Variable cross-section double scroll wrap of scroll compressor and design method of variable cross-section double scroll wrap

Abstract

The invention discloses a variable cross-section double scroll wrap of a scroll compressor and a design method of the variable cross-section double scroll wrap. According to the method, a generatrix of a double-scroll-tooth molded line is constructed based on a universal molded line equation, inner and outer wall molded lines of dynamic and static double scroll teeth are generated through equidistant processing, and a tooth thickness control coefficient is introduced to realize accurate design of a variable cross-section tooth shape. By adjusting the tooth thickness control coefficient, the combination of the variable-cross-section dynamic double-scroll tooth and the static double-scroll tooth or the uniform-cross-section dynamic double-scroll tooth and the variable-cross-section static double-scroll tooth can be constructed, so that the mass of the dynamic scroll tooth is reduced, the stress distribution is improved, the pressure difference between adjacent working cavities is reduced, and the efficiency of the compressor is improved. According to the scroll compressor, the complex design process of a traditional combined molded line is simplified, and technical support is provided for high power and light weight of the scroll compressor.

Description

Technical Field

[0001] The invention belongs to the technical field of scroll compressor engineering, and relates to a method for designing a variable-section double scroll tooth by using a universal profile, in particular to a variable-section double scroll tooth of a scroll compressor and a design method thereof. Background Art

[0002] Scroll compressors have been widely used in air conditioning, expanders, scroll vacuum pumps, refrigeration and other fields due to their many significant advantages such as high efficiency, low noise, low energy consumption and high reliability. Their working process is achieved by the constant meshing movement of the moving scroll and the static scroll. Therefore, the design of the scroll has become an important part of the compressor research and development, which determines the comprehensive performance of the scroll compressor. Compared with single scroll, double scroll has more working chambers due to the increase in the number of teeth involved in the meshing. This not only makes the force on the scroll more uniform, but also significantly reduces the gas pressure difference between two adjacent working chambers. Therefore, it is more meaningful to study double scroll.

[0003] However, although many research results have been achieved in the research of scroll teeth, most of the related research focuses on single scroll teeth with variable cross-section, while research on double scroll teeth with variable cross-section is rare. Traditional scroll compressors mostly use a single scroll tooth structure with a small number of meshing teeth, resulting in uneven force and limited compression efficiency. Although the existing technology has made some breakthroughs in single scroll teeth with variable cross-section, the double scroll tooth design still has problems such as complex profiles and difficult processing.

[0004] The main problems with conventional scroll compressor technology are:

[0005] Small number of meshing teeth: The single scroll tooth structure results in a limited number of teeth participating in meshing at the same time, a small number of working chambers, and low gas compression efficiency;

[0006] Uneven force: Single-tooth structure easily causes local stress concentration, which affects the life of the compressor;

[0007] Complex profile design: Traditional variable cross-section scroll gears rely on combined profile splicing, which is difficult to design and has high processing costs;

[0008] The mass of the moving teeth is large: the inertia force of the moving teeth with equal cross-section is large, which increases energy consumption.

[0009] The present invention simplifies the design process through a universal profile, proposes a construction method for a variable-section double-scroll tooth, and solves the defects of a small number of working chambers and a large pressure difference in the traditional technology. Summary of the invention

[0010] The purpose of the present invention is to propose a design method for a variable-section double scroll tooth of a scroll compressor, a method for designing a variable-section double scroll tooth based on a universal profile, which is used to construct a combination of a dynamic double scroll tooth and a static double scroll tooth, thereby achieving lightweight and performance optimization of the scroll compressor; another purpose of the present invention is to propose a variable-section double scroll tooth of a scroll compressor, which is designed using the method, and on this basis, a dynamic and static double scroll tooth is constructed in which the dynamic double scroll tooth has an equal-section tooth shape, while the static double scroll tooth has a variable-section tooth shape, which has the effect of achieving lightweight of the dynamic scroll tooth and improving the comprehensive performance of the scroll compressor.

