Static volute assembly, compressor and refrigeration device

Abstract

The embodiment of the utility model provides a kind of static scroll assembly, compressor and refrigeration equipment, wherein, disc body structure, disc body structure includes the exhaust part and compression part connected, compression part is equipped with compression cavity, exhaust part is equipped with first exhaust passage and second discharge passage, one end of first exhaust passage is communicated with compression cavity, the other end of first exhaust passage is communicated to the end face of the side of exhaust part far from compression part;Check valve group is connected with disc body structure, check valve group is used to limit the flow direction of fluid in second discharge passage;Wherein, one end of second discharge passage is communicated with first exhaust passage, and second discharge passage penetrates exhaust part.The utility model discloses technical scheme, under the effect of second discharge passage, can increase exhaust area, relieve the throttling pressure of main exhaust port, especially under the condition of high speed, effectively reduce exhaust pressure drop.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and more specifically, to a static scroll assembly, a compressor, and a refrigeration device. Background Technology

[0002] Currently, the compressor is operating at a variable frequency, and the discharge volume will change according to different frequencies. Under high speed conditions, the discharge volume per unit time increases significantly. The position and size of the main discharge port are relatively fixed, and throttling is likely to occur during the discharge process, resulting in increased discharge pressure drop, increased compression power consumption, and decreased system energy efficiency. Utility Model Content

[0003] The present invention aims to at least solve the technical problem of excessive exhaust volume leading to reduced energy efficiency in the prior art or related technologies.

[0004] In view of this, an embodiment of the present invention provides a static vortex disk assembly.

[0005] An embodiment of this utility model provides a compressor.

[0006] An embodiment of this utility model provides a refrigeration device.

[0007] To achieve the above objectives, embodiments of this utility model provide a static vortex disk assembly, comprising: a disk body structure, the disk body structure including a connected exhaust section and a compression section, the compression section having a compression chamber, the exhaust section having a first exhaust channel and a second discharge channel, one end of the first exhaust channel being connected to the compression chamber, and the other end of the first exhaust channel being connected to the end face of the exhaust section away from the compression section; a one-way valve assembly connected to the disk body structure, the one-way valve assembly being used to restrict the flow direction of fluid in the second discharge channel; wherein, one end of the second discharge channel is connected to the first exhaust channel, and the second discharge channel penetrates the exhaust section.

[0008] According to the static vortex disk assembly proposed in this utility model, efficient exhaust flow management is achieved by setting a first exhaust channel and a second exhaust channel in the disk structure and equipping it with a one-way valve group. Among them, the first exhaust channel serves as the main exhaust channel, directly connecting the compression chamber to the end face, and undertakes the main exhaust task; the second exhaust channel serves as the auxiliary exhaust channel, penetrating the exhaust section, increasing the exhaust area, and alleviating the throttling pressure of the main exhaust port, especially effectively reducing the exhaust pressure drop under high speed conditions.

[0009] By setting up two connected exhaust channels, which respectively undertake the main exhaust and auxiliary exhaust functions, and by using a second exhaust channel to pass through the exhaust section and equipped with a one-way valve group to realize the one-way flow and flow diversion of the auxiliary exhaust, the exhaust throttling phenomenon under high speed and variable frequency conditions is alleviated, the exhaust pressure drop is reduced, and the overall energy efficiency and operational stability of the compressor are improved.

[0010] In some technical solutions, optionally, there are multiple second emission channels, which extend radially along the disc structure and are arranged at intervals circumferentially along the disc structure.

[0011] In this design, multiple radially extending second exhaust channels are incorporated within the disc structure. These, in conjunction with the first exhaust channel and a one-way valve assembly, further enhance exhaust flow capacity and uniformity, increase the number of auxiliary exhaust channels, and expand the total exhaust area. The second exhaust channels are radially distributed, and multiple channels are spaced circumferentially, forming multiple auxiliary exhaust paths. This significantly increases the total effective flow area of ​​the exhaust section, alleviates the flow pressure at the main exhaust port, and improves exhaust efficiency under high-speed operating conditions.

[0012] In some technical solutions, optionally, the angle between the axis of the second exhaust channel and the end face of the exhaust section on the side away from the compression section is not greater than 15°.

[0013] In this technical solution, multiple radially extending second exhaust channels with their axes forming an angle of no more than 15° with the end face of the exhaust section away from the compression section are incorporated into the disc structure. These channels, in conjunction with the first exhaust channel and a one-way valve assembly, achieve a highly efficient auxiliary exhaust function. The fact that the axis of the second exhaust channel forms an angle of no more than 15° with the end face means that the channel direction is essentially parallel to or slightly inclined to the end face. This ensures that the auxiliary exhaust airflow direction is basically consistent with the main exhaust port's exhaust direction, reducing pressure loss and flow separation caused by abrupt changes in flow direction.

[0014] In some technical solutions, optionally, the end face of the exhaust section away from the compression section is provided with a main exhaust hole, and the other end of the first exhaust channel is connected to the main exhaust hole; wherein, the included angle between the axis of the main exhaust hole and the axis of the second exhaust channel is in the range of 70°~110°.

[0015] In this scheme, by forming a dual-path exhaust structure with a large angle between the main exhaust port and multiple radial auxiliary second exhaust channels, the exhaust flow and pressure are effectively dispersed, reducing single-channel throttling and pressure fluctuations. The axis of the auxiliary channels is close to the end face direction to ensure smooth airflow discharge, reduce flow loss and noise, and the one-way valve group ensures one-way passage of auxiliary exhaust, prevents backflow, maintains the stability of the compression chamber, and achieves a significant improvement in exhaust efficiency and system energy efficiency of the high-pressure chamber variable frequency scroll compressor under high-speed conditions, reducing the risk of mechanical failure.

[0016] In some technical solutions, the static vortex disk assembly may optionally include: a main exhaust valve group, located on the end face of the exhaust section away from the compression section, and the main exhaust valve group is connected to the exhaust section; wherein, the main exhaust valve group is used to open and close the main exhaust port.

[0017] In this technical solution, the main exhaust valve assembly is installed on the end face of the exhaust section away from the compression section and is connected to the exhaust section; the main exhaust valve assembly is used to open and close the main exhaust port and serves as a control device for the main exhaust flow rate; the first exhaust channel carries the main exhaust flow rate, and multiple radial second exhaust channels are equipped with one-way valve assemblies to assist in exhaust, forming a multi-path exhaust system; the valve and exhaust channel structures are reasonably matched to achieve improved exhaust efficiency, stable pressure, and reliable performance under high-speed operating conditions.

[0018] In some technical solutions, optionally, a first auxiliary exhaust port is provided on the side wall of the exhaust section, and the other end of the second exhaust channel is connected to the first auxiliary exhaust port.

[0019] In this technical solution, by setting a first auxiliary exhaust port on the side wall of the exhaust section and connecting multiple radial second exhaust channels to the first auxiliary exhaust port, the auxiliary exhaust passage extends to the side wall. Together with the main exhaust port and the main exhaust valve group, a multi-path, multi-directional exhaust system is formed, which can significantly increase the total exhaust flow area, reduce the burden on the main exhaust port, improve airflow distribution, reduce flow resistance and noise, and prevent backflow through the one-way valve group, thereby improving the sealing performance and operational stability of the compression chamber.

