A method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management.

Abstract

The application provides a CO2 scroll compressor stage variable wall thickness scroll profile generation method for vehicle thermal management, comprising the following steps: obtaining the required gap value between the outer wall of the moving scroll and the inner wall of the static scroll according to the temperature field of the scroll compressor compression cavity and the thermal deformation of the moving scroll and the static scroll; obtaining the required gap value between the outer wall of the static scroll and the inner wall of the moving scroll according to the temperature field of the scroll compressor compression cavity and the thermal deformation of the moving scroll and the static scroll; generating the inner side profile of the static scroll according to the required gap value between the outer wall of the moving scroll and the inner wall of the static scroll; generating the outer side profile of the moving scroll according to the required gap value between the outer wall of the moving scroll and the inner wall of the static scroll; generating the inner side profile of the moving scroll according to the required gap value between the outer wall of the static scroll and the inner wall of the moving scroll; and generating the outer side profile of the static scroll according to the required gap value between the outer wall of the static scroll and the inner wall of the moving scroll. The application can overcome the leakage and wear problems of the scroll compressor caused by thermal deformation, and improve the performance and reliability of the scroll compressor.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, and relates to a method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management. Background Technology

[0002] The automotive industry is a pillar industry in my country, and heat pump air conditioning is an important technological approach to improve the winter driving range of electric vehicles. Compared to other refrigerants, the natural refrigerant CO2 has advantages such as smaller specific volume and larger cooling capacity per unit volume, and CO2 does not harm the environment, meeting environmental protection requirements. Therefore, CO2 refrigerant has been applied to vehicle thermal management, leading to the development of CO2 compressors to improve cooling efficiency. Among them, CO2 scroll compressors, with their advantages of small size, light weight, and good stability, have become the optimal solution for CO2 circulation in vehicles. However, CO2 has a high transcritical discharge pressure, and CO2 scroll compressors generally suffer from wear on the moving and stationary scroll plates, resulting in a reduced lifespan. Similarly, in fields such as food, medical, and fuel cells, where high gas cleanliness is required, oil-free compressor technology is needed for pressurized gas supply. Among various compressors, oil-free scroll compressors, with their unique structure and excellent mechanical properties, are the preferred solution for achieving oil-free compressor operation within a small flow range. However, oil-free scroll compressors also generally suffer from problems such as short lifespan and poor reliability. The main reason for these problems is that to ensure the performance and reliability of the compressor during operation, precise meshing of the moving and stationary scrolls is essential to control the meshing clearance and prevent internal leakage. This meshing clearance is typically controlled by the machining and assembly precision of the moving and stationary scrolls, and current technologies use the scroll dimensions at room temperature to preset the meshing clearance. However, because oil-free scroll compressors and CO2 scroll compressors operate at high exhaust temperatures, the commonly used aluminum scroll discs undergo significant and uneven thermal deformation, causing changes in the meshing clearance between the moving and stationary scrolls. In some locations, increased clearance leads to greater leakage and decreased compressor performance; in other locations, decreased clearance can even cause interference between the moving and stationary scroll walls, resulting in severe wear and compressor failure. Therefore, thermal deformation is a key factor affecting the performance and reliability of scroll compressors at high exhaust temperatures, and clearance designs based on scroll dimensions at room temperature cannot overcome the leakage and wear problems caused by thermal deformation. Summary of the Invention

[0003] To address the leakage and wear problems caused by thermal deformation of the scroll ring in existing scroll compressors, this invention creatively provides a method for generating the scroll ring profile of a CO2 scroll compressor for vehicle thermal management. This method overcomes the leakage and wear problems caused by thermal deformation, thereby improving the performance and reliability of the scroll compressor.

[0004] This invention is achieved through the following technical solution:

[0005] A method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management, including:

[0006] S101. Based on the temperature field of the compression chamber of the CO2 scroll compressor and the thermal deformation of the moving scroll and the stationary scroll, obtain the required gap value between the outer wall of the moving scroll and the inner wall of the stationary scroll.

