Compressor and refrigeration apparatus

Abstract

The application provides a compressor and a refrigeration device. The compressor comprises a rack, a moving vane disc arranged on one side of the rack, a static vane disc arranged on the side of the moving vane disc away from the rack, a compression cavity formed by the moving vane disc and the static vane disc, a back pressure cavity formed by the static vane disc, the rack and the moving vane disc, a first back pressure channel arranged on the static vane disc, a first back pressure channel inlet communicating with the compression cavity, a second back pressure channel arranged on the moving vane disc, a second back pressure channel outlet communicating with the back pressure cavity, a second back pressure channel inlet communicating with the first back pressure channel outlet when the moving vane disc moves along a target trajectory to a first trajectory section, the second back pressure channel inlet being blocked by the static vane disc when the moving vane disc moves along the target trajectory to a second trajectory section, the second back pressure channel inlet being disconnected from the first back pressure channel outlet, and the length of the first trajectory section being smaller than the length of the second trajectory section. The structure reduces the risk of the moving vane disc overturning and avoids the gas backflow phenomenon caused by the change of the compression cavity pressure in the continuous communication state.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and more specifically, to a compressor and refrigeration equipment. Background Technology

[0002] Scroll compressors are prone to tipping during operation due to the pressure and torque of the high-pressure gas in the compression chamber. If the tipping is too large, it may cause the seal between the compression chamber and the intake and exhaust ports to fail, resulting in internal leakage, reduced compression efficiency, or even component wear or failure.

[0003] To suppress the overturning of the moving scroll plate, related technologies generally employ a back pressure structure to provide axial support. A typical solution involves creating a back pressure hole on the side of the moving scroll plate substrate and setting a back pressure chamber on its back (the side opposite to the stationary scroll plate). During operation, high-pressure gas in the compression chamber flows into the back pressure chamber through the back pressure hole, creating an axial thrust between the moving and stationary scroll plates, continuously pressing the moving scroll plate against the stationary scroll plate and balancing the overturning moment.

[0004] However, in the aforementioned scroll compressor, because the back pressure port is directly connected to the side of the moving scroll base plate and the compression chamber, the connection time between the back pressure port and the compression chamber is relatively long for each rotation of the moving scroll. As the moving scroll moves, the gas pressure in the compression chamber undergoes periodic and drastic changes with the working cycle (intake → compression → exhaust) (rising from low pressure to high pressure and then falling back down), causing simultaneous and significant fluctuations in the pressure within the back pressure chamber (alternating peaks and troughs). This pressure fluctuation makes the axial thrust on the moving scroll unstable, affecting its radial positioning accuracy; furthermore, when the pressure in the back pressure chamber is lower than the pressure in the compression chamber, gas backflow is likely to occur, weakening the back pressure support effect. Under long-term operation, the moving scroll may experience accelerated wear and increased vibration due to thrust fluctuations and backflow impacts, reducing the compressor's reliability and lifespan.

[0005] Therefore, how to reduce the fluctuation of the back pressure chamber has become an urgent technical problem to be solved. Utility Model Content

[0006] This application aims to address at least one of the technical problems existing in the prior art or related technologies.

[0007] Therefore, the first aspect of this application provides a compressor.

[0008] A second aspect of this application provides a refrigeration device.

[0009] In view of this, the first aspect of this application proposes a compressor, comprising: a frame; a moving scroll disposed on one side of the frame; a stationary scroll disposed on the side of the moving scroll away from the frame, forming a compression chamber with the moving scroll, wherein the stationary scroll, the frame, and the moving scroll form a back pressure chamber; a first back pressure channel disposed on the stationary scroll, the inlet of the first back pressure channel communicating with the compression chamber; and a second back pressure channel disposed on the moving scroll, the outlet of the second back pressure channel communicating with the back pressure chamber; wherein, when the moving scroll moves along the target trajectory to the first trajectory segment, the inlet of the second back pressure channel communicates with the outlet of the first back pressure channel; when the moving scroll moves along the target trajectory to the second trajectory segment, the inlet of the second back pressure channel is blocked by the stationary scroll, and the inlet of the second back pressure channel is disconnected from the outlet of the first back pressure channel; and the length of the first trajectory segment is less than the length of the second trajectory segment.

[0010] The compressor proposed in this embodiment mainly consists of a frame, a moving scroll, a stationary scroll, a first back pressure channel, and a second back pressure channel. The frame serves as the basic support component. The moving scroll is movably mounted on one side of the frame and can translate along a predetermined target trajectory (i.e., the moving scroll translates around the stationary scroll, essentially revolving rather than rotating). The stationary scroll is located on the side of the moving scroll away from the frame and meshes with it to form a compression chamber for compressing gas. The stationary scroll, frame, and moving scroll together form a back pressure chamber. The stationary scroll has a first back pressure channel, the inlet of which is connected to the compression chamber, introducing gas into the chamber. The moving scroll has a second back pressure channel, the outlet of which is connected to the back pressure chamber, guiding gas into the back pressure chamber. During operation, the moving scroll traverses two different trajectory segments—a first trajectory segment and a second trajectory segment—during its periodic motion along the target trajectory. When the moving scroll reaches the first trajectory segment, the inlet end of the second back pressure channel is aligned with the non-inlet end (i.e., the end furthest from the compression chamber) of the first back pressure channel, and the two are connected. At this time, the high-pressure gas in the compression chamber enters the back pressure chamber sequentially through the first and second back pressure channels, forming an axial thrust between the moving and stationary scrolls, pressing the moving scroll tightly against the stationary scroll, effectively suppressing the overturning tendency of the moving scroll due to the gas pressure and torque in the compression chamber. When the moving scroll reaches the second trajectory segment, the inlet end of the second back pressure channel is blocked by the inner wall of the stationary scroll, causing the inlet end of the second back pressure channel to disconnect from the outlet end of the first back pressure channel. At this time, the back pressure chamber no longer receives gas from the compression chamber, and the pressure inside the chamber remains at the stable value accumulated during the previous connection phase. This design allows the moving scroll to obtain gas from the compression chamber only in the relatively small first trajectory segment through the two back pressure channels. For most of the time (the second trajectory segment), the back pressure chamber is in a relatively closed state, and pressure fluctuations are significantly reduced. Stable back pressure chamber pressure provides continuous and uniform axial support for the moving scroll, avoiding thrust instability caused by pressure fluctuations. This reduces the risk of moving scroll overturning, lowers leakage within the compression chamber, and improves compression efficiency. Furthermore, it avoids gas backflow caused by pressure changes in the compression chamber during continuous operation, extending the service life of core components such as the moving and stationary scrolls. Compared to the pressure fluctuations caused by long-term continuous back pressure channels in related technologies, this solution achieves dynamic stability of the back pressure through trajectory segment control, effectively enhancing the reliability of compressor operation.