[0020] In some technical solutions, optionally, a second auxiliary exhaust port independent of the first auxiliary exhaust port is provided on the side wall of the exhaust section. The stationary vortex disk assembly also includes: a drain channel, one end of which is connected to the compression chamber and the other end of which is connected to the second auxiliary exhaust port; wherein the drain channel and the second exhaust channel are independent of each other, and the ratio of the effective flow area of ​​the drain channel to the effective flow area of ​​the first exhaust channel is in the range of 1.2 to 1.8.

[0021] In this technical solution, by setting independent first and second auxiliary exhaust ports on the side wall of the exhaust section, and equipping them with independent auxiliary exhaust channels and liquid discharge channels, a multi-path, multi-functional fluid discharge system is formed. The effective flow area of ​​the liquid discharge channel is 1.2 to 1.8 times that of the main exhaust channel, ensuring timely discharge of liquid refrigerant and significantly improving the compressor's resistance to liquid slugging and operational reliability.

[0022] In some technical solutions, optionally, the ratio of the effective flow area of ​​the second exhaust channel to the effective flow area of ​​the first exhaust channel is in the range of 1.2 to 1.8.

[0023] In this solution, by designing the effective flow area of ​​the second exhaust channel to be 1.2 to 1.8 times that of the first exhaust channel, the main and auxiliary exhaust areas are reasonably matched, which significantly improves the auxiliary exhaust capacity, alleviates exhaust throttling and pressure drop under high speed conditions, optimizes airflow distribution, reduces pressure fluctuations and noise, and improves valve dynamic response and durability.

[0024] In some technical solutions, optionally, one end of the drain channel is connected to the outermost compression chamber; and / or, the main exhaust valve assembly is detachably connected to the exhaust section; and / or, the one-way valve assembly is detachably connected to the disc structure.

[0025] One end of the drain channel is connected to the outermost compression chamber to ensure timely discharge of liquid refrigerant. The main exhaust valve assembly is detachably connected to the exhaust section, improving maintenance convenience. The one-way valve assembly is detachably connected to the disc structure, facilitating auxiliary valve maintenance and upgrades. It also facilitates the disassembly and assembly of auxiliary exhaust channel valves, making it convenient for testing, maintenance, and performance optimization, thereby enhancing the system's flexibility and reliability.

[0026] An embodiment of this utility model provides a compressor, including the aforementioned static scroll assembly.

[0027] The compressor has a stationary scroll assembly installed inside, which is fixedly mounted inside the compressor housing or body. It should be noted that since the compressor includes any of the aforementioned stationary scroll assemblies, it possesses the beneficial effects of any of those assemblies, which will not be elaborated further here.

[0028] An embodiment of this utility model provides a refrigeration device, including the aforementioned compressor.

[0029] The refrigeration equipment includes the aforementioned compressor. As the core power and gas compression unit of the refrigeration equipment, the compressor is connected to components such as the condenser, evaporator, and expansion valve of the refrigeration system to form a complete refrigeration cycle.

[0030] Additional aspects and advantages of this invention will become apparent in the description that follows, or may be learned by practice of this invention. Attached Figure Description

[0031] Figure 1 A schematic diagram of the structure of a stationary vortex disk assembly according to an embodiment of the present invention is shown;

[0032] Figure 2 A schematic diagram of the disk body structure according to an embodiment of the present invention is shown;

[0033] Figure 3 A schematic diagram of the disk body structure according to an embodiment of the present invention is shown;

[0034] Figure 4 A schematic diagram of the structure of a stationary vortex disk assembly according to an embodiment of the present invention is shown;

[0035] Figure 5 A schematic diagram of the structure of a compressor according to an embodiment of the present invention is shown;

[0036] Figure 6A schematic diagram of the structure of a static vortex disk assembly according to an embodiment of the present invention is shown.

[0037] Wherein, 1: Static vortex disk assembly; 11: disk structure; 111: exhaust section; 1111: main exhaust port; 1112: first auxiliary exhaust port; 1113: second auxiliary exhaust port; 112: compression section; 1121: compression chamber; 121: first exhaust channel; 122: second discharge channel; 123: liquid discharge channel; 13: one-way valve assembly; 14: main exhaust valve assembly;

[0038] 2: Compressor. Detailed Implementation

[0039] To better understand the above-mentioned objectives, features, and advantages of the embodiments of this utility model, the embodiments of this utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0040] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, embodiments of the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0041] Scroll compressors are widely used in air conditioning, heat pumps, and refrigeration equipment due to their high efficiency, low vibration, and low noise. High-pressure scroll compressors, in particular, have the exhaust chamber located behind the stationary scroll plate, using a reed valve or floating valve to achieve unidirectional exhaust flow. However, under variable frequency operation, especially at high speeds (e.g., above 4000 rpm), the exhaust volume per unit time increases significantly. Limited by the main exhaust port area and the dynamic response capability of the valve plates, significant throttling occurs during the exhaust process, leading to increased exhaust pressure drop, higher compression power consumption, and a decrease in system energy efficiency (COP).

[0042] In related technologies, the above problems are usually alleviated by optimizing the size of the main exhaust port or improving the valve plate material, but the improvement effect is limited by structural space and sealing reliability. Another solution attempts to add an exhaust port on the end face, but this is easy to damage the strength of the stationary scroll and may introduce new leakage paths or affect the balance of axial closing force. In addition, if an effective one-way control is not set, gas backflow may occur in the auxiliary exhaust channel during compression, resulting in reduced volumetric efficiency and even the risk of scroll overturning or reversing.

[0043] Therefore, there is an urgent need for a new type of exhaust structure that can effectively increase the exhaust flow area, reduce the exhaust pressure drop at high speeds, and ensure the sealing and structural stability during the compression process.

[0044] The following reference Figures 1 to 6Some embodiments of the present invention are described below.

[0045] like Figure 1 , Figure 2 and Figure 3 As shown, this embodiment provides a static vortex disk assembly 1, which achieves efficient exhaust flow management by setting a first exhaust channel 121 and a second exhaust channel 122 in the disk structure 11 and equipping it with a one-way valve group 13. The first exhaust channel 121 serves as the main exhaust channel, extending directly from the compression chamber to the end face, undertaking the main exhaust task; the second exhaust channel 122 serves as an auxiliary exhaust channel, penetrating the exhaust section 111, increasing the exhaust area, alleviating the throttling pressure of the main exhaust port, and effectively reducing exhaust pressure drop, especially under high-speed operating conditions.

[0046] like Figure 1 and Figure 6 As shown, the one-way valve assembly 13 is installed in the second discharge channel 122 to restrict the direction of fluid flow, prevent gas in the exhaust chamber from flowing back into the second discharge channel 122, improve the sealing and stability of the compression chamber, and avoid the risk of volumetric efficiency reduction and scroll plate overturning or reversing caused by gas backflow.

[0047] The second exhaust channel 122 penetrates the exhaust section 111 and connects to the first exhaust channel 121, enabling effective exhaust discharge while avoiding damage to the strength and sealing of the disc structure 11. In summary, this solution, through the synergistic effect of the dual exhaust channels and the one-way valve group 13, improves the exhaust performance of the scroll compressor 2 under variable frequency high-speed conditions, reduces pressure drop, improves system energy efficiency, and ensures stable operation and anti-liquid slugging capability of the compressor 2.

