Compressor pressure relief structure, compressor and air conditioner

Abstract

The invention provides a compressor pressure relief structure, a compressor and an air conditioner. The compressor pressure relief structure comprises a first-stage compression assembly and a second-stage compression assembly. A first pressure relief channel is formed in the partition plate assembly, an assembly avoiding groove and a second pressure relief channel are formed in the second-stage air cylinder, the assembly avoiding groove can communicate with a shell cavity of the compressor through the second pressure relief channel, and at least part of structure of an opening and closing element is arranged in the assembly avoiding groove; the opening and closing element can move in the assembling receding groove and the second pressure relief channel so that the second pressure relief channel and the first pressure relief channel can be connected or disconnected. The opening and closing element comprises a first end and a second end which are opposite to each other, the first end is opposite to the first pressure relief channel so as to bear gas pressure of the first pressure relief channel, and the second pressure relief channel can introduce gas into the assembling receding groove and reach the end face groove so as to apply pressure to the pressed area. According to the compressor, the technical problem that in the prior art, a rivet pressure relief valve plate structure is adopted for a compressor, and flutter occurs can be solved.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, specifically relating to a compressor pressure relief structure, a compressor, and an air conditioner. Background Technology

[0002] A conventional two-stage rotary compressor consists of main components such as a pump body assembly, a motor assembly, a distributor, and a sealed housing. The pump body assembly includes a crankshaft, upper and lower flange assemblies, a first-stage cylinder and rollers, a second-stage cylinder and rollers, an intermediate partition assembly, and a lower flange cover. These pump body components work together to form a primary compression chamber, a secondary compression chamber, and an intermediate chamber. Each compression chamber is divided into two sealed chambers by vanes. Driven by the crankshaft rotation, the vanes reciprocate, causing the volumes of the two chambers to change periodically, forming a high-pressure chamber (exhaust chamber) and a low-pressure chamber (intake chamber), thus achieving periodic gas compression. The low-pressure refrigerant enters the primary compression chamber from the receiver, is compressed to a medium temperature and pressure after primary compression, and then enters the intermediate chamber. The medium-pressure gas in the intermediate chamber finally flows into the secondary compression chamber, is compressed to a high temperature and high pressure state, and then exits through a silencer chamber into the compressor housing, and further exits the compressor into the system. High-temperature and high-pressure gas releases heat through heat exchange with the outside environment in the system condenser, its temperature decreases, and it further condenses into liquid. The low-temperature and high-pressure liquid is discharged, and the low-temperature and low-pressure wet vapor is discharged through the throttling valve. It enters the evaporator, where it evaporates and vaporizes to form low-temperature and low-pressure vapor. The vapor then enters the compressor pump body through the liquid receiver, completing the entire system cycle.

[0003] A two-stage enthalpy-increasing compressor is a type of two-stage compressor. Based on a conventional two-stage compressor, an enthalpy-increasing gas supply channel is added to the intermediate cavity. This means that the temperature and pressure of the intermediate cavity are further increased by increasing enthalpy, which can increase the pump's intake volume while reducing the working pressure ratio of the compression cylinder, thus significantly improving the compressor and system capacity and energy efficiency.

[0004] When conventional two-stage (enthalpy-increasing) compressors and systems using them are left stagnant for extended periods in low-temperature environments (especially ultra-low temperatures below -20°C), or when the system load fluctuates significantly or the evaporator heat exchange is poor, a large amount of liquid refrigerant will exist on the low-pressure side of the system. When the heating mode is started, a large amount of liquid refrigerant will enter the first-stage compression chamber of the compressor. Due to the incompressibility of liquid refrigerant, its volume is much smaller than that of gas, making it highly susceptible to liquid slugging. During the compression process in the chamber, this will cause a sudden increase in intermediate pressure and an abnormal increase in the pressure ratio of the first-stage compression chamber. When high-pressure refrigerant containing liquid enters the second-stage compression chamber, it will further cause the pressure in the second-stage compression chamber to rise rapidly, which will then trigger an overpressure trip in the second-stage compression chamber (when the pressure exceeds the safety threshold, the control system will trigger the overpressure trip protection), affecting the stable operation of the compressor and the system.

[0005] The existing technology CN112302939A uses a structure with rivet-mounted exhaust valve plates on the flange to relieve pressure in the intermediate cavity. However, this solution is prone to repeated fluttering of the free end of the thin-walled valve plate under the action of high-pressure airflow pulsation during the pressure relief process, which reduces the stability of the pressure relief process and easily causes noise or vibration.

[0006] Because existing compressors use a rivet-studded exhaust valve plate structure for depressurization of the intermediate cavity, technical problems such as chattering can occur. Therefore, this invention studies and designs a compressor depressurization structure and a compressor. Summary of the Invention

[0007] Therefore, the present invention provides a compressor pressure relief structure, a compressor, and an air conditioner, which can solve the technical problem that the use of riveted exhaust valve plates in the prior art can lead to vibration.

[0008] To solve the above problems, the present invention provides a compressor pressure relief structure, including: a primary compression assembly and a secondary compression assembly, wherein a partition assembly is provided between the primary compression assembly and the secondary compression assembly, and the partition assembly has an intermediate cavity, wherein the intermediate cavity is connected to the chamber of the primary compression assembly and the chamber of the secondary compression assembly respectively. The partition assembly is provided with a first pressure relief channel, which communicates with the intermediate cavity. The secondary compression assembly includes a secondary cylinder. The secondary cylinder is provided with an assembly clearance groove and a second pressure relief channel opposite to the first pressure relief channel. The second pressure relief channel is located between the assembly clearance groove and the first pressure relief channel. The second pressure relief channel can communicate the assembly clearance groove with the compressor housing chamber. At least a portion of the structure of an opening and closing element is provided in the assembly clearance groove. The opening and closing element can move within the assembly clearance groove and the second pressure relief channel to connect or disconnect the second pressure relief channel from the first pressure relief channel. The opening and closing element includes a first end and a second end facing away from each other. The first end is opposite to the first pressure relief channel to withstand the gas pressure of the first pressure relief channel. The area on the second end passing through the central axis of the opening and closing element is a pressure-bearing area. The pressure-bearing area is formed by a recessed end face groove. The second pressure relief channel can introduce gas into the assembly clearance groove and reach the end face groove to apply pressure to the pressure-bearing area.

[0009] In some implementations... The opening and closing element is a cylindrical structure, including a boss portion and a non-boob portion connected in its axial direction. The second end is opposite to the bottom of the mounting clearance groove. The boss portion is located on the second end and is connected to the outer periphery of the opening and closing element. The boss portion protrudes toward the bottom of the mounting clearance groove, so that the inner periphery of the boss portion forms the end face groove.

