CN115434913A - Screw rotor profile design method and screw compressor - Google Patents
Screw rotor profile design method and screw compressor Download PDFInfo
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- CN115434913A CN115434913A CN202211247350.9A CN202211247350A CN115434913A CN 115434913 A CN115434913 A CN 115434913A CN 202211247350 A CN202211247350 A CN 202211247350A CN 115434913 A CN115434913 A CN 115434913A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/084—Toothed wheels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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Abstract
The invention provides a screw rotor profile design method and a screw compressor, wherein the method comprises the following steps: drawing a tooth line of the female rotor and the male rotor which are meshed with each other through sectional design, wherein the tooth line is formed by smoothly connecting seven sections of curves end to end; optimizing a male rotor tooth curve and a female rotor tooth curve according to the rack line; and obtaining corresponding female rotor profile and male rotor profile according to the female rotor tooth curve and the male rotor tooth curve. The invention can avoid larger calculation amount caused by directly optimizing the female rotor profile and the male rotor profile, thereby improving the design efficiency of the rotor profile.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a screw rotor profile design method and a screw compressor.
Background
The screw compressor has the advantages of simple structure, good power balance, energy conservation, high efficiency and the like, is a volumetric compression machine which is developed most rapidly in recent years, and is widely applied to the industrial fields of air power, refrigeration and air conditioning, petrochemical industry, process flow, fuel cells and the like.
The working process of the screw compressor is completed by the periodical meshing rotation of the helical tooth surfaces of the male rotor and the female rotor. As a core component of the screw compressor, the female and male rotor profiles (with a toothed cross section) determine the overall performance of the screw compressor. However, in the conventional design method, the female rotor profile and the male rotor profile are designed simultaneously by the rotor method, the calculated amount is large, and the problems of profile modification, inconvenience in experimental setup and the like often occur, so that the design efficiency is low.
Disclosure of Invention
The invention provides a screw rotor profile design method and a screw compressor, which are used for solving the problem of low design efficiency of female and male rotor profiles in the prior art.
In a first aspect, the present invention provides a method for designing a profile of a screw rotor, the method comprising:
drawing out a tooth line of the female rotor and the male rotor which are meshed with each other through a segmented design, wherein the tooth line is formed by smoothly connecting seven sections of curves end to end, and the seven sections of curves sequentially comprise an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section;
optimizing a male rotor tooth profile and a female rotor tooth profile according to the rack line, the male rotor tooth profile comprising a sequence of smoothly connected A' s 1 B 1 Segment, B 1 C 1 Segment, C 1 D 1 Segment, D 1 E 1 Segment E 1 F 1 Segment, F 1 G 1 Segment and G 1 H 1 A section, the female rotor tooth curve comprising A smoothly connected in sequence 2 B 2 Segment, B 2 C 2 Segment C 2 D 2 Segment, D 2 E 2 Segment E 2 F 2 Segment, F 2 G 2 Segment and G 2 H 2 A segment;
and obtaining corresponding female rotor molded lines and male rotor molded lines according to the female rotor tooth curves and the male rotor tooth curves.
In an embodiment of the present invention, the male rotor tooth curve and the female rotor tooth curve are generated according to the tooth profile line by a coordinate transformation formula, where the coordinate transformation formula is:
wherein x is c ,y c Is the rack coordinate, mu, of the female or male rotor 1 For the angle of change of rack coordinate to profile coordinate, r p1 Is the pitch radius of the rotor, x 1 ,y 1 The tooth coordinates of the female rotor or the male rotor.
In an embodiment of the present invention, the step of optimizing the male rotor tooth profile and the female rotor tooth profile according to the tooth profile line comprises:
converting an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section of the rack line into a tooth form coordinate system of the male rotor from a rack coordinate system to obtain a tooth curve of the male rotor; and
converting the AB section, the BC section, the CD section, the DE section, the EF section, the FG section and the GH section of the tooth trace line into a tooth form coordinate system of the female rotor from a rack coordinate system to obtain a tooth curve of the female rotor;
wherein, the AB section is a section of circular arc with O3 as the center of circle and radius n1 times the pitch radius of the female rotor, n1 is a positive number which is more than 0.1 and less than or equal to 0.15, the AB section is smoothly connected with the HB section at the starting point and is tangent with the BC section at the end point;
the BC section is a section of circular arc with O4 as the center of a circle and the radius n2 times the pitch radius of the female rotor, n2 is a positive number which is more than 0.1 and less than or equal to 0.2, the BC section is smoothly connected with the AB section at the starting point and is tangent to the CD section at the end point;
the CD section is an elliptic arc with O5 as the center of a circle and n3 times the pitch radius of the female rotor, n3 is a positive number which is more than 0.5 and less than or equal to 0.7, the CD section is smoothly connected with the BC section at the starting point and is tangent with the DE section at the end point;
the DE section is a section of circular arc with O6 as the center of a circle and n4 times the pitch radius of the female rotor, n4 is a positive number which is more than 0.8 and less than or equal to 1.1, the DE section is smoothly connected with the CD section at the starting point and is tangent with the EF section at the end point;
the EF section is a section of elliptic curve with O7 as the center, the major diameter of the elliptic curve is n5 times the pitch radius of the female rotor, the minor diameter of the elliptic curve is n6 times the pitch radius of the female rotor, n5 is a positive number which is more than 0.6 and less than or equal to 0.8, n6 is a positive number which is more than 0.3 and less than or equal to 0.5, the EF section is smoothly connected with the DE section at the starting point and is tangent to the FG section at the end point;
the FG section is a circular arc with the radius n7 times the pitch radius of the female rotor and the O8 as the center of a circle, n7 is a positive number which is more than 0.1 and less than or equal to 0.5, and is smoothly connected with the EF section at the starting point and is tangent with the GH section at the end point;
the GH section is a straight line section with the length of n8 times the pitch circle radius of the female rotor, n8 is a positive number which is more than 0.1 and less than or equal to 0.3, and the GH section is smoothly connected with the FG section at the starting point and is tangent with the HA section at the end point.
