Static disc structure and scroll compressor thereof

Abstract

The utility model provides a kind of static disc structure and scroll compressor, static disc structure includes static disc and is arranged on the accommodating cavity and opening portion of static disc, opening portion is located the side of accommodating cavity towards dynamic disc, to passive disc plugging, to make accommodating cavity and the upper surface of dynamic disc jointly form compression cavity, static disc is also provided with cavity oil passage and end surface oil pipe section;Wherein, the inlet of cavity oil passage is connected with the oil delivery line outside static disc structure, the outlet of cavity oil passage is set apart on the inner wall surface of accommodating cavity and with opening portion, to spray oil to compression cavity;The inlet of end surface oil pipe section is connected with cavity oil passage, static disc has lower end surface, the outlet of end surface oil pipe section is located on lower end surface, to oil delivery between lower end surface and dynamic disc, to solve the problem of lower cooling efficiency of the cooling mode of scroll compressor in prior art to compression cavity.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and more specifically, to a static disc structure and its scroll compressor. Background Technology

[0002] In the field of compressor technology, the temperature gradually increases from the inlet to the outlet during gas compression. Maintaining the compressor discharge temperature below 115°C is crucial for the long-term stable operation of the equipment. Existing compressors typically employ a cooling method using rotating and stationary discs, controlling the temperature within the compression chamber through the circulation of refrigerant oil. However, this method has some inherent limitations. After initial cooling, due to friction and heat exchange between the rotating and stationary discs, the temperature of the refrigerant oil gradually approaches the gas temperature within the compression chamber. Consequently, it becomes unable to effectively absorb and remove heat from the compression chamber, easily leading to heat accumulation at the bottom of the chamber. Over prolonged operation, the temperature of the refrigerant oil accumulated within the compression chamber continuously rises, resulting in a decrease in cooling efficiency.

[0003] In response, some researchers have devised a flow path between the oil storage chamber and the back pressure chamber. The flow path guides the refrigeration oil to the end face of the stationary disc, and the movement of the moving disc introduces the refrigeration oil into the entire compression chamber. However, at this point, the refrigeration oil has already lost some of its cooling capacity due to the friction between the moving and stationary discs, and the refrigeration oil will accumulate at the bottom of the compression chamber, which is not conducive to carrying heat away and dissipating, thus causing the temperature inside the compression chamber to be too high. Utility Model Content

[0004] The main objective of this invention is to provide a static disc structure and its scroll compressor to solve the problem of low cooling efficiency of the compression chamber in the existing scroll compressor cooling method.

[0005] According to one aspect of the present invention, a stationary disc structure is provided, including a stationary disc and a receiving cavity and an opening disposed on the stationary disc. The opening is located on the side of the receiving cavity facing the moving disc and is blocked by the moving disc, so that the receiving cavity and the upper surface of the moving disc together form a compression cavity. The stationary disc is also provided with a cavity oil channel and an end face oil pipe section. The inlet of the cavity oil channel is connected to an oil supply pipeline outside the stationary disc structure, and the outlet of the cavity oil channel is opened on the inner wall of the receiving cavity and spaced apart from the opening to spray oil into the compression cavity. The inlet of the end face oil pipe section is connected to the cavity oil channel. The stationary disc has a lower end face, and the outlet of the end face oil pipe section is located on the lower end face to supply oil between the lower end face and the moving disc.

[0006] Furthermore, the stationary disc has a stationary disc axis, and the cavity oil passage also includes a first oil injection pipe section, a second oil injection pipe section, and a stationary disc oil injection pipe section connected in sequence. The first oil injection pipe section is arranged parallel to the stationary disc axis, and its inlet is connected to the outlet of the oil delivery pipeline. The second oil injection pipe section is arranged perpendicular to the stationary disc axis, and its inlet is connected to the outlet of the first oil injection pipe section. Its outlet is connected to the inlet of the stationary disc oil injection pipe section. The outlet of the stationary disc oil injection pipe section is connected to the inner wall surface of the receiving cavity to input oil into the receiving cavity.

[0007] Furthermore, the end face oil pipe section is arranged parallel to the axis of the stationary disc, the inlet of the end face oil pipe section is connected to the inner wall of the second injection pipe section, and the end face oil pipe section is located on the side of the second injection pipe section near the lower end face.