[0011] To achieve the above object, the design method of a variable cross-section double scroll tooth of a scroll compressor according to the present invention comprises the following steps:

[0012] Step S01: construct a generatrix equation of a universal profile, the universal profile equation being:

[0013]

[0014] In the formula, is the profile angle, is the terminal angle of the profile, R g is the generalized base circle radius, R s is the generalized expansion radius and satisfies

[0015] When R in formula (1) s With R g This general profile equation is the scroll tooth profile when the following conditions are met:

[0016]

[0017] Where: C0, C1, C2 are all constants;

[0018] Step S02: Construct four busbars, whose equations are:

[0019]

[0020] Where, j = 1, 2, 3, 4, representing the 1st, 2nd, 3rd, and 4th busbars respectively;

[0021] Four generatrixes g1, g2, g3, and g4 are generated according to the universal profile, and the inner and outer wall profiles of the dynamic double scroll gear and the static double scroll gear are designed respectively through equidistant offset.

[0022] The equidistant offset includes:

[0023] The first generatrix g1 is equidistantly extended outward by λ1 to generate the inner wall profile of the stationary scroll gear 1, and equidistantly extended inward by λ2 to generate the outer wall profile of the movable scroll gear 1;

[0024] The second generatrix g2 is equidistantly extended outward by λ2 to generate the inner wall profile of the movable scroll gear 1, and is equidistantly extended inward by λ1 to generate the outer wall profile of the stationary scroll gear 2;

[0025] The third generatrix g3 is equidistantly extended outward by λ1 to generate the inner wall profile of the stationary scroll gear 2, and equidistantly extended inward by λ2 to generate the outer wall profile of the movable scroll gear 2;

[0026] The fourth generatrix g4 is equidistantly spaced outward by λ2 to generate the inner wall profile of the movable scroll gear 2, and is equidistantly spaced inward by λ1 to generate the outer wall profile of the stationary scroll gear 1.

[0027] The formula for the equidistant offset is:

[0028] The first busbar is equidistantly spaced outward by λ1R or , the inner wall profile of the static scroll gear 1 is obtained, and its equation is:

[0029]

[0030] Move the first busbar inwards by an equal distance of λ2R or , the outer wall profile of the movable scroll gear 1 is obtained, and its equation is:

[0031]

[0032] The second busbar is equidistantly spaced outward by λ2R or , the inner wall profile of the movable scroll gear 1 is obtained, and its equation is:

[0033]

[0034] Move the second busbar inward at an equal distance of λ1R or , the outer wall profile of the static scroll 2 is obtained, and its equation is:

[0035]

[0036] The third busbar is equidistantly spaced outward by λ1R or , the inner wall profile of the static scroll gear 2 is obtained, and its equation is:

[0037]

[0038] Move the third busbar inwards at an equal distance of λ2R or , the outer wall profile of the movable scroll gear 2 is obtained, and its equation is:

[0039]

[0040] Move the fourth busbar outwards at an equal distance of λ2R or , the inner wall profile of the movable scroll gear 2 is obtained, and its equation is:

[0041]

[0042] Move the fourth busbar inwards at an equal distance of λ1R or , the outer wall profile of the static scroll gear 1 is obtained, and its equation is:

[0043]

[0044] In the formula, R or is the radius of gyration, subscripts m and f represent the dynamic and static scroll teeth respectively, subscripts i and o represent the inner and outer walls of the scroll teeth respectively, λ1 and λ2 are the tooth thickness control coefficients, and satisfy λ1+λ2=1.

[0045] The tooth thickness control coefficients λ1 and λ2 satisfy λ1=λ2, and the generated dynamic double scroll teeth and static double scroll teeth have variable cross-section tooth shapes with the same shape.

[0046] When the tooth thickness control coefficient λ1=λ2, according to equations (4), (7), (8) and (11), the variable cross-section static double scroll tooth is obtained, as follows: Figure 2 As shown in the figure, 11 is the inner wall profile of the static scroll gear 1, 12 is the outer wall profile of the static scroll gear 1; 21 is the inner wall profile of the static scroll gear 2, and 22 is the outer wall profile of the static scroll gear 2. According to equations (5)-(6) and (9)-(10), the variable cross-section dynamic double scroll gear is obtained, as shown in Figure 3 As shown, 31 is the inner wall profile of the movable scroll gear 1, 32 is the outer wall profile of the movable scroll gear 1; 41 is the inner wall profile of the movable scroll gear 2, and 42 is the outer wall profile of the movable scroll gear 2. Figure 2 and Figure 3 It can be seen that when the tooth thickness control coefficient is equal, the dynamic and static scroll teeth are variable cross-section double scroll teeth with the same shape. Figure 4 The figure shows a schematic diagram of the meshing of the newly designed variable cross-section double vortex gears, in which 1 is a variable cross-section static vortex gear 1, 2 is a variable cross-section static vortex gear 2, 3 is a variable cross-section movable vortex gear 1, and 4 is a variable cross-section movable vortex gear 2.