[0010] In some implementations... A flow channel is provided between the inner circumference and the outer circumference of the boss portion, and the flow channel can connect the end face groove with the assembly clearance groove on the outer circumference of the opening and closing element.

[0011] In some implementations... A first flow channel is formed from the bottom of the groove on the end face toward the interior of the non-protruding part, and a second flow channel is also formed inside the non-protruding part. One end of the second flow channel extends through to the outer periphery of the non-protruding part to communicate with the assembly clearance groove, and the other end of the second flow channel extends to communicate with the first flow channel.

[0012] In some implementations... The second pressure relief channel is disposed on the end face of the secondary cylinder facing the partition assembly. The second pressure relief channel extends in the radial direction of the secondary cylinder. The radial inner end of the second pressure relief channel extends beyond the radial inner end of the assembly clearance groove and beyond the radial inner end of the first pressure relief channel. The radial outer end of the second pressure relief channel extends to the radial outer end of the secondary cylinder.

[0013] In some implementations... Both the assembly clearance groove and the opening / closing element are cylindrical structures, and the inner diameter of the assembly clearance groove is larger than the outer diameter of the opening / closing element, so that there is a gap channel between the inner wall of the assembly clearance groove and the outer periphery of the opening / closing element. This gap channel is connected to the second pressure relief channel, so that the gas in the second pressure relief channel enters the assembly clearance groove through the gap channel to act on the pressure-bearing area of ​​the opening / closing element.

[0014] In some implementations... The crankshaft axis of the compressor is defined as the axial direction. The first pressure relief channel is a circular hole structure with an inner diameter of d1. The depth of the second pressure relief channel along the axial direction is H1. The outer diameter of the opening and closing element is d2. The height of the opening and closing element along the axial direction is H2. The inner diameter of the end face groove is d20. The depth of the end face groove along the axial direction is H20. The inner diameter of the assembly clearance groove is d3. The depth of the assembly clearance groove along the axial direction is H3. The parameters H1, H2, H3, d1, d2, and d3 satisfy: H3 > H2 > H1, d3 > d2 > d1, and d3 - d2 < (d3 - d1) / 2.

[0015] In some implementations... The parameters H1, H2, H20, H3, d1, d2, d20, and d3 also satisfy the following conditions: H20 > 0.5, H3 - H2 > 0.5, and 1 < d3 - d2 < (d3 - d1) / 2 - 2. The units of parameters H1, H2, H20, H3, d1, d2, d20, and d3 are all mm.

[0016] In some implementations... When the opening and closing element is connected to the partition assembly, the opening and closing element closes the connection between the first pressure relief channel and the second pressure relief channel; when the opening and closing element is not connected to the partition assembly, the opening and closing element opens the connection between the first pressure relief channel and the second pressure relief channel, so that the intermediate cavity releases gas into the shell chamber through the first pressure relief channel and the second pressure relief channel.

[0017] In some implementations... The secondary cylinder is located at the upper end of the partition assembly. The lower end of the opening and closing element is the first end, which is to withstand the upward gas pressure F1 exerted on it by the first pressure relief channel. The gas pressure in the first pressure relief channel is equal to the gas pressure in the intermediate cavity. The upper end of the opening and closing element is the second end. The pressure-bearing area of ​​the second end can withstand the downward gas pressure F2 exerted on it by the assembly clearance groove. The gas pressure in the assembly clearance groove is equal to the gas pressure in the second pressure relief channel. The opening and closing element also withstands its own downward gravity G.

[0018] In some implementations... When the force F1 on the opening and closing element is less than F2+G, the opening and closing element can move downward to connect with the partition assembly, thereby closing the connection between the first pressure relief channel and the second pressure relief channel; when the force F1 on the opening and closing element is greater than F2+G, the opening and closing element can move upward to not connect with the partition assembly, thereby opening the connection between the first pressure relief channel and the second pressure relief channel, so that the intermediate cavity can release gas pressure into the shell chamber through the first pressure relief channel and the second pressure relief channel.

[0019] In some implementations... The primary compression assembly includes a primary cylinder, and the partition assembly includes an upper partition and a lower partition. The upper partition is connected to the lower end face of the secondary cylinder, and the lower partition is connected to the upper end face of the primary cylinder. The intermediate cavity is disposed inside the lower partition. The assembly clearance groove is a recessed groove structure opened from the lower end face of the secondary cylinder upwards, and the first pressure relief channel is a circular hole structure that penetrates the upper partition plate, with its center line coinciding with the center line of the assembly clearance groove.

[0020] In some implementations... The first pressure relief channel, the second pressure relief channel, the assembly clearance groove, and the opening and closing element constitute a pressure relief assembly. The number of pressure relief assemblies is n, where n is a natural number greater than or equal to 1. When n is greater than 1, the n pressure relief assemblies are evenly spaced along the circumferential direction.

[0021] The present invention also provides a compressor that includes the aforementioned compressor pressure relief structure.

[0022] The present invention also provides an air conditioner that includes the aforementioned compressor.

[0023] The compressor pressure relief structure, compressor, and air conditioner provided by this invention have the following beneficial effects: This invention provides a first pressure relief channel on a partition assembly between a primary compressor assembly and a secondary compressor assembly, connecting it to an intermediate cavity on the partition assembly. Simultaneously, it provides a mounting clearance groove and a second pressure relief channel on the secondary cylinder, positioned opposite the first pressure relief channel. An opening / closing element is installed in the mounting clearance groove. The first end of the opening / closing element faces the first pressure relief channel to withstand the gas pressure of the intermediate cavity, while the second end faces the mounting clearance groove. The second pressure relief channel allows gas pressure from the housing chamber to enter the mounting clearance groove, thus ensuring that the pressure-bearing area at the second end of the opening / closing element withstands the gas pressure of the housing chamber. Specifically, the pressure introduced from within the housing through the end face groove acts on the pressure-bearing area. Therefore, the opening / closing element automatically moves according to the pressures of the intermediate cavity and the housing chamber at its two ends, respectively. In particular, it opens the connection between the first and second pressure relief channels when the pressure in the intermediate cavity exceeds the pressure in the housing chamber, achieving automatic pressure relief of the intermediate cavity. This is significantly different from the riveting method used in existing technologies. Regarding the riveted exhaust valve plate, this invention improves the reliability of resisting abnormal liquid slugging pressure, preventing the free end of the thin-arm valve plate from repeatedly vibrating under the action of high-pressure airflow pulsation. It effectively improves stability during pressure relief, preventing noise or vibration caused by vibration, and offers faster response and better timeliness of opening and closing. It effectively solves the technical problem of vibration caused by the riveted exhaust valve plate structure in existing compressors. Furthermore, the pressure-bearing area of ​​the opening and closing element of this invention introduces the pressure inside the housing. Compared to existing solutions that introduce pressure from the cylinder body, the pressure inside the cylinder is usually lower than the pressure inside the housing. If applied to the pressure relief valve of this invention, it would cause the valve to open prematurely, leading to backflow of gas inside the housing and preventing normal and effective pressure relief. Therefore, compared to various existing solutions, this invention achieves a stable pressure relief effect, prevents vibration, has a faster response speed, and more precise pressure relief action, achieving stable pressure relief. Moreover, this invention eliminates the need for additional pipelines for pressure relief, reducing compressor manufacturing costs and decreasing compressor size. Attached Figure Description