[0011] In any of the above technical solutions, optionally, the central angle corresponding to the first trajectory segment is greater than or equal to 50° and less than or equal to 90°.

[0012] In these technical solutions, the central angle corresponding to the first trajectory segment (i.e., the angle formed by connecting the starting position of the moving vortex disk and the end point of the trajectory segment to the vertex, with the center of motion of the moving vortex disk as the vertex) can be set to greater than or equal to 50° and less than or equal to 90°. When the moving vortex disk moves to the first trajectory segment, it is necessary to ensure that the connection time between the second back pressure channel and the first back pressure channel is sufficient so that a stable supporting pressure can be accumulated in the back pressure cavity; at the same time, it is necessary to avoid the connection time being too long, resulting in the second trajectory segment being too short (i.e., insufficient pressure holding time of the back pressure cavity). Through simulation verification or experimental testing, the central angle range of 50° to 90° can ensure that the back pressure cavity is in the air replenishment state for about 1 / 4 to 1 / 3 of the time within one revolution of the moving vortex disk, and maintains pressure holding for the rest of the time. This ensures the timely establishment of axial thrust and effectively reduces the reverse impact on the back pressure cavity caused by the periodic fluctuation of the compression cavity pressure (such as the alternation of low intake pressure and high compression pressure stages), ultimately achieving a balance between back pressure stability and the smoothness of the moving vortex disk movement.

[0013] In any of the above technical solutions, optionally, the second trajectory segment is a trajectory segment on the target trajectory with the starting position as the reference and the central angle from 0° to 270°, and the first trajectory segment is a trajectory segment on the target trajectory with the starting position as the reference and the central angle from 270° to 360°.

[0014] In these technical solutions, the second trajectory segment is a segment on the target trajectory with a central angle of 0° to 270°, based on the starting position. The first trajectory segment is a segment on the target trajectory with a central angle of 270° to 360°, also based on the starting position. The starting position is also the zero point, referring to the position where the moving vortex disk begins its movement in each motion cycle. The target trajectory is the complete circular path of the moving vortex disk around its center of motion. This design emphasizes that the first trajectory segment is located in the latter part of the target trajectory (i.e., the final stage where the moving vortex disk's movement is nearing completion), occupying only about 1 / 4 to 1 / 3 of the complete motion cycle (if the central angle of the first trajectory segment is 50° to 90°). During actual operation, the moving vortex disk starts moving from the starting position (0°). Within the second trajectory segment (0° to 270°), the inlet of the second back pressure channel is always blocked by the inner wall of the stationary vortex disk. The back pressure chamber and the compression chamber remain disconnected, and the pressure inside the chamber is maintained at the previously accumulated stable value, providing continuous axial support for the moving vortex disk. When the moving scroll reaches 270° and enters the first trajectory segment (the latter part), the inlet of the second back pressure channel aligns and connects with the outlet of the first back pressure channel. At this point, the high-pressure gas in the compression chamber flows into the back pressure chamber through both channels, quickly replenishing any slight pressure drop that may have occurred due to the previous closed pressure maintenance. This ensures that the moving scroll still receives sufficient axial thrust at the end of its movement, preventing overturning due to insufficient pressure. This design of connecting the latter part of the channel keeps the back pressure chamber in a closed and stable state for most of the moving scroll's movement (the first 270°), only briefly connecting at the end (within the last 90°) when pressure replenishment is most needed. This avoids pressure fluctuations caused by prolonged connection and ensures the effectiveness of back pressure support during critical stages (such as the end when the compression chamber pressure changes significantly). This more precisely suppresses the overturning tendency of the moving scroll, reduces the risk of leakage within the compression chamber, and improves the operational stability of the compressor.

[0015] In any of the above technical solutions, optionally, the moving scroll has a moving plate and moving scroll teeth, and the stationary scroll has a stationary plate and stationary scroll teeth. The moving plate and the stationary plate abut against each other, and the moving scroll teeth and the stationary scroll teeth are engaged with each other, so that a compression cavity is formed between the moving scroll and the stationary scroll. The second back pressure channel is disposed on the moving plate and along the radial direction of the compressor. The second back pressure channel is located outside the moving scroll teeth, and the first back pressure channel is disposed on the stationary plate.

[0016] In these technical solutions, the moving scroll consists of a moving plate and moving scroll teeth, while the stationary scroll consists of a stationary plate and stationary scroll teeth. During assembly, the moving plate and stationary plate directly abut against each other, forming a stable base support. The moving scroll teeth extend upwards from the surface of the moving plate, and the stationary scroll teeth extend downwards from the surface of the stationary plate. They interlock and maintain a small gap, together forming a compression chamber for gas compression. As the moving scroll moves around its center, the compression chamber gradually contracts radially from the outside to the inside, completing the cycle of intake, compression, and exhaust. The second back pressure channel is machined on the moving plate and extends radially along the compressor, specifically located outside the moving scroll teeth (i.e., on the side furthest from the center of the moving scroll). This layout allows the second back pressure channel to avoid the meshing area of ​​the moving and stationary scroll teeth as much as possible, reducing the space occupied in the compression chamber, while facilitating alignment and communication with the first back pressure channel on the stationary scroll. The first back pressure channel is directly formed on the stationary plate, with its inlet facing the inside of the compression chamber and its outlet corresponding to the position of the second back pressure channel on the moving scroll. In this application, since the second back pressure channel is located outside the moving vortex, the gas flow path is shorter and less affected by the meshing of the vortex, which can reduce flow resistance and improve back pressure transmission efficiency.

[0017] In any of the above technical solutions, optionally, the first back pressure channel includes: a first sub-channel, one end of which is connected to the compression chamber, and the other end of which extends away from the moving scroll; a second sub-channel, one end of which is connected to the other end of the first sub-channel, and the other end of which extends outward along the radial direction of the compressor; and a third sub-channel, one end of which is connected to the second sub-channel, and the other end of which extends towards the moving scroll to the end face of the stationary scroll near the moving scroll.

[0018] In these technical solutions, the first back pressure channel is disposed on the stationary plate substrate and adopts a multi-segment structure design, specifically including three interconnected sub-channels. One end of the first sub-channel is directly connected to the compression chamber, and the other end extends inside the stationary plate substrate in the direction away from the moving scroll (i.e., the side away from the center of the compressor). Its main function is to introduce the gas in the compression chamber into the channel network inside the stationary plate substrate. One end of the second sub-channel is connected to the extension end of the first sub-channel, and the whole extends outward along the radial direction of the compressor, which is equivalent to constructing a transverse gas transmission path within the stationary plate substrate, further guiding the gas from the vicinity of the compression chamber to the edge area of ​​the stationary plate substrate. The third sub-channel turns from the radially outer end of the second sub-channel and extends radially inward to the end face of the stationary plate substrate near the moving scroll (i.e., the surface where the stationary plate substrate and the moving plate substrate abut), and this end face is directly opposite the inlet position of the second back pressure channel on the moving plate substrate.