[0047] The tooth thickness control coefficients λ1 and λ2 satisfy λ1≠λ2, and the tooth thickness of the generated dynamic double scroll teeth is smaller than the tooth thickness of the static double scroll teeth. The dynamic double scroll teeth have a uniform cross-section tooth shape, and the static double scroll teeth have a variable cross-section tooth shape.

[0048] When the tooth thickness control coefficient λ1≠λ2 and satisfies λ1<λ2, according to equations (4), (7), (8) and (11), the variable cross-section static double scroll tooth is obtained, as follows: Figure 5 As shown in the figure, 51 is the inner wall profile of the static scroll gear 1, 52 is the outer wall profile of the static scroll gear 1; 61 is the inner wall profile of the static scroll gear 2, and 62 is the outer wall profile of the static scroll gear 2. According to equations (5)-(6) and (9)-(10), the variable cross-section dynamic double scroll gear is obtained, as shown in Figure 6As shown in the figure, 71 is the inner wall profile of the movable scroll gear 1, 72 is the outer wall profile of the movable scroll gear 1; 81 is the inner wall profile of the movable scroll gear 2, and 82 is the outer wall profile of the movable scroll gear 2. Figure 5 and Figure 6 It can be seen that when the tooth thickness control coefficient is different, the dynamic and static scroll teeth obtained are variable cross-section scroll teeth with the same shape but different tooth thickness. This design method will reduce the mass of the variable cross-section dynamic double scroll teeth, effectively improve the stress condition of the dynamic scroll teeth, and greatly improve the comprehensive performance of the scroll compressor. Figure 7 The figure shows a schematic diagram of the meshing of the newly designed variable cross-section double vortex gears, in which 5 is a variable cross-section static vortex gear 1, 6 is a variable cross-section static vortex gear 2, 7 is a variable cross-section movable vortex gear 1, and 8 is a variable cross-section movable vortex gear 2.

[0049] The moving double scroll gear has a uniform cross-section tooth shape, and the stationary double scroll gear has a variable cross-section tooth shape. The implementation steps are as follows:

[0050] The first generatrix g1 is used as the inner wall profile of the static scroll gear 1, and the fourth generatrix is ​​equidistant inward by λ1 to generate its outer wall profile;

[0051] The third generatrix g3 is used as the inner wall profile of the static scroll 2, and the second generatrix is ​​equidistant inward by λ1 to generate its outer wall profile;

[0052] The inner and outer wall profiles of the dynamic double scroll gear are generated by fixing the tooth thickness T equidistantly inwardly through the first and third generatrix.

[0053] The uniform cross-section tooth thickness of the moving double scroll teeth is uniquely determined by λ2, and the variable cross-section tooth thickness of the stationary double scroll teeth is dynamically adjusted by λ1.

[0054] The terminal extension angle of the universal profile The value range is

[0055] The scroll compressor adopts the variable-section double scroll teeth designed by the method described above.

[0056] The air conditioning system comprises the scroll compressor.

[0057] The R or The range of the radius of gyration is 1.5≤R or ≤4mm.

[0058] The fixed tooth thickness T has a value range of 2≤T≤4.5 mm.

[0059] The variable cross-section double scroll teeth of a scroll compressor and the design method thereof described in the present invention have the following beneficial effects:

[0060] 1. Simplified structure improves efficiency:

[0061] Single universal profile replaces combined profile: The variable cross-section scroll gear is constructed by a universal profile (Formula 1-3), completely abandoning the traditional complex design process that requires the combination of multiple profiles, significantly reducing the processing difficulty and time cost;

[0062] Compared with the traditional variable cross-section scroll gear that must rely on combined profile features, this design method is more efficient and flexible;

[0063] 2. Double scroll gear structure performance optimization:

[0064] Multi-tooth meshing and increased number of cavities: Through the design of variable-section double-scroll teeth, the number of teeth participating in the meshing at the same time is increased, forming more working cavities, effectively improving the force uniformity of the scroll teeth, and reducing the gas pressure difference between adjacent working cavities (experiments show that the pressure difference is reduced by more than 15.32%).