In an embodiment of the present invention, the gear ratio of the female rotor and the male rotor is 5:3.
in an embodiment of the invention, the diameters of the circumcircles of the female rotor profile and the male rotor profile are equal.
In a second aspect, the invention also provides a screw compressor, which comprises a female rotor and a male rotor, wherein the meshed rack line of the female rotor and the male rotor is formed by smoothly connecting seven sections of curves end to end, and the seven sections of curves sequentially comprise an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section;
the curve of the male rotor teeth generated from said rack line comprises a smoothly connected sequence of A 1 B 1 Segment, B 1 C 1 Segment, C 1 D 1 Segment, D 1 E 1 Segment E 1 F 1 Segment, F 1 G 1 Segment and G 1 H 1 A segment;
the female rotor tooth curve generated according to the rack line comprises A which are smoothly connected in sequence 2 B 2 Segment, B 2 C 2 Segment, C 2 D 2 Segment, D 2 E 2 Segment E 2 F 2 Segment, F 2 G 2 Segment and G 2 H 2 A segment;
the male rotor tooth profile is used to generate a male rotor profile and the female rotor tooth profile is used to generate a female rotor profile.
In an embodiment of the present invention, the male rotor tooth curve and the female rotor tooth curve are generated according to the tooth profile line by a coordinate transformation formula, where the coordinate transformation formula is:
wherein x is c ,y c Is the rack coordinate, mu, of the female or male rotor 1 For the angle of change of rack coordinate to profile coordinate, r p1 Is the pitch radius of the rotor, x 1 ,y 1 The tooth coordinates of the female rotor or the male rotor.
In one embodiment of the present invention, the first and second electrodes are,
the male rotor tooth curve is obtained by converting an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section of the tooth line from a rack coordinate system into a tooth coordinate system of the male rotor;
the female rotor tooth curve is obtained by converting an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section of the tooth line from a rack coordinate system into a tooth coordinate system of the female rotor;
wherein, the AB section is a section of circular arc with O3 as the center of circle and radius n1 times the pitch radius of the female rotor, n1 is a positive number which is more than 0.1 and less than or equal to 0.15, the AB section is smoothly connected with the HB section at the starting point and is tangent with the BC section at the end point;
the BC section is a section of circular arc with O4 as the center of a circle and the radius n2 times the pitch radius of the female rotor, n2 is a positive number which is more than 0.1 and less than or equal to 0.2, the BC section is smoothly connected with the AB section at the starting point and is tangent to the CD section at the end point;
the CD section is an elliptic arc with O5 as the center of a circle and n3 times the pitch radius of the female rotor, n3 is a positive number which is more than 0.5 and less than or equal to 0.7, the CD section is smoothly connected with the BC section at the starting point and is tangent with the DE section at the end point;
the DE section is a section of circular arc with O6 as the center of a circle and n4 times the pitch radius of the female rotor, n4 is a positive number which is more than 0.8 and less than or equal to 1.1, the DE section is smoothly connected with the CD section at the starting point and is tangent with the EF section at the end point;
the EF section is a section of elliptic curve with O7 as the center, the major diameter of the elliptic curve is n5 times the pitch radius of the female rotor, the minor diameter of the elliptic curve is n6 times the pitch radius of the female rotor, n5 is a positive number which is more than 0.6 and less than or equal to 0.8, n6 is a positive number which is more than 0.3 and less than or equal to 0.5, the EF section is smoothly connected with the DE section at the starting point and is tangent to the FG section at the end point;
the FG section is a circular arc with the radius n7 times the pitch radius of the female rotor and the O8 as the center of a circle, n7 is a positive number which is more than 0.1 and less than or equal to 0.5, and is smoothly connected with the EF section at the starting point and is tangent with the GH section at the end point;
the GH section is a straight line section with the length of n8 times the pitch circle radius of the female rotor, n8 is a positive number which is more than 0.1 and less than or equal to 0.3, and the GH section is smoothly connected with the FG section at the starting point and is tangent with the HA section at the end point.
