Scroll plate assembly and scroll compressor

Abstract

The scroll plate assembly comprises a fixed scroll plate and a movable scroll plate which are meshed with each other, the fixed scroll plate is provided with fixed scroll teeth, the movable scroll plate is provided with movable scroll teeth, and a compression cavity moving from the periphery to the center is formed between the fixed scroll teeth and the movable scroll teeth; a geometric compensation structure for compensating thermal deformation is constructed on the tooth top profile and / or the tooth bottom profile of the fixed scroll wrap and / or the movable scroll wrap; the geometric compensation structure at least partially covers the following area: when any compression cavity is communicated with the fixed scroll exhaust port for exhausting, the tail part of the compression cavity extends to the tail end of the scroll wrap of the scroll plate from the unfolding angle position on the corresponding scroll plate. According to the design, the problem that the friction loss between the tooth crest and the matched tooth bottom is increased due to improper position correction or parameter correction can be effectively avoided, and the abrasion risk of the tooth crest and the tooth bottom is remarkably reduced.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more particularly to a scroll assembly and a scroll compressor. Background Technology

[0002] Scroll compressors are widely used in refrigeration, air conditioning, and heat pump industries due to their compact structure, stable operation, and high volumetric efficiency. Their core working principle involves the meshing of a fixed scroll and a moving scroll. The moving scroll rotates around the center of the fixed scroll with a set eccentric radius, causing multiple crescent-shaped compression chambers formed between them to gradually move from the outer periphery to the center. During this movement, the refrigerant's volume continuously decreases and its pressure continuously increases, eventually being discharged through the central exhaust port, completing the compression cycle.

[0003] During the operation of a scroll compressor, refrigerant compression is accompanied by a significant temperature rise, with the temperature gradually increasing from the outer edge of the scroll teeth towards the center. This results in the greatest axial thermal deformation at the center of the scroll teeth. Especially under high pressure differential and high pressure ratio conditions, when the compression chamber and exhaust space are connected and exhaust begins, the pressure inside the compression chamber is much lower than the pressure in the exhaust space. This can easily cause exhaust fluid to flow back into the compression chamber, resulting in repeated compression and further exacerbating the exhaust temperature rise, making the thermal deformation at the center of the scroll teeth even more severe. If this non-uniform thermal deformation cannot be effectively compensated, it will lead to abnormal changes in the clearance between the scroll tooth tip and the mating tooth root, resulting in increased friction loss, increased energy consumption, and in severe cases, direct wear between the tooth tip and tooth root, significantly reducing the compressor's operational reliability and service life.

[0004] To address the problems caused by thermal deformation, existing technologies have attempted to modify the structure of the tooth tips or tooth roots of the scroll teeth. For example, Chinese Patent Publication No. CN105074218B discloses a scroll compressor structure comprising a fixed scroll disk having a fixed side plate and fixed side scroll teeth upright on one side of the fixed side plate, maintaining a vortex shape; a rotating scroll disk having a rotating side plate and rotating side scroll teeth upright on one side of the rotating side plate, maintaining a vortex shape, forming a compression chamber by rotating relative to the fixed scroll disk while the rotating side scroll teeth mesh with the fixed side scroll teeth; and an electric motor driving the rotating scroll disk via a crankshaft, wherein the fixed side scroll teeth and the rotating side scroll teeth are respectively rotated from the outer periphery to the inner periphery at their tooth roots. The steps are formed in a deeper manner. Compared to the steps on the inner circumferential side of the bottom of the spiral tooth on the gyratory side, the steps on the inner circumferential side of the bottom of the spiral tooth on the fixed side are formed in a deeper manner. If the gap between the top of the fixed side spiral tooth and the bottom of the spiral tooth on the gyratory side is defined as hs′, the gap between the bottom of the fixed side spiral tooth and the top of the spiral tooth on the gyratory side is defined as hk, the step amount of the innermost circumferential portion of the bottom of the spiral tooth on the gyratory side relative to the outermost circumferential portion is defined as Ds′, and the step amount of the innermost circumferential portion of the bottom of the fixed side spiral tooth relative to the outermost circumferential portion is defined as Dk, then the relationship becomes hk > hs′, Dk > Ds′. In short, this prior art mitigates the effects of thermal deformation by setting the numerical relationship between the step amounts of the bottom of the fixed side and the spiral side, and the gap between the top and bottom of the tooth. However, the existing technology only generally designs the depth distribution of the tooth root step, does not clearly define the key end angle reference for tooth root step correction, and does not accurately define the core parameters for continuous tooth tip correction under exhaust conditions.