[0019] This three-segment layout optimizes the gas flow path through directional changes: the first sub-channel, perpendicular to the compression chamber, guides gas into the stationary plate; the second sub-channel expands radially to increase the flow area and reduce resistance; and the third sub-channel is precisely aligned with the inlet of the second back pressure channel of the moving scroll. When the moving scroll reaches the first trajectory segment, the inlet of the second back pressure channel on the moving plate is precisely aligned with the end face outlet of the third sub-channel on the stationary plate. The high-pressure gas in the compression chamber flows into the second back pressure channel sequentially through the first, second, and third sub-channels, ultimately entering the back pressure chamber to form axial thrust. The multi-segment sub-channel design avoids abrupt changes in gas flow direction, reducing flow losses. Simultaneously, the layered guidance within the stationary plate ensures the stability of the back pressure gas supply under different operating conditions, providing more reliable axial support for the moving scroll.

[0020] In any of the above technical solutions, optionally, the second back pressure channel includes: a fourth sub-channel extending from the end face of the moving plate substrate near the stationary scroll plate in a direction away from the stationary scroll plate; and a fifth sub-channel extending radially outward from the fourth sub-channel to the side of the moving plate substrate, and connecting the fourth sub-channel and the back pressure chamber.

[0021] In these technical solutions, the second back pressure channel is located on the moving plate substrate and adopts a two-stage sub-channel structure, specifically including a fourth sub-channel and a fifth sub-channel. The fourth sub-channel starts from the end face of the moving plate substrate near the stationary scroll plate (i.e., the surface that abuts against the stationary plate substrate) and extends longitudinally in the direction away from the stationary scroll plate (inwards into the moving scroll plate). Its function is to introduce the gas flowing in from the first back pressure channel of the stationary scroll plate into the interior of the moving plate substrate. The fifth sub-channel extends radially outwards from a certain position in the extension path of the fourth sub-channel (usually near the radial edge inside the moving plate substrate) along the compressor until it extends to the side of the moving plate substrate (i.e., the outer peripheral surface away from the center), and finally directly connects with the back pressure cavity. This two-stage layout realizes the transfer of gas from the stationary scroll plate to the back pressure cavity through a direction conversion: the fourth sub-channel guides the gas longitudinally inside the moving plate substrate, avoiding interference with structures such as the moving scroll teeth; the fifth sub-channel extends radially to the side, precisely connecting with the back pressure cavity. When the moving scroll reaches the first trajectory segment, the outlet of the first back pressure channel of the stationary scroll aligns and connects with the inlet of the fourth sub-channel of the moving scroll substrate. The gas in the compression chamber enters the fourth sub-channel through the first back pressure channel, then flows radially along the fifth sub-channel to the side of the moving scroll substrate, and finally merges into the back pressure chamber. The two-stage sub-channel design shortens the gas flow path and reduces the resistance loss caused by turning. At the same time, the optimized layout of the internal space of the moving scroll substrate ensures that the back pressure gas enters the back pressure chamber efficiently and stably, providing continuous axial support force for the moving scroll and suppressing the tendency to overturn.

[0022] In any of the above technical solutions, optionally, an extension section is provided at the other end of the second sub-channel. The end of the extension section away from the second sub-channel extends radially outward along the compressor to the side wall that penetrates the stationary scroll plate. The extension section and the second sub-channel are connected as an integral structure. The compressor also includes a sealing part located on the extension section to seal the extension section.

[0023] In these technical solutions, the other end of the second sub-channel is directly machined to form an extension section. This extension section and the second sub-channel are integrally formed from the stationary scroll plate substrate, extending radially outward through the sidewall of the stationary scroll plate and reaching the outside. Simply put, the extension section is a natural extension of the second sub-channel at the sidewall of the stationary scroll plate; the two do not require additional splicing or welding and are manufactured entirely through a one-time molding process. To ensure that the extension section does not participate in gas transmission during normal operation, the compressor has a sealing part (such as a sealing plug or welded sealing layer) at the end of the extension section to completely seal it. The integrated structure of the extension section and the second sub-channel allows for the one-time machining of the internal channels of the stationary scroll plate using CNC milling, deep hole drilling, and other processes, significantly reducing assembly steps, lowering the risk of machining errors, and improving the overall sealing performance and flow consistency of the channel. The presence of the sealing section ensures the controllable flow of back pressure gas during compressor operation without affecting processing convenience: the extension section is closed under normal operating conditions, and the second sub-channel can be quickly accessed through the extension section only when maintenance or inspection is required, thus balancing processing economy and subsequent maintainability.

[0024] In any of the above technical solutions, optionally, the outlet of the first back pressure channel is located on the surface where the stationary scroll and the moving scroll abut, and the inlet of the second back pressure channel is located on the surface where the moving scroll and the stationary scroll abut. Along the radial direction of the compressor, the distance between the outer side of the outlet of the first back pressure channel and the central axis of the stationary scroll is less than the distance between the outer side of the outlet of the second back pressure channel and the central axis of the moving scroll.

[0025] In any of the above technical solutions, optionally, the distance L1 between the central axis of the outlet of the first back pressure channel and the central axis of the stationary vortex disk along the radial direction of the stationary vortex disk, the diameter of the outlet of the first back pressure channel is D1, the diameter of the inlet of the second back pressure channel is D3, and the minimum distance between the central axis of the inlet of the second back pressure channel and the outer surface of the moving vortex disk along the radial direction of the moving vortex disk is L2; ​​wherein: L1+1 / 2D1≤L2+1 / 2D3.

[0026] This configuration allows the back pressure chamber to receive high-pressure gas from the compression chamber only for a short period of time, maintaining a stable internal pressure most of the time. This avoids pressure fluctuations caused by continuous connection and ensures that the moving scroll still has sufficient axial thrust during critical stages (such as the end of one revolution), thereby effectively suppressing the overturning of the moving scroll, reducing leakage in the compression chamber, and improving the reliability and efficiency of the compressor operation.

[0027] In any of the above technical solutions, optionally, the distance L1 between the central axis of the outlet of the first back pressure channel and the central axis of the stationary vortex disk along the radial direction of the stationary vortex disk, the outlet of the first back pressure channel is located on the surface where the stationary vortex disk and the moving vortex disk abut, the diameter of the outlet of the first back pressure channel is D1, the outer diameter of the moving vortex disk is D2, the radius of motion of the moving vortex disk is R, and θ is the angle traversed by the moving vortex disk from the starting point of the first trajectory segment to the ending point of the first trajectory segment (i.e., the central angle corresponding to the first trajectory segment on the target trajectory segment), wherein:

[0028] .