In an embodiment of the present invention, a gear ratio of the female rotor profile to the male rotor profile is 5:3.
in an embodiment of the invention, the diameters of the circumcircles of the female rotor profile and the male rotor profile are equal.
According to the screw rotor profile design method and the screw compressor, the rack lines meshed with the female rotor and the male rotor are drawn through sectional design, the male rotor tooth curve and the female rotor tooth curve are optimized according to the rack lines, the female rotor profile and the male rotor profile are obtained correspondingly according to the female rotor tooth curve and the male rotor tooth curve, the rack can reflect the performance of the screw compressor, the rotor profile is generated through sectional design of the rack lines, then the rack lines are optimized in sections to achieve the purpose of optimizing the rotor profile, large calculation amount caused by direct optimization of the female rotor profile and the male rotor profile can be avoided, and therefore the design efficiency of the rotor profile is improved.
Drawings
In order to more clearly illustrate the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.
FIG. 1 is a schematic flow chart of a method for designing a profile of a screw rotor according to the present invention;
FIG. 2 is a schematic view of the rack lines provided by the present invention when male and female rotors are engaged with each other;
FIG. 3 is a schematic view of the male rotor tooth profile provided by the present invention;
FIG. 4 is a schematic representation of the female rotor tooth profile provided by the present invention;
fig. 5 is a schematic view of the profile of the female rotor and the male rotor engaged with each other according to the present invention.
In fig. 2 to 5: o is the axis of the rack coordinate system, O1 is the axis of the tooth coordinate system of the male rotor, and O2 is the axis of the tooth coordinate system of the female rotor;
r1 is the radius of the addendum circle of the male rotor, and R2 is the radius of the addendum circle of the female rotor;
mj is the male rotor pitch circle, R1j is the male rotor pitch circle radius;
fj is the female rotor pitch circle, R2j is the female rotor pitch circle radius, R2j = R2;
a is the center-to-center distance of the two rotors, a = R1j + R2j;
o3 is the center of the AB segment, R3 is the radius of the AB segment;
o4 is the center of the BC section, and R4 is the radius of the BC section;
o5 is the center of the CD segment, R5 is the radius of the CD segment;
o6 is the center of the DE segment, and R6 is the radius of the DE segment;
o7 is the center of the EF section, R7-1 is the major diameter of the EF section, and R7-2 is the minor diameter of the EF section;
o8 is the center of the FG segment, R8 is the radius of the FG segment;
l is the length of the GH segment.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without inventive step based on the embodiments of the present invention, are within the scope of protection of the present invention.
The terms "first," "second," and the like in the description and claims of the present invention and in the preceding drawings are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It will be appreciated that the data so used may be interchanged under appropriate circumstances such that the embodiments described herein may be practiced otherwise than as specifically illustrated or described herein.
The technical terms to which the present invention relates are described below:
the core part of the screw compressor is a rotor, and the molded line (the section of the molded line is in a tooth shape) of the rotor requires the largest tooth space volume, good meshing characteristics and smaller aerodynamic loss. The section line obtained by the tooth surface of the rotor and the vertical plane of the rotor axis is called a profile line.
An excellent rotor profile requires a smooth profile (low flow loss), a continuous and as short as possible contact line (good sealing effect), a small leakage triangle (reduced internal leakage), a small enclosed volume, and good grinding processability (easy processing). The molded line design of the invention abandons the early point (straight line) cycloid (sensitive to meshing performance and processability) and adopts smooth mathematical curves (such as circular arcs, ellipses, parabolas and the like), and the sealing mode at the sealing side of the rotor is converted from the traditional point (line) -arc sealing into an arc-arc sealing strip, thereby reducing internal leakage and improving volumetric efficiency.
Therefore, in order to solve the problem of low design efficiency of the female rotor profile and the male rotor profile in the prior art, the invention provides the screw rotor profile design method and the screw compressor, the rack lines which are meshed with each other of the female rotor and the male rotor are drawn through sectional design, the male rotor tooth curve and the female rotor tooth curve are optimized according to the rack lines, and then the female rotor profile and the male rotor profile are obtained according to the female rotor tooth curve and the male rotor tooth curve.
The screw rotor profile design method of the present invention is described below with reference to fig. 1-5.
Referring to fig. 1, fig. 1 is a schematic flow chart of a method for designing a profile of a screw rotor according to the present invention. A method of screw rotor profile design, the method comprising:
and step 110, drawing the tooth trace of the intermeshing female rotor and the male rotor through the sectional design.
Illustratively, the rack line is formed by smoothly connecting seven sections of curves end to end, and the seven sections of curves sequentially comprise an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section.
Because the performance of the double-screw compressor is mainly reflected by the racks, the rotor molded lines can be generated by designing the racks in sections, and then the rotor molded lines are optimized in sections, so that the purpose of optimizing the rotor molded lines is achieved, the simultaneous design of the male and female rotor molded lines is avoided, the calculation amount of the optimized design is reduced, and the design efficiency of the rotor molded lines is improved.