[0008] Furthermore, the second fuel injection pipe section and the outer peripheral surface of the stationary disc are provided with machining holes, which are connected to the end of the second fuel injection pipe section away from the receiving cavity. The stationary disc structure also includes a sealing component disposed in the machining hole to seal the machining hole.

[0009] Furthermore, the inner wall of the first fuel injection pipe section is cylindrical; and / or the inner wall of the second fuel injection pipe section is cylindrical; and / or the inner wall of the stationary disc fuel injection pipe section is frustum-shaped, and the diameter of the inner wall of the stationary disc fuel injection pipe section gradually decreases in the direction away from the second fuel injection pipe section; and / or the inner wall of the end face fuel pipe section is cylindrical.

[0010] Furthermore, the end of the stationary disc injection pipe section that communicates with the receiving cavity is an injection hole, and the stationary disc structure also includes a nozzle disposed at the injection hole.

[0011] Furthermore, the end of the static disc injection pipe section that connects to the receiving cavity is an injection hole. The distance between the center of the injection hole and the opening is H1, and the distance between the center of the injection hole and the upper end face of the receiving cavity is H2. Wherein, H1 / H2 is greater than or equal to 0.46 and less than or equal to 0.5; and / or, H1 is greater than or equal to 7.3 mm and less than or equal to 7.9 mm.

[0012] Furthermore, a high-pressure oil tank is provided on the lower end face, and the oil pipe section on the end face is connected to the high-pressure oil tank to allow the oil to flow into the high-pressure oil tank.

[0013] Furthermore, the high-pressure oil groove is a curved groove that is at least partially provided around the lower end face in the circumferential direction. The high-pressure oil groove is located between the outer peripheral surface of the compression chamber and the stationary plate, so that a portion of the oil in the chamber oil channel flows into the high-pressure oil groove and another portion of the oil in the chamber oil channel flows into the compression chamber.

[0014] According to another aspect of the present invention, a scroll compressor is provided, including a stationary disc structure, wherein the stationary disc structure is the stationary disc structure described above.

[0015] Applying the technical solution of this utility model, the stationary disc structure of this utility model includes a stationary disc and a receiving cavity and an opening disposed on the stationary disc. The opening is located on the side of the receiving cavity facing the moving disc and is blocked by the moving disc, so that the receiving cavity and the upper surface of the moving disc together form a compression cavity. The stationary disc is also provided with a cavity oil channel and an end face oil pipe section. The inlet of the cavity oil channel is connected to an oil supply pipeline outside the stationary disc structure, and the outlet of the cavity oil channel is opened on the inner wall of the receiving cavity and spaced apart from the opening to spray oil into the compression cavity. The inlet of the end face oil pipe section is connected to the cavity oil channel. The stationary disc has a lower end face, and the outlet of the end face oil pipe section is located on the lower end face to supply oil between the lower end face and the moving disc. In this way, the present invention directly sprays refrigerant oil into the compression chamber through the cavity oil channel, allowing the refrigerant oil to directly contact the compressed gas, increasing the heat exchange area and improving the heat exchange efficiency. This is more direct and effective than the existing technology that supplies oil through the gap between the end faces of the moving and stationary discs. It ensures that the refrigerant oil can quickly absorb the heat of the compressed gas, reduce the temperature of the compression chamber, and thus reduce the power consumption of the compressor and improve its performance. The spacing between the outlet and opening of the cavity oil channel, as well as the determination of the oil injection position, prevents excessive oil from remaining in the compression chamber, ensuring sufficient cooling effect while avoiding performance degradation caused by excessive oil. Furthermore, the oil pipe section on the end face supplies oil to the lower end face of the stationary disc, optimizing the lubrication effect between the moving and stationary discs, reducing friction, and improving the smoothness of compressor operation and lifespan. At the same time, this design helps to reduce the oil film thickness on the end faces of the moving and stationary discs, improving the cooling efficiency of the oil and effectively solving the problem of low cooling efficiency of the compression chamber in the existing scroll compressor cooling method. Attached Figure Description

[0016] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0017] Figure 1 A cross-sectional view of the entire scroll compressor according to an embodiment of the static disc structure and scroll compressor of the present invention is shown; and

[0018] Figure 2 It shows that according to Figure 1 The diagram shows the oil flow direction of the scroll compressor.