[0048] Specifically, the disk structure 11, serving as the overall frame of the stationary scroll disk assembly 1, is divided into two connected parts: an exhaust section 111 and a compression section 112. The compression section 112 contains a compression chamber, which serves as the volumetric space for gas compression, completing the gas volumetric compression process. The exhaust section 111, structurally connected to the compression section 112, is responsible for exporting the compressed gas, allowing the gas to smoothly flow from the compression chamber to the exhaust port. The compression chamber is a sealed space formed by the enclosed space between the scroll disks, used to complete the gas volumetric compression. Within the compression chamber, the relative motion between the passive and stationary scroll disks compresses the gas, gradually increasing the pressure. The sealing performance and geometry of the compression chamber directly affect the compression efficiency and volumetric efficiency, ensuring that the gas completes the entire compression process before exhaust, reaching the required exhaust pressure.

[0049] The first exhaust passage 121 serves as the main exhaust passage, responsible for guiding the high-pressure gas that has been compressed in the compression chamber to be discharged, ensuring unobstructed connection between the compression chamber and the exhaust section 111, allowing gas to flow smoothly into the first exhaust passage 121. The high-pressure gas is guided through the first exhaust passage 121 to the end face of the exhaust section 111, completing the main exhaust flow, ensuring that the gas pressure in the compression chamber is effectively released, and maintaining the normal working pressure of the compression chamber.

[0050] The other end of the first exhaust passage 121 is connected to the end face of the exhaust section 111 on the side away from the compression section 112. The end face serves as the main exhaust port, and the gas is discharged after reaching the end face through the first exhaust passage 121. The end face is located far from the compression section 112, resulting in a longer gas discharge path and more stable flow, which is beneficial for the smooth flow of the overall airflow of the compressor 2.

[0051] The second exhaust channel 122 serves as an auxiliary exhaust channel, with one end connected to the main exhaust channel to achieve the diversion and merging of auxiliary exhaust airflow. By connecting to the first exhaust channel 121, the second exhaust channel 122 can guide some high-pressure gas out, sharing the flow and pressure of the main exhaust port. This allows the second exhaust channel 122 to effectively utilize the compressed gas, avoiding dead zones or gas stagnation, ensuring that the gas pressure in the auxiliary exhaust channel is similar to that in the main exhaust channel, promoting smooth fluid flow and normal valve opening.

[0052] The second exhaust channel 122, through the structural design of the exhaust section 111, forms an independent and effective auxiliary exhaust path. The through structure allows the second exhaust channel 122 to extend from one end of the exhaust section 111 to the other side or the outside, which facilitates gas discharge, avoids direct interference with the main exhaust channel, and reduces the impact on the structural strength and sealing of the compression section 112.

[0053] Furthermore, the through-exhaust section 111 design facilitates the installation of auxiliary one-way valve assembly 13 on the side wall or other locations of the exhaust section 111, optimizing the flow control of the auxiliary exhaust. The one-way valve assembly 13, acting as a fluid flow direction restriction device, is installed on the second exhaust channel 122 and is designed to be detachable.

[0054] The one-way valve assembly 13 ensures that fluid can only flow out to the outside through the second discharge channel 122, preventing gas from flowing back into the exhaust chamber, avoiding gas in the high-pressure exhaust chamber from flowing back into the second discharge channel 122 due to pressure fluctuations or changes in operating conditions, maintaining pressure stability in the exhaust chamber, preventing volumetric efficiency reduction and compression process disorder caused by backflow, and reducing the risk of scroll plate overturning or reversing.

[0055] In summary, by setting up two connected exhaust channels to undertake the main exhaust and auxiliary exhaust functions respectively, and by using the second exhaust channel 122 to pass through the exhaust section 111 and equipped with a one-way valve group 13 to achieve one-way conduction and flow diversion of the auxiliary exhaust, the exhaust throttling phenomenon under high speed and variable frequency conditions is alleviated, the exhaust pressure drop is reduced, and the overall energy efficiency and operational stability of the compressor 2 are improved.

[0056] It is understandable that the first exhaust passage 121 ensures the smooth discharge of gas from the compression chamber to the end face and is the main exhaust path. The second exhaust passage 122 penetrates the exhaust section 111 and, through its connection with the first exhaust passage 121 and control by the one-way valve assembly 13, achieves auxiliary exhaust, expands the total exhaust area, and reduces the burden on the main exhaust port. The one-way valve assembly 13 restricts the direction of fluid flow, prevents backflow, maintains stable pressure within the compression chamber, and ensures normal force distribution on the scroll plate.

[0057] In some embodiments, optionally, such as Figure 6 As shown, the disc structure 11 is provided with multiple radially extending second exhaust channels 122, which, together with the first exhaust channel 121 and the one-way valve assembly 13, further enhance the exhaust flow capacity and flow uniformity, increase the number of auxiliary exhaust channels, and expand the total exhaust area. The second exhaust channels 122 are radially distributed, and multiple second exhaust channels 122 are spaced apart circumferentially, which can form multiple auxiliary exhaust paths, significantly increasing the total effective flow area of ​​the exhaust section 111, relieving the flow pressure of the main exhaust port, and improving the exhaust efficiency under high speed conditions.

[0058] The second exhaust channel 122 extends radially, which can more evenly guide compressed gas from the final pressure region of the exhaust chamber to the sidewall of the disc, reduce local high flow velocity or flow dead zones, reduce local pressure loss and turbulence, and improve overall exhaust stability. Multiple channels share the exhaust flow, avoiding severe throttling and pressure drop caused by excessive flow in a single channel, reducing the opening pressure of auxiliary channel valves, and improving dynamic response performance.

[0059] Each second discharge channel 122 outlet is equipped with a one-way valve group 13 to prevent gas backflow, maintain the sealing of the compression chamber, and avoid fluid backflow and abnormal stress on the vortex disk.

[0060] There are multiple second exhaust channels 122, which are evenly distributed radially and penetrate the exhaust section 111, forming multiple radial auxiliary exhaust paths. These multiple channels extend radially, enabling the uniform guidance of compressed gas from different radial positions within the exhaust chamber, thus avoiding localized pressure peaks caused by concentrated flow.

[0061] Specifically, such as Figure 6 As shown in the figure, there are two second emission channels 122.

[0062] Radial distribution ensures that the auxiliary exhaust channels cover the entire circumferential area of ​​the exhaust chamber, improving gas emission uniformity and flow stability. The multi-channel design disperses exhaust flow, reduces single-channel flow velocity, alleviates dynamic load on the valve plate, and enhances valve response speed and durability. Through radially extended channels, the gas discharge path is shorter, reducing flow resistance and minimizing local throttling and energy loss. Structurally, the radial channels penetrate the exhaust section 111, forming a gas convergence zone where they connect with the main exhaust channel, ensuring smooth exhaust of the auxiliary airflow.

[0063] In summary, based on the design of multiple radial second exhaust channels 122, the stationary scroll assembly 1, through multi-channel diversion and the rational arrangement of the one-way valve group 13, significantly increases the auxiliary exhaust flow area, reduces exhaust throttling and pressure drop under high-speed conditions, and improves the overall energy efficiency of the compressor 2. The radially extended and circumferentially uniformly distributed auxiliary channels optimize the exhaust airflow distribution, avoid local flow dead zones and pressure fluctuations, and improve exhaust stability.