[0007] S102. Based on the temperature field of the compression chamber of the CO2 scroll compressor and the thermal deformation of the moving scroll and stationary scroll, obtain the required clearance value between the outer wall of the stationary scroll and the inner wall of the moving scroll.

[0008] S103. Generate the inner profile of the static vortex ring according to the required gap value between the outer wall of the moving vortex ring and the inner wall of the static vortex ring.

[0009] S104. Generate the outer profile of the moving vortex according to the required gap value between the outer wall of the moving vortex and the inner wall of the stationary vortex.

[0010] S105. Generate the inner profile of the moving vortex according to the required gap value between the outer wall of the stationary vortex and the inner wall of the moving vortex.

[0011] S106. Generate the outer profile of the stationary vortex ring based on the required gap value between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring.

[0012] Preferably, in S101, the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex is determined as follows:

[0013] S601. Calculate the development angle of the centerline of the moving vortex based on the length of the inner profile of the moving vortex.

[0014] S602. Based on the temperature field of the compression chamber of the CO2 scroll compressor, the thermal deformation of the moving scroll and the stationary scroll, and the development angle of the center line of the moving scroll, calculate the change in the outer wall profile of the moving scroll and the change in the inner wall profile of the stationary scroll along the base circle involute.

[0015] S603. Determine the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex based on the change in the outer wall profile of the moving vortex and the change in the inner wall profile of the stationary vortex.

[0016] Furthermore, in S601, the aspect ratio of the centerline of the moving vortex is calculated based on the length of the inner profile of the moving vortex. Specifically:

[0017]

[0018] In the formula, β1 is the correction angle of the inner profile of the moving vortex, and t o For designing the wall thickness of the moving vortex at room temperature, L oi denoted as , where is the length of the inner profile of the moving vortex, and 'a' is the radius of the base circle.

[0019] Furthermore, in S602, the formula for calculating the change in the outer wall profile of the moving vortex is as follows:

[0020]

[0021] The formula for calculating the change in the inner wall profile of the static vortex is as follows:

[0022]

[0023] In the formula, Δl1(φ o ) represents the change in the outer wall profile of the moving vortex, Δl2(φ) o +π) represents the change in the inner wall profile of the static vortex, φ o Let denoted as the development angle of the centerline of the moving vortex, and Δx and Δy be the changes in the abscissa and ordinate of a point on the involute of the base circle after thermal deformation, respectively. These values ​​are known.

[0024] Furthermore, in S603, the required clearance between the outer wall of the moving vortex and the inner wall of the stationary vortex is determined by the following formula:

[0025] δ1(φ o )=Δl1(φ o )-Δl2(φ o +π)

[0026] In the formula, δ1(φ o ) represents the required clearance between the outer wall of the moving vortex and the inner wall of the stationary vortex, Δl1(φ) o ) represents the change in the outer wall profile of the moving vortex, Δl2(φ) o +π) represents the change in the inner wall profile of the static vortex, φ o The angle of the centerline of the moving vortex.

[0027] Preferably, the required clearance value between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring, S102, is determined as follows:

[0028] S701. Calculate the development angle of the centerline of the stationary vortex based on the length of the inner profile of the stationary vortex.

[0029] S702. Based on the temperature field of the compression chamber of the CO2 scroll compressor, the thermal deformation of the moving scroll and the stationary scroll, and the development angle of the center line of the stationary scroll, calculate the change in the inner wall profile of the moving scroll and the change in the outer wall profile of the stationary scroll along the base circle involute.

[0030] S703. Determine the required clearance value between the outer wall of the stationary vortex and the inner wall of the moving vortex based on the change in the inner wall profile of the moving vortex and the change in the outer wall profile of the stationary vortex.

[0031] Furthermore, in S701, the aspect ratio of the centerline of the stationary vortex is calculated based on the length of the inner profile of the stationary vortex, specifically:

[0032]

[0033] In the formula, β2 is the correction angle of the inner profile of the static vortex ring, and L si t is the length of the inner profile of the stationary vortex ring. s The wall thickness is designed for a stationary vortex at room temperature, where 'a' is the base circle radius.