[0024] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0025] Figure 1 This is the assembly structure of the compressor pressure relief structure of the present invention. Figure 1 ; Figure 2 yes Figure 1A magnified view of part K (with the opening and closing element in the closed state); Figure 3 yes Figure 1 A magnified view of part K (opening / closing element). Figure 4 yes Figure 1 A magnified view of part K (the point where the opening and closing element is in the open to closed state). Figure 5 yes Figure 1 The main view of the opening and closing element in the middle; Figure 6 yes Figure 1 A top view of the opening and closing elements in the middle; Figure 7 This is a schematic diagram of the working principle of the compressor pressure relief structure of the present invention; Figure 8 This is a partial enlarged view of part K of the compressor pressure relief structure in an alternative embodiment of the present invention (the point where the opening and closing element is in the open to closed state). Figure 9 yes Figure 8 A front sectional view of the opening and closing element in the middle; Figure 10 yes Figure 8 A top view of the opening and closing elements in the diagram.

[0026] The attached figures are labeled as follows: 1. Pump body assembly; 2. Motor assembly; 101. Primary compression chamber; 102. Secondary compression chamber; 103. Intermediate chamber; 104. Enthalpy-increasing gas supply channel; 121. Upper flange; 122. Lower flange; 131. Primary cylinder; 132. Secondary cylinder; 141. Upper partition; 142. Lower partition; 161. Primary cylinder roller; 162. Secondary cylinder roller; 18. Pressure relief assembly; 181. Opening and closing element; 1811 1812. Bossed section; 1813. Non-boobedient section; 1814. Flow channel; 18121. First flow channel; 18122. Second flow channel; 1821. First pressure relief channel; 1822. Second pressure relief channel; 183. Assembly clearance groove; 184. Gap channel; 1841. End face groove; 185. Pressure-bearing area; 3. First end; 4. Second end; 5. Housing chamber; 11. Crankshaft; 15. Lower flange cover. Detailed Implementation

[0027] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0028] In the description of this invention, 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 generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention 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 invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0029] 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.

[0030] 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 should not be construed as limiting the scope of protection of this invention.

[0031] See also Figure 1-10As shown, according to an embodiment of the present invention, a compressor pressure relief structure is provided, which includes: a primary compression assembly and a secondary compression assembly, a partition assembly is provided between the primary compression assembly and the secondary compression assembly, the partition assembly has an intermediate cavity 103, and the intermediate cavity 103 is connected to the chamber of the primary compression assembly and the chamber of the secondary compression assembly respectively. The partition assembly is provided with a first pressure relief channel 1821, which communicates with the intermediate cavity 103. The secondary compression assembly includes a secondary cylinder 132. The secondary cylinder 132 is provided with an assembly clearance groove 183 and a second pressure relief channel 1822 opposite to the first pressure relief channel 1821. The second pressure relief channel 1822 is located between the assembly clearance groove 183 and the first pressure relief channel 1821, and can communicate the assembly clearance groove 183 with the compressor housing chamber 5. The assembly clearance groove 183 is provided with at least a portion of the structure of an opening and closing element 181, which can be connected to the compressor housing chamber 5. The device moves within the mounting clearance groove 183 and the second pressure relief channel 1822 to connect or disconnect the second pressure relief channel 1822 from the first pressure relief channel 1821. The opening and closing element 181 includes a first end 3 and a second end 4 facing away from each other. The first end 3 is opposite to the first pressure relief channel 1821 to withstand the gas pressure of the first pressure relief channel 1821. The area on the second end 4 that is in contact with its outer periphery is a pressure-bearing area 185. The pressure-bearing area 185 is formed by a recessed end face groove 1841. The second pressure relief channel 1822 can introduce gas into the mounting clearance groove 183 and reach the end face groove 1841 to apply pressure to the pressure-bearing area 185.

[0032] This invention provides a first pressure relief channel on a partition assembly between a primary compressor assembly and a secondary compressor assembly, connecting it to an intermediate cavity on the partition assembly. Simultaneously, it provides a mounting clearance groove and a second pressure relief channel on the secondary cylinder, positioned opposite the first pressure relief channel. An opening / closing element is installed in the mounting clearance groove. The first end of the opening / closing element faces the first pressure relief channel to withstand the gas pressure of the intermediate cavity, while the second end faces the mounting clearance groove. The second pressure relief channel allows gas pressure from the housing chamber to enter the mounting clearance groove, thus ensuring that the pressure-bearing area of ​​the opening / closing element is subjected to the gas pressure of the housing chamber. Specifically, the pressure introduced from within the housing through the end face groove acts on the pressure-bearing area. Therefore, the opening / closing element automatically moves according to the pressures of the intermediate cavity and the housing chamber at its two ends, respectively. In particular, it can open the connection between the first and second pressure relief channels when the pressure in the intermediate cavity is greater than the pressure in the housing chamber, achieving automatic pressure relief of the intermediate cavity. This is significantly different from the rivet-type structures used in existing technologies. Regarding the valve plate, this invention improves the reliability of resisting abnormal liquid slugging pressure, preventing the free end of the riveted thin-arm valve plate from repeatedly vibrating under the action of high-pressure airflow pulsation. It effectively improves stability during pressure relief, preventing noise or vibration caused by vibration, and offers faster response and better timeliness of opening and closing. It effectively solves the technical problem of vibration caused by the riveted exhaust valve plate structure in existing compressors. Furthermore, the pressure-bearing area of ​​the opening and closing element of this invention introduces the pressure inside the housing. Compared to existing solutions that introduce pressure from the cylinder body, the pressure inside the cylinder is usually lower than the pressure inside the housing. If applied to the pressure relief valve of this invention, it would cause the valve to open prematurely, leading to backflow of gas inside the housing and preventing normal and effective pressure relief. Therefore, compared to various existing solutions, this invention achieves a stable pressure relief effect, prevents vibration, has a faster response speed, and more precise pressure relief action, achieving stable pressure relief. Moreover, this invention eliminates the need for additional pipelines for pressure relief, reducing compressor manufacturing costs and decreasing compressor size.