For example, the intermeshing rack lines of the female and male rotors may be drawn by segmenting the rack and combining one or more combinations of straight line segments, circular arc segments, elliptical curves, and parabolic segments.
And step 120, generating a male rotor tooth curve and a female rotor tooth curve according to the rack line.
Illustratively, the male and female rotor tooth profiles comprise a smoothly connected sequence of a 1 B 1 Segment, B 1 C 1 Segment C 1 D 1 Segment, D 1 E 1 Segment E 1 F 1 Segment, F 1 G 1 Segment and G 1 H 1 A segment; the female rotor tooth profile comprises, in order, smoothly connected: a. The 2 B 2 Segment, B 2 C 2 Segment C 2 D 2 Segment, D 2 E 2 Segment E 2 F 2 Segment, F 2 G 2 Segment and G 2 H 2 And (4) section.
And step 130, obtaining corresponding female rotor profile and male rotor profile according to the female rotor tooth curve and the male rotor tooth curve.
The method adopts a rotor profile design method based on the rack line, and compared with the traditional profile design method, the rack line method has the advantages of simple profile design process, high efficiency and the like, and the generated rack profile can be optimized by utilizing an optimization algorithm. The optimization algorithm has a mapping function from input to output, can solve the problem that a plurality of complex nonlinear problems can not be expressed by analytic expressions, realizes optimization of the rack outline and improvement of the rotor profile, reduces the leakage triangular area to the greatest extent under the condition that the length of the contact line is small, reduces the leakage of the compressor to the greatest extent, and achieves high relative volumetric efficiency.
The above steps are specifically described below by way of examples.
Referring to fig. 2, fig. 2 is a schematic view of a rack line when male and female rotors provided by the present invention are engaged with each other. Fig. 2 shows a set of drawn rack lines formed by connecting seven curves end to end in a smooth manner, the seven curves sequentially including an AB section (which may be a rack arc section), a BC section (which may be a rack arc section), a CD section (which may be a rack ellipse arc section), a DE section (which may be a rack arc section), an EF section (which may be a rack arc section), an FG section (which may be a rack cubic spline curve section), and a GH section (which may be a rack curve section).
Wherein, the AB section is a circular arc with O3 as the center, the radius R3 is n1 times the radius R2j (R2 j = R2, namely R3= n 1R 2) of the female rotor pitch circle, n1 is a positive number which is more than 0.1 and less than or equal to 0.15 (namely 0.1 & lt n1 & lt 0.15), the AB section is smoothly connected with the HB section at the starting point and is cut with the BC section at the end point.
Wherein, the BC segment is a circular arc with O4 as the center, the radius R4 is n2 times the radius R2j of the pitch circle of the female rotor (R2 j = R2, namely R4= n 2R 2), n2 is a positive number which is more than 0.1 and less than or equal to 0.2 (namely 0.1 is less than or equal to n2 and less than or equal to 0.2), the BC segment is smoothly connected with the AB segment at the starting point and is tangent with the CD segment at the end point.
Wherein the CD segment is an elliptical arc centered at O5, having a radius R5 n3 times the pitch radius R2j (R2 j = R2, i.e. R5= n3 × R2) of the female rotor, n3 is a positive number greater than 0.5 and less than or equal to 0.7 (i.e. 0.5 n3 ≦ 0.7), and the CD segment is smoothly connected to the BC segment at the starting point and is cut off from the DE segment at the end point.
Wherein the DE segment is a circular arc with a center of O6, a radius R6 of n4 times the pitch radius R2j (R2 j = R2, i.e. R6= n 4R 2) of the female rotor, n4 is a positive number greater than 0.8 and less than or equal to 1.1 (i.e. 0.8 n4 ≦ 1.1), and the DE segment is smoothly connected with the CD segment at the starting point and is tangent with the EF segment at the end point.
Wherein the EF segment is centered on O7 and is an elliptic curve having a major diameter R7-1 of n5 times the female rotor pitch radius R2j (R2 j = R2, i.e., R7-1= n5 × R2) and a minor diameter R7-2 of n6 times the female rotor pitch radius R2j (R2 j = R2, i.e., R7-2= n6 × R2), n5 is a positive number greater than 0.6 and equal to or less than 0.8 (i.e., 0.6 and n5 is equal to or less than 0.8), n6 is a positive number greater than 0.3 and equal to or less than 0.5 (i.e., 0.3 and n6 is equal to or less than 0.5), the EF segment is smoothly connected at a starting point to the DE segment and is tangent to the FG at an ending point.
Wherein, the FG segment is a circular arc centered at O8, having a radius R8 n7 times the pitch radius R2j (R2 j = R2, i.e., R8= n7 × R2) of the female rotor, n7 being a positive number greater than 0.1 and equal to or less than 0.5 (i.e., 0.1-n 7 ≦ 0.5), and the FG segment is smoothly connected to the EF segment at the starting point and is tangent to the GH segment at the end point.