[0034] Furthermore, in S702, the formula for calculating the change in the outer wall profile of the stationary vortex ring is as follows:

[0035]

[0036] The formula for calculating the change in the inner wall profile of the moving vortex is as follows:

[0037]

[0038] In the formula, Δl3(φ s ) represents the change in the outer wall profile of the static vortex ring, Δl4(φ) s +π) represents the change in the inner wall profile of the moving vortex, φ s Let denoted as the development angle of the centerline of the static vortex, and Δx and Δy be the changes in the abscissa and ordinate of a point on the involute of the base circle after thermal deformation, respectively. These values ​​are known.

[0039] Furthermore, in S703, the required clearance between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring is determined by the following formula:

[0040] δ2(φ s )=Δl3(φ s )-Δl4(φ s +π)

[0041] In the formula, δ2(φ s ) represents the required clearance between the outer wall of the stationary vortex and the inner wall of the moving vortex, Δl3(φ) s ) represents the change in the outer wall profile of the static vortex ring, Δl4(φ) s +π) represents the change in the inner wall profile of the moving vortex, φ s The angle of the centerline of the stationary vortex.

[0042] Preferably, in S103, the inner profile of the stationary vortex ring is generated according to the following parametric equation:

[0043]

[0044] In S104, the outer profile of the moving vortex is generated according to the following parametric equation:

[0045]

[0046] In S105, the inner profile of the moving vortex is generated according to the following parametric equation:

[0047]

[0048] In S106, the outer profile of the stationary vortex ring is generated according to the following parametric equation:

[0049]

[0050] In the formula, a is the radius of the base circle, φ s φ is the aspect ratio of the centerline of the static vortex. o φ is the aspect ratio of the centerline of the moving vortex. o With φ s A difference of 180°, x si y is the abscissa of the inner profile of the static vortex ring. si The ordinate of the inner profile of the static vortex ring is t. s The wall thickness is designed for the stationary vortex at room temperature, δ1(φ) s -π) is the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex, x oo y is the abscissa of the outer profile of the moving vortex. oo t is the ordinate of the outer profile of the moving vortex ring. o The wall thickness is designed for the moving vortex at room temperature, δ1(φ o ) represents the required clearance between the outer wall of the moving vortex and the inner wall of the stationary vortex, x oi y is the abscissa of the inner profile of the moving vortex. oi δ2(φ) represents the ordinate of the inner profile of the moving vortex ring. o -π) is the required clearance value between the outer wall of the stationary vortex and the inner wall of the moving vortex, x so y is the abscissa of the outer profile of the static vortex ring. so δ2(φ) represents the ordinate of the outer profile of the static vortex ring. s ) represents the required clearance between the outer wall of the stationary vortex and the inner wall of the moving vortex.

[0051] Compared with the prior art, the present invention has the following beneficial effects:

[0052] This invention, based on the temperature field of a CO2 scroll compressor used in vehicle thermal management, and considering the thermal deformation of the moving and stationary scrolls in the temperature field, obtains the required thermal clearance values ​​between the outer wall of the moving scroll and the inner wall of the stationary scroll, respectively, under thermal deformation conditions without interference. Then, based on the obtained clearance values, it generates moving and stationary scroll profiles with segmented variable wall thickness characteristics on a constant wall thickness profile at room temperature. In other words, it optimizes and corrects the inner and outer profiles of the moving and stationary scrolls based on their thermal deformation in the temperature field to better adapt to scroll profile deformation caused by temperature changes. Under stable operating conditions, temperature affects the scrolls, causing thermal deformation. The combination of moving and stationary scroll profiles generated by this invention ensures normal meshing clearance between the moving and stationary scrolls during compressor operation, effectively avoiding interference wear caused by thermal deformation and improving compressor reliability. The combination of moving and stationary scroll profiles generated by this invention ensures that the outer profile of the stationary scroll and the inner profile of the moving scroll, as well as the inner profile of the stationary scroll and the outer profile of the moving scroll, maintain a fixed meshing clearance value, effectively controlling leakage at the meshing clearance and improving the volumetric efficiency of the compressor. Compared to the clearance setting under normal temperature scroll design dimensions, this invention can better overcome problems such as wear and leakage caused by scroll thermal deformation. Attached Figure Description

[0053] Figure 1 This is a flowchart of the method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management disclosed in this invention.