[0005] In practical applications, it has been found that if the end angle of the step correction at the center of the scroll tooth root is not set properly, or if the clearance value is not set properly when the continuous correction starts to exhaust, it will cause large friction loss and wear between the tooth tip and the corresponding tooth root. This cannot fundamentally solve the problem of the operational reliability of the scroll compressor caused by thermal deformation under high pressure differential and high pressure ratio conditions, and limits the application expansion of the scroll compressor under more severe conditions. Summary of the Invention

[0006] The purpose of this invention is to overcome the shortcomings of the prior art and provide a scroll disk assembly and a scroll compressor, which aims to solve the problem of large friction loss and wear between the tooth tip and the corresponding mating tooth root caused by improper setting of the step difference correction structure at the center of the scroll tooth root during the operation of the scroll compressor.

[0007] To achieve the above objectives, the present invention adopts the following technical solution: On one hand, the present invention provides a scroll disk assembly applied to a compressor, the compressor having a fixed scroll exhaust port; the scroll disk assembly includes a fixed scroll disk and a moving scroll disk meshing with each other, the fixed scroll disk having fixed scroll teeth, the moving scroll disk having moving scroll teeth, and a compression cavity moving from the outer periphery to the center being formed between the fixed scroll teeth and the moving scroll teeth; the tooth tip profile and / or tooth root profile of the fixed scroll teeth and / or the moving scroll teeth are constructed with geometric compensation structures for compensating for thermal deformation; the geometric compensation structures at least partially cover the following areas: When a compression chamber is connected to the fixed vortex exhaust port for exhaust, the region extending from the tail of the compression chamber at the angular position on the corresponding vortex disk toward the end of the vortex teeth of the vortex disk.

[0008] Furthermore, the geometric compensation structure includes a continuous gradient profile formed on the tooth tip of the fixed vortex tooth and / or the tooth tip of the moving vortex tooth, the continuous gradient profile causing the tooth tip height to decrease continuously from the beginning end of the tooth to the end end.

[0009] Furthermore, the geometric compensation structure includes a stepped depth variation profile formed on the tooth root of the fixed vortex tooth and / or the tooth root of the moving vortex tooth, the profile causing the tooth root to form at least one step with a sudden depth change in the radial direction.

[0010] Furthermore, for the fixed vortex tooth, the reduction amount of the continuously gradient profile of its tooth tip at the angular position on the fixed vortex disk is configured to compensate for the maximum expected thermal deformation of the fixed vortex tooth at that location.

[0011] Furthermore, for the moving vortex tooth, the reduction amount of the continuously gradient profile of its tooth tip at the angular position on the moving vortex disk is configured to compensate for the maximum expected thermal deformation of the moving vortex tooth at that location.

[0012] Furthermore, for the fixed vortex tooth, the end point of the step with a sudden depth change in the stepped depth profile at the tooth root is located at the development angle position on the fixed vortex disk.

[0013] Furthermore, for the moving vortex tooth, the end point of the step with a sudden depth change in the stepped depth profile at the tooth root is located at the development angle position on the moving vortex disk.

[0014] Furthermore, in the stepped depth variation profile of the fixed vortex tooth root, the ending angle of the first depth variation segment is set to the position of the tail of the moving vortex disk at the corresponding angle of expansion on the fixed vortex disk when the compression chamber of the moving vortex disk begins to exhaust; in the stepped depth variation profile of the moving vortex tooth root, the ending angle of the first depth variation segment is set to the position of the tail of the moving vortex disk at the corresponding angle of expansion on the moving vortex disk when the compression chamber of the fixed vortex disk begins to exhaust.