[0033] This invention also solves the following technical problems: 1. The use of riveted exhaust valve plates in existing compressor technologies can lead to vibration issues. 2. Avoid introducing pressure into the cylinder body as back pressure, which could cause gas to flow into the housing and prevent normal pressure relief.

[0034] 3. When conventional two-stage (enthalpy-increasing) compressors and systems using them are left stagnant for a long time in low-temperature environments (especially ultra-low temperature environments below -20℃), or when the system load changes significantly or the evaporator heat exchange is poor, liquid slugging can cause a sudden increase in the pressure of the intermediate-pressure chamber, which in turn can lead to overpressure tripping of the secondary compression chamber, affecting the stable operation of the system.

[0035] 4. Existing pressure relief technology solutions that involve setting external pipelines and differential pressure control valves require additional system pipelines and control valves, which increases manufacturing costs and makes the pipeline layout more complex, thus affecting the overall heating performance and system reliability.

[0036] Example 1, such as Figure 1-6 In some implementation methods, The opening and closing element 181 is a cylindrical structure, including a boss portion 1811 and a non-boob portion 1812 connected in its axial direction. The second end 4 is opposite to the bottom of the mounting clearance groove 183. The boss portion 1811 is located on the second end 4 and is connected to the outer periphery of the opening and closing element 181. The boss portion 1811 protrudes toward the bottom of the mounting clearance groove 183, so that the inner periphery of the boss portion 1811 forms the end face groove 1841.

[0037] This is a preferred structural form of the opening and closing element in Embodiment 1 of the present invention, which forms an end face groove. By providing an upwardly protruding boss at the upper edge, an end face groove that can introduce gas can be formed on its inner circumference. This allows the end face groove to introduce gas from the inner cavity of the housing and act on the pressure-bearing area of ​​the opening and closing element, thereby achieving automatic pressure relief when the pressure in the intermediate cavity is greater than the pressure in the inner cavity of the housing. Compared with the valve plate structure, this can prevent chatter and improve the stability of pressure relief. The back pressure introduced into the inner cavity of the housing, compared with the back pressure introduced into the cylinder pressure, will not cause gas in the inner cavity of the housing to flow back into the intermediate cavity, avoiding the situation where normal and stable pressure relief cannot be performed, and further improving the stability of pressure relief.

[0038] In some implementations... A flow channel 1813 is provided between the inner circumference and the outer circumference of the boss portion 1811, and the flow channel 1813 can connect the end face groove 1841 with the assembly clearance groove 183 on the outer circumference of the opening and closing element 181.

[0039] In a further preferred embodiment of the present invention, a through-flow channel is provided between the inner and outer circumferences of the boss portion. This allows gas in the assembly clearance groove to be introduced into the end face groove through the flow channel, thereby acting on the pressure area to achieve the purpose and effect of providing back pressure to the top of the opening and closing element. This allows for automatic pressure relief based on the relationship between the pressure in the intermediate cavity and the pressure in the inner cavity of the housing.

[0040] Example 2, as Figure 8-10 In some implementation methods, A first flow channel 18121 is formed from the bottom of the end face groove 1841 toward the interior of the non-protrusion portion 1812. A second flow channel 18122 is also formed inside the non-protrusion portion 1812. One end of the second flow channel 18122 extends to the outer periphery of the non-protrusion portion 1812 to communicate with the assembly clearance groove 183. The other end of the second flow channel 18122 extends to communicate with the first flow channel 18121.

[0041] This is a preferred structural form of the assembly clearance groove and the end face groove of the inner circumference in Embodiment 2 of the present invention. By providing first and second flow channels inside the non-protruding part of the opening and closing element, the first flow channel is used to connect the end face groove to the inside of the non-protruding part, and the second flow groove is used to connect the assembly clearance groove and the first flow channel. This allows gas from the inside of the housing cavity to be introduced into the end face groove at the upper end of the opening and closing element and act on the pressure area of ​​the opening and closing element, realizing automatic pressure relief when the pressure in the intermediate cavity is greater than the pressure in the housing cavity. Compared with the valve plate structure, it can prevent chatter and improve the stability of pressure relief. The back pressure is introduced into the housing cavity pressure. Compared with the back pressure is introduced into the cylinder pressure, the gas in the housing cavity will not flow back into the intermediate cavity, avoiding the situation where normal and stable pressure relief cannot be performed, and further improving the stability of pressure relief.

[0042] In some implementations... The second pressure relief channel 1822 is disposed on the end face of the secondary cylinder 132 facing the partition assembly. The second pressure relief channel 1822 extends in the radial direction of the secondary cylinder 132. The radial inner end of the second pressure relief channel 1822 extends beyond the radial inner end of the mounting clearance groove 183 and beyond the radial inner end of the first pressure relief channel 1821. The radial outer end of the second pressure relief channel 1822 extends to the radial outer end of the secondary cylinder 132.

[0043] This is a preferred structural form of the second pressure relief channel of the present invention, namely, a channel provided on the end face of the secondary cylinder facing the partition assembly and extending radially. Moreover, the radial inner end of the second pressure relief channel extends beyond the inner end of the mounting clearance groove and the radial inner end of the first pressure relief channel, which can increase the length of the pressure relief channel and increase the length of the second pressure relief channel as an air duct to the second end of the opening and closing element, thereby improving the pressure relief effect and the air ducting performance. The radial outer end of the second pressure relief channel extends to the radial outer end of the secondary cylinder, which can enhance its communication with the inner cavity of the housing, effectively ducting air from the inner cavity of the housing and effectively releasing the gas in the intermediate cavity into the inner cavity of the housing.

[0044] In some implementations... Both the assembly clearance groove 183 and the opening / closing element 181 are cylindrical structures, and the inner diameter of the assembly clearance groove 183 is larger than the outer diameter of the opening / closing element 181, so that there is a gap channel 184 between the inner wall of the assembly clearance groove 183 and the outer periphery of the opening / closing element 181. The gap channel 184 is connected to the second pressure relief channel 1822, so that the gas in the second pressure relief channel 1822 enters the assembly clearance groove 183 through the gap channel 184 to act on the pressure-bearing area 185 of the opening / closing element 181.

[0045] This is a further preferred structural form of the assembly clearance groove and the opening and closing element of the present invention. By setting the inner diameter of the assembly clearance groove to be larger than the outer diameter of the opening and closing element, the above-mentioned gap channel can be effectively formed between the assembly clearance groove and the opening and closing element, thereby effectively ensuring the communication between the second pressure relief channel and the assembly clearance groove, reliably introducing the gas pressure in the inner cavity of the housing to act on the pressure-bearing area of ​​the opening and closing element, and improving the accuracy and stability of the automatic pressure relief process according to the pressure magnitude.