[0064] The multi-channel design reduces the flow rate and valve load in individual auxiliary channels, improving dynamic response and valve durability.

[0065] In some embodiments, optionally, the disc structure 11 is provided with a plurality of radially extending second exhaust channels 122, the angle between the axis and the end face of the exhaust section 111 away from the compression section 112 being no greater than 15°. These, in conjunction with the first exhaust channel 121 and the one-way valve assembly 13, achieve a highly efficient auxiliary exhaust function. The fact that the axis of the second exhaust channel 122 is at an angle no greater than 15° to the end face means that the channel direction is essentially parallel to or slightly inclined to the end face, ensuring that the auxiliary exhaust airflow direction is basically consistent with the main exhaust port exhaust direction, reducing pressure loss and flow separation caused by abrupt changes in flow direction.

[0066] Multiple auxiliary exhaust channels are evenly distributed radially, and the channel axis is close to the end face direction, which widens the exhaust outlet flow area, alleviates the throttling phenomenon of excessive exhaust volume per unit time at high speed of the main exhaust port, significantly reduces exhaust pressure drop, and improves the energy efficiency performance of compressor 2 in variable frequency operation.

[0067] Because the angle between the axis of the auxiliary exhaust channel and the end face is small, the airflow can smoothly transition to the high-pressure space or silencing cavity of the casing near the end face, effectively reducing local turbulence and pressure pulsation, reducing noise generation, and improving overall noise reduction performance.

[0068] In summary, by rationally setting multiple radial second exhaust channels 122 with an angle between the axis and the end face not exceeding 15°, the solution optimizes the auxiliary exhaust flow direction and effectively expands the flow area, significantly improving the exhaust performance and reliability of the high-pressure chamber variable frequency scroll compressor 2 under high-speed conditions.

[0069] Specifically, the angle between the axis of the second exhaust channel 122 and the end face of the exhaust section 111 away from the compression section 112 is no greater than 15°, so that the axial direction of the second exhaust channel 122 is close to the end face direction, and the airflow discharge path is basically consistent with the direction of the main exhaust port, reducing sharp turns in the airflow direction and reducing local eddies, flow separation and pressure loss. This helps the airflow to smoothly transition to the high-pressure space of the casing or the silencer cavity, reducing noise and improving exhaust stability.

[0070] In general, the axis of the second discharge channel 122 is basically parallel to the end face, which optimizes the airflow discharge direction and reduces pressure loss and flow noise.

[0071] In some embodiments, optionally, a first exhaust channel 121 and a second exhaust channel 122 are provided within the disc structure 11, which, together with the main exhaust port 1111 and the one-way valve assembly 13, achieve efficient multi-path exhaust. The angle between the axial direction of the first exhaust channel 121 and the main exhaust port 1111 and the axis of the second exhaust channel 122 is within the range of 70° to 110°, forming a nearly vertical or oblique dual exhaust flow path layout. The main exhaust port 1111 serves as the outlet of the first exhaust channel 121 and undertakes the main exhaust function; multiple radially extending second exhaust channels 122 serve as auxiliary exhaust paths, discharging gas from different angles.

[0072] The main exhaust port 1111 and the second exhaust channel 122 have a large angle between their axes, which is close to vertical. The gas is discharged from different directions, avoiding throttling and eddies caused by excessive flow in a single path, dispersing exhaust pressure, reducing pressure fluctuations inside the exhaust chamber, and improving exhaust stability.

[0073] By connecting the first exhaust passage 121 directly to the main exhaust port 1111 and multiple second exhaust passages 122 for auxiliary exhaust, the total effective exhaust area is expanded, the exhaust throttling pressure drop is reduced, and the system energy efficiency under high-speed operation of variable frequency is improved.

[0074] The exhaust section 111 has a main exhaust port 1111 on its end face away from the compression section 112. The other end of the first exhaust passage 121 is connected to the main exhaust port 1111. The main exhaust port 1111 serves as the outlet of the first exhaust passage 121 and is the main discharge port for the compressed gas. Its end face position is far from the compression section 112, which facilitates the smooth discharge of the compressed gas and reduces flow resistance. This ensures that the high-pressure gas in the compression chamber is directly discharged through the first exhaust passage 121, bearing the main exhaust flow.

[0075] The angle between the axis of the main exhaust port 1111 and the axis of the second exhaust channel 122 ranges from 70° to 110°, causing the exhaust directions of the two exhaust channels to be distributed at large angles, forming an approximately perpendicular or oblique exhaust flow path. This bidirectional exhaust path creates multi-directional exhaust, effectively dispersing the exhaust flow and reducing the velocity and pressure load of a single channel. It also prevents airflow from concentrating in the exhaust chamber, reducing localized high-speed airflow and pressure fluctuations, and improving exhaust stability.

[0076] One end of the first exhaust passage 121 is connected to the compression chamber, and the other end is connected to the main exhaust port 1111, ensuring that the high-pressure gas in the compression chamber flows smoothly into the main exhaust path. Multiple second exhaust passages 122 radially penetrate the exhaust section 111, with one end connected to the first exhaust passage 121, making the inlet pressure of the auxiliary exhaust passages similar to that of the main exhaust passages, thus achieving reasonable flow diversion. The radial distribution of multiple passages increases the auxiliary exhaust area while maintaining uniform airflow and avoiding dead zones.

[0077] In summary, this solution effectively disperses exhaust flow and pressure by forming a dual-path exhaust structure with a large angle between the main exhaust port 1111 and multiple radial auxiliary second exhaust channels 122. This reduces single-channel throttling and pressure fluctuations. The auxiliary channel axis is close to the end face direction to ensure smooth airflow discharge, reduce flow loss and noise, and the one-way valve group 13 ensures one-way auxiliary exhaust, prevents backflow, maintains the stability of the compression chamber, and achieves a significant improvement in exhaust efficiency and system energy efficiency of the high-pressure chamber variable frequency scroll compressor 2 under high-speed conditions, while reducing the risk of mechanical failure.

[0078] In some embodiments, optionally, by rationally designing the disc structure 11, setting a first exhaust channel 121 and a main exhaust port 1111, multiple radial second exhaust channels 122 and a one-way valve group 13, and supplementing it with a main exhaust valve group 14 located on the end face of the exhaust section 111 away from the compression section 112, efficient and controllable multi-path exhaust is achieved. The main exhaust valve group 14 realizes reliable opening and closing control of the main exhaust port 1111. The main exhaust valve group 14 is located on the end face of the exhaust section 111 away from the compression section 112, directly controlling the opening and closing state of the main exhaust port 1111, ensuring accurate adjustment of the main exhaust flow rate of the compressor 2 under different operating conditions.

[0079] The main exhaust valve assembly 14 is connected to the exhaust section 111. The first exhaust passage 121, the main exhaust port 1111, and the main exhaust valve assembly 14 constitute the main exhaust path, bearing the main exhaust flow. Multiple radial second exhaust passages 122 are equipped with one-way valve assemblies 13 as auxiliary exhaust paths, expanding the total effective exhaust area, alleviating the exhaust throttling phenomenon at high speeds, and reducing exhaust pressure drop. The opening and closing of the main exhaust valve assembly 14 achieves dynamic regulation of the flow rate of the main exhaust port 1111. In conjunction with the one-way valve control of the auxiliary exhaust passages, it ensures the stability of the exhaust process and prevents gas backflow and pressure fluctuations in the compression chamber.

