Conical twin-screw compressor rotor design method, rotor and compressor

Abstract

A kind of conical double-screw compressor rotor design method, rotor and compressor, in the method, establish spatial coordinate system;Plane rotor profile is converted into spatial rotor profile;Helical surface equation is established, male and female rotors are conical, and the axis intersects to form the angle of δ conical angle;Machine body includes the conical working chamber corresponding to male and female rotors, and the axial suction and discharge orifice corresponding to the suction and discharge end of rotor.Working, gas is inhaled by large end, is discharged by small end after being compressed, completes suction, compression and exhaust process.The present application can improve the compression ratio of double-screw compressor, space utilization rate, and can reduce leakage.

Description

Technical Field

[0001] This invention belongs to the field of screw compressor technology, and in particular to a design method for a conical twin-screw compressor rotor, the rotor, and the compressor. Background Technology

[0002] A twin-screw compressor is a positive displacement rotary compressor used to obtain high-pressure gases and is widely used in mining, power, metallurgy, construction, machinery, and refrigeration industries. It inherits the advantages of rotary machinery, such as long service life, low noise, low vibration, smooth operation, and no surge, while also featuring a simple structure and the absence of easily damaged parts like inlet and outlet valves. Therefore, it is a core component in high-pressure gas transmission, refrigeration, and waste heat recovery systems.

[0003] In existing technologies, traditional twin-screw compressors typically use cylindrical rotors of equal diameter, with the male and female rotors having parallel axes and maintaining a certain center distance. The two rotors mesh to achieve gas compression. This design limits the rotor geometry and operational performance, requiring larger equipment to achieve a sufficiently high compression ratio. Furthermore, due to the leakage triangle between the male and female rotors and the compressor body, gas leakage occurs during compression, leading to reduced energy efficiency. Therefore, a more efficient and compact screw compressor is needed to address these issues.

[0004] The information disclosed in the background section is only intended to enhance the understanding of the background of the present invention, and therefore may contain information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0005] To address the problems existing in the prior art, this invention proposes a design method for a conical twin-screw compressor rotor, a rotor, and a compressor, which improves the compression ratio and space utilization of the twin-screw compressor, and can reduce the leakage triangle to reduce leakage.

[0006] The objective of this invention is achieved through the following technical solution: the design method for a conical twin-screw compressor rotor includes the following steps.

[0007] The rotor of the conical twin-screw compressor to be designed consists of a female rotor and a male rotor that mesh with each other. The female rotor and the male rotor are conical and their axes intersect to form a cone angle of δ.

[0008] Establish a female rotor plane coordinate system and a male rotor plane coordinate system o1x1y1, o2x2y2. The male rotor plane coordinate system o2x2y2 is obtained by translating the female rotor coordinate system o1x1y1 in the positive x1 direction by a center distance A between the female and male rotors. Any point m on the rotor profile of the female and male rotors is determined by the center distance A and the azimuth angle of point m in the female rotor plane coordinate system and the male rotor plane coordinate system o1x1y1, o2x2y2. and azimuth The coordinates of point m in the male rotor coordinate system o1x1y1 are (x1, y1), and the coordinates in the male rotor plane coordinate system o2x2y2 are (x2, y2). The center distance A and azimuth angle are also specified. and azimuth The following conditions are satisfied between (x1, y1) and (x2, y2):

[0009]

[0010] Establish the male and female rotor spatial coordinate systems O1X1Y1Z1 and O2X2Y2Z2. The male rotor spatial coordinate system O2X2Y2Z2 is obtained by rotating the female rotor coordinate system O1X1Y1Z1 clockwise around the Y1 axis by an angle δ. Any point M on the rotor profile is determined by the cone angle δ, the sphere radius R, and the azimuth angle. and azimuth It is determined that the coordinates of point M in the male rotor spatial coordinate system O1X1Y1Z1 are (x1′, y1′, z1′), and the coordinates in the female rotor spatial coordinate system O2X2Y2Z2 are (x2′, y2′, z2′), δ, R, The following conditions are satisfied between (x1′, y1′, z1′) and (x2′, y2′, z2′):