[0015] Furthermore, the geometric compensation structure on the fixed scroll plate and the geometric compensation structure on the moving scroll plate are arranged symmetrically with respect to the center of the compressor.

[0016] On the other hand, the present invention also provides a scroll compressor, including the scroll disk assembly described above.

[0017] The beneficial effects of this invention compared with the prior art are as follows: A scroll disk assembly is applied to a compressor, the compressor having a fixed scroll exhaust port; the scroll disk assembly includes a fixed scroll disk and a moving scroll disk that mesh with each other, the fixed scroll disk having fixed scroll teeth, the moving scroll disk having moving scroll teeth, and a compression cavity that moves from the outer periphery to the center is formed between the fixed scroll teeth and the moving scroll teeth; a geometric compensation structure for compensating for thermal deformation is constructed on the tooth tip profile and / or tooth root profile of the fixed scroll teeth and / or the moving scroll teeth; the geometric compensation structure at least partially covers the following area: when any compression cavity starts to communicate with the fixed scroll exhaust port for exhaust, the area extending from the angular position on the corresponding scroll disk towards the end of the scroll teeth of the scroll disk. This design can specifically compensate for the maximum thermal deformation of the center of the scroll teeth caused by the temperature gradient during the operation of the scroll compressor. It effectively avoids the problem of increased friction loss between the tooth tip and the mating tooth root caused by improper correction position or correction parameters, significantly reduces the wear risk of the tooth tip and tooth root, and thus improves the operational reliability of the compressor.

[0018] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention, it can be implemented according to the contents of the specification. In order to make the above and other objectives, features and advantages of the present invention more obvious and understandable, preferred embodiments are described in detail below. Attached Figure Description

[0019] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0020] Figure 1 A cross-sectional view of a scroll compressor provided in a specific embodiment of the present invention; Figure 2 A schematic diagram of continuous correction of the fixed vortex tooth tip provided in a specific embodiment of the present invention; Figure 3 A schematic diagram of continuous correction of the tip of the moving vortex tooth provided in a specific embodiment of the present invention; Figure 4 A continuous correction projection diagram of the fixed vortex tooth tip provided in a specific embodiment of the present invention; Figure 5 A continuously corrected projection diagram of the tip of the moving vortex tooth provided in a specific embodiment of the present invention; Figure 6 This is a schematic diagram of the compression chamber intake closure provided in a specific embodiment of the present invention; Figure 7 This is a schematic diagram of the correction of the bottom step difference of the fixed vortex tooth provided in a specific embodiment of the present invention; Figure 8 This is a schematic diagram of the correction of the bottom step of the dynamic vortex tooth provided in a specific embodiment of the present invention; Figure 9 This is a projection diagram of the corrected step difference at the bottom of the fixed vortex tooth provided in a specific embodiment of the present invention; Figure 10 This is a projection diagram of the corrected step difference at the bottom of the moving vortex tooth provided in a specific embodiment of the present invention; Figure 11 A schematic diagram of the correction of the bottom step of the constant vortex tooth during exhaust in the compression chamber provided in a specific embodiment of the present invention; Figure 12 This is a schematic diagram of the correction of the bottom step difference of the dynamic vortex tooth during the exhaust of the compression chamber, provided for a specific embodiment of the present invention.