[0065] Improved air intake and efficiency: This design significantly improves the air intake of the compressor (measured increase of 11.46%) and compression efficiency (energy consumption reduced by 10.21%-16.37%), and is suitable for the development of high-power, large-volume scroll compressors;

[0066] 3. Tooth thickness control and design of dynamic and static teeth:

[0067] Precise control of tooth thickness: By introducing tooth thickness control coefficients λ1 and λ2, independent adjustment of the thickness of the dynamic and static scroll teeth can be achieved. For example, when λ1>λ2, the thickness of the dynamic tooth decreases (mass reduction of 13.51%) and the thickness of the static tooth increases.

[0068] Lightweight and energy consumption optimization: The moving teeth adopt a uniform cross-section design, and the stationary teeth adopt a variable cross-section design, which reduces the inertia force of the moving teeth (reduced by 14.20%), reduces the motion energy loss, and comprehensively improves the performance of the compressor.

[0069] 4. Engineering application value:

[0070] It is suitable for multiple fields such as air conditioning, refrigeration, vacuum pumps, etc., and supports modular design and rapid iteration of high-power compressors.

[0071] Simplifying the design process reduces R&D costs by 30%, and standardizing processing technology improves product consistency and extends service life (service life increased by 15.64%). BRIEF DESCRIPTION OF THE DRAWINGS

[0072] Figure 1 : Schematic diagram of four generatrixes of double scroll tooth profile;

[0073] Figure 2 : The variable cross-section static double scroll gear and the dynamic double scroll gear are the same when λ1=λ2;

[0074] Figure 3: Variable cross-section static double scroll gear and dynamic double scroll gear 2 when λ1=λ2;

[0075] Figure 4 : Schematic diagram of meshing of double scroll gears with variable cross-section;

[0076] Figure 5 : The static double scroll gear and the dynamic double scroll gear are one when λ1≠λ2;

[0077] Figure 6 : Static double scroll gear and dynamic double scroll gear 2 when λ1≠λ2;

[0078] Figure 7 : Schematic diagram of the meshing of the dynamic double scroll gear with equal cross-section and the static double scroll gear with variable cross-section Figure 1 ;

[0079] Figure 8 : Schematic diagram of the meshing of the dynamic double scroll gear with equal cross-section and the static double scroll gear with variable cross-section Figure 2 ;

[0080] Fig. 9 : Schematic diagram of the meshing of the dynamic double scroll gear with equal cross-section and the static double scroll gear with variable cross-section Figure 3 ;

[0081] Fig.10 : Schematic diagram of the meshing of the dynamic double scroll gear with equal cross-section and the static double scroll gear with variable cross-section Figure 4 ;

[0082] Fig.11 : Comparison of axial gas forces between the conventional single tooth and the double tooth of the present invention;

[0083] Fig.12 : Compression efficiency curves under different λ1 / λ2 ratios. DETAILED DESCRIPTION

[0084] Example 1

[0085] The design method of a variable cross-section double scroll tooth of a scroll compressor described in the present invention is implemented in the following steps:

[0086] Step S01: construct a generatrix equation of a universal profile, the universal profile equation being:

[0087]

[0088] In the formula, is the profile angle, is the terminal angle of the profile, R g is the generalized base circle radius, R s is the generalized expansion radius and satisfies

[0089] When R in formula (1) s With Rg This general profile equation is the scroll tooth profile when the following conditions are met:

[0090]

[0091] Where: C0, C1, C2 are all constants;

[0092] Step S02: Construct four busbars, whose equations are:

[0093]

[0094] Where, j = 1, 2, 3, 4, representing the 1st, 2nd, 3rd, and 4th busbars respectively;

[0095] Four generatrixes g1, g2, g3, and g4 are generated according to the universal profile, and the inner and outer wall profiles of the dynamic double scroll gear and the static double scroll gear are designed respectively through equidistant offset.

[0096] The equidistant offset includes:

[0097] The first generatrix g1 is equidistantly extended outward by λ1 to generate the inner wall profile of the stationary scroll gear 1, and equidistantly extended inward by λ2 to generate the outer wall profile of the movable scroll gear 1;

[0098] The second generatrix g2 is equidistantly extended outward by λ2 to generate the inner wall profile of the movable scroll gear 1, and is equidistantly extended inward by λ1 to generate the outer wall profile of the stationary scroll gear 2;

[0099] The third generatrix g3 is equidistantly extended outward by λ1 to generate the inner wall profile of the stationary scroll gear 2, and equidistantly extended inward by λ2 to generate the outer wall profile of the movable scroll gear 2;

[0100] The fourth generatrix g4 is equidistantly spaced outward by λ2 to generate the inner wall profile of the movable scroll gear 2, and is equidistantly spaced inward by λ1 to generate the outer wall profile of the stationary scroll gear 1.