[0080] Specifically, the main exhaust valve assembly 14 is directly installed on the end face to control the opening and closing of the main exhaust port 1111. As a device for regulating the main exhaust flow, the end face position facilitates the valve's direct control of the main exhaust port 1111, reduces flow path resistance, improves valve response speed, and the end face installation facilitates valve sealing design and maintenance operations, thereby improving the overall reliability of the system.

[0081] Optionally, the main exhaust valve assembly 14 and the exhaust section 111 are detachably connected. This detachable connection allows the valve assembly to be easily disassembled and installed, facilitating valve maintenance and replacement, shortening maintenance time, and reducing maintenance costs.

[0082] The main exhaust valve assembly 14 is used to open and close the main exhaust port 1111, control the opening and closing of the main exhaust port 1111, realize the regulation of the main exhaust flow, dynamically adjust the exhaust flow according to the operating conditions of the compressor 2, meet the exhaust demand under different loads and speeds, and work with the one-way valve assembly 13 of the auxiliary exhaust channel to ensure unidirectional stable flow in the exhaust process, prevent gas backflow, maintain stable pressure in the compression chamber, and reduce the risk of scroll plate overturning and reversing.

[0083] In summary, the main exhaust valve assembly 14 is installed on the end face of the exhaust section 111 away from the compression section 112 and is connected to the exhaust section 111. The main exhaust valve assembly 14 is used to open and close the main exhaust port 1111, serving as a control device for the main exhaust flow. The first exhaust passage 121 carries the main exhaust flow, and multiple radial second exhaust passages 122 are equipped with one-way valve assemblies 13 to assist in exhaust, forming a multi-path exhaust system. The valve and exhaust passage structures are reasonably matched to achieve improved exhaust efficiency, stable pressure, and reliable performance under high-speed operating conditions.

[0084] In some embodiments, optionally, the disc structure 11 is rationally arranged with a first exhaust channel 121 and a main exhaust port 1111, multiple radial second exhaust channels 122, and a one-way valve group 13. A first auxiliary exhaust port 1112 is provided on the side wall of the exhaust section 111, and the other end of the second exhaust channel 122 is connected to the first auxiliary exhaust port 1112, realizing a multi-path, multi-directional high-efficiency exhaust system. The auxiliary exhaust passage extends to the side wall of the exhaust section 111, dispersing the exhaust pressure and flow. The second exhaust channel 122 connects to the first auxiliary exhaust port 1112 on the side wall of the exhaust section 111, allowing the auxiliary exhaust airflow to be discharged from the side wall, widening the gas exhaust path, effectively dispersing the flow and pressure of the main exhaust port 1111, reducing exhaust throttling and pressure drop, and improving exhaust efficiency under high-speed conditions.

[0085] The first auxiliary exhaust port 1112 is located on the side wall, working in conjunction with the main exhaust port 1111 to achieve multi-point exhaust from the exhaust chamber, reducing airflow concentration, pressure fluctuations and noise, and improving exhaust stability and the noise reduction performance of the compressor 2. The second exhaust channel 122 passes through the exhaust section 111 and connects to the first auxiliary exhaust port 1112. The gas flow path is direct and has low flow resistance, preventing auxiliary airflow from stagnating in the exhaust chamber or causing backflow. A one-way valve assembly 13 is installed at the first auxiliary exhaust port 1112 to prevent gas backflow, ensure the sealing and volumetric efficiency of the compression chamber, and reduce the risk of the scroll plate tipping overturning or reversing.

[0086] Specifically, a first auxiliary exhaust port 1112 is provided on the side wall of the exhaust section 111 as an auxiliary exhaust outlet. The first auxiliary exhaust port 1112 provides an exhaust port for the second exhaust channel 122, extending the exhaust outlet position to the side wall. The side wall position allows the auxiliary exhaust fluid to be discharged from a direction different from the main exhaust port 1111, dispersing the exhaust flow and pressure, effectively increasing the total exhaust area, alleviating the throttling and pressure drop caused by the high flow rate of the main exhaust port 1111, and the side wall orifice design facilitates smooth airflow discharge, reduces flow separation and eddies, and lowers noise.

[0087] The other end of the second exhaust channel 122 is connected to the first auxiliary exhaust port 1112, forming a direct airflow path between the second exhaust channel 122 and the first auxiliary exhaust port 1112, thus achieving effective exhaust gas discharge. This ensures that the auxiliary exhaust gas flows smoothly radially from the exhaust chamber to the side wall exhaust port, reducing airflow backflow and stagnation. It also shortens the auxiliary exhaust path and reduces flow resistance, improving auxiliary exhaust flow rate and response speed. Furthermore, it facilitates the installation of a one-way valve assembly 13 on the side wall to control the gas flow direction and maintain the sealing and stability of the compression chamber.

[0088] The main exhaust port 1111 and the first exhaust channel 121 undertake the main exhaust task and are located on the end face; multiple radial second exhaust channels 122 pass through the exhaust section 111, one end of which is connected to the first exhaust channel 121 and the other end is connected to the first auxiliary exhaust port 1112 on the side wall, forming an auxiliary exhaust path; a one-way valve group 13 is set at the first auxiliary exhaust port 1112 to prevent backflow of auxiliary exhaust and ensure stable pressure in the compression chamber; the main exhaust valve group 14 is set at the main exhaust port 1111 on the end face to control the main exhaust flow and realize the coordinated control of the main and auxiliary exhaust valves; the overall structure is reasonably laid out to ensure that the exhaust path is diversified, the flow is uniform, and the structural strength and sealing are good.

[0089] In summary, this solution extends the auxiliary exhaust passage to the side wall by setting a first auxiliary exhaust port 1112 on the side wall of the exhaust section 111 and connecting multiple radial second exhaust channels 122 to the first auxiliary exhaust port 1112. This, together with the main exhaust port 1111 and the main exhaust valve group 14, forms a multi-path, multi-directional exhaust system, which can significantly increase the total exhaust flow area, reduce the burden on the main exhaust port 1111, improve airflow distribution, reduce flow resistance and noise, and prevent backflow through the one-way valve group 13, thereby improving the sealing performance and operational stability of the compression chamber.

[0090] In some embodiments, optionally, such as Figure 3 and Figure 4 As shown, the disc structure 11 is rationally arranged with a first exhaust channel 121, a main exhaust port 1111, multiple radial second exhaust channels 122, and a one-way valve group 13. The side wall of the exhaust section 111 is provided with independent first auxiliary exhaust ports 1112 and second auxiliary exhaust ports 1113. It is equipped with a liquid discharge channel 123 to realize the discharge of liquid refrigerant, forming a high-efficiency and multi-functional exhaust and liquid discharge system.

[0091] The first exhaust passage 121 and the main exhaust port 1111 handle the main gas discharge. Multiple radial second exhaust passages 122 connect to the first auxiliary exhaust port 1112 to assist in exhaust, widening the exhaust area and alleviating exhaust pressure under high-speed conditions. The independently set liquid drain passage 123 connects to the second auxiliary exhaust port 1113 and is specifically used for liquid refrigerant discharge, improving the problem of liquid accumulation during operation with liquid, and significantly enhancing the compressor 2's resistance to liquid slugging and operational reliability.