[0054] Figure 2 This is the minimum gap value required for the dynamic and static vortex coils to not interfere with each other in the embodiments of the present invention;

[0055] Figure 3 This is a schematic diagram of the vortex profile change;

[0056] Figure 4 This is a schematic diagram of the staged variable wall thickness profile of the scroll compressor according to an embodiment of the present invention. Detailed Implementation

[0057] To further understand the present invention, the present invention will be described below with reference to embodiments. These descriptions are only for further explaining the features and advantages of the present invention and are not intended to limit the claims of the present invention.

[0058] This invention, based on the operating conditions of a CO2 scroll compressor, simulates and calculates the temperature field of the compression chamber using an involute profile. Based on this temperature field, it obtains the required clearance values ​​between the outer wall of the moving scroll and the inner wall of the stationary scroll, as well as between the outer wall of the stationary scroll and the inner wall of the moving scroll. Based on this, it generates the inner and outer profiles of the moving and stationary scrolls to better adapt to scroll thermal deformation caused by temperature changes. Compared to traditional scroll profile generation methods, this invention can better avoid wear failure and leakage caused by thermal deformation. This invention creatively generates a staged variable wall thickness scroll profile based on the calculated scroll thermal deformation, thereby reducing the adverse effects of scroll thermal deformation in scroll compressors.

[0059] like Figure 1 As shown, this invention discloses a method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management, comprising the following steps:

[0060] S101. Based on the temperature field of the compression chamber of the CO2 scroll compressor and the thermal deformation of the moving and stationary scrolls, obtain the required clearance value (δ1(φ) between the outer wall of the moving scroll and the inner wall of the stationary scroll under the condition that no interference occurs. o ));

[0061] S102. Based on the temperature field of the CO2 scroll compressor's compression chamber and the thermal deformation of the moving and stationary scrolls, obtain the required clearance value (δ2(φ) between the outer wall of the stationary scroll and the inner wall of the moving scroll under the condition that no interference occurs. s ));

[0062] S103. Generate the inner profile (P2) of the stationary vortex ring based on the required gap value between the outer wall of the moving vortex ring and the inner wall of the stationary vortex ring.

[0063] S104. Generate the outer profile (P1) of the moving vortex according to the required gap value between the outer wall of the moving vortex and the inner wall of the stationary vortex.

[0064] S105. Generate the inner profile of the moving vortex (P4) based on the required gap value between the outer wall of the stationary vortex and the inner wall of the moving vortex.

[0065] S106. Generate the outer profile (P3) of the stationary vortex ring based on the required gap value between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring.

[0066] In specific implementation, in step S101, the temperature distribution and thermal deformation of the scroll compressor are analyzed using CFD simulation and experiments; the required clearance value between the outer wall of the moving scroll and the inner wall of the stationary scroll is determined as follows:

[0067] S601. Calculate the development angle of the center line of the moving scroll ring based on the inner profile length of the moving scroll ring; the inner profile length of the moving scroll ring is the non-optimized profile length calculated when designing the compressor.

[0068] S602. Based on the temperature field of the compressor cavity of the scroll compressor, the thermal deformation of the moving scroll and the stationary scroll, and the development angle of the center line of the moving scroll, calculate the change in the outer wall profile of the moving scroll and the change in the inner wall profile of the stationary scroll along the involute of the base circle caused by thermal deformation.

[0069] S603. Based on the changes in the outer wall profile of the moving vortex and the inner wall profile of the stationary vortex, determine the required clearance value (δ1(φ)) between the outer wall of the moving vortex and the inner wall of the stationary vortex. o )).