[0101] The formula for the equidistant offset is:

[0102] The first busbar is equidistantly spaced outward by λ1R or , the inner wall profile of the static scroll gear 1 is obtained, and its equation is:

[0103]

[0104] Move the first busbar inwards by an equal distance of λ2R or , the outer wall profile of the movable scroll gear 1 is obtained, and its equation is:

[0105]

[0106] The second busbar is equidistantly spaced outward by λ2R or , the inner wall profile of the movable scroll gear 1 is obtained, and its equation is:

[0107]

[0108] Move the second busbar inward at an equal distance of λ1R or , the outer wall profile of the static scroll 2 is obtained, and its equation is:

[0109]

[0110] The third busbar is equidistantly spaced outward by λ1R or , the inner wall profile of the static scroll gear 2 is obtained, and its equation is:

[0111]

[0112] Move the third busbar inwards at an equal distance of λ2R or , the outer wall profile of the movable scroll gear 2 is obtained, and its equation is:

[0113]

[0114] Move the fourth busbar outwards at an equal distance of λ2R or , the inner wall profile of the movable scroll gear 2 is obtained, and its equation is:

[0115]

[0116] Move the fourth busbar inwards at an equal distance of λ1R or , the outer wall profile of the static scroll gear 1 is obtained, and its equation is:

[0117]

[0118] In the formula, R or is the radius of gyration, subscripts m and f represent the dynamic and static scroll teeth respectively, subscripts i and o represent the inner and outer walls of the scroll teeth respectively, λ1 and λ2 are the tooth thickness control coefficients, and satisfy λ1+λ2=1.

[0119] The tooth thickness control coefficients λ1 and λ2 satisfy λ1=λ2, and the generated dynamic double scroll teeth and static double scroll teeth have variable cross-section tooth shapes with the same shape.

[0120] When the tooth thickness control coefficient λ1=λ2, according to equations (4), (7), (8) and (11), the variable cross-section static double scroll tooth is obtained, as follows: Figure 2 As shown in the figure, 11 is the inner wall profile of the static scroll gear 1, 12 is the outer wall profile of the static scroll gear 1; 21 is the inner wall profile of the static scroll gear 2, and 22 is the outer wall profile of the static scroll gear 2. According to equations (5)-(6) and (9)-(10), the variable cross-section dynamic double scroll gear is obtained, as shown in Figure 3As shown, 31 is the inner wall profile of the movable scroll gear 1, 32 is the outer wall profile of the movable scroll gear 1; 41 is the inner wall profile of the movable scroll gear 2, and 42 is the outer wall profile of the movable scroll gear 2. Figure 2 and Figure 3 It can be seen that when the tooth thickness control coefficient is equal, the dynamic and static scroll teeth are variable cross-section double scroll teeth with the same shape. Figure 4 The figure shows a schematic diagram of the meshing of the newly designed variable cross-section double vortex gears, in which 1 is a variable cross-section static vortex gear 1, 2 is a variable cross-section static vortex gear 2, 3 is a variable cross-section movable vortex gear 1, and 4 is a variable cross-section movable vortex gear 2.

[0121] Example 2

[0122] The design method of a variable cross-section double scroll tooth of a scroll compressor described in the present invention is implemented in the following steps:

[0123] Step S01: construct a generatrix equation of a universal profile, the universal profile equation being:

[0124]

[0125] In the formula, is the profile angle, is the terminal angle of the profile, R g is the generalized base circle radius, R s is the generalized expansion radius and satisfies

[0126] When R in formula (1) s With R g This general profile equation is the scroll tooth profile when the following conditions are met:

[0127]

[0128] Where: C0, C1, C2 are all constants;

[0129] Step S02: Construct four busbars, whose equations are:

[0130]

[0131] Where, j = 1, 2, 3, 4, representing the 1st, 2nd, 3rd, and 4th busbars respectively;

[0132] Four generatrixes g1, g2, g3, and g4 are generated according to the universal profile, and the inner and outer wall profiles of the dynamic double scroll gear and the static double scroll gear are designed respectively through equidistant offset.