[0011]

[0012] Projecting the rotor profile from the planar coordinate system onto the spatial coordinate system yields the spatial rotor profile. Specifically, transforming a point p in the planar coordinate system into a point P in the spatial coordinate system... and The following conditions must be met:

[0013]

[0014] By transforming the planar coordinates into spatial coordinates, each point on the planar rotor profile is transformed into a point in the spatial coordinate system, thus obtaining the spatial rotor profile.

[0015] Establish the rotor helical surface equation in the spatial coordinate system. Specifically, in the male rotor's spatial coordinate system O1X1Y1Z1, the helical surface equation of the male rotor is:

[0016]

[0017] Alternatively, in the male rotor's spatial coordinate system O2X2Y2Z2, the equation of the male rotor's helical surface is:

[0018]

[0019] Where r = R - pτ, p is the helical characteristic number, τ is the helical angle; x1′, y1′, z1 are the spatial rotor profiles in the female rotor spatial coordinate system O1X1Y1Z1, and x2′, y2′z2 are the spatial rotor profiles in the male rotor spatial coordinate system O2X2Y2Z2.

[0020] Based on the spatial rotor profile and helical surface equation, a male and female rotor mesh with each other and have a conical structure with one end larger than the other. Their axes intersect to form a cone angle of δ.

[0021] In the method described, the conical rotor profile is a spatial profile on a sphere, which is transformed from the rotor profile in a planar coordinate system.

[0022] A conical twin-screw compressor rotor is generated via the conical twin-screw compressor rotor design method.

[0023] A conical twin-screw compressor rotor, characterized in that,

[0024] The rotor of the conical twin-screw compressor consists of a female rotor and a male rotor that mesh with each other. The female rotor and the male rotor are conical and their axes intersect to form a cone angle of δ.

[0025] For the male rotor plane coordinate system o1x1y1, o2x2y2, where...

[0026] The male rotor plane coordinate system o2x2y2 is obtained by translating the female rotor coordinate system o1x1y1 in the positive x1 direction by the center distance A between the female and male rotors;

[0027] Any point m on the rotor profile of the female and male rotors is determined by the center distance A and the azimuth angle of point m in the female rotor plane coordinate system and the male rotor plane coordinate system o1x1y1, o2x2y2. and azimuth Sure;

[0028] Point m has coordinates (x1, y1) in the male rotor coordinate system o1x1y1 and (x2, y2) in the male rotor plane coordinate system o2x2y2. The center distance A and azimuth angle are also given. and azimuth The following conditions are satisfied between (x1, y1) and (x2, y2):

[0029]

[0030] For the male rotor spatial coordinate system O1X1Y1Z1 and the female rotor spatial coordinate system O2X2Y2Z2, the female rotor spatial coordinate system O2X2Y2Z2 is obtained by rotating the female rotor coordinate system O1X1Y1Z1 clockwise around the Y1 axis by an angle δ.

[0031] Any point M on the rotor profile is determined by the cone angle δ, the sphere radius R, and the azimuth angle. and azimuth It is determined that the coordinates of point M in the male rotor spatial coordinate system O1X1Y1Z1 are (x1′, y1′, z1′), and the coordinates in the female rotor spatial coordinate system O2X2Y2Z2 are (x2′, y2′, z2′), δ, R, The following conditions are satisfied between (x1′, y1′, z1′) and (x2′, y2′, z2′):

[0032]

[0033] For the spatial rotor profile obtained by projecting the rotor profile in the planar coordinate system onto the spatial coordinate system, where a point p in the planar coordinate system is transformed into a point P in the spatial coordinate system, then... and The following conditions must be met:

[0034]

[0035] By transforming the planar coordinates into spatial coordinates, each point on the planar rotor profile is transformed into a point in the spatial coordinate system, thus obtaining the spatial rotor profile.