[0046] In some implementations... The crankshaft axis of the compressor is defined as the axial direction. The first pressure relief channel 1821 is a circular hole structure with an inner diameter of d1. The second pressure relief channel 1822 has a depth of H1 along the axial direction. The outer diameter of the opening and closing element 181 is d2, and the height of the opening and closing element 181 along the axial direction is H2. The inner diameter of the end face groove 1841 is d20, and the depth of the end face groove 1841 along the axial direction is H20. The inner diameter of the assembly clearance groove 183 is d3, and the depth of the assembly clearance groove 183 along the axial direction is H3. The parameters H1, H2, H3, d1, d2, and d3 satisfy: H3 > H2 > H1, d3 > d2 > d1, and d3 - d2 < (d3 - d1) / 2.

[0047] The present invention, by setting the inner diameter of the first pressure relief channel as d1, the depth of the second pressure relief channel as H1, the total height and outer diameter of the opening and closing element 181 as H2 and d2, the inner diameter and depth of the end face groove as d20 and H20, and the inner diameter and depth of the assembly clearance groove as d3 and H3 respectively, and the parameters H1, H2, H3, d1, d2, and d3 satisfying: H3 > H2 > H1, d3 > d2 > d1, enables the opening and closing element 181 to be normally assembled in the clearance groove and to move axially back and forth in the clearance groove, while ensuring that the opening and closing element 181 can be effectively constrained in the radial direction when the pressure relief channel is closed and open; furthermore, the parameters d1, d2, and d3 satisfying: d3 - d2 < (d3 - d1) / 2, under the premise of ensuring normal assembly, ensures that the opening and closing element can achieve the isolation between the medium pressure cavity and the inner cavity of the shell when it is in the extreme position in the closed state, and that the end of the opening and closing element away from the low pressure cavity can be continuously subjected to pressure.

[0048] In some implementations... The parameters H1, H2, H20, H3, d1, d2, d20, and d3 also satisfy the following conditions: H20 > 0.5, H3 - H2 > 0.5, and 1 < d3 - d2 < (d3 - d1) / 2 - 2. The units of parameters H1, H2, H20, H3, d1, d2, d20, and d3 are all mm.

[0049] This invention further satisfies the following conditions for the opening and closing element: H1, H2, H20, H3, d1, d2, d20, and d3: H20 > 0.5, H3 - H2 > 0.5, and 1 < d3 - d2 < (d3 - d1) / 2 - 2. This ensures unobstructed flow of pressure relief through the opening and closing element when it is open, and effectively fills the cavity of the end face groove of the opening and closing element away from the intermediate cavity 103 with high-pressure gas during the closing process or when it is closed. This allows the opening and closing element to close promptly and ensures the sealing performance of the opening and closing element to the intermediate cavity. All parameters mentioned in this invention are in mm.

[0050] In some implementations... When the opening and closing element 181 is connected to the partition assembly, the opening and closing element 181 closes the connection between the first pressure relief channel 1821 and the second pressure relief channel 1822; when the opening and closing element 181 is not connected to the partition assembly, the opening and closing element 181 opens the connection between the first pressure relief channel 1821 and the second pressure relief channel 1822, so that the intermediate cavity 103 releases gas into the shell chamber 5 through the first pressure relief channel 1821 and the second pressure relief channel 1822.

[0051] This is the preferred relationship between the movement state of the opening and closing element of the present invention and whether or not there is a connection between the first and second pressure relief channels. That is, when the opening and closing element moves to the point of contact with the partition assembly, the connection between the first and second pressure relief channels is effectively closed and no pressure is released. When the opening and closing element moves to the point of not contacting the partition assembly, the connection between the first and second pressure relief channels is effectively opened and the gas in the intermediate cavity is released into the housing cavity through the first and second pressure relief channels.

[0052] In some implementations... The secondary cylinder 132 is located at the upper end of the partition assembly. The lower end of the opening and closing element 181, i.e. the first end 3, is to withstand the upward gas pressure F1 exerted on it by the first pressure relief channel 1821. The gas pressure in the first pressure relief channel 1821 is equal to the gas pressure in the intermediate cavity 103. The upper end of the opening and closing element 181, i.e. the second end 4, is to withstand the downward gas pressure F2 exerted on it by the assembly clearance groove 183. The gas pressure in the assembly clearance groove 183 is equal to the gas pressure in the second pressure relief channel 1822. The opening and closing element 181 also withstands its own downward gravity G.

[0053] This invention describes the automatic pressure relief process where the opening and closing element automatically opens or closes the connection between the first and second pressure relief channels based on the magnitude of the pressure at both ends and the magnitude of gravity. Specifically, the pressure-bearing area at the upper end of the opening and closing element bears the pressure of the second pressure relief channel, i.e., the inner cavity of the housing, while the lower end of the opening and closing element bears the pressure of the first pressure relief channel, i.e., the intermediate cavity. The gravity of the opening and closing element of this invention is G. Since its gravity is relatively small compared to the gas pressure above and below, it can be ignored. Therefore, it can automatically open the pressure relief channel to relieve pressure in the intermediate cavity or close the pressure relief channel based on the pressure relationship between the intermediate cavity and the inner cavity of the housing.

[0054] In some implementations... When the force on the opening and closing element 181 is F1 < F2 + G, the opening and closing element 181 can move downward to connect with the partition assembly, thereby closing the connection between the first pressure relief channel 1821 and the second pressure relief channel 1822; when the force on the opening and closing element 181 is F1 > F2 + G, the opening and closing element 181 can move upward to not connect with the partition assembly, thereby opening the connection between the first pressure relief channel 1821 and the second pressure relief channel 1822, so that the intermediate cavity 103 releases gas into the shell chamber 5 through the first pressure relief channel 1821 and the second pressure relief channel 1822.

[0055] This invention further describes the automatic pressure relief process where the opening and closing element automatically opens or closes the connection between the first and second pressure relief channels based on the magnitude of the pressure at both ends and the magnitude of gravity. Specifically, the upper end of the opening and closing element bears the pressure of the second pressure relief channel (i.e., the inner cavity of the housing), and the lower end bears the pressure of the first pressure relief channel (i.e., the intermediate cavity). The weight of the opening and closing element in this invention is G. Since its weight is relatively small compared to the gas pressure above and below, it can be ignored. Preferably, when F1 < F2 + G, the pressure in the intermediate cavity is not very high. At this time, the opening and closing element connects with the partition assembly to close the connection between the first and second pressure relief channels, and no pressure is released. Preferably, when F1 > F2 + G, the pressure in the intermediate cavity is larger. At this time, the opening and closing element is automatically pushed upward to open the connection between the first and second pressure relief channels, achieving automatic pressure relief. Therefore, it can achieve the effect of automatically opening the pressure relief channel to relieve pressure in the intermediate cavity or closing the pressure relief based on the pressure relationship between the intermediate cavity and the inner cavity of the housing.