[0070] In specific implementation, in step S601, the length of the vortex profile based on the base circle involute is calculated according to the following formula:

[0071]

[0072] In the formula, L is the length of the vortex profile, φ is the development angle of the vortex centerline, φ1 is the initial development angle of the profile, φ2 is the final development angle of the profile, and a is the radius of the base circle.

[0073] For the inner profile of the moving vortex in this embodiment, the aspect ratio φ of the center line of the moving vortex is... o The transformation of the inner profile length of the moving vortex is calculated using the following formula:

[0074]

[0075] In the formula, β1 is the correction angle of the inner profile of the moving vortex, and t o For designing the wall thickness of the moving vortex at room temperature, L oi denoted as , where is the length of the inner profile of the moving vortex, and 'a' is the radius of the base circle.

[0076] Therefore, the aspect ratio φ of the centerline of the moving vortex can be calculated based on the inner profile length of the moving vortex using the method described above. o .

[0077] In specific implementation, in step S602, the amount of profile change of the vortex along the involute of the base circle is determined as follows:

[0078] like Figure 3 Given the deformation along the x-axis and y-axis, the change in profile of the vortex along the involute of the base circle can be calculated. If there is a point A on the involute of the base circle, and its coordinates change from (x, y) to A'(x+Δx, y+Δy) after thermal deformation, then the displacement of the vortex along the involute of the base circle in the forming line direction can be calculated using the following formula:

[0079]

[0080] In the formula, Δl is the change in the vortex wall profile caused by thermal deformation, φ is the vortex centerline development angle, and Δx and Δy are the changes in the abscissa and ordinate of a point on the involute of the base circle after thermal deformation, respectively. These values ​​are known.

[0081] Based on the above method, the change in the outer wall profile of the moving vortex ring along the base circle involute caused by thermal deformation, Δl1(φ), is calculated. o ), Change in the inner wall profile of the static vortex ring Δl2(φ) o +π):

[0082]

[0083]

[0084] In the formula, Δl1(φ o ) represents the change in the outer wall profile of the moving vortex, Δl2(φ) o +π) represents the change in the inner wall profile of the static vortex, φ o Let denoted as the development angle of the centerline of the moving vortex, and Δx and Δy be the changes in the abscissa and ordinate of a point on the involute of the base circle after thermal deformation, respectively. These values ​​are known.

[0085] In specific implementation, in step S603, the required clearance value between the outer wall of the moving vortex ring and the inner wall of the stationary vortex ring is determined by the following formula:

[0086] δ1(φ o )=Δl1(φ o )-Δl2(φ o +π)

[0087] In the formula, δ1(φ o ) represents the required clearance between the outer wall of the moving vortex and the inner wall of the stationary vortex, Δl1(φ o ) represents the change in the outer wall profile of the moving vortex, Δl2(φ) o +π) represents the change in the inner wall profile of the static vortex, φ o The angle of the centerline of the moving vortex.

[0088] The required gap function curve between the outer wall of the moving vortex ring and the inner wall of the stationary vortex ring in this embodiment of the invention is shown in the figure. Figure 2 Solid line curve.

[0089] In specific implementation, the required clearance value between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring in step S102 is determined as follows:

[0090] S701. Calculate the development angle of the center line of the stationary vortex ring based on the inner profile length of the stationary vortex ring; the inner profile length of the stationary vortex ring is the non-optimized profile length calculated when designing the compressor.

[0091] S702. Based on the temperature field of the compression chamber of the scroll compressor, the thermal deformation of the moving scroll and the stationary scroll, and the development angle of the center line of the stationary scroll, calculate the change in the inner wall profile of the moving scroll and the change in the outer wall profile of the stationary scroll along the base circle involute.

[0092] S703. Determine the required clearance value between the outer wall of the stationary vortex and the inner wall of the moving vortex based on the change in the inner wall profile of the moving vortex and the change in the outer wall profile of the stationary vortex.