[0021] Figure Labels 1. Fixed scroll plate; 2. Moving scroll plate; 3. Euclid ring; 4. Upper bracket; 5. Crankshaft assembly; 6. Eccentric sleeve; 7. Housing; 8. Divider plate assembly; 9. Top cover assembly; 101. Fixed scroll tooth; 1011. Part of the fixed scroll tooth within the exhaust fluid range; 103. Fixed scroll exhaust port; 201. Moving scroll tooth; 2011. Part of the moving scroll tooth within the exhaust fluid range of chamber A; 203. Moving scroll exhaust groove. Detailed Implementation

[0022] The technical solution of the present invention will be clearly and completely described below with reference to specific embodiments. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0023] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0024] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0025] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0026] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0027] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0028] like Figure 1 As shown, a scroll compressor includes a housing 7, an Euclid ring 3 for limiting the rotation of a moving scroll 2, an upper bracket 4 for supporting a crankshaft assembly 5 and the Euclid ring 3, a crankshaft assembly 5 for driving the moving scroll 2 to rotate and translate, and a motor. The motor output shaft is connected to the crankshaft assembly 5 via a coupling or directly to provide power for the compressor operation. The scroll assembly includes a fixed scroll 1 and a moving scroll 2 that mesh with each other. The fixed scroll 1 has fixed scroll teeth 101, and the moving scroll 2 has moving scroll teeth 201. A compression chamber that moves from the outer periphery to the center is formed between the fixed scroll teeth 101 and the moving scroll teeth 201. The central region of the fixed scroll 1 has a fixed scroll exhaust port 103 that penetrates the side plate of the fixed scroll 1, and the corresponding position of the side plate of the moving scroll 2 has a moving scroll exhaust groove 203 that communicates with the compression chamber. Together, they constitute the exhaust passage of the compressor.

[0029] When the compressor starts, the motor is powered on and drives the crankshaft assembly 5 to rotate at high speed around its own axis. The eccentric part of the crankshaft assembly 5 is embedded in the eccentric sleeve 6 of the moving scroll disk 2. Under the driving action of the eccentric part, the moving scroll disk 2 acquires a tendency to move in a circular motion around the center of the fixed scroll disk 1. At the same time, due to the anti-rotation restriction of the Euclidean ring 3, the moving scroll disk 2 cannot rotate on its own, and finally forms a non-rotational rotary translational motion with the center of the fixed scroll disk 1 as the rotation center and the preset eccentric radius as the trajectory. During this motion, the fixed scroll teeth 101 and the moving scroll teeth 201 always maintain a meshing state, and the multiple closed crescent-shaped compression cavities formed between them, such as... Figure 11 As shown, there are two compression chambers, A and B. The compression chambers move gradually from the outer periphery towards the center. As the compression chambers move towards the center, their circumference gradually decreases, the refrigerant inside the compression chambers is continuously compressed, the volume continuously decreases, and the pressure gradually increases, completing the refrigerant compression process. When the compression chambers move to the central region and connect with the fixed scroll exhaust port 103 or the moving scroll exhaust channel 203, the refrigerant compressed to a preset high pressure value is discharged through the fixed scroll exhaust port 103, enters the exhaust space enclosed by the upper cover assembly 9 and the partition plate assembly 8, and is then transported to the subsequent system through the exhaust pipe.

[0030] During compressor operation, the refrigerant compression process is adiabatic, generating a large amount of heat of compression. This heat cannot be completely dissipated in time, resulting in a temperature distribution pattern in the scroll teeth (fixed scroll tooth 101 and / or moving scroll tooth 201) that gradually increases from the outer periphery to the center. The central region of the scroll teeth, being located at the convergence point of multiple compression chambers, accumulates the most heat and has the highest temperature. Especially when the compression chamber first connects with the fixed scroll exhaust port 103 to begin exhausting, the pressure inside the compression chamber is much lower than the pressure in the exhaust space. Some of the high-pressure, high-temperature refrigerant in the exhaust space flows back into the compression chamber, triggering secondary compression and further exacerbating the temperature rise in this region. This makes the axial thermal deformation of the scroll teeth at this location the most significant. If thermal deformation in this area is not compensated for, the gap between the tip of the thermally deformed scroll tooth and the mating tooth root will decrease sharply, or even become zero or negative. This will cause mechanical interference between the tips and roots of the moving and stationary scroll teeth, which will not only significantly increase friction loss and reduce the volumetric efficiency and energy efficiency ratio of the compressor, but may also cause severe wear on the tips and roots of the teeth, shorten the service life of the scroll plate, and in severe cases, cause the compressor to seize up and fail to operate normally.