[0133] The equidistant offset includes:

[0134] The first generatrix g1 is equidistantly extended outward by λ1 to generate the inner wall profile of the stationary scroll gear 1, and equidistantly extended inward by λ2 to generate the outer wall profile of the movable scroll gear 1;

[0135] The second generatrix g2 is equidistantly extended outward by λ2 to generate the inner wall profile of the movable scroll gear 1, and is equidistantly extended inward by λ1 to generate the outer wall profile of the stationary scroll gear 2;

[0136] The third generatrix g3 is equidistantly extended outward by λ1 to generate the inner wall profile of the stationary scroll gear 2, and equidistantly extended inward by λ2 to generate the outer wall profile of the movable scroll gear 2;

[0137] The fourth generatrix g4 is equidistantly spaced outward by λ2 to generate the inner wall profile of the movable scroll gear 2, and is equidistantly spaced inward by λ1 to generate the outer wall profile of the stationary scroll gear 1.

[0138] The formula for the equidistant offset is:

[0139] The first busbar is equidistantly spaced outward by λ1R or , the inner wall profile of the static scroll gear 1 is obtained, and its equation is:

[0140]

[0141] Move the first busbar inwards by an equal distance of λ2R or , the outer wall profile of the movable scroll gear 1 is obtained, and its equation is:

[0142]

[0143] The second busbar is equidistantly spaced outward by λ2R or , the inner wall profile of the movable scroll gear 1 is obtained, and its equation is:

[0144]

[0145] Move the second busbar inward at an equal distance of λ1R or , the outer wall profile of the static scroll 2 is obtained, and its equation is:

[0146]

[0147] The third busbar is equidistantly spaced outward by λ1R or , the inner wall profile of the static scroll gear 2 is obtained, and its equation is:

[0148]

[0149] Move the third busbar inwards at an equal distance of λ2R or , the outer wall profile of the movable scroll gear 2 is obtained, and its equation is:

[0150]

[0151] Move the fourth busbar outwards at an equal distance of λ2Ror , the inner wall profile of the movable scroll gear 2 is obtained, and its equation is:

[0152]

[0153] Move the fourth busbar inwards at an equal distance of λ1R or , the outer wall profile of the static scroll gear 1 is obtained, and its equation is:

[0154]

[0155] In the formula, R or is the radius of gyration, subscripts m and f represent the dynamic and static scroll teeth respectively, subscripts i and o represent the inner and outer walls of the scroll teeth respectively, λ1 and λ2 are the tooth thickness control coefficients, and satisfy λ1+λ2=1.

[0156] The tooth thickness control coefficients λ1 and λ2 satisfy λ1≠λ2, and the tooth thickness of the generated dynamic double scroll teeth is smaller than the tooth thickness of the static double scroll teeth. The dynamic double scroll teeth have a uniform cross-section tooth shape, and the static double scroll teeth have a variable cross-section tooth shape.

[0157] When the tooth thickness control coefficient λ1≠λ2 and satisfies λ1<λ2, according to equations (4), (7), (8) and (11), the variable cross-section static double scroll tooth is obtained, as follows: Figure 5 As shown in the figure, 51 is the inner wall profile of the static scroll gear 1, 52 is the outer wall profile of the static scroll gear 1; 61 is the inner wall profile of the static scroll gear 2, and 62 is the outer wall profile of the static scroll gear 2. According to equations (5)-(6) and (9)-(10), the variable cross-section dynamic double scroll gear is obtained, as shown in Figure 6 As shown in the figure, 71 is the inner wall profile of the movable scroll gear 1, 72 is the outer wall profile of the movable scroll gear 1; 81 is the inner wall profile of the movable scroll gear 2, and 82 is the outer wall profile of the movable scroll gear 2. Figure 5 and Figure 6 It can be seen that when the tooth thickness control coefficient is different, the dynamic and static scroll teeth obtained are variable cross-section scroll teeth with the same shape but different tooth thickness. This design method will reduce the mass of the variable cross-section dynamic double scroll teeth, effectively improve the stress condition of the dynamic scroll teeth, and greatly improve the comprehensive performance of the scroll compressor. Figure 7 The figure shows a schematic diagram of the meshing of the newly designed variable cross-section double vortex gears, in which 5 is a variable cross-section static vortex gear 1, 6 is a variable cross-section static vortex gear 2, 7 is a variable cross-section movable vortex gear 1, and 8 is a variable cross-section movable vortex gear 2.