[0019] Figure 3 It shows that according to Figure 1 The cross-sectional view of the cavity oil passage shown;

[0020] Figure 4 A top view of the stationary disc according to an embodiment of the stationary disc structure and its scroll compressor according to the present invention is shown;

[0021] Figure 5 It shows Figure 1 A magnified view of a portion of point A shown.

[0022] The above figures include the following reference numerals:

[0023] 10. Static plate; 110. Receiving cavity; 120. Opening;

[0024] 130. Cavity oil passage; 131. First fuel injection pipe section; 132. Second fuel injection pipe section; 133. Static disc fuel injection pipe section;

[0025] 140. End face oil pipe section;

[0026] 150. Oil pipeline; 151. Oil chamber; 152. Oil pump; 153. Crankshaft oil passage; 154. Upper bracket high-pressure oil chamber; 155. Throttle pin;

[0027] 160. Lower end face; 161. High-pressure oil tank;

[0028] 170. Machining hole; 180. Sealing component; 190. Oil injection hole;

[0029] 20. Moving disc; 30. Compression chamber; 40. Exhaust port; 50. Intake port; 60. Pressure relief valve. Detailed Implementation

[0030] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0031] like Figures 1 to 5 As shown, the stationary disc structure of this utility model includes a stationary disc 10 and a receiving cavity 110 and an opening 120 disposed on the stationary disc 10. The opening 120 is located on the side of the receiving cavity 110 facing the moving disc 20 and is blocked by the moving disc 20, so that the upper surfaces of the receiving cavity 110 and the moving disc 20 together form a compression cavity 30. The stationary disc 10 is also provided with a cavity oil channel 130 and an end face oil pipe section 140. The inlet of the cavity oil channel 130 is connected to the oil supply pipeline 150 outside the stationary disc structure, and the outlet of the cavity oil channel 130 is opened on the inner wall of the receiving cavity 110 and spaced apart from the opening 120 to spray oil into the compression cavity 30. The inlet of the end face oil pipe section 140 is connected to the cavity oil channel 130. The stationary disc 10 has a lower end face 160, and the outlet of the end face oil pipe section 140 is located on the lower end face 160 to supply oil between the lower end face 160 and the moving disc 20.

[0032] In this way, the present invention directly sprays refrigerant oil into the compression chamber 30 through the cavity oil channel 130, allowing the refrigerant oil to directly contact the compressed gas, increasing the heat exchange area and improving the heat exchange efficiency. This is more direct and effective than the prior art of supplying oil through the gap between the end faces of the moving and stationary discs, ensuring that the refrigerant oil can quickly absorb the heat of the compressed gas, reduce the temperature of the compression chamber, and thus reduce the power consumption of the compressor and improve its performance. The spacing between the outlet and the opening 120 of the cavity oil channel 130, as well as the determination of the oil injection position, can prevent excessive oil from remaining in the compression chamber 30, ensuring sufficient cooling effect while avoiding performance degradation caused by excessive oil. Furthermore, the oil pipe section 140 supplies oil to the lower end face 160 of the stationary disc 10, optimizing the lubrication effect between the moving and stationary discs, reducing friction, and improving the smoothness and lifespan of the compressor. At the same time, this design helps to reduce the oil film thickness on the end faces of the moving and stationary discs, improving the cooling efficiency of the oil and effectively solving the problem of low cooling efficiency of the compression chamber in the existing design of scroll compressors.

[0033] Preferably, the oil is a refrigeration oil.

[0034] like Figure 1 and Figure 3 As shown, the stationary disc 10 has a stationary disc axis. The cavity oil channel 130 also includes a first oil injection pipe section 131, a second oil injection pipe section 132, and a stationary disc oil injection pipe section 133 connected in sequence. The first oil injection pipe section 131 is arranged parallel to the stationary disc axis, ensuring the stability and straight delivery of the refrigeration oil when it initially enters the stationary disc structure, reducing the resistance to oil flow and unnecessary pressure loss. The inlet of the first oil injection pipe section 131 is connected to the outlet of the oil delivery pipeline 150. The second oil injection pipe section 132 is arranged perpendicular to the stationary disc axis. The inlet of pipe section 132 is connected to the outlet of the first oil injection pipe section 131, and the outlet of the second oil injection pipe section 132 is connected to the inlet of the stationary plate oil injection pipe section 133. The outlet of the stationary plate oil injection pipe section 133 is connected to the inner wall of the receiving cavity 110 to input oil into the receiving cavity 110. This ensures that the refrigerant oil can be directly and accurately sprayed to the designated position of the receiving cavity 110 and fully exchange heat with the compressed gas. At the same time, this design makes full use of the space inside the stationary plate and reduces the impact of additional structures on the size and weight of the compressor.