[0093] In specific implementation, step S701 involves calculating the aspect ratio of the centerline of the stationary vortex ring based on the inner profile length of the stationary vortex ring. Specifically:

[0094]

[0095] In the formula, β2 is the correction angle of the inner profile of the static vortex ring, and L si t is the length of the inner profile of the stationary vortex ring. s The wall thickness is designed for a stationary vortex at room temperature, where 'a' is the base circle radius.

[0096] Therefore, the development angle φ of the centerline of the stationary vortex can be calculated based on the inner profile length of the stationary vortex using the method described above. s .

[0097] In specific implementation, in step S702, the changes in the outer wall profile of the stationary vortex and the inner wall profile of the moving vortex are determined according to the following formula:

[0098]

[0099] Specifically, the formula for calculating the change in the outer wall profile of the stationary vortex ring is as follows:

[0100]

[0101] Specifically, the formula for calculating the change in the inner wall profile of the moving vortex is as follows:

[0102]

[0103] In the formula, Δl3(φ s ) represents the change in the outer wall profile of the static vortex ring, Δl4(φ) s +π) represents the change in the inner wall profile of the moving vortex, φ s Let denoted as the development angle of the centerline of the static vortex, and Δx and Δy be the changes in the abscissa and ordinate of a point on the involute of the base circle after thermal deformation, respectively. These values ​​are known.

[0104] In specific implementation, in step S703, the required clearance value between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring is determined by the following formula:

[0105] δ2(φ s )=Δl3(φ s )-Δl4(φ s +π)

[0106] In the formula, δ2(φ s ) represents the required clearance between the outer wall of the stationary vortex and the inner wall of the moving vortex, Δl3(φ)s ) represents the change in the outer wall profile of the static vortex ring, Δl4(φ) s +π) represents the change in the inner wall profile of the moving vortex, φ s The angle of the centerline of the stationary vortex.

[0107] The required gap function curve between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring in this embodiment of the invention is shown in the figure. Figure 2 Dashed curve.

[0108] In specific implementation, in step S103, the inner profile (P2) of the stationary vortex ring is generated according to the following parametric equation:

[0109]

[0110] In the formula, a is the radius of the base circle, φ s x is the aspect ratio of the centerline of the static vortex. si y is the abscissa of the inner profile of the static vortex ring. si The ordinate of the inner profile of the static vortex ring is t. s The wall thickness of the stationary vortex at room temperature is designed as δ1(φ). s -π) is the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex.

[0111] In specific implementation, in step S104, the outer profile (P1) of the moving vortex is generated according to the following parametric equation:

[0112]

[0113] In the formula, a is the radius of the base circle, φ o x is the aspect ratio of the centerline of the moving vortex. oo y is the abscissa of the outer profile of the moving vortex. oo t is the ordinate of the outer profile of the moving vortex ring. o The wall thickness is designed for the moving vortex at room temperature, δ1(φ o ) represents the required clearance between the outer wall of the moving vortex and the inner wall of the stationary vortex, δ1(φ) o φ is also the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex. o With φ s A difference of 180°, δ1(φ o This indicates that the meshing point of the profiles of the moving scroll and the stationary scroll differs by 180°.

[0114] In specific implementation, in step S105, the inner profile (P4) of the moving vortex is generated according to the following parametric equation:

[0115]

[0116] In the formula, a is the radius of the base circle, φ o x is the aspect ratio of the centerline of the moving vortex. oiy is the abscissa of the inner profile of the moving vortex. oi t is the ordinate of the inner profile of the moving vortex ring. o The wall thickness is designed for the moving vortex at room temperature, δ2(φ o -π) is the required clearance value between the outer wall of the stationary vortex and the inner wall of the moving vortex.

[0117] In specific implementation, in step S106, the outer profile (P3) of the stationary vortex ring is generated according to the following parametric equation:

[0118]

[0119] In the formula, a is the radius of the base circle, φ s x is the aspect ratio of the centerline of the static vortex. so y is the abscissa of the outer profile of the static vortex ring. so The ordinate of the outer profile of the static vortex ring is t. s The wall thickness is designed for the stationary vortex at room temperature, δ2(φ) s This also represents the required clearance between the outer wall of the stationary vortex and the inner wall of the moving vortex. φ o With φ s A difference of 180°, δ2(φ) s This indicates that the meshing point of the profiles of the moving scroll and the stationary scroll differs by 180°.