[0029] These technical solutions achieve precise control over the timing of back pressure channel connection: only when the moving vortex disk moves to the first trajectory segment (the small angle interval of the latter part of the target trajectory) can the entrance of the second back pressure channel (located on the surface where the moving vortex disk and the stationary vortex disk meet, away from the center of the moving vortex disk) be aligned with the exit of the first back pressure channel, thus achieving connection between the two; while when the moving vortex disk moves to the second trajectory segment (accounting for most of the motion cycle), due to the positional shift of the moving vortex disk, the entrance of the second back pressure channel will be blocked by the main structure of the stationary vortex disk, and cannot contact the exit of the first back pressure channel.

[0030] The essence of this geometric constraint is to strongly bind the connectivity of the back pressure channel to the movement position of the moving scroll, opening it only when back pressure gas needs to be replenished (in the first trajectory segment) and keeping it closed the rest of the time. This design allows the back pressure chamber to receive high-pressure gas from the compression chamber only for a short period of time, maintaining a stable internal pressure most of the time. This avoids pressure fluctuations caused by continuous connectivity and ensures that the moving scroll still has sufficient axial thrust during critical stages (such as at the end of one revolution), thereby effectively suppressing the overturning of the moving scroll, reducing leakage within the compression chamber, and improving the reliability and efficiency of the compressor operation.

[0031] According to a second aspect of this application, a refrigeration device is also proposed, comprising: a compressor as described in any of the above embodiments.

[0032] The refrigeration equipment provided in the second aspect of this application, since it includes the compressor proposed in any of the above embodiments, has all the beneficial effects of a compressor.

[0033] The refrigeration equipment can be air conditioners, refrigerators, etc.

[0034] Additional aspects and advantages of this application will become apparent in the following description or may be learned by practice of this application. Attached Figure Description

[0035] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0036] Figure 1 A schematic diagram of the compressor in one embodiment of this application is shown;

[0037] Figure 2 One of the structural schematic diagrams of the stationary scroll plate of a compressor according to one embodiment of this application is shown;

[0038] Figure 3 This is a second schematic diagram of the structure of the stationary scroll plate of a compressor according to one embodiment of this application;

[0039] Figure 4 One of the schematic diagrams of the moving scroll of a compressor according to one embodiment of this application is shown;

[0040] Figure 5 This is a second schematic diagram of the structure of the moving scroll of a compressor according to one embodiment of this application;

[0041] Figure 6 A schematic diagram of the structure of the compressor with the cooperation of the moving scroll and the stationary scroll in one embodiment of this application is shown;

[0042] Figure 7 This is a schematic diagram of the moving scroll of the compressor in the relevant scheme.

[0043] in:

[0044] 1 Frame, 2 Moving scroll, 22 Moving scroll base plate, 24 Moving scroll tooth, 3 Stationary scroll, 32 Stationary scroll base plate, 34 Stationary scroll tooth, 4 Compression chamber, 5 Back pressure chamber, 6 First back pressure channel, 62 First sub-channel, 64 Second sub-channel, 66 Third sub-channel, 68 Extension section, 7 Second back pressure channel, 72 Fourth sub-channel, 74 Fifth sub-channel, 8 Sealing part, 2' Moving scroll, 22' Back pressure hole. Detailed Implementation

[0045] To better understand the above-mentioned objectives, features, and advantages of this application, the application 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.

[0046] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application 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.

[0047] The compressor and refrigeration equipment in this embodiment will be further described below with reference to the accompanying drawings.

[0048] According to the first aspect of this application, a compressor is proposed, such as Figures 1 to 6As shown, the compressor mainly consists of a frame 1, a moving scroll 2, a stationary scroll 3, a first back pressure channel 6, and a second back pressure channel 7. The frame 1 serves as the basic support component. The moving scroll 2 is movably mounted on one side of the frame 1 and can move along a predetermined target trajectory. The stationary scroll 3 is located on the side of the moving scroll 2 away from the frame 1, meshing with the moving scroll 2 to form a compression chamber 4 for compressing gas. The stationary scroll 3, frame 1, and moving scroll 2 together form a back pressure chamber 5. The stationary scroll 3 has a first back pressure channel 6, the inlet of which is connected to the compression chamber 4, introducing gas into the compression chamber 4. The moving scroll 2 has a second back pressure channel 7, the outlet of which is connected to the back pressure chamber 5, responsible for guiding gas into the back pressure chamber 5. During operation, the moving scroll 2 moves along the target trajectory, passing through two trajectory segments of different lengths: a first trajectory segment and a second trajectory segment. When the moving volute 2 moves to the first trajectory segment, the inlet end of the second back pressure channel 7 is aligned with the non-inlet end (i.e., the end furthest from the compression chamber 4) of the first back pressure channel 6, and the two are connected. At this time, the high-pressure gas in the compression chamber 4 enters the back pressure chamber 5 sequentially through the first back pressure channel 6 and the second back pressure channel 7, forming an axial thrust between the moving volute 2 and the stationary volute 3, pressing the moving volute 2 tightly onto the stationary volute 3, effectively suppressing the overturning tendency of the moving volute 2 caused by the gas pressure and torque in the compression chamber 4. When the moving volute 2 moves to the second trajectory segment, the inlet end of the second back pressure channel 7 is blocked by the inner wall of the stationary volute 3, causing the inlet end of the second back pressure channel 7 to disconnect from the outlet end of the first back pressure channel 6. At this time, the back pressure chamber 5 no longer replenishes gas from the compression chamber 4, and the pressure inside the chamber remains at the stable value accumulated during the previous connection stage. This design allows the moving scroll 2 to obtain gas from the compression chamber 4 only within the relatively small first trajectory segment through two back pressure channels. For the majority of the time (the second trajectory segment), the back pressure chamber 5 remains relatively closed, significantly reducing pressure fluctuations. The stable pressure in the back pressure chamber 5 provides continuous and uniform axial support for the moving scroll 2, avoiding thrust instability caused by pressure fluctuations. This reduces the risk of the moving scroll 2 overturning, lowers leakage within the compression chamber 4, and improves compression efficiency. Furthermore, it avoids gas backflow caused by pressure changes in the compression chamber 4 under continuous connection, extending the service life of core components such as the moving scroll 2 and the stationary scroll 3. Compared to the pressure fluctuation problems caused by long-term connection of the back pressure channels in related technologies, this solution achieves dynamic stability of the back pressure through trajectory segment control, effectively enhancing the reliability of compressor operation.