[0035] Preferably, by sequentially connecting the first oil injection pipe section 131 and the second oil injection pipe section 132, the flow rate and volume of the refrigeration oil can be precisely controlled. The second oil injection pipe section 132 is perpendicular to the axis of the stationary plate, and its length and diameter are different from those of the first oil injection pipe section 131, which optimizes the flow rate of the refrigeration oil at different stages and ensures that the best cooling effect is achieved before it is injected into the compression chamber 30. This design also helps to maintain the pressure balance in different areas of the stationary plate 10 during compressor operation.

[0036] like Figure 1and Figure 4 As shown, the end-face oil pipe section 140 is arranged parallel to the axis of the stationary disc. The inlet of the end-face oil pipe section 140 is connected to the inner wall of the second oil injection pipe section 132, and the end-face oil pipe section 140 is located on the side of the second oil injection pipe section 132 near the lower end face 160. This allows the refrigerant oil to be directly delivered to the contact area between the moving and stationary discs, providing more direct and effective lubrication. This helps reduce friction between the moving and stationary discs, reduces wear, and thus extends the compressor's service life and improves operating efficiency.

[0037] By connecting the inlet of the end face oil pipe section 140 to the inner wall of the second oil injection pipe section 132, this utility model can evenly distribute a portion of the refrigerant oil in the oil flow of the second oil injection pipe section 132 to the contact surface of the moving and stationary discs, ensuring that the contact surface of the moving and stationary discs in the entire compression chamber 30 can obtain sufficient lubrication and cooling.

[0038] like Figure 3 As shown, the second oil injection pipe section 132 and the outer peripheral surface of the stationary plate 10 are provided with machining holes 170. The machining holes 170 are connected to the end of the second oil injection pipe section 132 away from the receiving cavity 110. The stationary plate structure also includes a sealing component 180 disposed in the machining hole 170 to seal the machining hole 170. The presence of the sealing component 180 allows technicians to temporarily remove the sealing component 180 during the compressor commissioning or maintenance process to check or adjust the oil flow inside the second oil injection pipe section 132, which helps to ensure the correct flow of refrigeration oil in the oil passage and optimize the cooling and lubrication effect of the compressor.

[0039] Specifically, during the manufacturing stage, the second oil injection pipe section 132 can be better machined through the machining hole 170. The machining hole 170 provides a channel for cleaning, inspecting or repairing the second oil injection pipe section 132 during the manufacturing process of the stationary plate 10, which facilitates manufacturing and subsequent maintenance. Furthermore, the sealing component 180 seals the machining hole 170 when the compressor is running normally, preventing compressed gas leakage or the entry of foreign impurities, and ensuring the airtightness and cleanliness of the compressor.

[0040] Preferably, the inner wall of the first oil injection pipe section 131 is cylindrical, which can ensure the smooth flow of cooling oil in the first oil injection pipe section 131, reduce turbulence, reduce flow resistance, help improve the delivery efficiency of refrigeration oil, ensure that refrigeration oil can reach the compression chamber at a stable speed and pressure, and improve the cooling effect and the lubrication quality of the moving and stationary discs.

[0041] Furthermore, the inner wall of the second oil injection pipe section 132 is cylindrical, which can ensure the smooth flow of cooling oil in the second oil injection pipe section 132, reduce turbulence, reduce flow resistance, help improve the delivery efficiency of refrigeration oil, ensure that refrigeration oil can reach the compression chamber at a stable speed and pressure, and improve the cooling effect and lubrication quality of the moving and stationary discs.

[0042] In an embodiment of this utility model, the inner wall of the stationary disc oil injection pipe section 133 is frustum-shaped, and the diameter of the inner wall of the stationary disc oil injection pipe section 133 gradually decreases along the direction away from the second oil injection pipe section 132, forming a tapered structure. This makes the speed of the refrigeration oil significantly increase when it approaches the oil injection outlet, forming a high-speed oil jet, which can mix with the compressed gas more effectively, improve the heat exchange efficiency, and also facilitate the discharge of the refrigeration oil and gas together from the compression chamber, carrying away more heat.