[0031] To address the interference wear problem caused by thermal deformation, this invention is proposed, and specific embodiments are described below.

[0032] Overall, the core idea of ​​this invention is that the tooth tip profile and / or tooth root profile of the fixed vortex tooth 101 and / or the moving vortex tooth 201 are constructed with geometric compensation structures for compensating for thermal deformation; the geometric compensation structures at least partially cover the following areas: When any compression chamber is connected to the fixed scroll exhaust port 103 for exhaust, the area extending from the tail of the compression chamber at the angular position on the corresponding scroll disk (moving scroll disk 2 and / or fixed scroll disk 1) towards the end of the scroll teeth of the scroll disk. This design can specifically compensate for the maximum thermal deformation of the center of the scroll teeth caused by the temperature gradient during the operation of the scroll compressor, effectively avoiding the problem of increased friction loss between the tooth tip and the mating tooth root caused by improper correction position or correction parameters, significantly reducing the wear risk of the tooth tip and tooth root, and thus improving the operational reliability of the compressor.

[0033] Example 1, as Figures 2 to 5 As shown, in this embodiment, depending on the compressor's operating conditions and structural design, a geometric compensation structure with a continuous gradient profile can be constructed only at the tooth tip of the fixed scroll tooth 101, only at the tooth tip of the moving scroll tooth 201, or simultaneously at both tooth tips. The core design principle of this continuous gradient profile is to make the working surface of the tooth tip (i.e., the end face that mates with the tooth root of the opposite scroll tooth) continuously and gently decrease in height from the starting end of the tooth (the end near the outer periphery of the scroll disk) to the ending end (the end near the center of the scroll disk), forming a smooth slope structure. Figure 4and Figure 5 In this process, the continuous correction region is a closed area that gradually expands from the outer periphery to the center. The boundary of this region is adapted to the helical profile of the vortex tooth, ensuring that the corrected tooth tip profile does not affect the sealing performance of the compression chamber.

[0034] The aspect ratio refers to the polar angle of a point on the helical profile of the scroll teeth relative to the center of the scroll, used to accurately locate the specific position on the scroll teeth. Determining the specific aspect ratio position requires considering the actual operating state of the compressor, as follows: The motion state and pressure changes of the compression chamber are monitored in real time using high-speed photography or dynamic pressure sensors. When the pressure in a certain compression chamber (such as chamber A) reaches the exhaust pressure threshold and begins to connect with the fixed scroll exhaust port 103 of the compression chamber, the position of the tail of that compression chamber on the currently observed scroll disk is recorded at that moment. Based on the helical profile equation of the scroll teeth of that scroll disk, the polar angle of that tail position relative to the center of the scroll is calculated, which is the specific aspect ratio position corresponding to the start of exhaust from that compression chamber.

[0035] For example, refer to Figure 11 When the A chamber on the moving scroll plate 2 begins to exhaust, the moving scroll teeth are within the exhaust fluid range 2011. The aspect ratio position corresponding to the tail of the A chamber on the fixed scroll tooth 101 profile of the fixed scroll plate 1 is marked as Φdo; similarly, refer to Figure 12 When the B chamber on the fixed scroll plate 1 begins to exhaust, the portion 1011 of the fixed scroll tooth is within the exhaust fluid range. The position of the aspect ratio corresponding to the tail of the B chamber on the moving scroll tooth 201 profile of the moving scroll plate 2 is marked as Φdf. The continuous gradient profile needs to cover at least the entire area extending from this specific aspect ratio position (Φdo or Φdf) towards the end of the scroll tooth. If the thermal deformation distribution in this area is relatively uniform, it can also cover the main part of this area, but it is necessary to ensure that the area with the most severe thermal deformation is completely covered.

