CN113757121B - Space internal meshing conical double-screw compressor rotor driven by intersecting shafts and compressor - Google Patents

Space internal meshing conical double-screw compressor rotor driven by intersecting shafts and compressor Download PDF

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CN113757121B
CN113757121B CN202110785786.2A CN202110785786A CN113757121B CN 113757121 B CN113757121 B CN 113757121B CN 202110785786 A CN202110785786 A CN 202110785786A CN 113757121 B CN113757121 B CN 113757121B
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rotor
inner rotor
tooth
profile
coordinate system
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CN113757121A (en
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何志龙
胡汪锋
李丹童
邢子文
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Xian Jiaotong University
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Xian Jiaotong University
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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
    • 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
    • F04C18/10—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 internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member
    • F04C18/107—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 internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member with helical teeth
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • F04C2250/201—Geometry of the rotor conical shape
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/13—Noise
    • F04C2270/135—Controlled or regulated

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Abstract

A space inner gearing conical double-screw compressor rotor and a compressor driven by intersecting shafts are disclosed, the double-screw compressor rotor comprises an inner rotor and an outer rotor which are meshed with each other, the tooth top profile of the inner rotor is a spiral surface generated by an epicycloid, one tooth surface of the outer rotor is formed by connecting the tooth top profile of the outer rotor with the tooth socket profile of the outer rotor, the tooth top profile of the outer rotor is connected with the tooth socket profile of the outer rotor to be a conjugate curved surface of the tooth top profile of the inner rotor, and the complete tooth surface of the outer rotor is obtained by mirroring one tooth surface of the outer rotor; the tooth space profile of the inner rotor is a conjugate curved surface of the tooth space profile of the outer rotor, one tooth surface of the inner rotor is formed by connecting the tooth top profile of the inner rotor with the tooth space profile of the inner rotor, and the complete tooth surface of the inner rotor is obtained by mirroring one tooth surface of the inner rotor; along with the meshing rotation of the inner rotor and the outer rotor, the volume of the element is gradually reduced from the large end to the small end, the internal compression process is realized, and the compressed fluid is sucked from the large end and is discharged from the small end. The invention improves the space utilization rate and the compression ratio of the screw compressor.