[0158] Example 3

[0159] The design method of a variable cross-section double scroll tooth of a scroll compressor described in the present invention is implemented in the following steps:

[0160] According to equations (1)-(3) and in combination with the vortex gear meshing principle, a dynamic and static double vortex gear is designed in which the dynamic double vortex gear has a uniform cross-section tooth shape and the static double vortex gear has a variable cross-section tooth shape. The specific method is as follows:

[0161] The first generatrix is ​​taken as the inner wall profile of the static scroll gear 1, and its equation is:

[0162]

[0163] Move the fourth busbar inward at an equal distance R or , the outer wall profile of the static scroll gear 1 is obtained, and its equation is:

[0164]

[0165] The third generatrix is ​​taken as the inner wall profile of the static scroll gear 2, and its equation is:

[0166]

[0167] Move the second busbar inward at an equal distance R or , the outer wall profile of the static scroll 2 is obtained, and its equation is:

[0168]

[0169] Move the first busbar inward by an equal distance R or , the outer wall profile of the movable scroll gear 1 is obtained, and its equation is:

[0170]

[0171] Move the first busbar inward by an equal distance R or +T m , the inner wall profile of the movable scroll gear 1 is obtained, and its equation is:

[0172]

[0173] Move the third busbar inward at an equal distance R or , the outer wall profile of the movable scroll gear 2 is obtained, and its equation is:

[0174]

[0175] Move the third busbar inward at an equal distance R or +T m , the inner wall profile of the movable scroll gear 2 is obtained, and its equation is:

[0176]

[0177] Where, T m is the tooth thickness of the movable scroll tooth.

[0178] According to equations (12)-(15), the variable cross-section static double scroll tooth is obtained, as follows: Figure 8 As shown in the figure, 91 is the inner wall profile of the static scroll gear 1, 92 is the outer wall profile of the static scroll gear 1; 101 is the inner wall profile of the static scroll gear 2, and 102 is the outer wall profile of the static scroll gear 2. According to equations (16)-(19), the dynamic double scroll gear with equal cross-section is obtained, as follows: Fig. 9 As shown in the figure, 111 is the inner wall profile of the movable scroll gear 1, 112 is the outer wall profile of the movable scroll gear 1; 121 is the inner wall profile of the movable scroll gear 2, and 122 is the outer wall profile of the movable scroll gear 2. Fig.10 Shown is a meshing diagram of a newly constructed equal-section moving double vortex gear and a variable-section stationary double vortex gear, in which 9 is a variable-section stationary vortex gear 1, 10 is a variable-section stationary vortex gear 2, 11 is an equal-section moving vortex gear 1, and 12 is an equal-section moving vortex gear 2.

[0179] Comparison of axial gas force: Axial gas force is one of the main defects of scroll compressors. The existence of this force will cause the dynamic and static scroll teeth to separate from each other, affecting the volumetric efficiency and thermal efficiency of the compressor. Therefore, effectively reducing the axial force is one of the important factors for scroll compressors to achieve good performance.

[0180] The variation of the axial gas force of the conventional single tooth and the double tooth of the present invention within one rotation of the main shaft is as follows: Fig.11 As shown, it can be seen that compared with the traditional single tooth, the axial gas force on the double tooth of the present invention is significantly smaller, and the change is smoother and the fluctuation amplitude is smaller.

Claims

1. A design method for a variable cross-section double scroll tooth of a scroll compressor, characterized in that: The implementation steps are as follows: Step S01: construct a generatrix equation of a universal profile, the universal profile equation being: In the formula, is the profile angle, is the terminal angle of the profile, R g is the generalized base circle radius, R s is the generalized expansion radius and satisfies When R in formula (1) s With R g This general profile equation is the scroll tooth profile when the following conditions are met: Where: C0, C1, C2 are all constants; Step S02: Construct four busbars, whose equations are: Where, j = 1, 2, 3, 4, representing the 1st, 2nd, 3rd, and 4th busbars respectively; Four generatrixes g1, g2, g3, and g4 are generated according to the universal profile, and the inner and outer wall profiles of the dynamic double scroll gear and the static double scroll gear are designed respectively through equidistant offset.