[0056] The working principle of the pressure relief structure of the present invention is as follows: Before startup, the pressure in the intermediate cavity equals the pressure in the inner cavity of the shell, and the opening and closing elements are in the closed state under the action of gravity.

[0057] During normal operation, the pressure in the intermediate cavity is less than the pressure in the inner cavity of the shell (gravity is relatively small and can be ignored). Under the action of the dynamic pressure difference (the lower end face is subjected to the pressure of the intermediate cavity, and the upper end face is subjected to the pressure of the inner cavity of the shell), the opening and closing element 181 is in the closed state, such as... Figure 2 As shown.

[0058] During liquid slugging, the pressure in the intermediate cavity rises sharply. When the pressure in the intermediate cavity exceeds the pressure in the inner cavity of the housing (where gravity is relatively small and negligible), the opening and closing element 181 moves upward under the dynamic pressure difference, opening the pressure relief channel. The intermediate cavity then connects with the inner cavity of the housing, and the high pressure in the intermediate cavity is rapidly released to the inner cavity of the housing, preventing excessive secondary compression pressure and thus achieving trip protection. Figure 3 As shown.

[0059] After depressurization, the pressure in the intermediate cavity is less than the pressure in the inner cavity of the shell. Under the action of the dynamic pressure difference, the opening and closing element 181 quickly closes, blocking the intermediate pressure cavity from the inner cavity of the shell, thus keeping the intermediate pressure cavity in a sealed state. Figure 4 As shown.

[0060] In some implementations... The primary compression assembly includes a primary cylinder 131, and the partition assembly includes an upper partition 141 and a lower partition 142. The upper partition 141 is connected to the lower end face of the secondary cylinder 132, and the lower partition 142 is connected to the upper end face of the primary cylinder 131. The intermediate cavity 103 is disposed inside the lower partition 142. The assembly clearance groove 183 is a recessed groove structure opened from the lower end face of the secondary cylinder 132 upwards, and the first pressure relief channel 1821 is a circular hole structure that penetrates the upper partition 141, and its center line coincides with the center line of the assembly clearance groove 183.

[0061] This is a preferred structural form of the primary compression assembly, a preferred structural form of the partition assembly, and a preferred structural form of the assembly clearance groove and the first pressure relief channel of the present invention, which can achieve the effect of automatically controlling the movement of the opening and closing elements according to the pressure relationship between the intermediate gas and the shell chamber to automatically depressurize or automatically close the pressure relief of the intermediate cavity.

[0062] This invention provides a two-stage rolling rotor compressor, comprising a pump body assembly, a motor assembly, a housing, and a liquid receiver. The pump body assembly has a primary compression chamber, an intermediate chamber, a secondary compression chamber, and a pressure relief assembly. The primary compression chamber mainly consists of a primary cylinder, primary cylinder rollers, and lower partitions and lower flanges located on the upper and lower end faces of the primary cylinder, respectively. The secondary compression chamber mainly consists of a secondary cylinder, secondary cylinder rollers, and upper flanges and upper partitions located on the upper and lower end faces of the secondary cylinder, respectively. The intermediate chamber, located between the primary and secondary compression chambers, is composed of upper and lower partitions. The pressure relief structure has two ports connected to the intermediate pressure chamber and the inner cavity of the housing, respectively.

[0063] The pressure relief assembly of the present invention includes an opening and closing element, an assembly clearance groove, and a pressure relief channel structure. The opening and closing element is assembled in the clearance groove and can reciprocate along the axis of the clearance groove to achieve communication and isolation between the intermediate cavity and the inner cavity of the outer shell. The assembly clearance groove is located on the end face of the secondary cylinder near the upper partition plate and is an axial recessed groove structure adapted to the opening and closing element. The pressure relief channel includes a first pressure relief channel and a second pressure relief channel. The first pressure relief channel passes through the upper partition plate in the axial direction and is connected to the intermediate pressure cavity and the assembly clearance groove at both ends, respectively. The second pressure relief channel is located on the end face of the secondary cylinder near the upper partition plate and is a groove structure extending radially away from the central axis of the secondary cylinder, and is connected to the inner cavity of the outer shell and the assembly clearance groove, respectively.

[0064] Preferably, the first pressure relief channel is a circular hole structure, the opening and closing element is a cylindrical structure, the assembly clearance groove is a countersunk hole structure, and the first pressure relief channel and the assembly clearance groove are coaxial.

[0065] In some implementations... The first pressure relief channel 1821, the second pressure relief channel 1822, the assembly clearance groove 183 and the opening and closing element 181 constitute at least part of the structure of the pressure relief assembly 18. The number of pressure relief assemblies 18 is n, where n is a natural number greater than or equal to 1. When n is greater than 1, the n pressure relief assemblies are evenly spaced along the circumferential direction.

[0066] By setting up the above-mentioned multiple pressure relief components, the present invention can further enhance the flow area of ​​the pressure relief channel of the intermediate cavity. When the pressure in the intermediate cavity rises suddenly, the pressure in the intermediate cavity can be relieved and reduced more quickly in multiple directions, thereby improving the effect of automatic pressure relief.

[0067] The present invention also provides a compressor that includes the aforementioned compressor pressure relief structure.

[0068] A two-stage enthalpy-increasing compressor is a type of two-stage compressor. Based on a conventional two-stage compressor, it adds an enthalpy-increasing gas supply channel 104 and enthalpy-increasing gas supply components to the intermediate cavity. That is, by increasing enthalpy, the temperature and pressure of the intermediate cavity are further increased. This can increase the pump body's suction volume while reducing the working pressure ratio of the compression cylinder, which can significantly improve the compressor and system capacity and energy efficiency.

[0069] When conventional two-stage (enthalpy-increasing) compressors and systems using them are left stagnant for extended periods in low-temperature environments (especially ultra-low temperatures below -20°C), or when the system load fluctuates significantly or the evaporator heat exchange is poor, a large amount of liquid refrigerant will exist on the low-pressure side (liquid receiver side) of the system. When the heating mode is started, a large amount of liquid refrigerant will enter the first-stage compression chamber of the compressor. Due to the incompressibility of liquid refrigerant, its volume is much smaller than that of gas, making it highly susceptible to liquid slugging. During the compression process in the chamber, this will cause a sudden increase in intermediate pressure and an abnormal increase in the pressure ratio of the first-stage compression chamber. When high-pressure refrigerant containing liquid enters the second-stage compression chamber, it will further cause the pressure in the second-stage compression chamber to rise rapidly, which will then trigger an overpressure trip in the second-stage compression chamber (when the pressure exceeds the safety threshold, the control system will trigger the overpressure trip protection), affecting the stable operation of the compressor and the system.