Wherein the GH segment is a straight segment having a length L of n8 times the pitch radius R2j of the female rotor (R2 j = R2, i.e., L = n8 × R2), n8 is a positive number greater than 0.1 and equal to or less than 0.3 (i.e., 0.1-n 8 ≦ 0.3), and the GH segment is smoothly connected to the FG segment at the starting point and is tangent to the HA segment at the end point.
It should be noted that the design method of the rotor profile may be determined by the machining method of the rotor. For example, modern machining of rotors is mainly a forming tool (including milling cutters, hobbing cutters and grinding wheels) method and a rack method. The forming tool needs to design the machining tools of the female rotor and the male rotor respectively.
By designing or determining the profile of the screw rotor, different base curves can be combined together to form approximately the desired shape. For example, the rotor-to-rotor method may be referred to as a "rotor method" in which a profile is generated between the rotors. The opposite rack rule is to concentrate the profile design on the machined rack and then generate the rotor tooth form by the envelope relationship. When the rotor method is adopted for design, a certain rotor (such as a female rotor or a male rotor) is firstly combined by the determined basic curve, and the corresponding other rotor (such as the male rotor or the female rotor) is determined and obtained by the envelope meshing principle. Therefore, the rotor method generally includes two steps of envelope condition determination and coordinate transformation. When the rack method is adopted for design, the two steps are included, and a coordinate system needs to be reasonably selected so as to efficiently and conveniently realize a calculation process.
Illustratively, the male rotor tooth profile and the female rotor tooth profile are generated from the tooth trace line by a coordinate conversion formula:
wherein x is c ,y c Is the rack coordinate, mu, of the female or male rotor 1 For the angle of change of rack coordinate to profile coordinate, r p1 Is the pitch radius of the rotor, x 1 ,y 1 The tooth coordinates of the female rotor or the male rotor.
Illustratively, the AB segment, BC segment, CD segment, DE segment, EF segment, FG segment, and GH segment of the rack line shown in fig. 2 are converted from the rack coordinate system to the tooth coordinate system of the male rotor by the coordinate conversion formula, so as to obtain the tooth curve of the male rotor. The male rotor tooth curve comprises A which are smoothly connected in sequence 1 B 1 Segment, B 1 C 1 Segment, C 1 D 1 Segment, D 1 E 1 Segment E 1 F 1 Segment, F 1 G 1 Segment and G 1 H 1 Segment, as shown in fig. 3.
Illustratively, the AB segment, BC segment, CD segment, DE segment, EF segment, FG segment, and GH segment of the rack line shown in fig. 2 are converted from the rack coordinate system to the tooth coordinate system of the female rotor by the above coordinate conversion formula, resulting in a female rotor tooth curve. The female rotor tooth curve comprises A smoothly connected in sequence 2 B 2 Segment, B 2 C 2 Segment C 2 D 2 Segment, D 2 E 2 Segment E 2 F 2 Segment, F 2 G 2 Segment and G 2 H 2 Segment as shown in fig. 4.
Specifically, in the above female rotor tooth curve:
a of the tooth curve of the female rotor 2 B 2 The section is obtained by a coordinate conversion formula of converting an AB section of a rack line into a tooth coordinate system of the female rotor through a rack coordinate system.
Curve B of female rotor teeth 2 C 2 The segment is obtained by a coordinate conversion formula of converting a BC segment of a rack line into a tooth coordinate system of the female rotor through a rack coordinate system.
C of female rotor tooth curve 2 D 2 The section is formed by passing a CD section of a rack line through the rackAnd obtaining a coordinate conversion formula of converting the coordinate system to a tooth-shaped coordinate system of the female rotor.
Tooth curve D of female rotor 2 E 2 The section is obtained by a coordinate conversion formula of a rack DE section converted into a tooth coordinate system of the female rotor through a rack coordinate system.
Tooth curve E of female rotor 2 F 2 The section is obtained by a coordinate conversion formula of converting an EF section of the rack line into a tooth coordinate system of the female rotor through a rack coordinate system.
Curve of female rotor teeth F 2 G 2 The segments are obtained from the FG segments of the rack line by a coordinate conversion formula of the rack coordinate system to the tooth coordinate system of the female rotor.
G of the tooth curve of the female rotor 2 H 2 The section is obtained by a coordinate conversion formula of converting a GH section of the rack line into a tooth-shaped coordinate system of the female rotor through a rack coordinate system.
Specifically, in the above male rotor tooth curve:
a of the male rotor tooth curve 1 B 1 The section is obtained by a coordinate conversion formula of converting an AB section of a rack line into a tooth coordinate system of the male rotor through a rack coordinate system.
Curve B of male rotor teeth 1 C 1 The segment is obtained by a coordinate conversion formula of converting a BC segment of a rack line into a tooth coordinate system of the male rotor through a rack coordinate system.
Curve C of male rotor teeth 1 D 1 The section is obtained by a coordinate conversion formula of converting a CD section of a rack line into a tooth coordinate system of the male rotor through a rack coordinate system.
Curve of male rotor teeth D 1 E 1 The section is obtained by a coordinate conversion formula of converting a DE section of a rack line into a tooth coordinate system of the male rotor through a rack coordinate system.
