cylinder 2, a lower end cover 1 and a static scroll 13, the lower end cover 1 is connected to the cylinder 2 by bolts, and the contact surface of the lower end cover 1 and the cylinder 2 is provided with a first annular sealing groove 2a, the static scroll 13 is connected to the cylinder 2 by bolts, and the contact surface of the static scroll 13 and the cylinder 2 is provided with a second annular sealing groove 2b, to prevent the compressor from sucking air and lubricating oil from leaking to the atmosphere. The static 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 provided with an air intake port 18, an oil outlet pipe 20 and a main shaft oil return pipe 21, and the lower part of the cavity is a lubricating oil pool 17. The lower end of the lower bearing seat 14 is concentrically provided with a lubricating oil pump 15 that rotates with the rotation of the main shaft 6 through a lubricating oil pump seat 16, and the lubricating oil pump 15 is placed in the lubricating oil pool 17. In the space formed between the frame 4 and the fixed scroll 13, a ball anti-rotation mechanism 5 and a movable scroll 12 are sequentially installed along the axial direction, a main bearing 8 is provided between the main shaft 6 and the frame 4, and a waist-shaped exhaust hole 134 is provided at the top of the fixed 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, and the lubricating oil is divided into two P2P3 pipelines and P2P4 in the oil circuit block 221a. The P2P3 pipeline is connected to the main shaft oil return pipe 21, and 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 P4P5 pipelines and P4P6 pipelines in the oil circuit block 221b. This part of the lubricating oil is sprayed into the suction chamber of the scroll compressor after being atomized by the nozzle opened on the fixed scroll 13. 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 refrigerant leakage. In order to accurately measure and control the oil injection amount, a regulating valve 222a and a flow meter 228 are installed in the P2P4 pipeline. In order to accurately measure and control the injection temperature, a heat exchanger 227 is installed in the P2P4 pipeline, and a temperature gauge 226 is installed in the P4P5 pipeline. When the ball valve 224 is in a fully closed state, the suction chamber injection passage P2P4 is completely disconnected, and the minimum oil supply to the friction pair inside the compressor can be guaranteed by changing the opening of the regulating valve 222b.

[0031] In order to make the fuel injection control system 22 reflect the state of the lubricating oil more clearly, some auxiliary equipment is added. The 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 pipeline of the fuel injection control system 22. The air intake port 18 is installed on the cylinder 2 and is located in the annular space formed between the lower bearing seat 14 and the lower end cover 1. The lower bearing seat 14 is installed at 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. 15 is 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 by a key 9. The rotation of the main shaft 6 drives the rotation of the lubricating oil pump 15 to provide 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 by a hot-fitting 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 auxiliary balance block 11 after the secondary balance design of the scroll compressor dynamics 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, that is, the crank pin, and an eccentric bearing 7 is installed on its outer side. A ball anti-rotation mechanism 5 is installed between the frame 4 and the movable scroll 12, which can realize the horizontal rotation movement of the movable scroll. The involute vortex body of the movable scroll and the involute vortex body 132 of the fixed scroll mesh with each other, and at the same time form multiple pairs of crescent-shaped suction chambers, compression chambers and exhaust chambers. 134 is a waist-shaped exhaust hole, which can not only increase the structural strength of the tooth end and maximize the use of the exhaust space, but also reduce the exhaust loss and air flow pulsation. The high-temperature and high-pressure refrigerant gas flows into the refrigeration system cycle after passing through the waist-shaped exhaust hole.

[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 suction port 18, and then 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 suction 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 mesh with each other to form multiple pairs of compression chambers. With the horizontal rotation of the movable scroll 12, the refrigerant completes the suction, 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 control system 22, the lubricating oil enters the oil supply passage 6a inside the main shaft through the main shaft return oil pipe 21. 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 auxiliary bearing 9 downward, and then passes through the axial through hole 14b opened on the lower bearing seat 14 and flows back to the lubricating oil pool 17, completing the circulation of the lubricating oil inside the compressor.

[0034] like Figure 2 As shown, the figure is an oil injection control system. It can be seen from the figure that the function of the system is to flexibly adjust and accurately control the mass flow rate and oil temperature of the lubricating oil sprayed into the suction chamber on the basis of ensuring the normal lubrication of the internal moving parts of the scroll compressor. 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, and the lubricating oil is divided into two routes P2P3 and P2P4 in the oil circuit block 221a. The P2P3 pipeline is connected to the main shaft oil return pipe 21, and this part of the lubricating oil is mainly used to lubricate the friction pair inside the scroll compressor. The lubricating oil in the P2P4 pipeline is divided into two routes P4P5 and P4P6 in the oil circuit block 221b. This part of the lubricating oil is sprayed into the suction chamber of the scroll compressor after being atomized by the nozzle opened on the fixed scroll 13. During the compression process, the lubricating oil can form an oil film in the leakage channel between the movable scroll and the fixed scroll to reduce the refrigerant leakage. In order to accurately measure and control the injection amount, the P2P4 pipeline is equipped with a regulating valve 222a and a flow meter 228. In order to accurately measure and control the injection temperature, the P2P4 pipeline is equipped with a heat exchanger 227, and the P4P5 pipeline is equipped with a temperature meter 226. When the ball valve 224 is in a fully closed state, the suction chamber injection passage P2P4 is completely disconnected, and the minimum oil supply to the friction pair inside the compressor can be guaranteed by changing the opening of the regulating valve 222b.