[0049] In any of the above embodiments, optionally, the central angle corresponding to the first trajectory segment can be set to greater than or equal to 50° and less than or equal to 90° (the angle formed by the line connecting the starting position of the moving vortex disk 2 and the end point of the trajectory segment with the center of motion of the moving vortex disk 2 as the vertex). Specifically, this angle range is determined by matching the motion cycle of the moving vortex disk 2 with the pressure change law of the compression chamber 4: when the moving vortex disk 2 moves to the first trajectory segment, it is necessary to ensure that the connection time between the second back pressure channel 7 and the first back pressure channel 6 is sufficient so that a stable supporting pressure can be accumulated in the back pressure chamber 5; at the same time, it is necessary to avoid the connection time being too long, resulting in the second trajectory segment being too short (i.e., the pressure holding time of the back pressure chamber 5 is insufficient). Through simulation verification or experimental testing, a central angle range of 50° to 90° allows the back pressure chamber 5 to be in a gas-filling state for about 1 / 4 to 1 / 3 of the time during one motion cycle of the moving scroll 2, while maintaining closed pressure for the rest of the time. This ensures the timely establishment of axial thrust and effectively reduces the reverse impact on the back pressure chamber 5 caused by the periodic pressure fluctuations in the compression chamber 4 (such as the alternation of low intake pressure and high compression pressure stages), ultimately achieving a balance between back pressure stability and the smoothness of the moving scroll 2's motion.

[0050] In any of the above embodiments, optionally, the second trajectory segment is a trajectory segment on the target trajectory with a central angle of 0° to 270° based on the starting position, and the first trajectory segment is a trajectory segment on the target trajectory with a central angle of 270° to 360° based on the starting position. The starting position is also the zero point position, i.e., the position where the moving vortex disk 2 begins to move in each motion cycle, and the target trajectory is the complete circular path of the moving vortex disk 2 around the motion center. This design emphasizes that the first trajectory segment is located in the latter part of the target trajectory (i.e., the final stage where the moving vortex disk 2 is nearing completion), occupying only about 1 / 4 to 1 / 3 of the total motion cycle (if the central angle of the first trajectory segment is 50° to 90°). In actual operation, the moving vortex disk 2 starts moving from the starting position (0°). Within the second trajectory segment from 0° to 270°, the inlet of the second back pressure channel 7 is always blocked by the inner wall of the stationary vortex disk 3, the back pressure cavity 5 remains disconnected from the compression cavity 4, and the pressure inside the cavity is maintained at the previously accumulated stable value, providing continuous axial support for the moving vortex disk 2. When the moving scroll 2 moves to 270° and enters the first trajectory segment (the latter part), the inlet of the second back pressure channel 7 is aligned and connected with the outlet of the first back pressure channel 6. At this time, the high-pressure gas in the compression chamber 4 flows into the back pressure chamber 5 through the two channels, quickly replenishing the slight pressure drop that may have occurred due to the previous closed pressure maintenance. This ensures that the moving scroll 2 can still obtain sufficient axial thrust at the end of a motion cycle, avoiding overturning due to insufficient pressure. This design of connecting the latter part of the cycle keeps the back pressure chamber 5 in a closed and stable state for most of the movement time of the moving scroll 2 (the first 270°), and only briefly connects at the end of the period when pressure replenishment is most needed (within the last 90°). This avoids pressure fluctuations caused by long-term connection and ensures the effectiveness of back pressure support in critical stages (such as the end of the period when the pressure in the compression chamber 4 changes significantly). This more accurately suppresses the overturning tendency of the moving scroll 2, reduces the risk of leakage in the compression chamber 4, and improves the operating stability of the compressor.

[0051] In any of the above embodiments, optionally, as Figure 2 , Figure 3 , Figure 4 and Figure 5 As shown, the moving scroll 2 has a moving plate base 22 and moving scroll teeth 24, and the stationary scroll 3 has a stationary plate base 32 and stationary scroll teeth 34. The moving plate base 22 and the stationary plate base 32 abut against each other, and the moving scroll teeth 24 and the stationary scroll teeth 34 are engaged with each other so that the moving scroll 2 and the stationary scroll 3 form a compression cavity 4. The second back pressure channel 7 is disposed on the moving plate base 22 and along the radial direction of the compressor. The second back pressure channel 7 is located outside the moving scroll teeth 24, and the first back pressure channel 6 is disposed on the stationary plate base 32.

[0052] In these embodiments, the moving scroll 2 is composed of a moving plate base 22 and moving scroll teeth 24, while the stationary scroll 3 comprises a stationary plate base 32 and stationary scroll teeth 34. During assembly, the moving plate base 22 and the stationary plate base 32 directly abut against each other, forming a stable base support. The moving scroll teeth 24 extend upwards from the surface of the moving plate base 22, and the stationary scroll teeth 34 extend downwards from the surface of the stationary plate base 32. They interlock and maintain a small gap, together forming a compression chamber 4 for gas compression. As the moving scroll 2 moves around its center, the compression chamber 4 gradually contracts radially from the outside to the inside, completing the cycle of intake, compression, and exhaust. The second back pressure channel 7 is machined on the moving plate base 22 and extends radially along the compressor, specifically located outside the moving scroll teeth 24 (i.e., on the side away from the center of the moving scroll 2). This arrangement allows the second back pressure channel 7 to avoid the meshing area of ​​the moving scroll teeth 24 and the stationary scroll teeth 34 as much as possible, reducing the space occupied by the compression chamber 4, while facilitating alignment and communication with the first back pressure channel 6 on the stationary scroll 3. The first back pressure channel 6 is directly formed on the stationary disk substrate 32, with its inlet end facing the inside of the compression chamber 4 and its outlet end corresponding to the position of the second back pressure channel 7 of the moving volute 2. In this application, since the second back pressure channel 7 is located outside the moving volute 24, the gas flow path is shorter and less affected by the meshing of the volute, which can reduce flow resistance and improve back pressure transmission efficiency.

[0053] In any of the above embodiments, optionally, as Figure 2 , Figure 3 , Figure 4 and Figure 5 As shown, the first back pressure channel 6 includes: a first sub-channel 62, one end of which is connected to the compression chamber 4, and the other end of which extends away from the moving scroll 2; a second sub-channel 64, one end of which is connected to the other end of the first sub-channel 62, and the other end of which extends outward along the radial direction of the compressor; and a third sub-channel 66, one end of which is connected to the second sub-channel 64, and the other end of which extends towards the moving scroll 2 to the end face of the stationary scroll 3 near the moving scroll 2.