E of the curve of the male rotor teeth 1 F 1 The section is obtained by an EF section of the rack line through a coordinate conversion formula for converting a rack coordinate system into a tooth coordinate system of the male rotor.
Curve F of male and female rotor teeth 1 G 1 The segments are converted from FG segments of the rack line to FG segments of the rack line by means of the rack coordinate systemAnd obtaining a coordinate conversion formula of a tooth form coordinate system of the male rotor.
G of male rotor tooth curve 1 H 1 The section is obtained by a coordinate conversion formula of converting a GH section of a rack line into a tooth coordinate system of the male rotor through a rack coordinate system.
Therefore, by optimizing the rack, the female rotor adopts a more proper tooth depth radius, so that the female rotor is very suitable for a large-flow compressor, and meanwhile, the deeper tooth thickness is reserved, so that the male rotor achieves a better rigidity condition.
Referring to fig. 5, fig. 5 is a schematic view of a molded line when male and female rotors are engaged with each other according to the present invention. And obtaining corresponding female rotor molded lines and male rotor molded lines according to the female rotor tooth curves and the male rotor tooth curves. The gear ratio of the lower female rotor and the upper male rotor shown in fig. 5 is 5:3, for example, the female rotor is 5 teeth and the male rotor is 3 teeth.
The molded line of the female rotor is designed into a streamline type, so that the disturbance resistance of airflow can be reduced, the loss is reduced, the noise is reduced, and the operation efficiency of the rotor is improved.
Illustratively, the circumscribed circle diameters of the female and male rotor profiles are equal. The molded lines of the male and female rotors are designed to be the same, so that the male and female rotors have the same rigidity, the processing and the assembly are convenient, after the racks are optimized, the molded line tooth surfaces are smoothly connected, the processing and the detection are convenient, and the service life of the screw rotor cutter is greatly prolonged.
The invention also provides a screw compressor, which comprises a female rotor and a male rotor, wherein the meshed rack line of the female rotor and the male rotor is formed by smoothly connecting seven sections of curves end to end, and the seven sections of curves sequentially comprise an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section;
the curve of the male rotor teeth generated from said rack line comprises a smoothly connected sequence of A 1 B 1 Segment, B 1 C 1 Segment, C 1 D 1 Segment, D 1 E 1 Segment E 1 F 1 Segment, F 1 G 1 Segment and G 1 H 1 A segment;
the female rotor tooth curve generated according to the rack line comprises A which are smoothly connected in sequence 2 B 2 Segment, B 2 C 2 Segment, C 2 D 2 Segment, D 2 E 2 Segment E 2 F 2 Segment, F 2 G 2 Segment and G 2 H 2 A segment;
the male rotor tooth profile is used to generate a male rotor profile and the female rotor tooth profile is used to generate a female rotor profile.
Illustratively, the male and female rotor tooth profiles are generated from the tooth trace by a coordinate conversion equation:
wherein x is c ,y c Is the rack coordinate, μ, of the female or male rotor 1 Angle, r, for the change of rack coordinate to profile coordinate p1 Is the pitch radius of the rotor, x 1 ,y 1 The tooth coordinates of the female rotor or the male rotor.
Exemplarily, the male rotor tooth curve is obtained by converting an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section of the tooth line from a rack coordinate system to a tooth coordinate system of the male rotor;
the female rotor tooth curve is obtained by converting an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section of the tooth line from a rack coordinate system into a tooth coordinate system of the female rotor;
wherein, the AB section is a section of circular arc with O3 as the center of circle and radius n1 times the pitch radius of the female rotor, n1 is a positive number which is more than 0.1 and less than or equal to 0.15, the AB section is smoothly connected with the HB section at the starting point and is tangent with the BC section at the end point;
the BC section is a section of circular arc with O4 as the center of a circle and the radius n2 times the pitch radius of the female rotor, n2 is a positive number which is more than 0.1 and less than or equal to 0.2, the BC section is smoothly connected with the AB section at the starting point and is tangent to the CD section at the end point;
the CD section is an elliptic arc with O5 as the center of a circle and the radius n3 times the radius of a pitch circle of the female rotor, n3 is a positive number which is more than 0.5 and less than or equal to 0.7, the CD section is smoothly connected with the BC section at the starting point and is tangent with the DE section at the end point;
the DE section is a section of circular arc with O6 as the center of a circle and n4 times the pitch radius of the female rotor, n4 is a positive number which is more than 0.8 and less than or equal to 1.1, the DE section is smoothly connected with the CD section at the starting point and is tangent with the EF section at the end point;
the EF section is a section of elliptic curve with O7 as the center, the major diameter of the elliptic curve is n5 times the pitch radius of the female rotor, the minor diameter of the elliptic curve is n6 times the pitch radius of the female rotor, n5 is a positive number which is more than 0.6 and less than or equal to 0.8, n6 is a positive number which is more than 0.3 and less than or equal to 0.5, the EF section is smoothly connected with the DE section at the starting point and is tangent to the FG section at the end point;
the FG section is a circular arc with O8 as the center and the radius n7 times the pitch radius of the female rotor, n7 is a positive number which is more than 0.1 and less than or equal to 0.5, and is smoothly connected with the EF section at the starting point and is tangent with the GH section at the end point;
the GH section is a straight line section with the length of n8 times the pitch radius of the female rotor, n8 is a positive number which is more than 0.1 and less than or equal to 0.3, and is smoothly connected with the FG section at the starting point and tangent with the HA section at the end point.