[0043] Preferably, the inner wall of the end face oil pipe section 140 is cylindrical. The cylindrical inner wall design usually has high mechanical strength, can withstand the impact of high pressure oil flow, enhance the durability and fatigue resistance of the pipeline, and help improve the overall operating stability of the compressor and extend its service life.

[0044] Specifically, the end of the stationary disc oil injection pipe section 133 that communicates with the receiving cavity 110 is an oil injection hole 190. The stationary disc structure also includes a nozzle set at the oil injection hole 190, which can further focus the injection direction of the refrigeration oil, improve the concentration and speed of the refrigeration oil injection. This focusing effect allows the refrigeration oil to enter the receiving cavity 110 with higher kinetic energy, mix with the compressed gas more quickly and fully, and thus more effectively remove heat and reduce the temperature in the compression cavity.

[0045] In this invention, the nozzle forms the refrigeration oil into fine droplets or mist, which increases the contact area between the oil and the compressed gas, significantly improving the heat exchange efficiency. More heat can be transferred from the compressed gas to the refrigeration oil, and then discharged from the compressor by the refrigeration oil, which helps to maintain the compressor in a highly efficient and temperature-controlled state.

[0046] On the other hand, the nozzle design allows for adjustment of the size and shape of the oil injection hole 190 according to different operating conditions, thereby precisely controlling the flow rate and velocity of the refrigerant oil through the oil injection hole 190. This helps to ensure good lubrication of the moving and stationary discs 10 while preventing excessive refrigerant oil from accumulating in the compression chamber 30, reducing the negative impact on compressor performance.

[0047] like Figure 1 and Figure 5 As shown, the end of the static disc injection pipe section 133 that connects to the receiving cavity 110 is the injection hole 190. The distance between the center of the injection hole 190 and the opening 120 is H1, and the distance between the center of the injection hole 190 and the upper end face of the receiving cavity 110 is H2. Wherein, H1 / H2 is greater than or equal to 0.46 and less than or equal to 0.5; and / or, H1 is greater than or equal to 7.3 mm and less than or equal to 7.9 mm.

[0048] This invention ensures that the refrigerant oil is sprayed from the injection hole 190 at a suitable position by limiting the H1 / H2 ratio to between 0.46 and 0.5. This prevents the oil from being too close to the top of the compression chamber 30, which would cause uneven oil flow, or too close to the bottom, which would cause oil accumulation. This optimizes the distribution of refrigerant oil in the compression chamber 30, increases the contact area with the compressed gas, and improves the heat exchange efficiency. Furthermore, the specific value of H1 is between 7.3 mm and 7.9 mm, which allows the refrigerant oil sufficient space to spread during injection and form a thin layer covering the inner wall of the compression chamber 30. This not only increases the contact area between the refrigerant oil and the compressed gas but also promotes the uniform distribution of the refrigerant oil, further enhancing the cooling effect and effectively controlling the compressor's exhaust temperature.

[0049] like Figure 4 As shown, a high-pressure oil tank 161 is also provided on the lower end face 160. The end face oil pipe section 140 is connected to the high-pressure oil tank 161 to allow oil to flow into the high-pressure oil tank 161. The design of the high-pressure oil tank 161 can increase the contact area between the refrigeration oil and the lower end face 160, so that the refrigeration oil forms a layer of oil film in the high-pressure oil tank 161 that helps to continuously cool. This oil film directly contacts the moving plate 20 and the stationary plate 10, and can more effectively absorb and remove the heat generated during the compression process, thereby reducing the temperature in the compression chamber 30 and improving the cooling efficiency. In addition, the direct connection between the end face oil pipe section 140 and the high-pressure oil tank 161 simplifies the structure of the oil circuit, reduces the bends and branches in the oil circuit, reduces the oil flow resistance, and ensures that the refrigeration oil can flow smoothly and efficiently to the high-pressure oil tank 161, providing a stable oil source for the cooling of the moving and stationary plates 10.