[0120] Figure 4 This is a schematic diagram of the staged variable wall thickness profile of the scroll compressor according to an embodiment of the present invention. Experiments were conducted on this prototype, and the results were compared with simulation data of the compressor after profile optimization. The experimental results show that the wear condition and scroll temperature distribution of the prototype are consistent with the simulation analysis. Compared with the prototype, the optimized scroll compressor has a 10°C lower exhaust temperature and a 3.69% higher volumetric efficiency, verifying the reliability of the simulation results and the rationality of the profile optimization.

[0121] In summary, this invention discloses a method for generating the profile of a staged variable wall thickness scroll compressor for vehicle thermal management. Based on the thermal deformation of the moving and stationary scrolls, this invention generates the inner and outer profiles of the moving scroll and the stationary scroll according to the changes in their contours caused by thermal deformation. This adapts to the scroll contour deformation caused by temperature changes. Compared to the clearance setting under normal temperature scroll design dimensions, this invention can better overcome problems such as wear and leakage caused by scroll thermal deformation, effectively improving the reliability and efficiency of the CO2 scroll compressor.

[0122] The method described above is also applicable to the generation of the scroll profile in an oil-free scroll compressor, and can similarly improve the reliability and efficiency of the oil-free scroll compressor.

[0123] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit it. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that modifications or equivalent substitutions can still be made to the specific implementation of the present invention. Any modifications or equivalent substitutions that do not depart from the spirit and scope of the present invention should be covered within the scope of protection of the claims of the present invention.

Claims

1. A method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management, characterized in that, include: S101. Based on the temperature field of the compression chamber of the CO2 scroll compressor and the thermal deformation of the moving scroll and the stationary scroll, obtain the required gap value between the outer wall of the moving scroll and the inner wall of the stationary scroll. S102. Based on the temperature field of the compression chamber of the CO2 scroll compressor and the thermal deformation of the moving scroll and stationary scroll, obtain the required clearance value between the outer wall of the stationary scroll and the inner wall of the moving scroll. S103. Generate the inner profile of the static vortex ring according to the required gap value between the outer wall of the moving vortex ring and the inner wall of the static vortex ring. S104. Generate the outer profile of the moving vortex according to the required gap value between the outer wall of the moving vortex and the inner wall of the stationary vortex. S105. Generate the inner profile of the moving vortex according to the required gap value between the outer wall of the stationary vortex and the inner wall of the moving vortex. S106. Generate the outer profile of the stationary vortex ring according to the required gap value between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring. In S103, the inner profile of the stationary vortex ring is generated according to the following parametric equation: In S104, the outer profile of the moving vortex is generated according to the following parametric equation: In S105, the inner profile of the moving vortex is generated according to the following parametric equation: In S106, the outer profile of the stationary vortex ring is generated according to the following parametric equation: In the formula, a The radius of the base circle, The angle of the centerline of the static vortex. The angle of the centerline of the moving vortex. and 180° difference The x-axis of the inner profile of the static vortex ring is... The vertical coordinate of the inner profile of the static vortex ring is given. t s The wall thickness is designed for static vortex rings at room temperature. This is the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex. The x-axis represents the outer profile of the moving vortex. The vertical axis represents the outer profile of the moving vortex ring. The wall thickness is designed for dynamic vortex coils operating at room temperature. This is the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex. The x-axis represents the inner profile of the moving vortex. The vertical coordinate of the inner profile of the moving vortex ring is given. This is the required clearance value between the outer wall of the stationary vortex and the inner wall of the moving vortex. The x-axis represents the outer profile of the static vortex ring. This represents the ordinate of the outer profile of the static vortex ring. This is the required clearance value between the outer wall of the stationary vortex and the inner wall of the moving vortex.