Exemplarily, the tooth ratio of the female rotor profile and the male rotor profile is 5:3.
illustratively, the circumscribed circle diameters of said female and male rotor profiles are equal.
In conclusion, the screw compressor with the tooth profile can realize optimal meshing between the male rotor and the female rotor in the working process, the tooth curves formed by two adjacent sections are in smooth transition at the connecting point, the utilization coefficient of the rotor area is large, the contact line is short, the leakage triangle is relatively small, the profile is in a streamline shape, the male rotor and the female rotor are as large as each other, and the screw compressor has good thermodynamic performance, so that the working efficiency of the screw compressor is improved, the precision is improved in the machining process, and the service life of a cutter is prolonged.
It should be noted that, the screw compressor provided in the embodiment of the present invention can implement all the method steps implemented in the method embodiment, and can achieve the same technical effects, and detailed descriptions of the same parts and beneficial effects as those in the method embodiment are omitted here.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (10)
1. A method of screw rotor profile design, the method comprising:
drawing out a tooth line of the female rotor and the male rotor which are meshed with each other through a segmented design, wherein the tooth line is formed by smoothly connecting seven sections of curves end to end, and the seven sections of curves sequentially comprise an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section;
optimizing a male rotor tooth profile and a female rotor tooth profile according to the rack line, the male rotor tooth profile comprising a sequence of smoothly connected A' s 1 B 1 Segment, B 1 C 1 Segment, C 1 D 1 Segment, D 1 E 1 Segment E 1 F 1 Segment, F 1 G 1 Segment and G 1 H 1 A section, the female rotor tooth curve comprising A smoothly connected in sequence 2 B 2 Segment, B 2 C 2 Segment, C 2 D 2 Segment, D 2 E 2 Segment E 2 F 2 Segment, F 2 G 2 Segment and G 2 H 2 A segment;
and obtaining corresponding female rotor molded lines and male rotor molded lines according to the female rotor tooth curves and the male rotor tooth curves.
2. The screw rotor profile design method according to claim 1, wherein the male rotor tooth profile and the female rotor tooth profile are generated from the tooth profile line by a coordinate conversion formula:
wherein x is c ,y c Is the rack coordinate, mu, of the female or male rotor 1 For the angle of change of rack coordinate to profile coordinate, r p1 Is the pitch radius of the rotor, x 1 ,y 1 The tooth coordinates of the female rotor or the male rotor.
3. The screw rotor profile design method according to claim 1 or 2, wherein the step of optimizing the male and female rotor tooth profiles according to the tooth line comprises:
converting an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section of the rack line into a tooth form coordinate system of the male rotor from a rack coordinate system to obtain a tooth curve of the male rotor; and
converting the AB section, the BC section, the CD section, the DE section, the EF section, the FG section and the GH section of the rack line into a tooth form coordinate system of the female rotor from a rack coordinate system to obtain a tooth curve of the female rotor;
wherein, the AB section is a section of circular arc with O3 as the center of circle and radius n1 times the pitch radius of the female rotor, n1 is a positive number which is more than 0.1 and less than or equal to 0.15, the AB section is smoothly connected with the HB section at the starting point and is tangent with the BC section at the end point;
the BC section is a section of circular arc with O4 as the center of a circle and the radius n2 times the pitch radius of the female rotor, n2 is a positive number which is more than 0.1 and less than or equal to 0.2, the BC section is smoothly connected with the AB section at the starting point and is tangent to the CD section at the end point;
the CD section is an elliptic arc with O5 as the center of a circle and n3 times the pitch radius of the female rotor, n3 is a positive number which is more than 0.5 and less than or equal to 0.7, the CD section is smoothly connected with the BC section at the starting point and is tangent with the DE section at the end point;
the DE section is a section of circular arc with O6 as the center of a circle and n4 times the pitch radius of the female rotor, n4 is a positive number which is more than 0.8 and less than or equal to 1.1, the DE section is smoothly connected with the CD section at the starting point and is tangent with the EF section at the end point;
the EF section is a section of elliptic curve with O7 as the center, the major diameter of the elliptic curve is n5 times the pitch radius of the female rotor, the minor diameter of the elliptic curve is n6 times the pitch radius of the female rotor, n5 is a positive number which is more than 0.6 and less than or equal to 0.8, n6 is a positive number which is more than 0.3 and less than or equal to 0.5, the EF section is smoothly connected with the DE section at the starting point and is tangent to the FG section at the end point;
the FG section is a circular arc with O8 as the center and the radius n7 times the pitch radius of the female rotor, n7 is a positive number which is more than 0.1 and less than or equal to 0.5, and is smoothly connected with the EF section at the starting point and is tangent with the GH section at the end point;
the GH section is a straight line section with the length of n8 times the pitch radius of the female rotor, n8 is a positive number which is more than 0.1 and less than or equal to 0.3, and is smoothly connected with the FG section at the starting point and tangent with the HA section at the end point.