[0036] In the spatial coordinate system O1X1Y1Z1 of the female rotor, the equation of the helical surface of the female rotor is:

[0037]

[0038] In the male rotor's spatial coordinate system O2X2Y2Z2, the equation of the male rotor's helical surface is:

[0039]

[0040] in,

[0041] r = R - pτ, where p is the helical characteristic number and τ is the helical angle;

[0042] x1′, y1′, z1 are the spatial rotor profiles in the male rotor spatial coordinate system O1X1Y1Z1;

[0043] x2′, y2′, z2 are the spatial rotor profiles in the male rotor spatial coordinate system O2X2Y2Z2;

[0044] The spatial rotor profiles of the male and female rotors and the helical surface equations of the male and female rotors are used to characterize the meshing male and female rotors.

[0045] The conical twin-screw compressor rotor has a left-handed helical surface.

[0046] A compressor includes,

[0047] The body includes a conical working cavity;

[0048] The conical twin-screw compressor rotor is adapted to be housed in the conical working chamber.

[0049] The compressor body also includes axial intake and exhaust ports corresponding to the intake and exhaust ends of the rotor.

[0050] In the compressor, the axial intake and exhaust port profile is a spatial profile on a spherical surface.

[0051] The compressor body also includes a radial intake port.

[0052] Compared with existing technologies, this invention has the following advantages: Traditional twin-screw compressor rotors are typically cylindrical with equal diameters, and the male and female rotor axes are parallel and maintain a certain center distance, with the two rotors meshing to achieve gas compression. This design limits the rotor geometry and operational performance, requiring larger equipment to achieve a sufficiently high compression ratio. This invention designs the male and female rotors as a conical structure with one end larger than the other, resulting in a more compact structure, improved space utilization, and a gradual reduction in the basic volume from the intake end to the exhaust end, thus providing a higher compression ratio. Furthermore, a leakage triangle exists between the male and female rotors and the compressor body, leading to gas leakage. The conical structure of this invention allows the leakage triangle area to gradually decrease from the intake end to the exhaust end, reducing leakage and improving compressor efficiency. Attached Figure Description

[0053] Various other advantages and benefits of the present invention will become apparent to those skilled in the art upon reading the detailed description of the preferred embodiments below. The accompanying drawings are for illustrative purposes only and are not intended to limit the invention. It is obvious that the drawings described below are merely some embodiments of the invention, and those skilled in the art can obtain other drawings based on these drawings without any inventive effort. Furthermore, the same reference numerals denote the same parts throughout the drawings.

[0054] In the attached diagram:

[0055] Figure 1 This is a schematic diagram of the assembly structure of the conical twin-screw compressor according to an embodiment of the present invention;

[0056] Figure 2 This is a schematic diagram of the planar rotor profile of a traditional twin-screw compressor;

[0057] Figure 3 This is a schematic diagram of the spatial rotor profile of the conical twin-screw compressor of the present invention;

[0058] Figure 4 This is a schematic diagram of the male and female rotors meshing in the conical twin-screw compressor of the present invention;

[0059] Figure 5 This is a schematic diagram of the suction port of the conical twin-screw compressor of the present invention;

[0060] Figure 6 This is a schematic diagram of the exhaust port of the conical twin-screw compressor of the present invention.

[0061] The present invention will be further explained below with reference to the accompanying drawings and embodiments. Detailed Implementation

[0062] The following will refer to the appendix. Figures 1 to 6 Specific embodiments of the invention will be described in more detail below. While specific embodiments of the invention are shown in the accompanying drawings, it should be understood that the invention can be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided to enable a more thorough understanding of the invention and to fully convey the scope of the invention to those skilled in the art.