[0050] Preferably, the high-pressure oil groove 161 is a curved groove that is at least partially provided around the lower end face 160 in the circumferential direction. The high-pressure oil groove 161 is located between the outer peripheral surfaces of the compression chamber 30 and the stationary plate 10, so that a portion of the oil in the cavity oil channel 130 flows into the high-pressure oil groove 161 and another portion of the oil in the cavity oil channel 130 flows into the compression chamber 30. The position and design of the high-pressure oil groove 161 can increase the contact area between the oil and the moving and stationary plates and the inner wall of the compression chamber 30, promote the diffusion and uniform coating of the oil, help the rapid conduction and dissipation of heat, reduce the temperature of the compression chamber 30, improve the cooling efficiency of the compressor, and make the oil form a stable oil film in the high-pressure oil groove 161, providing continuous lubrication for the moving and stationary plates, reducing direct friction and wear, improving the stability of the moving and stationary plates and extending the service life of the compressor.

[0051] This utility model also provides a scroll compressor, including a stationary disc structure, which is the stationary disc structure described above.

[0052] In the field of compressors, the temperature of the compression chamber is usually one of the important factors affecting the performance and long-term stable operation of the compressor. The existing technology reduces the temperature of the compression chamber by diverting the refrigeration oil to the end face of the stationary plate and collecting the refrigeration oil into the compression chamber through the high-speed rotation of the moving plate. This utility model can directly introduce the refrigeration oil into the compression chamber 30, so that it can directly contact the compressed gas and fully exchange heat. By utilizing the structure of the stationary plate oil injection pipe section 133 and the oil injection hole 190, the speed of the refrigeration oil is increased and the flow rate of the refrigeration oil is reduced, so that the refrigeration oil and the gas are discharged from the compression chamber 30 together, carrying away heat, thereby reducing heat exchange loss, improving heat exchange efficiency, timely dissipating heat, and reducing the exhaust temperature.

[0053] like Figure 1 As shown, in this utility model, the oil pipeline 150 also includes an oil chamber 151, an oil pump 152, a crankshaft oil passage 153, an upper support high-pressure oil chamber 154, and a throttle pin 155.

[0054] Figure 2 This is a partial oil circuit diagram of the compressor. The arrows indicate the flow direction of the oil circuit. During high-speed operation of the crankshaft, the oil pump 152 introduces the refrigerant oil in the oil chamber 151 into the high-pressure oil chamber 154 of the upper support through the crankshaft oil circuit 153. Because the high-pressure oil chamber 154 of the upper support is in a high-pressure environment, the high-pressure gas in the compression chamber is completely compressed and directly discharged and flows into the high-pressure oil chamber 154 of the upper support. Meanwhile, the cavity oil passage 130 in the compression chamber 30 is in a relatively low-pressure gas environment formed by partial compression. Oil is supplied through the pressure difference between the high-pressure oil chamber 154 of the upper support and the compression chamber 30. The refrigerant oil flows through the throttling pin 155 and is introduced into the high-pressure oil tank 161 and the compression chamber 30. The refrigerant oil is sprayed into the compression chamber 30 through the structure of the stationary disc oil spray pipe section 133 and the oil spray hole 190, where it is fully mixed with the compressed gas. In the compression chamber 30, the refrigerant oil and gas are compressed by the circumferential motion of the moving disc 20. Figure 4 The process, indicated by the arrow, involves inhalation, compression, mixing, recompression, and expulsion, ultimately carrying away heat.

[0055] Specifically, in this utility model, the gas discharged from the exhaust port 40 is fully compressed and has the highest pressure. Therefore, the pressure in other positions inside the stationary plate is lower than the pressure discharged from the exhaust port 40. The entire area outside the compression chamber and between it and the housing is a high-pressure environment and is connected to the exhaust port of the stationary plate. The oil injection pipe section 133 of the stationary plate is located on the outside of the stationary plate. Therefore, this position is at a low pressure relative to the environment of the high-pressure oil chamber 154 of the upper support.

[0056] Figure 4The diagram shows the stationary plate component. The exhaust port 40 compresses the low-pressure gas into high-pressure gas through the compression chamber 30 and discharges it into the compressor. Then, it is discharged into the air conditioning system through the exhaust pipe. The end face oil pipe section 140 and the high-pressure oil tank 161 introduce oil from the high-pressure oil chamber 154 of the upper bracket into the stationary plate 10. The suction port 50 is connected to the suction pipe to draw in low-pressure gas from the external air conditioning system. The pressure relief valve 60 ensures that the exhaust conditions are met in advance when the compressor is operating at low operating conditions, so as to discharge the gas in advance and reduce power consumption.