[0092] The independent design of the drain channels 123 ensures smooth discharge of liquid refrigerant, preventing confusion with the auxiliary gas discharge channel, avoiding liquid backflow or blockage of the auxiliary exhaust flow path, and maintaining the flow stability and sealing performance of the auxiliary exhaust channel.

[0093] The effective flow area of ​​the drain channel 123 is 20% to 80% larger than that of the first exhaust channel 121, which is 1.2 to 1.8 times larger than that of the first exhaust channel 121. This ensures rapid discharge of liquid and timely discharge of liquid refrigerant under liquid conditions, preventing liquid from accumulating in the exhaust chamber and causing liquid slugging and mechanical damage.

[0094] Multiple exhaust ports and liquid drain ports are rationally distributed, and the gas and liquid discharge paths are separated to avoid mutual interference, optimize the gas-liquid flow field, and improve the operating stability and lifespan of compressor 2.

[0095] Of course, the drain channel 123 and the auxiliary exhaust channel are independent of each other, with a reasonable design that facilitates processing and assembly. Furthermore, the connection position between the drain channel 123 and the second auxiliary exhaust port 1113 is conducive to the installation of valves and seals, making maintenance convenient.

[0096] Specifically, the side wall of the exhaust section 111 is provided with a second auxiliary exhaust port 1113, which is independent of the first auxiliary exhaust port 1112. The second auxiliary exhaust port 1113 serves as the outlet of the liquid discharge channel 123, and is independent of the first auxiliary exhaust port 1112, specifically for the discharge of liquid refrigerant. The independent orifice prevents the mixing of liquid and gas discharge paths, reducing the impact of liquid on the auxiliary exhaust channel. The side wall position facilitates liquid discharge to the high-pressure space of the casing or the silencer cavity, preventing liquid from entering the main exhaust flow path. This ensures smooth discharge of liquid refrigerant and reduces the risk of liquid slugging.

[0097] The drain channel 123 connects the compression chamber and the second auxiliary exhaust port 1113, providing a dedicated path for the discharge of liquid refrigerant. Under liquid-containing conditions, the liquid refrigerant can be promptly guided out of the compression chamber, preventing liquid accumulation and potential mechanical impact. This achieves gas-liquid separation, avoiding liquid interference with the gas discharge path and ensuring stable exhaust flow. The design of the drain channel 123 ensures smooth liquid flow, reduces localized liquid stagnation, and improves the compressor's resistance to liquid slugging.

[0098] The liquid discharge channel 123 and the second discharge channel 122 are independent of each other, ensuring that the liquid refrigerant discharge path is separated from the auxiliary gas discharge path and preventing liquid-gas mixing.

[0099] The first exhaust channel 121, together with the main exhaust port 1111 and the main exhaust valve group 14, constitutes the main exhaust path; multiple radial second exhaust channels 122 are connected to the first auxiliary exhaust port 1112 to achieve auxiliary exhaust; the liquid discharge channel 123 is independent of the second exhaust channel 122 and connects the compression chamber to the second auxiliary exhaust port 1113 to achieve liquid discharge; the layout of each exhaust port and liquid discharge port is reasonable to ensure gas-liquid separation and smooth discharge; the one-way valve group 13 is set in the auxiliary exhaust channel to prevent backflow and ensure sealing and stability.

[0100] In summary, this solution forms a multi-path, multi-functional fluid discharge system by providing independent first auxiliary exhaust port 1112 and second auxiliary exhaust port 1113 on the side wall of the exhaust section 111, along with independent auxiliary exhaust channels and liquid discharge channels 123. The effective flow area of ​​the liquid discharge channel 123 is 1.2 to 1.8 times that of the main exhaust channel, ensuring timely discharge of liquid refrigerant and significantly improving the compressor 2's resistance to liquid slugging and operational reliability.

[0101] In some embodiments, the first exhaust passage 121 and a plurality of radial second exhaust passages 122 may constitute a multi-path exhaust system, and the effective flow area of ​​the second exhaust passage 122 is 1.2 to 1.8 times that of the first exhaust passage 121, forming an exhaust network with a reasonable match between the main and auxiliary exhaust areas, significantly increasing the area of ​​the auxiliary exhaust passage, improving the high-speed exhaust capacity, and the cross-section of the second exhaust passage 122 is larger than the cross-section of the first exhaust passage 121, increasing the auxiliary exhaust capacity, alleviating the throttling and pressure drop problems of the main exhaust port at high speeds, and improving exhaust efficiency.

[0102] The area ratio of 1.2 to 1.8 balances the auxiliary exhaust flow requirements with structural compactness, avoiding excessive flow resistance due to an undersized auxiliary channel, and also avoiding reduced structural strength or manufacturing complexity due to an oversized auxiliary channel. A reasonable ratio of main and auxiliary channel areas facilitates uniform gas discharge from multiple paths, reducing flow concentration and pressure pulsation, and improving exhaust stability and noise reduction performance.

[0103] A larger auxiliary exhaust area reduces the opening pressure difference and flow rate of the check valve, improves the valve response speed and fatigue life, and ensures stable operation under high-frequency exhaust conditions.

[0104] Specifically, the ratio of the effective flow area of ​​the second exhaust channel 122 to the effective flow area of ​​the first exhaust channel 121 ranges from 1.2 to 1.8. This controls the area of ​​the auxiliary exhaust channel to be larger than that of the main exhaust channel, ensuring that the auxiliary exhaust can handle the significant exhaust flow under high-speed operating conditions. This effectively expands the total exhaust area, significantly reduces the exhaust throttling pressure drop, avoids flow bottlenecks and valve overload caused by insufficient auxiliary channel area, and avoids reduced structural strength and increased manufacturing complexity caused by excessively large auxiliary channel area. It also promotes low-pressure differential opening of the auxiliary check valve, improving dynamic response performance and valve lifespan.

[0105] The first exhaust passage 121, together with the main exhaust port 1111 and the main exhaust valve group 14, forms the main exhaust path and bears the main exhaust flow. The area of ​​multiple radial second exhaust passages 122 is 1.2 to 1.8 times that of the main exhaust passage, which undertake the auxiliary exhaust task and relieve the pressure load of the main exhaust. The auxiliary exhaust passage and the drain passage 123 are independent of each other to ensure gas-liquid separation. The one-way valve group 13 is set at the outlet of the auxiliary exhaust passage to prevent backflow and ensure the sealing and stability of the compression chamber.

[0106] In summary, this solution, by designing the effective flow area of ​​the second exhaust channel 122 to be 1.2 to 1.8 times that of the first exhaust channel 121, rationally matches the main and auxiliary exhaust areas, significantly improves the auxiliary exhaust capacity, alleviates exhaust throttling and pressure drop under high-speed operating conditions, optimizes airflow distribution, reduces pressure fluctuations and noise, improves valve dynamic response and durability, and the area ratio design takes into account both structural strength and manufacturing convenience, meeting the needs of high-pressure chamber variable frequency scroll compressor for efficient and stable operation.