[0054] In these embodiments, the first back pressure channel 6 is disposed on the stationary plate substrate 32 and adopts a multi-segment structure design, specifically including three interconnected sub-channels. One end of the first sub-channel 62 is directly connected to the compression chamber 4, and the other end extends inside the stationary plate substrate 32 in a direction away from the moving scroll 2 (i.e., away from the center of the compressor). Its main function is to introduce the gas in the compression chamber 4 into the channel network inside the stationary plate substrate 32. One end of the second sub-channel 64 is connected to the extended end of the first sub-channel 62, and the whole extends outward along the radial direction of the compressor, which is equivalent to constructing a transverse gas transmission path in the stationary plate substrate 32, further guiding the gas from the vicinity of the compression chamber 4 to the edge area of ​​the stationary plate substrate 32. The third sub-channel 66 turns from the radially outer end of the second sub-channel 64 and extends radially inward to the end face of the stationary plate substrate 32 near the moving scroll 2 (i.e., the surface where the stationary plate substrate 32 and the moving plate substrate 22 abut), which is directly opposite the inlet position of the second back pressure channel 7 on the moving plate substrate 22.

[0055] This three-segment layout optimizes the gas flow path through directional changes: the first sub-channel 62, perpendicular to the compression chamber 4, guides gas into the stationary plate 32; the second sub-channel 64 expands radially to increase the flow area and reduce resistance; and the third sub-channel 66 is precisely aligned with the inlet of the second back pressure channel 7 of the moving scroll 2. When the moving scroll 2 moves to the first trajectory segment, the inlet of the second back pressure channel 7 on the moving plate 22 is precisely aligned with the end face outlet of the third sub-channel 66 on the stationary plate 32. The high-pressure gas in the compression chamber 4 flows into the second back pressure channel 7 sequentially through the first sub-channel 62, the second sub-channel 64, and the third sub-channel 66, and finally enters the back pressure chamber 5 to form axial thrust. The multi-segment sub-channel design avoids abrupt changes in the gas flow direction, reduces flow losses, and ensures the stability of the back pressure gas supply under different operating conditions through the layered guidance inside the stationary plate 32, providing more reliable axial support for the moving scroll 2.

[0056] In any of the above embodiments, optionally, as Figure 2 , Figure 3 , Figure 4 and Figure 5 As shown, the second back pressure channel 7 includes: a fourth sub-channel 72, which extends from the end face of the moving plate substrate 22 near the stationary scroll plate 3 in a direction away from the stationary scroll plate 3; and a fifth sub-channel 74, which extends from the fourth sub-channel 72 radially outward to the side of the moving plate substrate 22 and connects the fourth sub-channel 72 and the back pressure chamber 5.

[0057] In these embodiments, the second back pressure channel 7 is disposed on the moving plate substrate 22 and adopts a two-stage sub-channel structure, specifically including a fourth sub-channel 72 and a fifth sub-channel 74. The fourth sub-channel 72 starts from the end face of the moving plate substrate 22 near the stationary scroll plate 3 (i.e., the surface that abuts against the stationary plate substrate 32) and extends longitudinally in a direction away from the stationary scroll plate 3 (inward to the interior of the moving scroll plate 2). Its function is to introduce the gas that subsequently flows in from the first back pressure channel 6 of the stationary scroll plate 3 into the interior of the moving plate substrate 22. The fifth sub-channel 74 extends radially outward from a certain position in the extension path of the fourth sub-channel 72 (usually near the radial edge inside the moving plate substrate 22) along the compressor until it extends to the side of the moving plate substrate 22 (i.e., the outer peripheral surface away from the center), and finally directly communicates with the back pressure cavity 5. This two-stage layout achieves gas transfer from the stationary volute 3 to the back pressure chamber 5 through directional switching: the fourth sub-channel 72 guides the gas longitudinally within the moving plate 22, avoiding interference with structures such as the moving volute 24; the fifth sub-channel 74 extends radially to the side, precisely connecting to the back pressure chamber 5. When the moving volute 2 moves to the first trajectory segment, the outlet of the first back pressure channel 6 of the stationary volute 3 aligns and connects with the inlet of the fourth sub-channel 72 of the moving plate 22. The gas in the compression chamber 4 enters the fourth sub-channel 72 through the first back pressure channel 6, then flows radially along the fifth sub-channel 74 to the side of the moving plate 22, and finally merges into the back pressure chamber 5. The two-stage sub-channel design shortens the gas flow path, reduces resistance loss caused by turns, and optimizes the layout using the internal space of the moving plate 22, ensuring efficient and stable entry of back pressure gas into the back pressure chamber 5, providing continuous axial support for the moving volute 2 and suppressing the tendency to overturn.

[0058] In any of the above embodiments, optionally, as Figure 2 and Figure 3 As shown, an extension section 68 is provided at the other end of the second sub-channel 64. The end of the extension section 68 away from the second sub-channel 64 extends radially outward along the compressor to the side wall that penetrates the stationary scroll 3. The extension section 68 and the second sub-channel 64 are connected as an integral structure. The compressor also includes a sealing part 8, which is provided on the extension section 68 to seal the extension section 68.

[0059] In these embodiments, the other end of the second sub-channel 64 is directly machined to form an extension section 68. This extension section 68 and the second sub-channel 64 are integrally formed with the base plate of the stationary scroll 3, extending radially outward through the side wall of the stationary scroll 3 and reaching the outside. Simply put, the extension section 68 is a natural extension of the second sub-channel 64 at the side wall of the stationary scroll 3; the two do not require additional splicing or welding and are processed entirely through a one-time molding process. To ensure that the extension section 68 does not participate in gas transmission during normal operation, the compressor provides a sealing part 8 (such as a sealing plug or welded sealing layer) at the end of the extension section 68 to completely seal it. The integrated structure of the extension section 68 and the second sub-channel 64 allows the internal channels of the stationary scroll 3 to be machined in one step using CNC milling, deep hole drilling, or other processes, significantly reducing assembly steps, lowering the risk of machining errors, and improving the overall sealing and flow consistency of the channels. The presence of the sealing part 8 ensures the controllable flow of back pressure gas during compressor operation without affecting processing convenience: under normal operating conditions, the extension section 68 is closed, and only when maintenance or inspection is required can the sealing part 8 be removed to quickly access the second sub-channel 64 through the extension section 68, thus balancing processing economy and subsequent maintainability.

[0060] In any of the above embodiments, optionally, as Figure 2 , Figure 3 , Figure 4 and Figure 5 As shown, the outlet of the first back pressure channel 6 is located on the surface where the stationary volute 3 and the moving volute 2 abut, and the inlet of the second back pressure channel 7 is located on the surface where the moving volute 2 and the stationary volute 3 abut. The distance between the outer side of the outlet of the first back pressure channel 6 and the central axis of the stationary volute 3 is less than the distance between the outer side of the outlet of the second back pressure channel 7 and the central axis of the moving volute 2.