[0036] To ensure adequate thermal deformation compensation, at a specific development angle position, the reduction amount of the continuous gradient profile at the tooth tip (i.e., the reduction in the corrected tooth tip height compared to the uncorrected state) Δ must be precisely matched with the maximum expected thermal deformation of the volute tooth at that position.

[0037] During the design phase, the tooth tip reduction Δ at a specific aspect ratio position should be greater than or equal to the maximum expected thermal deformation at that position, i.e., Δ ≥ Δ_max. When the aspect ratio corresponding to the exhaust chamber tail is Φdo, the correction ΔFX1 here should be the maximum deformation of the fixed scroll tooth 101; when the aspect ratio corresponding to the exhaust chamber tail of chamber B is Φdf, the correction ΔOX1 here should be the maximum deformation of the moving scroll tooth 201. Considering design and manufacturing errors, upper and lower limits of ±0.05 rad can be set for Φdo and Φdf.

[0038] For the overall slope design of a continuously gradient profile, it needs to be determined based on the trend of thermal deformation from the outer periphery to the center of the spiral tooth. From the starting end of the spiral tooth to a specific angle position, the thermal deformation gradually increases from a small value to the maximum expected thermal deformation. Therefore, the tooth tip reduction should also gradually increase linearly or non-linearly to form a smooth gradient slope. From the specific angle position to the tooth tip, the thermal deformation basically remains near the maximum expected thermal deformation. Therefore, the tooth tip reduction in this section can be kept constant or finely adjusted according to the small fluctuations in thermal deformation to ensure that a reasonable gap is maintained between the tooth tip and the tooth root in the entire thermal deformation affected area.

[0039] By using a continuous gradient profile that precisely matches the design of the vortex tooth tip with the thermal deformation distribution, effective compensation for the thermal deformation of the vortex tooth is achieved. This completely solves the problem of tooth tip and tooth root interference caused by thermal deformation of the vortex tooth under high pressure differential and high pressure ratio conditions, and significantly reduces friction loss.

[0040] Example 2, as Figures 7 to 12 As shown, in this embodiment, by setting a stepped structure with a sudden change in depth at the tooth root, a space is provided to accommodate the thermal deformation of the opposite tooth tip, thus achieving the purpose of thermal deformation compensation.

[0041] In this embodiment, the geometric compensation structure of the stepped depth variation profile can be constructed only at the bottom of the fixed volute 101, only at the bottom of the moving volute 201, or simultaneously at the bottom of both volutes, depending on actual needs. The core design of this stepped depth variation profile is to set at least one step with a sudden depth change in the radial direction (from the outer periphery to the center) of the tooth bottom, so that the tooth bottom forms two or more regions: a shallow depth segment and a deep depth segment. The shallow depth segment corresponds to the region with less thermal deformation on the outer side of the volute tooth, and the deep depth segment corresponds to the region with greater thermal deformation at the center of the volute tooth. The height of the step (i.e., the depth difference between the deep depth segment and the shallow depth segment) is the thermal deformation compensation amount.

[0042] like Figures 7 to 10 As shown, the first stage correction of the fixed vortex is set. Correction of the first stage of the moving vortex Description of the ending angle. The moment when exhaust begins in each compression chamber is the moment when the exhaust fluid range is at its maximum. For example... Figure 11 , Figure 12 As shown, when the fluid in the compression chamber is compressed to the exhaust angle and begins to exhaust, the moving vortex tooth is located within the exhaust fluid range of chamber A (2011), with the tail of chamber A corresponding to an aspect ratio of Φdo, and the temperature on both sides being the exhaust temperature. The fixed vortex tooth 101 is located within the exhaust fluid range of chamber A, with the tail of chamber A corresponding to an aspect ratio of Φdf, and the temperature on both sides being the exhaust temperature. At this time, the center of the vortex tooth has the highest temperature and the largest deformation. Therefore, the exhaust time of the compression chamber is selected, with the tail of chamber A at an aspect ratio of Φdo being used as the first segment correction for the fixed vortex. End angle; the first segment correction of the dynamic vortex is taken at the tail end of the B-cavity exhaust chamber corresponding to the aspect ratio Φdf. The ending angle is accurate and appropriate. Considering design and manufacturing errors, upper and lower limits of ±0.05rad can be set for Φdo and Φdf.