[0070] This invention addresses the aforementioned problems by proposing an innovative two-stage compressor structure. Through the inclusion of a pressure relief structure in the intermediate pressure chamber, dynamic pressure difference relief between the intermediate chamber pressure and the shell pressure is achieved. The specific technical solution and implementation method are as follows: This invention relates to a two-stage rolling rotor compressor, comprising a pump body assembly 1, a motor assembly 2, a housing, and a liquid receiver, among other main components. The pump body assembly 1 includes a primary compression chamber 101, an intermediate chamber 103, a secondary compression chamber 102, and at least one pressure relief assembly 18. The primary compression chamber 101 mainly consists of a primary cylinder 131, a primary cylinder roller 161, and a lower partition 142 and a lower flange 122 located at the upper and lower end faces of the primary cylinder, respectively. The secondary compression chamber 102 mainly consists of a secondary cylinder 132, a secondary cylinder roller 162, and an upper flange 121 and an upper partition 141 located at the upper and lower end faces of the secondary cylinder, respectively. The intermediate chamber 103, located between the primary and secondary compression chambers 101 and 102, is composed of an upper partition 141 and a lower partition 142.

[0071] The two ports of the pressure relief assembly 18 are connected to the intermediate cavity 103 and the inner cavity of the outer shell, respectively, and mainly consist of the opening and closing element 181, the assembly clearance groove 183 and the pressure relief channel structure. The assembly clearance groove 183 is preferably located on the end face of the secondary cylinder 132 near the upper partition 141 and is an axial recessed groove structure. The pressure relief channel includes a first pressure relief channel 1821 and a second pressure relief channel 1822. The first pressure relief channel 1821 passes through the upper partition in the axial direction and is connected to the intermediate cavity 103 and the assembly clearance groove 183 at both ends, respectively. The second pressure relief channel 1822 is located on the end face of the secondary cylinder 132 near the upper partition 141 and is a groove structure extending radially away from the central axis of the secondary cylinder 132. It is connected to the inner cavity of the outer shell and the assembly clearance groove 183, respectively. The opening and closing element 181 is adapted to the structure of the assembly clearance groove 183 and is installed in the assembly clearance groove 183. It can reciprocate in the clearance groove along the axis of the clearance groove to realize the connection and isolation between the intermediate cavity and the inner cavity of the outer shell.

[0072] Preferably, the first pressure relief channel 1821 of the present invention has a circular hole structure, the opening and closing element 181 has a cylindrical structure, and the assembly clearance groove 183 has a countersunk hole structure. The first pressure relief channel 1821 and the assembly clearance groove 183 are coaxial. The structure is simple, easy to process, and has a low manufacturing cost.

[0073] This invention addresses the aforementioned problems by proposing an innovative two-stage compressor structure. By incorporating a pressure relief structure in the intermediate pressure chamber, it achieves dynamic pressure relief based on the pressure difference between the intermediate chamber and the casing. This solves the problem of liquid slugging in conventional two-stage (enthalpy-increasing) compressors and systems using them, which can lead to a sudden pressure surge in the intermediate pressure chamber and subsequently cause overpressure tripping in the secondary compression chamber, affecting system stability, when subjected to prolonged static conditions in low-temperature environments, significant system load changes, or poor evaporator heat exchange. This invention requires no additional piping, has a simple structure, low manufacturing costs, and is easy to implement. It reduces compressor manufacturing costs and avoids the potential impact of complex piping layouts on overall heating performance and system reliability.

[0074] The present invention also provides an air conditioner that includes the aforementioned compressor.

[0075] The beneficial effects of this invention are: This invention proposes an innovative two-stage compressor structure, which achieves the following beneficial effects by setting a pressure relief structure in the intermediate pressure chamber: 1. This invention can avoid vibrations caused by flutter during the pressure relief process, thus achieving stable pressure relief; 2. This invention also avoids introducing cylinder pressure as back pressure, which would cause the gas in the housing to flow back into the intermediate cavity, thus ensuring the accuracy of pressure relief and achieving stable pressure relief; 3. To achieve dynamic pressure relief between the intermediate chamber pressure and the shell pressure, when the two-stage (enthalpy-increasing) compressor and the system using it are left stagnant in a low-temperature environment for a long time, or when the system load changes significantly or the evaporator heat exchange is poor, the pressure in the intermediate chamber may rise suddenly due to liquid slugging. This can relieve pressure in time to avoid overpressure tripping of the secondary compression chamber, thereby achieving precise tripping protection for the compressor and system and ensuring stable system operation.

[0076] 4. The present invention has a simple structure and is easy to implement. It does not require additional piping and control valve components, and the system piping layout does not need to be changed. The manufacturing cost is low. At the same time, changes to the wall system piping layout will not affect the overall heating performance and system reliability. It reduces the manufacturing cost of the compressor and avoids the impact on the overall heating performance and system reliability due to the complexity of the piping layout.

[0077] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features and embodiments of the above-described methods can be freely combined and superimposed.

[0078] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A compressor pressure relief structure, characterized in that: include: A primary compression assembly and a secondary compression assembly are provided, and a partition assembly is provided between the primary compression assembly and the secondary compression assembly. The partition assembly has an intermediate cavity (103) which is connected to the chamber of the primary compression assembly and the chamber of the secondary compression assembly, respectively. The partition assembly is provided with a first pressure relief channel (1821), which communicates with the intermediate cavity (103). The secondary compression assembly includes a secondary cylinder (132). The secondary cylinder (132) is provided with an assembly clearance groove (183) and a second pressure relief channel (1822) opposite to the first pressure relief channel (1821). The second pressure relief channel (1822) is located between the assembly clearance groove (183) and the first pressure relief channel (1821). The second pressure relief channel (1822) can communicate the assembly clearance groove (183) with the housing chamber (5) of the compressor. The assembly clearance groove (183) is provided with at least a portion of the structure of an opening and closing element (181). The opening and closing element (181) can open and close the assembly clearance groove (183) in the compressor housing chamber (5). 83) and the second pressure relief channel (1822) move to make the second pressure relief channel (1822) connect or disconnect from the first pressure relief channel (1821); the opening and closing element (181) includes a first end (3) and a second end (4) facing away from each other. The first end (3) is opposite to the first pressure relief channel (1821) to withstand the gas pressure of the first pressure relief channel (1821). The area on the second end (4) passing through the central axis of the opening and closing element (181) is a pressure-bearing area (185). The pressure-bearing area (185) is formed by a recessed end face groove (1841). The second pressure relief channel (1822) can introduce gas into the assembly clearance groove (183) and reach the end face groove (1841) to apply pressure to the pressure-bearing area (185).