[0061] Optionally, the distance L1 between the central axis of the third sub-channel 66 and the central axis of the stationary vortex disk 3, the diameter of the third sub-channel 66 is D1, the minimum distance from the central axis of the fourth sub-channel 72 to the outer side of the moving vortex disk 2 is L2, and the diameter of the fourth sub-channel 72 (i.e. the diameter of the inlet of the second back pressure channel) is D3, where: L1+1 / 2D1≤L2+1 / 2D3.

[0062] This configuration allows the back pressure chamber to receive high-pressure gas from the compression chamber only for a short period of time, maintaining a stable internal pressure most of the time. This avoids pressure fluctuations caused by continuous connection and ensures that the moving scroll still has sufficient axial thrust during critical stages (such as the end of one revolution), thereby effectively suppressing the overturning of the moving scroll, reducing leakage in the compression chamber, and improving the reliability and efficiency of the compressor operation.

[0063] In any of the above embodiments, optionally, the distance L between the central axis of the outlet of the first back pressure channel 6 and the central axis of the static vortex disk 3 along the radial direction of the static vortex disk 3 is...1, The outlet of the first back pressure channel 6 is located on the surface where the stationary vortex disk 3 and the moving vortex disk 2 abut. The diameter of the outlet of the first back pressure channel 6 is D1, the outer diameter of the moving vortex disk 2 is D2, the radius of motion of the moving vortex disk 2 is R, and θ is the angle traversed by the moving vortex disk 2 from the starting point to the ending point of the first trajectory segment, where:

[0064] .

[0065] In these embodiments, precise control of the timing of back pressure channel connection is achieved: only when the moving vortex disk 2 moves to the first trajectory segment (the small angle interval of the latter part of the target trajectory) can the entrance of the second back pressure channel 7 (located on the surface where the moving vortex disk 2 and the stationary vortex disk 3 abut, away from the center of the moving vortex disk 2) be aligned with the exit of the first back pressure channel 6, and the two are connected; while when the moving vortex disk 2 moves to the second trajectory segment (accounting for most of the motion cycle), due to the positional shift of the moving vortex disk 2, the entrance of the second back pressure channel 7 will be blocked by the main structure of the stationary vortex disk 3, and cannot contact the exit of the first back pressure channel 6.

[0066] The essence of this geometric constraint is to strongly bind the connection state of the back pressure channel to the movement position of the moving scroll 2, opening it only when back pressure gas needs to be replenished (in the first trajectory segment), and keeping it closed at other times. This design allows the back pressure chamber 5 to receive high-pressure gas from the compression chamber 4 for only a short period of time, maintaining a stable internal pressure most of the time. This avoids pressure fluctuations caused by continuous connection and ensures that the moving scroll 2 still has sufficient axial thrust during critical stages (such as the end of one revolution), thereby effectively suppressing the overturning of the moving scroll 2, reducing leakage inside the compression chamber 4, and improving the reliability and efficiency of the compressor operation.

[0067] When the moving vortex disk 2 moves, it moves along the target trajectory, and each point on the moving vortex disk 2 moves around the same circular trajectory. Figure 6 In the diagram, S represents the circular motion trajectory of the center of the entrance of the fourth sub-channel 72, and the radius of the circular motion trajectory is R.

[0068] According to a second aspect of this application, a refrigeration device is also proposed, comprising: a compressor as described in any of the above embodiments.

[0069] The refrigeration equipment provided in the second aspect of this application, since it includes the compressor proposed in any of the above embodiments, has all the beneficial effects of a compressor.

[0070] The refrigeration equipment can be air conditioners, refrigerators, etc.

[0071] The following reference Figures 1 to 6 This describes a compressor proposed according to some embodiments of the present application.

[0072] The scroll compressor in the relevant scheme, such as Figure 7 As shown. The back pressure is drawn out from the back pressure hole 22' on the side of the substrate of the moving scroll 2'. During one rotation of the moving scroll 2', the back pressure is connected at an angle of 296°. The back pressure is connected to the compression chamber for a long time. As the gas pressure in the compression chamber changes, the back pressure shows a wave peak and trough change. There is a countercurrent trend between the back pressure and the pressure in the chamber.

[0073] Based on the shortcomings of the aforementioned scroll compressors, this embodiment provides a scroll compressor. The core structure of the scroll compressor includes a frame 1, a moving scroll 2, and a stationary scroll 3, which together form the basic framework for compression and back pressure regulation. The moving scroll 2 has a moving base plate 22 and moving scroll teeth 24, and the stationary scroll 3 has a stationary base plate 32 and fixed scroll teeth. The end faces of the moving base plate 22 and the stationary base plate 32 abut against each other, and the moving scroll teeth 24 and the fixed scroll teeth maintain a small meshing gap, respectively, and are engaged to form a compression chamber 4. The moving base plate 22 extends into the interior of the frame 1, and together with the frame 1 and the stationary scroll 3, forms a back pressure chamber 5.

[0074] The first back pressure channel 6 on the stationary scroll plate 3 is used to guide the high-pressure gas in the compression chamber 4 to the inlet of the back pressure chamber 5 of the moving scroll plate 2. It is opened on the stationary plate base plate 32 and has a multi-segment integrated structure: one end of the first sub-channel 62 is connected to the compression chamber 4, and the other end extends into the interior of the stationary plate base plate 32 in a direction away from the moving scroll plate 2; the second sub-channel 64 is connected to the first sub-channel 62 and extends radially outward along the stationary scroll plate 3; the third sub-channel 66 is connected to the second sub-channel 64, and after turning, extends radially inward to the end face where the stationary plate base plate 32 and the moving plate base plate 22 abut, forming the outlet of the first back pressure channel 6; the other end of the second sub-channel 64 is provided with an extension section 68 integrally formed with the second sub-channel 64. This section extends radially outward through the side wall of the stationary scroll plate 3, and the end of the extension section 68 is provided with a sealing part 8 (such as a sealing plug) to achieve the closure of the end of the extension section 68.

[0075] The second back pressure channel 7 on the moving scroll 2 is used to introduce the gas from the first back pressure channel 6 into the back pressure cavity 5. It is opened on the moving plate substrate 22 and is a two-stage radial channel: the fourth sub-channel 72 starts from the end face where the moving plate substrate 22 abuts against the stationary plate substrate 32, extends away from the stationary scroll 3 and into the interior of the moving plate substrate 22, forming the entrance of the second back pressure channel 7; the fifth sub-channel 74 is connected to the fourth sub-channel 72, extends radially outward along the moving plate substrate 22 to the side of the moving plate substrate 22, and finally connects with the back pressure cavity 5.