[0063] It should be noted that certain terms are used in the specification and claims to refer to specific components. Those skilled in the art will understand that different terms may be used to refer to the same component. This specification and claims do not distinguish components based on differences in terminology, but rather on differences in function. The terms "comprising" or "including" used throughout the specification and claims are open-ended and should be interpreted as "comprising but not limited to." The following descriptions are preferred embodiments for carrying out the invention; however, these descriptions are for the purpose of understanding the general principles of the specification and are not intended to limit the scope of the invention. The scope of protection of this invention is determined by the appended claims.

[0064] To facilitate understanding of the embodiments of the present invention, further explanations and descriptions will be provided below with reference to the accompanying drawings and specific embodiments. The accompanying drawings do not constitute a limitation on the embodiments of the present invention.

[0065] For better understanding, in one embodiment, such as Figures 1 to 6 As shown, the design method for the rotor of a conical twin-screw compressor includes the following steps:

[0066] The rotor of the conical twin-screw compressor to be designed consists of a female rotor and a male rotor that mesh with each other. The female rotor and the male rotor are conical and their axes intersect to form a cone angle of δ.

[0067] Establish a plane coordinate system for the female rotor and a plane coordinate system for the male rotor, o1x1y1 and o2x2y2. The male rotor plane coordinate system o2x2y2 is obtained by translating the female rotor coordinate system o1x1y1 in the positive x1 direction by a center distance A. Any point m on the rotor profile of the female and male rotors is determined by the center distance A and the azimuth angle. and azimuth It is determined that the coordinates of point m in the male rotor coordinate system o1x1y1 are (x1, y1), and the coordinates in the male rotor plane coordinate system o2x2y2 are (x2, y2). The center distance A and the azimuth angle are also determined. and azimuth The following conditions are satisfied between (x1, y1) and (x2, y2):

[0068]

[0069] Establish the male and female rotor spatial coordinate systems O1X1Y1Z1 and O2X2Y2Z2. The male rotor spatial coordinate system O2X2Y2Z2 is obtained by rotating the female rotor coordinate system O1X1Y1Z1 clockwise around the Y1 axis by an angle δ. Any point M on the rotor profile is determined by the cone angle δ, the sphere radius R, and the azimuth angle. and azimuth It is determined that the coordinates of point M in the male rotor spatial coordinate system O1X1Y1Z1 are (x1′, y1′, z1′), and the coordinates in the female rotor spatial coordinate system O2X2Y2Z2 are (x2′, y2′, z2′), δ, R, The following conditions are satisfied between (x1′, y1′, z1′) and (x2′, y2′, z2′):

[0070]

[0071] Projecting the rotor profile from the planar coordinate system onto the spatial coordinate system yields the spatial rotor profile. Specifically, transforming a point p in the planar coordinate system into a point P in the spatial coordinate system... and The following conditions must be met:

[0072]

[0073] By transforming the planar coordinates into spatial coordinates, each point on the planar rotor profile is transformed into a point in the spatial coordinate system, thus obtaining the spatial rotor profile.

[0074] Establish the rotor helical surface equation in the spatial coordinate system. Specifically, in the male rotor's spatial coordinate system O1X1Y1Z1, the helical surface equation of the male rotor is:

[0075]

[0076] Alternatively, in the male rotor's spatial coordinate system O2X2Y2Z2, the equation of the male rotor's helical surface is:

[0077]

[0078] Where r = R - pτ, p is the helical characteristic number, τ is the helical angle; x1′, y1′, z1 are the spatial rotor profiles in the male rotor spatial coordinate system O1X1Y1Z1, and x2′, y2′, z2 are the spatial rotor profiles in the female rotor spatial coordinate system O2X2Y2Z2.

[0079] Based on the spatial rotor profile and helical surface equation, a male and female rotor mesh with each other and have a conical structure with one end larger than the other. Their axes intersect to form a cone angle of δ.

[0080] In a preferred embodiment of the method, the conical rotor profile is a spatial profile on a sphere, which is derived from the rotor profile in a planar coordinate system.