2. The method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management according to claim 1, characterized in that, In S101, the required clearance between the outer wall of the moving vortex and the inner wall of the stationary vortex is determined as follows: S601. Calculate the development angle of the centerline of the moving vortex based on the length of the inner profile of the moving vortex. S602. Based on the temperature field of the compressor cavity of the scroll compressor, the thermal deformation of the moving scroll and the stationary scroll, and the development angle of the center line of the moving scroll, calculate the change in the outer wall profile of the moving scroll and the change in the inner wall profile of the stationary scroll along the base circle involute. S603. Determine the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex based on the change in the outer wall profile of the moving vortex and the change in the inner wall profile of the stationary vortex.

3. The method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management according to claim 2, characterized in that, In S601, the aspect ratio of the centerline of the moving vortex is calculated based on the length of the inner profile of the moving vortex. Specifically: In the formula, This is the correction angle for the inner profile of the moving vortex. The wall thickness is designed for dynamic vortex coils operating at room temperature. The length of the inner profile of the moving vortex ring. Let be the radius of the base circle.

4. The method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management according to claim 2, characterized in that, In S602, the formula for calculating the change in the outer wall profile of the moving vortex is as follows: The formula for calculating the change in the inner wall profile of the static vortex is as follows: In the formula, This represents the change in the outer wall profile of the moving vortex. This represents the change in the profile of the inner wall of the stationary vortex. The angle of the centerline of the moving vortex. These are the changes in the x and y coordinates of a point on the involute of the base circle after thermal deformation, respectively. These values ​​are known.

5. The method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management according to claim 2, characterized in that, In S603, the required clearance between the outer wall of the moving vortex ring and the inner wall of the stationary vortex ring is determined by the following formula: In the formula, This is the required clearance value between the outer wall of the moving vortex and the inner wall of the stationary vortex. This represents the change in the outer wall profile of the moving vortex. This represents the change in the profile of the inner wall of the stationary vortex. The angle of the centerline of the moving vortex.

6. The method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management according to claim 1, characterized in that, S102. The required clearance between the outer wall of the stationary volute and the inner wall of the moving volute is determined as follows: S701. Calculate the development angle of the centerline of the stationary vortex based on the length of the inner profile of the stationary vortex. S702. Based on the temperature field of the compression chamber of the CO2 scroll compressor, the thermal deformation of the moving scroll and the stationary scroll, and the development angle of the center line of the stationary scroll, calculate the change in the inner wall profile of the moving scroll and the change in the outer wall profile of the stationary scroll along the base circle involute. S703. Determine the required clearance value between the outer wall of the stationary vortex and the inner wall of the moving vortex based on the change in the inner wall profile of the moving vortex and the change in the outer wall profile of the stationary vortex.

7. The method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management according to claim 6, characterized in that, In S701, the development angle of the centerline of the stationary vortex is calculated based on the length of the inner profile of the stationary vortex. Specifically: In the formula, This is the correction angle for the profile inside the stationary vortex ring. The length of the profile inside the stationary vortex ring. t s The wall thickness is designed for static vortex rings at room temperature. Let be the radius of the base circle.

8. The method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management according to claim 6, characterized in that, In S702, the formula for calculating the change in the outer wall profile of the stationary vortex ring is as follows: The formula for calculating the change in the inner wall profile of the moving vortex is as follows: In the formula, This represents the change in the outer wall profile of the stationary vortex ring. This represents the change in the profile of the inner wall of the moving vortex. The angle of the centerline of the static vortex. These are the changes in the x and y coordinates of a point on the involute of the base circle after thermal deformation, respectively. These values ​​are known.

9. The method for generating the staged variable wall thickness scroll profile of a CO2 scroll compressor for vehicle thermal management according to claim 7, characterized in that, In S703, the required clearance between the outer wall of the stationary vortex ring and the inner wall of the moving vortex ring is determined by the following formula: In the formula, This is the required clearance value between the outer wall of the stationary vortex and the inner wall of the moving vortex. This represents the change in the outer wall profile of the stationary vortex ring. This represents the change in the profile of the inner wall of the moving vortex. The angle of the centerline of the stationary vortex.

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