[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-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. The lubricating oil is cooled by the external heat exchanger, which is beneficial to reduce the suction superheat and the exhaust temperature; 4. The injection pressure, lubricating oil temperature and mass flow rate are displayed in real time.

[0036] The fixed scroll includes an end plate 131, an involute scroll body 132 and a swirl cone straight nozzle. The involute scroll 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 scroll 13 is composed of an end plate 131, an involute scroll body 132, a sealing groove 133 provided on the top surface of the scroll body 132, and a waist-shaped exhaust port 134. The static scroll end plate 131 is symmetrically provided with nozzles 139a and 139b. The angle between the nozzle 139b and the outer end surface of the involute scroll 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. The static scroll end plate 131 is provided with 8 bolt holes 135 for fixing the static scroll 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. The static scroll end plate 131 is also provided with bolt holes 135, a first positioning pin hole 136a and a second positioning pin hole 136b to facilitate the installation of the static disk. See. Figure 4 , which is a bottom view of the fixed scroll, from which it can be seen that the first swirl chamber 138a and the second swirl chamber 138b are symmetrically provided on the top surface of the fixed scroll end plate 131. In order to connect with the compressor exhaust pipe, an annular sealing groove 137 is also provided on the top surface of the fixed scroll end plate 131 for sealing the exhaust pipe.

[0037] like Figure 5 As shown, this figure is a cross-sectional view of the static scroll 13 along the AA direction. It can be seen from the figure that compared with the R134a scroll compressor with the same refrigeration capacity, the tooth height of the static scroll involute vortex body 132 is very short, only 7mm, and the straight-line distance between the center lines of the two nozzles is less than 60mm, which increases the processing difficulty and assembly difficulty of the nozzle. It can be seen from the partial enlarged figure I that a sealing groove 133 is provided on the top surface of the vortex body 132. It can be seen from the partial enlarged figure II that 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 passes through the guiding effect of 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: the swirl chamber diameter D 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.

[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 processed on a cylinder, and the shape of the flow cross section is 2 symmetrical fan rings with an angle of 60°. When the shape and position of the flow cross section are 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 from top to bottom remains unchanged and the position rotates along the central axis, it is the first spiral groove 229c and the second spiral groove 229d. The processing of the straight groove is relatively simple, and the local resistance loss is small. The processing of the spiral groove rotary core is more complicated. The rotational tangential speed is gradually increased during the movement of the lubricating oil, which can make it easier to realize the atomization of the lubricating oil, 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 at the same leakage rate, thereby reducing the manufacturing cost.

[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 port 18, the oil outlet pipe 20 and the 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 applied to intelligent air conditioning, they can be replaced by 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-way 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 injection CO2 scroll compressor with a large pressure difference working condition, and divides the lubricating oil into two paths, one path lubricates the friction pair (eccentric bearing, main bearing and auxiliary bearing) inside the compressor, and the other path is sprayed into the suction chamber after being atomized by the swirl cone straight nozzle symmetrically opened on the static scroll. The use of a spiral groove vortex 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 leakage of the refrigerant, thereby reducing the exhaust temperature, ensuring the reliable and efficient operation of the scroll compressor.

[0042] The above embodiments are only used to illustrate the technical solution of the present invention rather than to limit it. 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 solution of the present invention can still be modified or replaced by equivalents, and these modifications or equivalent replacements cannot cause the modified technical solution to deviate from the spirit and scope of the technical solution of the present invention.

Claims

1. A CO2 scroll compressor with atomizing oil injection under large pressure difference working conditions, characterized in that: It includes a cylinder, a lower end cover and a static vortex disk. 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. The static vortex disk is connected to the cylinder by bolts, and a second annular sealing groove is provided on the contact surface of the static vortex disk and the cylinder. The static vortex disk is located above the cylinder, and the lower end cover is located below the cylinder. The static vortex disk includes an end plate, an involute vortex body and a swirl cone straight nozzle. The involute vortex body is composed of a sealing groove and a waist-shaped exhaust port, and nozzles are symmetrically opened on the end plate.

2. The atomizing oil-injected CO2 scroll compressor for large pressure difference working condition according to claim 1 is characterized in that: The cylinder is provided with a lower bearing seat and a main shaft, and 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, and the lower part of the main shaft oil return pipe is a lubricating oil pool; A main balance block and a secondary balance block are respectively installed on the main shaft, 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.

3. The atomizing oil-injected CO2 scroll compressor for large pressure difference working condition according to claim 2 is characterized in that: A lubricating oil pump that rotates with the rotation of the main shaft is coaxially mounted at 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; A ball anti-rotation mechanism and a 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 arranged between the main shaft and the frame. A waist-shaped exhaust hole is opened on the top of the static scroll.

4. The atomizing oil-injected CO2 scroll compressor for large pressure difference working condition according to claim 3 is characterized in that: 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 pipeline and P2P4 pipeline in the oil circuit 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 pipeline and P4P6 pipeline in the oil circuit block.

5. The atomizing oil-injected CO2 scroll compressor for large pressure difference working condition 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.

6. The atomizing oil-injected CO2 scroll compressor for large pressure difference working condition according to claim 1 is characterized in that: The top surface of the static vortex disc end plate is symmetrically provided with swirl chambers, and the top surface of the static vortex disc end plate is also provided with an annular sealing groove.

7. The atomizing oil-injected CO2 scroll compressor for large pressure difference working condition according to claim 6 is characterized in that: 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.

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