[0081] The male and female rotors are conical, and their axes intersect to form a conical angle of δ. The machine body includes a conical working chamber corresponding to the male and female rotors, and axial intake and exhaust ports corresponding to the intake and exhaust ends of the rotors. During operation, gas is drawn in from the large end, compressed, and discharged from the small end, completing the intake, compression, and exhaust processes.

[0082] See Figures 2 to 3 This invention proposes a method for designing a conical twin-screw compressor rotor, comprising the following steps:

[0083] Establish a planar coordinate system o1x1y1, o2x2y2. The coordinate system o2x2y2 is obtained by translating the coordinate system o1x1y1 in the positive x1 direction by a center distance A. Any point m on the rotor profile can be determined by the center distance A between the male and female rotors and the azimuth angle. and azimuth It is uniquely determined that the coordinates of point m in o1x1y1 are (x1, y1), and the coordinates in o2x2y2 are (x2, y2). A, The following conditions are satisfied between (x1, y1) and (x2, y2):

[0084]

[0085] Establish spatial coordinate systems O1X1Y1Z1 and O2X2Y2Z2. Coordinate system O2X2Y2Z2 is obtained by rotating coordinate system O1X1Y1Z1 clockwise by an angle δ around the Y1 axis. Any point M on the rotor profile can be determined by the cone angle δ of the male and female rotors, the sphere radius R, and the azimuth angle. and azimuth It is uniquely determined that the coordinates of point M in O1X1Y1Z1 are (x1′, y1′, z1′), and the coordinates in O2X2Y2Z2 are (x2′, y2′, z2′). δ, R, The following conditions are satisfied between (x1′, y1′, z1′) and (x2′, y2′, z2′):

[0086]

[0087] Transform a point p in a planar coordinate system into a point P in a spatial coordinate system, then and The following conditions must be met:

[0088]

[0089] By using the above-mentioned transformation relationship between planar coordinates and spatial coordinates, each point on the traditional planar rotor profile can be transformed into a point in the spatial coordinate system, thereby obtaining the spatial rotor profile.

[0090] The equation for the helical surface of a conical rotor (taking a right-handed helical surface as an example) is:

[0091] (in the O1X1Y1Z1 coordinate system);

[0092] or

[0093] (In the O2X2Y2Z2 coordinate system)

[0094] Where r = R - pτ, p is the helical characteristic number, and τ is the helical angle; x1, y1, z1 are the spatial rotor profiles in O1X1Y1Z1, and x2, y2, z2 are the spatial rotor profiles in O2X2Y2Z2.

[0095] The conical twin-screw compressor rotor obtained through the above design method is as follows: Figure 3 As shown, the male and female rotors have a conical structure with one end larger than the other, and their axes intersect to form a cone angle of δ.

[0096] See Figures 5 to 6 The axial intake and exhaust orifice profile is a spatial profile on a sphere, which can also be transformed from the orifice profile in the traditional planar coordinate system through the coordinate system transformation method described above.

[0097] This invention designs the male and female rotors as a conical structure with one end larger than the other, which is more compact and improves space utilization. At the same time, it makes the basic unit volume gradually decrease from the intake end to the exhaust end, which can provide a larger compression ratio. Furthermore, the conical structure can make the leakage triangle area gradually decrease from the intake end to the exhaust end, which can reduce leakage and improve compressor efficiency.

[0098] A conical twin-screw compressor rotor is generated via the conical twin-screw compressor rotor design method.

[0099] The rotor of the conical twin-screw compressor has a left-handed helical surface.

[0100] Preferably, the end face of the machine body is provided with a conical working cavity corresponding to the male and female rotors, and an axial intake and exhaust port corresponding to the intake and exhaust ends of the rotors.

[0101] Preferably, the axial intake and exhaust orifice profile is a spatial profile on a spherical surface, which can be transformed from the orifice profile in the traditional planar coordinate system through the coordinate system transformation method described above.

[0102] A compressor includes,

[0103] The body includes a conical working cavity;

[0104] The described conical twin-screw compressor rotor is adapted to be housed in a conical working chamber.