2. The compressor pressure relief structure according to claim 1, characterized in that: The opening and closing element (181) is a cylindrical structure, including a boss portion (1811) and a non-boss portion (1812) connected in its axial direction. The second end (4) is opposite to the bottom of the mounting clearance groove (183). The boss portion (1811) is located on the second end (4) and is connected to the outer periphery of the opening and closing element (181). The boss portion (1811) protrudes toward the bottom of the mounting clearance groove (183), so that the inner periphery of the boss portion (1811) forms the end face groove (1841).

3. The compressor pressure relief structure according to claim 2, characterized in that: A flow channel (1813) is provided between the inner circumference and the outer circumference of the boss (1811), and the flow channel (1813) can connect the end face groove (1841) with the assembly clearance groove (183) on the outer circumference of the opening and closing element (181).

4. The compressor pressure relief structure according to claim 2, characterized in that: A first flow channel (18121) is provided from the bottom of the end face groove (1841) toward the interior of the non-protruding part (1812). A second flow channel (18122) is also provided inside the non-protruding part (1812). One end of the second flow channel (18122) extends to the outer periphery of the non-protruding part (1812) to communicate with the assembly clearance groove (183). The other end of the second flow channel (18122) extends to communicate with the first flow channel (18121).

5. The compressor pressure relief structure according to claim 1, characterized in that: The second pressure relief channel (1822) is disposed on the end face of the secondary cylinder (132) facing the partition assembly. The second pressure relief channel (1822) extends in the radial direction of the secondary cylinder (132). The radial inner end of the second pressure relief channel (1822) extends beyond the radial inner end of the mounting clearance groove (183) and beyond the radial inner end of the first pressure relief channel (1821). The radial outer end of the second pressure relief channel (1822) extends to the radial outer end of the secondary cylinder (132).

6. The compressor pressure relief structure according to claim 1, characterized in that: Both the assembly clearance groove (183) and the opening and closing element (181) are cylindrical structures, and the inner diameter of the assembly clearance groove (183) is larger than the outer diameter of the opening and closing element (181) so that there is a gap channel (184) between the inner wall of the assembly clearance groove (183) and the outer periphery of the opening and closing element (181). The gap channel (184) is connected to the second pressure relief channel (1822) so that the gas in the second pressure relief channel (1822) enters the assembly clearance groove (183) through the gap channel (184) to act on the pressure area (185) of the opening and closing element (181).

7. The compressor pressure relief structure according to claim 1, characterized in that: The crankshaft axis of the compressor is defined as the axial direction. The first pressure relief channel (1821) is a circular hole structure with an inner diameter of d1. The second pressure relief channel (1822) has a depth of H1 along the axial direction. The outer diameter of the opening and closing element (181) is d2. The height of the opening and closing element (181) along the axial direction is H2. The inner diameter of the end face groove (1841) is d20. The depth of the end face groove (1841) along the axial direction is H20. The inner diameter of the assembly clearance groove (183) is d3. The depth of the assembly clearance groove (183) along the axial direction is H3. The parameters H1, H2, H3, d1, d2, and d3 satisfy: H3 > H2 > H1, d3 > d2 > d1, and d3 - d2 < (d3 - d1) / 2.

8. The compressor pressure relief structure according to claim 7, characterized in that: The parameters H1, H2, H20, H3, d1, d2, d20, and d3 also satisfy the following conditions: H20 > 0.5, H3 - H2 > 0.5, and 1 < d3 - d2 < (d3 - d1) / 2 - 2. The units of parameters H1, H2, H20, H3, d1, d2, d20, and d3 are all mm.

9. The compressor pressure relief structure according to claim 1, characterized in that: When the opening and closing element (181) is connected to the partition assembly, the opening and closing element (181) closes the connection between the first pressure relief channel (1821) and the second pressure relief channel (1822); when the opening and closing element (181) is not connected to the partition assembly, the opening and closing element (181) opens the connection between the first pressure relief channel (1821) and the second pressure relief channel (1822), so that the intermediate cavity (103) releases gas into the shell chamber (5) through the first pressure relief channel (1821) and the second pressure relief channel (1822).

10. The compressor pressure relief structure according to claim 9, characterized in that: The secondary cylinder (132) is located at the upper end of the partition assembly. The lower end of the opening and closing element (181), namely the first end (3), is to withstand the upward gas pressure F1 in the first pressure relief channel (1821). The gas pressure in the first pressure relief channel (1821) is equal to the gas pressure in the intermediate cavity (103). The upper end of the opening and closing element (181), namely the second end (4), is to withstand the downward gas pressure F2 applied to it in the assembly clearance groove (183). The gas pressure in the assembly clearance groove (183) is equal to the gas pressure in the second pressure relief channel (1822). The opening and closing element (181) also withstands its own downward gravity G.

11. The compressor pressure relief structure according to claim 10, characterized in that: When the force on the opening and closing element (181) is F1 < F2 + G, the opening and closing element (181) can move downward to connect with the partition assembly, and close the connection between the first pressure relief channel (1821) and the second pressure relief channel (1822) through the opening and closing element (181); when the force on the opening and closing element (181) is F1 > F2 + G, the opening and closing element (181) can move upward to not connect with the partition assembly, and open the connection between the first pressure relief channel (1821) and the second pressure relief channel (1822) through the opening and closing element (181), so that the intermediate cavity (103) releases gas into the shell chamber (5) through the first pressure relief channel (1821) and the second pressure relief channel (1822).

12. The compressor pressure relief structure according to claim 10, characterized in that: The primary compression assembly includes a primary cylinder (131), and the partition assembly includes an upper partition (141) and a lower partition (142). The upper partition (141) is connected to the lower end face of the secondary cylinder (132), and the lower partition (142) is connected to the upper end face of the primary cylinder (131). The intermediate cavity (103) is disposed inside the lower partition (142). The assembly clearance groove (183) is a recessed groove structure opened from the lower end face of the secondary cylinder (132) upwards, and the first pressure relief channel (1821) is a circular hole structure that penetrates the upper partition (141), and its center line coincides with the center line of the assembly clearance groove (183).

13. The compressor pressure relief structure according to claim 1, characterized in that: The first pressure relief channel (1821), the second pressure relief channel (1822), the assembly clearance groove (183) and the opening and closing element (181) constitute at least part of the structure of the pressure relief assembly (18). The number of pressure relief assemblies (18) is n, where n is a natural number greater than or equal to 1. When n is greater than 1, the n pressure relief assemblies are evenly spaced along the circumferential direction.

14. A compressor, characterized in that, The compressor pressure relief structure includes any one of claims 1 to 13.

15. An air conditioner, characterized in that, Includes the compressor as described in claim 14.

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