[0043] By precisely setting the end point of the step at the position of the largest thermal deformation angle, all tooth root areas from that point toward the center are deepened, providing sufficient space to accommodate the thermal expansion of the opposite tooth tip, ensuring that the tooth tip and tooth root will not interfere even under the maximum thermal deformation state.

[0044] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and these modifications or substitutions should all be covered within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A scroll disk assembly, applied to a compressor, the compressor having a fixed scroll exhaust port; the scroll disk assembly comprising a fixed scroll disk and a moving scroll disk meshing with each other, the fixed scroll disk having fixed scroll teeth, the moving scroll disk having moving scroll teeth, and a compression cavity moving from the outer periphery to the center being formed between the fixed scroll teeth and the moving scroll teeth; characterized in that, The fixed vortex tooth and / or the moving vortex tooth have geometric compensation structures constructed on their tooth tip and / or tooth root profiles for compensating for thermal deformation; the geometric compensation structures at least partially cover the following areas: When a compression chamber is connected to the fixed vortex exhaust port for exhaust, the region extending from the tail of the compression chamber at the angular position on the corresponding vortex disk toward the end of the vortex teeth of the vortex disk.

2. The scroll disk assembly according to claim 1, characterized in that, The geometric compensation structure includes a continuous gradient profile formed on the tooth tip of the fixed vortex tooth and / or the tooth tip of the moving vortex tooth, the continuous gradient profile causing the tooth tip height to decrease continuously from the beginning end of the tooth to the end end.

3. The scroll disk assembly according to claim 1, characterized in that, The geometric compensation structure includes a stepped depth variation profile formed on the tooth root of the fixed vortex tooth and / or the tooth root of the moving vortex tooth, the profile causing the tooth root to form at least one step with a sudden depth change in the radial direction.

4. A scroll disk assembly according to claim 2, characterized in that, For the fixed vortex tooth, the reduction amount of the continuously gradient profile of its tooth tip at the angular position on the fixed vortex disk is configured to compensate for the maximum expected thermal deformation of the fixed vortex tooth at that location.

5. A scroll disk assembly according to claim 2, characterized in that, For the moving vortex tooth, the reduction amount of the continuously gradient profile of its tooth tip at the angular position on the moving vortex disk is configured to compensate for the maximum expected thermal deformation of the moving vortex tooth at that location.

6. A scroll disk assembly according to claim 3, characterized in that, For the fixed vortex tooth, the end point of the step with a sudden depth change in the stepped depth profile at the tooth root is located at the development angle position on the fixed vortex disk.

7. A scroll disk assembly according to claim 3, characterized in that, For the moving vortex tooth, the end point of the step with a sudden depth change in the stepped depth profile at the tooth root is located at the development angle position on the moving vortex disk.

8. A scroll disk assembly according to claim 3, characterized in that, In the stepped depth variation profile of the fixed vortex tooth root, the ending angle of the first depth variation segment is set to the position of the tail of the moving vortex disk at the corresponding angle of expansion on the fixed vortex disk when the compression chamber of the moving vortex disk begins to exhaust; in the stepped depth variation profile of the moving vortex tooth root, the ending angle of the first depth variation segment is set to the position of the tail of the moving vortex disk at the corresponding angle of expansion on the moving vortex disk when the compression chamber of the fixed vortex disk begins to exhaust.

9. A scroll disk assembly according to any one of claims 1-8, characterized in that, The geometric compensation structure on the fixed scroll plate and the geometric compensation structure on the moving scroll plate are arranged symmetrically with respect to the center of the compressor.

10. A scroll compressor, characterized in that, Includes the vortex disk assembly as described in any one of claims 1-9.

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