[0057] This application utilizes the existing oil circuit structure and adds a new cavity oil channel 130 to ensure a sufficiently large pressure difference, so that the refrigerant oil is continuously supplied into the compression cavity 30. In addition, a portion of the oil volume in the end face oil pipe section 140 is diverted away, further reducing the accumulation of refrigerant oil in the compression cavity 30, which affects the heat exchange efficiency and reduces performance in the compression cavity 30. Furthermore, the diameter of the newly designed oil injection hole 190 is smaller than that of the end face oil pipe section 140. Calculations based on Bernoulli's equation show that the flow velocity of the newly designed stationary disc oil injection pipe section 133 and oil injection hole 190 is greater than that of the end face oil pipe section 140, while the flow rate is less. After acceleration by the stationary disc oil injection pipe section 133, the flow velocity at the oil injection hole 190 ranges from 0.5 to 2 m / s. Thus, the newly designed stationary disc oil injection pipe section 133 and oil injection hole 190 play the role of providing a low-volume, high-speed oil supply that is discharged from the compression chamber 30 along with the compressed gas. The cooling oil used will not accumulate in the compression chamber 30, thus carrying away heat in time and reducing the temperature inside the compression chamber and the exhaust gas.

[0058] In this invention, the active cooling structure is simple, requiring no additional cold source. Utilizing its own pressure differential oil-guided structure, a new cooling path is added to lower the temperature of the compression chamber. Furthermore, the energy is recycled, eliminating the need for an additional power source. This design not only ensures the compressor's efficient, stable, and reliable long-term operation but also reduces heat exchange losses, improves heat exchange efficiency and speed, facilitates timely heat removal, lowers exhaust temperature, and enhances overall performance by lowering the temperature.

[0059] As can be seen from the above description, the embodiments of this utility model achieve the following technical effects:

[0060] The stationary disc structure of this utility model includes a stationary disc 10 and a receiving cavity 110 and an opening 120 disposed on the stationary disc 10. The opening 120 is located on the side of the receiving cavity 110 facing the moving disc 20 and is blocked by the moving disc 20, so that the upper surfaces of the receiving cavity 110 and the moving disc 20 together form a compression cavity 30. The stationary disc 10 is also provided with a cavity oil channel 130 and an end face oil pipe section 140. The inlet of the cavity oil channel 130 is connected to the oil supply pipeline 150 outside the stationary disc structure, and the outlet of the cavity oil channel 130 is opened on the inner wall of the receiving cavity 110 and spaced apart from the opening 120 to spray oil into the compression cavity 30. The inlet of the end face oil pipe section 140 is connected to the cavity oil channel 130. The stationary disc 10 has a lower end face 160, and the outlet of the end face oil pipe section 140 is located on the lower end face 160 to supply oil between the lower end face 160 and the moving disc 20.

[0061] As can be seen, this utility model directly sprays refrigerant oil into the compression chamber 30 through the cavity oil channel 130, allowing the refrigerant oil to directly contact the compressed gas, increasing the heat exchange area and improving the heat exchange efficiency. This is more direct and effective than the prior art's oil supply through the gap between the end faces of the moving and stationary discs, ensuring that the refrigerant oil can quickly absorb the heat of the compressed gas, reduce the temperature of the compression chamber, and thus reduce the power consumption of the compressor and improve its performance. The spacing between the outlet and opening 120 of the cavity oil channel 130, as well as the determination of the oil spray position, can prevent excessive oil from remaining in the compression chamber 30, ensuring sufficient cooling effect while avoiding performance degradation caused by excessive oil. Furthermore, the oil pipe section 140 supplies oil to the lower end face 160 of the stationary disc 10, optimizing the lubrication effect between the moving and stationary discs, reducing friction, and improving the compressor's operational stability and lifespan. At the same time, this design helps to reduce the oil film thickness on the end faces of the moving and stationary discs, improving the cooling efficiency of the oil and effectively solving the problem of low cooling efficiency of the compression chamber in the existing scroll compressor cooling method.

[0062] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that 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.