[0076] The outlet of the first back pressure channel 6 (located on the end face of the stationary disk substrate 32) and the inlet of the second back pressure channel 7 are only intermittently connected during the first trajectory segment (short angle interval) of the moving scroll 2, and disconnected at other times (second trajectory segment).

[0077] Specifically, the control is realized through geometric constraints: let the distance between the outer side of the outlet of the first back pressure passage 6 and the central axis of the fixed scroll 3 be A, and the distance between the outer side of the inlet of the second back pressure passage 7 and the central axis of the orbiting scroll 2 be B, then A < B; combined with the rotation radius R of the orbiting scroll 2, the central angle θ of the first trajectory segment (50° ≤ θ ≤ 90°), the diameter D1 of the outlet of the first back pressure passage 6, the outer diameter D2 of the orbiting scroll 2, and the distance L1 from the center of the outlet of the first back pressure passage 6 to the center of the fixed scroll 3, the following formula is satisfied:

[0078] .

[0079] During operation, when the orbiting scroll 2 moves to the first trajectory segment, the inlet of the second back pressure passage 7 is aligned and communicated with the outlet of the first back pressure passage 6, and the high-pressure gas in the compression chamber 4 sequentially passes through the first sub-passage 62, the second sub-passage 64, the third sub-passage 66, and the second back pressure passage 7 to enter the back pressure chamber 5, generating an axial thrust to suppress the tipping of the orbiting scroll; when moving to the second trajectory segment, the two passages are disconnected, and the back pressure chamber 5 maintains a stable pressure to avoid backflow loss.

[0080] In this embodiment, through the back pressure regulation mode of short-time communication and long-time sealing, the communication angle of the back pressure hole is shortened to less than 90° (such as 64°), which reduces the compression loss caused by the refrigerant gas flowing back from the back pressure chamber to the compression chamber, realizes peak clipping treatment of the back pressure, stabilizes the back pressure support, improves the compression efficiency, and solves the problems of excessively long communication time and large pressure fluctuation of the traditional back pressure structure.

[0081] In this application, the term "a plurality of" refers to two or more, unless otherwise clearly specified. The terms "mounted", "connected", "joined", "fixed" and the like shall be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or an integral connection; "joined" may be directly joined, or indirectly joined through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific situations.

[0082] In the description of this specification, the descriptions of terms such as "one embodiment", "some embodiments", and "specific embodiments" mean that the specific features, structures, materials or characteristics described in combination with the embodiment or example are included in at least one embodiment or example of this application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0083] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A compressor, characterized in that, include: frame; A moving scroll plate is located on one side of the frame; A stationary scroll plate is located on the side of the moving scroll plate away from the frame, and together with the moving scroll plate, they form a compression cavity, wherein the stationary scroll plate, the frame, and the moving scroll plate form a back pressure cavity; A first back pressure channel is disposed on the static vortex disk, and the inlet of the first back pressure channel is connected to the compression chamber; A second back pressure channel is provided on the moving scroll plate, and the outlet of the second back pressure channel is connected to the back pressure cavity; Specifically, when the moving vortex disk moves along the target trajectory to the first trajectory segment, the inlet of the second back pressure channel is connected to the outlet of the first back pressure channel. When the moving vortex disk moves along the target trajectory to the second trajectory segment, the inlet of the second back pressure channel is blocked by the stationary vortex disk, and the inlet of the second back pressure channel is disconnected from the outlet of the first back pressure channel. The length of the first trajectory segment is less than the length of the second trajectory segment.

2. The compressor according to claim 1, characterized in that, The central angle corresponding to the first trajectory segment is greater than or equal to 50° and less than or equal to 90°.

3. The compressor according to claim 2, characterized in that, The second trajectory segment is a trajectory segment on the target trajectory with a central angle of 0° to 270° based on the starting position of the target trajectory, and the first trajectory segment is a trajectory segment on the target trajectory with a central angle of 270° to 360° based on the starting position.

4. The compressor according to claim 1, characterized in that, The moving scroll has a moving plate and moving scroll teeth, and the stationary scroll has a stationary plate and stationary scroll teeth. The moving plate and the stationary plate abut against each other, and the moving scroll teeth and the stationary scroll teeth are engaged with each other so that the moving scroll and the stationary scroll form the compression cavity. The second back pressure channel is disposed on the moving plate substrate and along the radial direction of the compressor. The second back pressure channel is located outside the moving scroll tooth, and the first back pressure channel is disposed on the stationary plate substrate.

5. The compressor according to claim 4, characterized in that, The first back pressure channel includes: The first sub-channel has one end connected to the compression chamber and the other end extending away from the moving scroll plate. The second sub-channel has one end connected to the other end of the first sub-channel, and the other end of the second sub-channel extends radially outward along the compressor. The third sub-channel has one end connected to the second sub-channel, and the other end of the third sub-channel extends toward the end face of the stationary volute near the moving volute.

6. The compressor according to claim 5, characterized in that, The second back pressure channel includes: The fourth sub-channel extends from the end of the moving disk substrate near the stationary vortex disk in a direction away from the stationary vortex disk. The fifth sub-channel extends radially outward from the fourth sub-channel to the side of the moving plate substrate and connects the fourth sub-channel and the back pressure chamber.

7. The compressor according to claim 6, characterized in that, An extension section is provided at the other end of the second sub-channel. The end of the extension section away from the second sub-channel extends radially outward along the compressor to penetrate the side wall of the static scroll plate. The extension section is connected to the second sub-channel as an integral structure. The compressor also includes a sealing section disposed in the extension section to seal the extension section.

8. The compressor according to any one of claims 1 to 7, characterized in that, Along the radial direction of the stationary volute, the distance L1 between the central axis of the outlet of the first back pressure channel and the central axis of the stationary volute, the diameter of the outlet of the first back pressure channel is D1, the diameter of the inlet of the second back pressure channel is D3, and along the radial direction of the moving volute, the minimum distance L2 between the central axis of the inlet of the second back pressure channel and the outer surface of the moving volute, wherein: L1+1 / 2D1≤L2+1 / 2D3.

9. The compressor according to any one of claims 1 to 7, characterized in that, Along the radial direction of the stationary vortex disk, the distance L1 between the central axis of the outlet of the first back pressure channel and the central axis of the stationary vortex disk; the outlet of the first back pressure channel is located on the surface where the stationary vortex disk and the moving vortex disk abut; the diameter of the outlet of the first back pressure channel is D1; ​​the outer diameter of the moving vortex disk is D2; the radius of motion of the moving vortex disk is R; θ is the angle traversed by the moving vortex disk from the starting point to the ending point of the first trajectory segment; where: 。 10. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 9.

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