[0107] In some embodiments, optionally, one end of the drain channel 123 is connected to the outermost compression chamber 1121 to ensure timely discharge of liquid refrigerant. Liquid refrigerant typically accumulates in the outermost region of the compression chamber 1121. The drain channel 123 is connected to this region to ensure priority discharge of liquid, reduce the risk of liquid slugging, and improve the safety and reliability of the compressor operating with liquid.

[0108] The main exhaust valve assembly 14 is detachably connected to the exhaust section 111, which improves maintenance convenience. The detachable connection facilitates the disassembly, replacement and maintenance of the valve assembly, shortens maintenance time, reduces maintenance costs and improves the overall service life of the compressor.

[0109] The one-way valve assembly 13 is detachably connected to the disc structure 11, which facilitates the maintenance and upgrading of auxiliary valves, the disassembly and assembly of auxiliary exhaust channel valves, and the testing, maintenance and performance optimization, thereby improving the flexibility and reliability of the system.

[0110] Specifically, one end of the drain channel 123 is connected to the outermost compression chamber 1121, with the inlet of the drain channel 123 located in the outermost compression chamber 1121, a position where liquid refrigerant easily accumulates. Liquid preferentially enters the drain channel 123, quickly guiding the liquid refrigerant out, preventing liquid accumulation that could lead to liquid slugging, improving the mechanical safety and stability of the compressor during liquid-carrying start-up and operation, and preventing liquid from entering the main or auxiliary exhaust channels, thus reducing the risk of flow blockage.

[0111] The main exhaust valve assembly 14 is connected to the exhaust section 111 via a detachable structure, making the valve easy to disassemble and install, facilitating valve maintenance, replacement and performance adjustment, shortening maintenance time, supporting valve upgrades and modifications, improving the compressor's ability to adapt to changing operating conditions, ensuring valve sealing and mechanical strength while enhancing maintenance convenience.

[0112] The one-way valve group 13 on the auxiliary exhaust channel is installed on the disc structure 11 in a detachable connection manner, which facilitates the detection, maintenance and replacement of the auxiliary valve, ensures the long-term stable operation of the auxiliary exhaust channel, facilitates the adjustment of the valve structure or the replacement of valve plates with different performance, and improves the system flexibility.

[0113] In summary, this solution achieves rapid discharge of liquid refrigerant and reduces the risk of liquid slugging by connecting one end of the drain channel 123 to the outermost compression chamber 1121; the main exhaust valve assembly 14 is detachably connected to the exhaust section 111, improving maintenance convenience and system reliability; and the auxiliary exhaust check valve assembly 13 is detachably connected to the disc structure 11, facilitating maintenance and performance optimization.

[0114] like Figure 5 As shown, another embodiment of this application provides a compressor 2, which has a static scroll assembly 1 disposed inside the compressor 2.

[0115] A scroll compressor generally includes a stationary scroll assembly, a moving scroll assembly, a main frame assembly, a rotor shaft assembly, a stator assembly, a secondary frame assembly, and a housing. Specifically, the housing may include a main housing and a bottom cover that closes to the open bottom of the main housing. The main housing and the bottom cover together form a receiving cavity, within which the stationary scroll assembly, moving scroll assembly, main frame assembly, rotor shaft assembly, stator assembly, and secondary frame assembly are all installed. The rotor shaft assembly may include a crankshaft and a rotor sleeved around the crankshaft. The two ends of the crankshaft are supported by the main frame assembly and the secondary frame assembly, respectively. The upper end of the crankshaft passes through the bearings of the main frame assembly, and the lower end of the crankshaft passes through the bearings of the secondary frame assembly. The lower end face of the crankshaft slides in contact with the thrust surface of the secondary frame assembly. The stator assembly surrounds the rotor assembly and is fixed to the housing by a heat-sealed interference fit and spot welding. The moving scroll assembly is lubricated and contacted with the upper end of the crankshaft via bearings, and its rotation is caused by the rotation of the crankshaft. The stationary scroll assembly is fixed inside the housing by the main frame assembly. The stationary scroll assembly and the main frame assembly can be fixed together by screws around the perimeter. Alternatively, in some embodiments of the scroll compressor, the stationary scroll assembly can move up and down slightly along the screw guide posts. The stationary scroll assembly and the moving scroll assembly mesh with each other, and the contact surfaces are lubricated and supported by an oil film.

[0116] It should be added that, since the compressor 2 includes any of the aforementioned static scroll assembly 1, it has the beneficial effects of any of the aforementioned static scroll assembly 1, which will not be elaborated here.

[0117] Another embodiment of this application provides a refrigeration device, which includes the aforementioned compressor 2. The compressor 2 serves as the core power and gas compression unit of the refrigeration device and is connected to components such as the condenser, evaporator, and expansion valve of the refrigeration system to form a complete refrigeration cycle.

[0118] By employing the aforementioned compressor 2 and static scroll assembly 1, the refrigeration equipment achieves a highly efficient, stable, and low-noise refrigeration process, enhancing user experience and equipment performance.

[0119] It should be added that, since the refrigeration equipment includes any of the above-mentioned compressors 2, it has the beneficial effects of any of the above-mentioned compressors 2, which will not be elaborated here.

[0120] This application also provides a specific embodiment of an auxiliary exhaust structure for a high-pressure chamber variable frequency scroll compressor, which solves the problems of severe exhaust throttling and low energy efficiency at high speeds in the prior art, and further overcomes the defect of poor anti-liquid slugging ability caused by the lack of radial flexibility in high-pressure chamber scroll compressors. By setting an auxiliary exhaust channel on the back plate of the stationary scroll plate, not only can the high-speed exhaust performance be improved, but the liquid refrigerant can also be guided out during operation with liquid, thereby improving the reliability of compressor operation.

[0121] An auxiliary exhaust structure and compressor for a high-pressure chamber variable frequency scroll compressor are disclosed. A transverse through-hole is formed on the back plate of the stationary scroll to guide the compressed gas in the high-pressure exhaust chamber to the side wall of the stationary scroll. An auxiliary reed valve is installed at the outlet of the side wall to achieve one-way auxiliary exhaust. This invention effectively increases the total exhaust flow area at high speeds, significantly reduces the exhaust throttling pressure drop, and improves the energy efficiency under variable frequency conditions. Simultaneously, the one-way valve prevents gas backflow, ensuring the sealing performance and force balance of the scroll during compression. In particular, the transverse through-hole can also serve as a venting channel for liquid refrigerant, discharging the liquid during operation with liquid, significantly improving the compressor's resistance to liquid slugging. The structure is compact, easy to integrate, and suitable for various high-pressure chamber variable frequency scroll compressors.

[0122] Specifically, an auxiliary exhaust structure for a high-pressure chamber variable frequency scroll compressor is provided. The compressor includes a moving scroll, a stationary scroll, a main exhaust port, and a main reed valve. A high-pressure exhaust chamber is formed on the back of the stationary scroll. At least one transverse through hole is opened on the back plate of the stationary scroll. One end of the transverse through hole is connected to the final pressure area of ​​the high-pressure exhaust chamber, and the other end is connected to the outer surface of the side wall of the stationary scroll. An auxiliary reed valve is installed at the outlet of the transverse through hole on the outer surface of the side wall of the stationary scroll. The auxiliary reed valve only allows gas to be discharged from the high-pressure exhaust chamber to the outside, preventing external gas from flowing back into the exhaust chamber.