[0105] The machine body also includes axial intake and exhaust ports corresponding to the intake and exhaust ends of the rotor.

[0106] The axial intake and exhaust port profile is a spatial profile on a spherical surface. The body also includes a radial intake port.

[0107] Although embodiments of the present invention have been described above in conjunction with the accompanying drawings, the present invention is not limited to the specific embodiments and application fields described above. The specific embodiments described above are merely illustrative and instructive, and not restrictive. Those skilled in the art can make many other forms based on the guidance of this specification and without departing from the scope of protection of the claims of the present invention, and all of these are within the scope of protection of the present invention.

Claims

1. A method for designing a conical twin-screw compressor rotor, characterized in that, It includes the following steps, The conical twin-screw compressor to be designed consists of two meshing rotors, a female rotor and a male rotor. The female and male rotors are conical, and their axes intersect at an angle of [angle missing]. The cone angle; Establish the male rotor plane coordinate system and the female rotor plane coordinate system. male rotor plane coordinate system From the male rotor coordinate system The distance A between the center distances of the female and male rotors is obtained by translating the rotor profiles of the female and male rotors in the positive x1 direction. Any point m on the rotor profiles of the female and male rotors is determined by the center distance. The profile point m in the male rotor plane coordinate system and the female rotor plane coordinate system azimuth and azimuth It is confirmed that point m lies in the male rotor plane coordinate system. The coordinates in are In the male rotor plane coordinate system The coordinates in are center distance Azimuth and azimuth , and The following conditions must be met: ； Establish the male rotor spatial coordinate system and the female rotor spatial coordinate system. The male rotor spatial coordinate system O2X2Y2Z2 is rotated clockwise around the Y1 axis by the female rotor coordinate system O1X1Y1Z1. The angle is obtained by determining the cone angle at any point M on the rotor profile. sphere radius azimuth and azimuth It is confirmed that point M lies in the male rotor spatial coordinate system. The coordinates in are In the male rotor space coordinate system The coordinates in are , , , , , and The following conditions must be met: ； Projecting the rotor profile from the planar coordinate system onto the spatial coordinate system yields the spatial rotor profile. This involves transforming a point m in the planar coordinate system into a point M in the spatial coordinate system. , , and The following conditions must be met: ， By transforming the planar coordinates into spatial coordinates, each point on the planar rotor profile is transformed into a point in the spatial coordinate system, thus obtaining the spatial rotor profile. Establish the rotor helical surface equation in the spatial coordinate system, where, in the male rotor spatial coordinate system... In the middle, the equation of the helical surface of the male rotor is: ， In the space coordinate system of the male rotor In the equation of the helical surface of the male rotor, the equation is: ， in , For the spiral characteristic number, The helix angle; The spatial rotor profile in the male rotor spatial coordinate system O1X1Y1Z1. For the male rotor spatial coordinate system O ２ X ２ Y ２ Z ２ The space rotor profile in; Based on the spatial rotor profile and helical surface equation, a male and female rotor mesh with each other and have a conical structure with one end larger than the other. Their axes intersect to form a cone angle of δ.

2. A conical twin-screw compressor rotor, characterized in that, It is generated by the conical twin-screw compressor rotor design method as described in claim 1.

3. The conical twin-screw compressor rotor as described in claim 2, characterized in that, The rotor of the conical twin-screw compressor has a left-handed helical surface.

4. A compressor, characterized in that, It includes, The body includes a conical working chamber. The conical twin-screw compressor rotor as described in claim 2 or 3 is adaptedly housed in a conical working chamber.

5. The compressor as described in claim 4, characterized in that, The machine body also includes axial intake and exhaust ports corresponding to the intake and exhaust ends of the rotor.

6. The compressor as described in claim 5, characterized in that, The axial intake and exhaust port profile is a spatial profile on a spherical surface.

7. The compressor as claimed in claim 4, characterized in that, The body also includes radial air intake ports.

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