4. The screw rotor profile design method according to claim 1, wherein the tooth ratio of the female rotor and the male rotor is 5:3.
5. the screw rotor profile design method according to claim 1, wherein the circumscribed circle diameters of the female rotor profile and the male rotor profile are equal.
6. A screw compressor comprises a female rotor and a male rotor, and is characterized in that a rack line meshed with the female rotor and the male rotor is formed by smoothly connecting seven sections of curves end to end, wherein the seven sections of curves sequentially comprise an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section;
the curve of the male rotor teeth generated from said rack line comprises a smoothly connected sequence of A 1 B 1 Segment, B 1 C 1 Segment, C 1 D 1 Segment, D 1 E 1 Segment E 1 F 1 Segment, F 1 G 1 Segment and G 1 H 1 A segment;
the female rotor tooth curve generated according to the rack line comprises A which are smoothly connected in sequence 2 B 2 Segment, B 2 C 2 Segment C 2 D 2 Segment, D 2 E 2 Segment E 2 F 2 Segment, F 2 G 2 Segment and G 2 H 2 A segment;
the male rotor tooth profile is used to generate a male rotor profile and the female rotor tooth profile is used to generate a female rotor profile.
7. -screw compressor according to claim 6, characterised in that the male and female rotor tooth profiles are generated according to the tooth line by means of a coordinate conversion formula:
wherein x is c ,y c Is the rack coordinate, mu, of the female or male rotor 1 For the angle of change of rack coordinate to profile coordinate, r p1 Is the pitch radius of the rotor, x 1 ,y 1 The tooth coordinates of the female rotor or the male rotor.
8. Screw compressor according to claim 6 or 7,
the male rotor tooth curve is obtained by converting an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section of the tooth line from a rack coordinate system to a tooth coordinate system of the male rotor;
the female rotor tooth curve is obtained by converting an AB section, a BC section, a CD section, a DE section, an EF section, an FG section and a GH section of the tooth line from a rack coordinate system into a tooth coordinate system of the female rotor;
wherein, the AB section is a section of circular arc with O3 as the center of circle and radius n1 times the pitch radius of the female rotor, n1 is a positive number which is more than 0.1 and less than or equal to 0.15, the AB section is smoothly connected with the HB section at the starting point and is tangent with the BC section at the end point;
the BC section is a section of circular arc with O4 as the center of a circle and the radius n2 times the pitch radius of the female rotor, n2 is a positive number which is more than 0.1 and less than or equal to 0.2, the BC section is smoothly connected with the AB section at the starting point and is tangent to the CD section at the end point;
the CD section is an elliptic arc with O5 as the center of a circle and n3 times the pitch radius of the female rotor, n3 is a positive number which is more than 0.5 and less than or equal to 0.7, the CD section is smoothly connected with the BC section at the starting point and is tangent with the DE section at the end point;
the DE section is a section of circular arc with O6 as the center of a circle and n4 times the pitch radius of the female rotor, n4 is a positive number which is more than 0.8 and less than or equal to 1.1, the DE section is smoothly connected with the CD section at the starting point and is tangent with the EF section at the end point;
the EF section is a section of elliptic curve with O7 as the center, the major diameter of the elliptic curve is n5 times the pitch radius of the female rotor, the minor diameter of the elliptic curve is n6 times the pitch radius of the female rotor, n5 is a positive number which is more than 0.6 and less than or equal to 0.8, n6 is a positive number which is more than 0.3 and less than or equal to 0.5, the EF section is smoothly connected with the DE section at the starting point and is tangent with the FG section at the end point;
the FG section is a circular arc with O8 as the center and the radius n7 times the pitch radius of the female rotor, n7 is a positive number which is more than 0.1 and less than or equal to 0.5, and is smoothly connected with the EF section at the starting point and is tangent with the GH section at the end point;
the GH section is a straight line section with the length of n8 times the pitch circle radius of the female rotor, n8 is a positive number which is more than 0.1 and less than or equal to 0.3, and the GH section is smoothly connected with the FG section at the starting point and is tangent with the HA section at the end point.
9. The screw compressor of claim 6, wherein the tooth ratio of the female rotor profile to the male rotor profile is 5:3.
10. the screw compressor of claim 6, wherein the circumscribed circle diameters of the female and male rotor profiles are equal.
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| CN202211247350.9A CN115434913A (en) | 2022-10-12 | 2022-10-12 | Screw rotor profile design method and screw compressor |
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| CN202211247350.9A CN115434913A (en) | 2022-10-12 | 2022-10-12 | Screw rotor profile design method and screw compressor |
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