[0063] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices 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 drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0064] In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0065] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0066] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0067] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A static disk structure, characterized in that, The system includes a stationary disk (10) and a receiving cavity (110) and an opening (120) disposed on the stationary disk (10). The opening (120) is located on the side of the receiving cavity (110) facing the moving disk (20) and is blocked by the moving disk (20) so that the receiving cavity (110) and the upper surface of the moving disk (20) together form a compression cavity (30). The stationary disk (10) is also provided with a cavity oil channel (130) and an end face oil pipe section (140). The inlet of the cavity oil passage (130) is connected to the oil supply pipeline (150) outside the static disc structure, and the outlet of the cavity oil passage (130) is opened on the inner wall of the receiving cavity (110) and spaced apart from the opening (120) to spray oil into the compression cavity (30). The inlet of the end face oil pipe section (140) is connected to the cavity oil channel (130), the stationary plate (10) has a lower end face (160), and the outlet of the end face oil pipe section (140) is located on the lower end face (160) to supply oil between the lower end face (160) and the moving plate (20).

2. The static disk structure according to claim 1, characterized in that, The stationary disc (10) has a stationary disc axis. The cavity oil passage (130) further includes a first oil injection pipe section (131), a second oil injection pipe section (132), and a stationary disc oil injection pipe section (133) connected in sequence. The first oil injection pipe section (131) is arranged parallel to the stationary disc axis. The inlet of the first oil injection pipe section (131) is connected to the outlet of the oil supply pipeline (150). The second oil injection pipe section (132) is arranged perpendicular to the stationary disc axis. The inlet of the second oil injection pipe section (132) is connected to the outlet of the first oil injection pipe section (131). The outlet of the second oil injection pipe section (132) is connected to the inlet of the stationary disc oil injection pipe section (133). The outlet of the stationary disc oil injection pipe section (133) is connected to the inner wall of the receiving cavity (110) to input oil into the receiving cavity (110).

3. The static disk structure according to claim 2, characterized in that, The end face oil pipe section (140) is arranged parallel to the axis of the stationary disc. The inlet of the end face oil pipe section (140) is connected to the inner wall of the second oil injection pipe section (132), and the end face oil pipe section (140) is located on the side of the second oil injection pipe section (132) near the lower end face (160).

4. The static disk structure according to claim 2, characterized in that, The second fuel injection pipe section (132) and the outer peripheral surface of the stationary disc (10) are provided with a machining hole (170). The machining hole (170) is connected to the end of the second fuel injection pipe section (132) away from the receiving cavity (110). The stationary disc structure also includes a sealing component (180) disposed in the machining hole (170) to seal the machining hole (170).

5. The static disk structure according to claim 2, characterized in that, The inner wall of the first fuel injection pipe section (131) is cylindrical; and / or The inner wall of the second fuel injection pipe section (132) is cylindrical; and / or The inner wall of the stationary disc injection pipe section (133) is frustum-shaped, and the diameter of the inner wall of the stationary disc injection pipe section (133) gradually decreases in the direction away from the second injection pipe section (132); and / or The inner wall of the end face oil pipe section (140) is cylindrical.

6. The static disk structure according to claim 5, characterized in that, One end of the stationary disc injection pipe section (133) that communicates with the receiving cavity (110) is an injection hole (190), and the stationary disc structure also includes a nozzle disposed at the injection hole (190).

7. The static disk structure according to claim 5, characterized in that, The end of the static disc injection pipe section (133) that connects to the receiving cavity (110) is an injection hole (190). The distance between the center of the injection hole (190) and the opening (120) is H1, and the distance between the center of the injection hole (190) and the upper end face of the receiving cavity (110) is H2. H1 / H2 is greater than or equal to 0.46 and less than or equal to 0.5; and / or, H1 is greater than or equal to 7.3 mm and less than or equal to 7.9 mm.

8. The static disk structure according to claim 2, characterized in that, A high-pressure oil tank (161) is also provided on the lower end face (160), and the end face oil pipe section (140) is connected to the high-pressure oil tank (161) to allow the oil to flow into the high-pressure oil tank (161).

9. The static disk structure according to claim 8, characterized in that, The high-pressure oil groove (161) is a curved groove that is at least partially provided around the lower end face (160) in the circumferential direction. The high-pressure oil groove (161) is located between the outer peripheral surface of the compression chamber (30) and the stationary plate (10) so that a part of the oil in the cavity oil channel (130) flows into the high-pressure oil groove (161) and another part of the oil in the cavity oil channel (130) flows into the compression chamber (30).

10. A scroll compressor, characterized in that, It includes a static disk structure, wherein the static disk structure is the static disk structure according to any one of claims 1 to 9.

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