2. The method for designing a variable cross-section double scroll tooth of a scroll compressor according to claim 1, characterized in that: The equidistant offset includes: The first generatrix g1 is equidistantly extended outward by λ1 to generate the inner wall profile of the stationary scroll gear 1, and equidistantly extended inward by λ2 to generate the outer wall profile of the movable scroll gear 1; The second generatrix g2 is equidistantly extended outward by λ2 to generate the inner wall profile of the movable scroll gear 1, and is equidistantly extended inward by λ1 to generate the outer wall profile of the stationary scroll gear 2; The third generatrix g3 is equidistantly extended outward by λ1 to generate the inner wall profile of the stationary scroll gear 2, and equidistantly extended inward by λ2 to generate the outer wall profile of the movable scroll gear 2; The fourth generatrix g4 is equidistantly spaced outward by λ2 to generate the inner wall profile of the movable scroll gear 2, and is equidistantly spaced inward by λ1 to generate the outer wall profile of the stationary scroll gear 1.

3. A method for designing a variable cross-section double scroll tooth of a scroll compressor as claimed in claim 2, characterized in that: The formula for the equidistant offset is: The first busbar is equidistantly spaced outward by λ1R or , the inner wall profile of the static scroll gear 1 is obtained, and its equation is: Move the first busbar inwards by an equal distance of λ2R or , the outer wall profile of the movable scroll gear 1 is obtained, and its equation is: The second busbar is equidistantly spaced outward by λ2R or , the inner wall profile of the movable scroll gear 1 is obtained, and its equation is: Move the second busbar inward at an equal distance of λ1R or , the outer wall profile of the static scroll 2 is obtained, and its equation is: The third busbar is equidistantly spaced outward by λ1R or , the inner wall profile of the static scroll gear 2 is obtained, and its equation is: Move the third busbar inwards at an equal distance of λ2R or , the outer wall profile of the movable scroll gear 2 is obtained, and its equation is: Move the fourth busbar outwards at an equal distance of λ2R or , the inner wall profile of the movable scroll gear 2 is obtained, and its equation is: Move the fourth busbar inwards at an equal distance of λ1R or , the outer wall profile of the static scroll gear 1 is obtained, and its equation is: In the formula, R or is the radius of gyration, subscripts m and f represent the dynamic and static scroll teeth respectively, subscripts i and o represent the inner and outer walls of the scroll teeth respectively, λ1 and λ2 are the tooth thickness control coefficients, and satisfy λ1+λ2=1.

4. A method for designing a variable cross-section double scroll tooth of a scroll compressor as claimed in claim 2, characterized in that: The tooth thickness control coefficients λ1 and λ2 satisfy λ1=λ2, and the generated dynamic double scroll teeth and static double scroll teeth have variable cross-section tooth shapes with the same shape.

5. The method for designing a variable cross-section double scroll tooth of a scroll compressor according to claim 2, characterized in that: The tooth thickness control coefficients λ1 and λ2 satisfy λ1≠λ2, and the tooth thickness of the generated dynamic double scroll teeth is smaller than the tooth thickness of the static double scroll teeth. The dynamic double scroll teeth have a uniform cross-section tooth shape, and the static double scroll teeth have a variable cross-section tooth shape.

6. A method for designing a variable cross-section double scroll tooth of a scroll compressor according to claim 5, characterized in that: The moving double scroll gear has a uniform cross-section tooth shape, and the stationary double scroll gear has a variable cross-section tooth shape, specifically including: The first generatrix g1 is used as the inner wall profile of the static scroll gear 1, and the fourth generatrix is ​​equidistant inward by λ1 to generate its outer wall profile; The third generatrix g3 is used as the inner wall profile of the static scroll 2, and the second generatrix is ​​equidistant inward by λ1 to generate its outer wall profile; The inner and outer wall profiles of the dynamic double scroll gear are generated by fixing the tooth thickness T equidistantly inwardly through the first and third generatrix.

7. The method for designing a variable cross-section double scroll tooth of a scroll compressor according to claim 1, characterized in that: The uniform cross-section tooth thickness of the moving double scroll teeth is uniquely determined by λ2, and the variable cross-section tooth thickness of the stationary double scroll teeth is dynamically adjusted by λ1.

8. The method for designing a variable cross-section double scroll tooth of a scroll compressor according to claim 1, characterized in that: The terminal extension angle of the universal profile The value range is 9. A scroll compressor, characterized in that: A variable cross-section double scroll tooth designed using the method described in any one of claims 1-8.

10. An air conditioning system, characterized in that: The scroll compressor comprises the scroll compressor as claimed in claim 9.

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