[0123] Optionally, the inlet of the transverse through hole is located on the back plate of the stationary vortex disk in the area corresponding to the end of the vortex exhaust, ensuring that the extracted gas has completed the entire compression process.

[0124] Optionally, the auxiliary reed valve includes a valve plate, a valve seat, and a fixed gland. The valve plate is made of fatigue-resistant stainless steel and has an opening pressure differential of less than 0.05 MPa to adapt to high-frequency exhaust conditions.

[0125] Optionally, the number of transverse through holes is 1 to 3, which are evenly distributed along the circumference of the stationary vortex disk, and the total flow cross-sectional area is 120% to 180% of the area of ​​the main exhaust port.

[0126] Optionally, the thickness of the static vortex disk back plate is verified by finite element analysis to ensure that the structural strength and stiffness requirements are still met after the opening is made.

[0127] The above solution can increase the total effective area of ​​exhaust, reduce high-frequency exhaust throttling and pressure drop, improve energy efficiency and exhaust stability, suppress backflow with a one-way valve, reduce repeated pressure fluctuations in the vortex chamber, reduce the risk of overturning and reversal, require minimal structural modifications, and is easy to manufacture and assemble, facilitating industrial application and upgrading of existing models.

[0128] Specifically, an auxiliary exhaust structure for a high-pressure chamber variable frequency scroll compressor is provided. The compressor includes a moving scroll, a stationary scroll, a main exhaust port, and a main reed valve. A high-pressure exhaust chamber is formed on the back of the stationary scroll. At least one transverse through hole is provided on the back plate of the stationary scroll, so that the central exhaust chamber and the side of the stationary scroll form a lateral exhaust channel. A side exhaust port communicating with the lateral exhaust channel is provided on the side of the stationary scroll, and a one-way anti-backflow valve is provided at the side exhaust port to prevent gas from flowing back into the central exhaust chamber from the side exhaust port.

[0129] Optionally, the one-way anti-backflow valve is a reed valve, which includes a valve plate, a valve seat and a limiting structure. The opening stroke of the valve plate is limited by the limiting structure to prevent overturning.

[0130] Optionally, the axis of the transverse through hole is substantially parallel to the plane of the fixed vortex back plate, and the lateral exhaust channel is connected to the high-pressure space or silencing cavity of the casing.

[0131] Optionally, the transverse through holes are multiple parallel through holes distributed circumferentially along the back plate of the fixed vortex disk.

[0132] Optionally, the side exhaust ports are arranged tangentially relative to the outer circle of the fixed turbine disk to reduce flow resistance and noise.

[0133] Optionally, the total effective flow area of ​​the lateral exhaust channels is increased by 20% to 80% relative to the effective flow area of ​​the central exhaust port.

[0134] Optionally, the valve plate of the reed valve is made of elastic stainless steel, the opening differential pressure is set to 0.01 to 0.2 MPa, and the valve plate limit stroke is 2 to 10 mm.

[0135] In addition, a fixed scroll assembly for a scroll compressor is provided, including a fixed scroll body, a back plate, a central exhaust chamber and a central exhaust port. The back plate is provided with a transverse through hole that connects the central exhaust chamber with the side of the fixed scroll, and a side exhaust port and its one-way anti-backflow valve are provided on the side of the fixed scroll that communicate with the transverse through hole.

[0136] In addition, a method for reducing the high-speed exhaust pressure drop of a high-pressure chamber variable frequency scroll compressor is provided, including: forming at least one transverse through hole on the back plate of the fixed scroll to connect the central exhaust chamber on the back of the scroll with the side of the fixed scroll to form a lateral exhaust channel; and setting a one-way anti-backflow valve at the side exhaust port to expand the exhaust flow area, reduce the exhaust pressure drop and prevent gas backflow under high-speed operating conditions.

[0137] Optionally, based on the target speed range and engine parameters, the total effective area of ​​the lateral exhaust passage is determined to be 20% to 80% of the effective area of ​​the central exhaust port, and the opening pressure difference and dynamic response are set by adjusting the thickness of the reed valve plate and the limit stroke.

[0138] In this invention, the terms "sealed," "fixed," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance; the term "multiple" refers to two or more unless otherwise explicitly defined. The terms "installed," "connected," "joined," and "fixed," etc., should be interpreted broadly. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "joined" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0139] In the description of this utility model, it should be understood that the terms "upper", "lower", "left", "right", "front", "rear", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or unit referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0140] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0141] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements 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 vortex disk assembly, characterized in that, include: The disc structure includes a connected exhaust section and a compression section. The compression section has a compression chamber, and the exhaust section has a first exhaust channel and a second exhaust channel. One end of the first exhaust channel is connected to the compression chamber, and the other end of the first exhaust channel is connected to the end face of the exhaust section away from the compression section. A one-way valve assembly, connected to the disc structure, is used to restrict the flow direction of fluid in the second discharge channel; One end of the second exhaust channel is connected to the first exhaust channel, and the second exhaust channel passes through the exhaust section.

2. The static scroll assembly according to claim 1, characterized in that, The number of the second discharge channels is multiple, the second discharge channels extend radially along the disc structure, and the multiple second discharge channels are arranged at circumferential intervals along the disc structure.

3. The static vortex disk assembly according to claim 2, characterized in that, The angle between the axis of the second discharge channel and the end face of the exhaust section on the side away from the compression section is no greater than 15°.

4. The static scroll assembly according to claim 1, characterized in that, The exhaust section is provided with a main exhaust port on the end face away from the compression section, and the other end of the first exhaust channel is connected to the main exhaust port; The angle between the axis of the main exhaust port and the axis of the second exhaust channel is in the range of 70° to 110°.

5. The static scroll assembly according to claim 4, characterized in that, The static scroll assembly also includes: The main exhaust valve assembly is located on the end face of the exhaust section away from the compression section, and the main exhaust valve assembly is connected to the exhaust section; The main exhaust valve assembly is used to open and close the main exhaust port.

6. The static scroll assembly according to claim 1, characterized in that, The exhaust section has a first auxiliary exhaust port on its side wall, and the other end of the second exhaust channel is connected to the first auxiliary exhaust port.

7. The static scroll assembly according to claim 6, characterized in that, The side wall of the exhaust section is provided with a second exhaust port that is independent of the first exhaust port. The stationary vortex disk assembly further includes: A drain channel, one end of which is connected to the compression chamber and the other end of which is connected to the second auxiliary exhaust port; The drainage channel and the second discharge channel are independent of each other, and the ratio of the effective flow area of ​​the drainage channel to the effective flow area of ​​the first exhaust channel is in the range of 1.2 to 1.

8.

8. The static scroll assembly according to any one of claims 1 to 7, characterized in that, The ratio of the effective flow area of ​​the second exhaust channel to the effective flow area of ​​the first exhaust channel is in the range of 1.2 to 1.

8.

9. The static scroll assembly according to claim 7, characterized in that, One end of the drainage channel is connected to the outermost compression chamber; And / or, the main exhaust valve assembly is detachably connected to the exhaust section; And / or, the one-way valve assembly is detachably connected to the disc structure.

10. A compressor, characterized in that, include: The static scroll assembly as described in any one of claims 1 to 9.

11. A refrigeration device, characterized in that, Includes the compressor as described in claim 10.

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