Description

Space internal meshing conical double-screw compressor rotor driven by intersecting shafts and compressor
Technical Field
The invention belongs to the field of mechanical engineering design, and particularly relates to a space internal meshing conical double-screw compressor rotor driven by intersecting shafts and a compressor.
Background
The twin screw compressor is a positive displacement rotary compressor for obtaining high pressure gas and has wide application in modern industry. The rotary compressor inherits the advantages of long service life, reliable operation, small vibration, low noise, stable work, no surge phenomenon and the like of the rotary machine, has the characteristics of no wearing parts such as an air valve and the like, forced air suction and exhaust, simple processing and the like, and is a core part in systems such as air supply, refrigeration, waste heat recovery and the like. At present, in order to facilitate processing, the commonly used double-screw compressor rotors are in external meshing, which results in larger center distance between the rotors and longer leakage line length, thereby reducing space utilization rate and increasing leakage strength, and finally resulting in that the conventional screw rotors cannot be miniaturized.
Compared with an external-meshing double-screw compressor, the internal-meshing double-screw compressor can effectively reduce the center distance of the rotor and avoid a leakage channel between the shell and the rotor, so that the internal-meshing double-screw compressor has the characteristics of high rotor space utilization rate and low leakage strength, and is an ideal scheme for miniaturization of the double-screw rotor. In order to further improve the space utilization rate and the compression ratio, the internally meshed double screws can adopt a conical form. The conical screw has a good application prospect in the fields of miniaturization, high pressure ratio and low noise. In order to more easily realize the tapering of the screw, a conical screw driven by a parallel shaft is provided, the principle is a plane meshing principle, the conical design is realized by the size change of the cross section of each rotor, but the pitch circle radiuses of the inner rotor and the outer rotor are fixed and unchanged due to the parallel shaft transmission, so that the change amplitude of the cross-section molded line of the rotor is smaller under the condition of ensuring the correct meshing, the taper of the conical screw is smaller, and the ideal effect of the high pressure ratio of the conical screw is difficult to achieve. Under the condition of parallel shaft transmission, the axial length of the conical screw has to be increased in order to achieve high compression ratio, so that the power consumption of compressed gas is increased, and the strength of the screw is reduced.
Disclosure of Invention
The invention aims to solve the problems in the prior art, and provides a crossed-shaft transmission space internal-meshing conical double-screw compressor rotor and a compressor, so that the space utilization rate and the compression ratio of the screw compressor are improved, and the power consumption and the noise are reduced.
In order to achieve the purpose, the invention has the following technical scheme:
a space inner meshing conical twin-screw compressor rotor driven by intersecting shafts comprises an inner rotor and an outer rotor which are meshed with each other, wherein the tooth crest profile of the inner rotor is a spiral surface generated by an epicycloid, one tooth surface of the outer rotor is formed by connecting the tooth crest profile of the outer rotor with the tooth socket profile of the outer rotor, the tooth crest profile of the outer rotor is connected with the tooth socket profile of the outer rotor and is a conjugate curved surface of the tooth crest profile of the inner rotor, and the complete tooth surface of the outer rotor is obtained by mirroring one tooth surface of the outer rotor; the tooth space profile of the inner rotor is a conjugate curved surface of the tooth space profile of the outer rotor, one tooth surface of the inner rotor is formed by connecting the tooth top profile of the inner rotor with the tooth space profile of the inner rotor, and the complete tooth surface of the inner rotor is obtained by mirroring one tooth surface of the inner rotor; along with the meshing rotation of the inner rotor and the outer rotor, the volume of the element is gradually reduced from the large end to the small end, the inner compression process is realized, and the compressed fluid is sucked from the large end and is discharged from the small end.
As a preferred scheme of the invention, the bottom surface radius R of the inner rotor pitch cone1Angle of taper delta1Radius R of the bottom surface of the outer rotor pitch cone2Angle of taper delta2Satisfies the following conditions:
Figure BDA0003158711050000021
θ＝δ2-δ1
Z2number of teeth of outer rotor, Z1The number of teeth of the inner rotor.
As a preferred solution of the invention, a spatial coordinate system is established, the coordinate system OX1Y1Z1And a coordinate system OX2Y2Z2For a coordinate system fixed to the machine frame, coordinate system OX2Y2Z2Is a coordinate system OX1Y1Z1Around OY1Is generated by rotating theta, and a moving coordinate system ox is respectively established on the inner rotor and the outer rotor1y1z1And ox2y2z2；
From a coordinate system OX1Y1Z1Transformation to the coordinate System OX2Y2Z2Is M12，M12The solving expression of (1) is as follows:
Figure BDA0003158711050000022
from the coordinate system ox1y1z1Transformation to the coordinate System OX1Y1Z1Is Mm1From the coordinate system OX2Y2Z2Transformation to coordinate system ox2y2z2Is M2m，Mm1And M2mThe solving expressions of (a) are respectively as follows:
Figure BDA0003158711050000031
Figure BDA0003158711050000032
as a preferred aspect of the present invention, the calculation equation of the epicycloid is:
Figure BDA0003158711050000033
inner rotor tooth top profile sigma11The calculation equation of (a) is:
Figure BDA0003158711050000034
namely:
Figure BDA0003158711050000035
wherein, γ1The helix angle of the inner rotor, and p is the pitch of the inner rotor;
the generating circle radius R of the epicycloid changes along the axial direction, namely:
Figure BDA0003158711050000036
the radius R of the rolling circle is always equal to 1/Z of R1。
In a preferred embodiment of the present invention, the tooth top surface Σ of the inner rotor is set11Is determined by a coordinate transformation of the secondary coordinate system ox1y1z1Conversion to a moving coordinate system ox2y2z2Obtaining a family of conjugate surfaces Σ (Φ) of the inner rotor, and a coordinate equation of the family of conjugate surfaces Σ (Φ) of the inner rotor tooth tip profile Σ 11 is as follows:
Figure BDA0003158711050000037
namely:
Figure BDA0003158711050000038
where phi is phi1，Φ1，Φ2Satisfies the following conditions:
Figure BDA0003158711050000041
therefore, the method comprises the following steps:
Figure BDA0003158711050000042
the meshing equation is:
Figure BDA0003158711050000043
and determining a parameter phi by using a meshing equation of space meshing so as to determine a conjugate curved surface of the tooth top profile of the inner rotor.
As a preferable aspect of the present invention, the tooth tip profile Σ of the outer rotor21The equation of (a) is:
Figure BDA0003158711050000044
outer rotor gullet profile sigma22The equation of (a) is:
Figure BDA0003158711050000045
inner rotor tooth space profile sigma12The equation of (a) is:
Figure BDA0003158711050000046
as a preferable mode of the present invention, the number of teeth Z of the outer rotor2Number of teeth Z of inner rotor1Mostly 1, helix angle γ of outer rotor1With helix angle gamma of the inner rotor2Satisfies the following conditions:
Figure BDA0003158711050000047
the inner and outer rotors rotate in the same direction, and the angular velocity omega of the inner rotor1And angular velocity ω of the outer rotor2Satisfies the following conditions:
Figure BDA0003158711050000048
a compressor, the rotor adopts the space of the intersecting shaft transmission to internally mesh the conical twin-screw compressor rotor.
Compared with the prior art, the invention has the following beneficial effects: because the rotors of the double-screw compressor are in an inner meshing mode, a compression cavity can be automatically formed between the inner rotor and the outer rotor, a machine shell does not need to be installed, parts are reduced, and the screw compressor is more compact. Because the rotor of the invention is a conical screw, the volume of the element is continuously changed along the axial direction, so that the compression process is also continuous, and the noise of the double-screw compressor can be greatly reduced. Meanwhile, the conical form enables the screw compressor to naturally realize axial reduction of the volume of the element without additionally designing an air inlet and an air outlet through the meshing motion of the inner rotor and the outer rotor, and the processes of air suction, compression and air exhaust are completed. Because the invention is a space meshing mode of intersecting shaft transmission, the taper of the conical screw is improved, the variation amplitude of the element volume is larger, the achievable compression ratio is higher, and the meshing mode also enables the conical screw to have smaller volume and higher space utilization rate. The invention is more compact, the space utilization rate is higher and the noise is lower under the same working condition requirement.
Furthermore, in the face of different working condition requirements, the invention can adjust the independent variable in the rotor solving process, thereby achieving the requirements of applying different compression ratios and air displacement and having the advantage of wide application range.
Drawings
FIG. 1 is a schematic view of a coordinate system and a pitch cone of the present invention in conjunction with a frame;
FIG. 2 is a schematic view of a moving coordinate system for fixing the inner and outer rotors according to the present invention:
(a) a moving coordinate system with the fixed inner rotor; (b) a moving coordinate system for outer rotor consolidation;
FIG. 3 is a schematic diagram illustrating a process for generating a tip profile of an inner rotor according to the present invention;
fig. 4 schematic profile of the outer rotor of the present invention: (a) a top view; (b) a front view;
FIG. 5 is a schematic diagram of the inner rotor generation process of the present invention;
FIG. 6 is a schematic view of the assembly of the inner and outer rotors of the present invention;
FIG. 7 is a schematic view of the process of the present invention for meshing the inner and outer rotors.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and examples.
The invention provides a space inner meshing conical twin-screw compressor rotor in intersecting shaft transmission, as shown in figure 1, according to a space meshing theory, a space coordinate system is firstly established, and inner and outer rotor pitch cones are determined. Coordinate system OX in the figure1Y1Z1And a coordinate system OX2Y2Z2For a coordinate system fixed to the machine frame, coordinate system OX2Y2Z2Is a coordinate system OX1Y1Z1Around OY1Rotated by theta. The radius of the bottom surface of the pitch cone of the inner rotor is R1The angle of the cone being delta1Central axis and OZ1And (4) overlapping. The radius of the bottom surface of the outer rotor pitch cone is R2The angle of the cone being delta2Central axis and OZ2And (4) overlapping. The coincident generatrix of the two sections of cones is a transient center line L. As shown in (a) and (b) of fig. 2, in order to solve the conjugate curved surface, a moving coordinate system ox is established on each of the inner and outer rotors1y1z1And ox2y2z2. As shown in FIG. 3, the present invention designs the tooth top profile of the inner rotor as a spiral surface generated by epicycloid (curved surface Σ)11) The curved surface is formed by scanning an epicycloid in a spiral motion, and the generating circle radius R and the rolling circle radius R of the cycloid are gradually reduced while the spiral motion is carried out. The ratio of R to R determines the number of teeth Z in the inner rotor1(R/(2R) ═ Z in FIG. 3)12). As shown in fig. 4 (a) and (b), the tip profile Σ of the inner rotor is obtained by the spatial meshing relationship11Conjugate curved surface (curved surface Σ)21+ curved surface Σ22) Curved surface Σ21As tooth tip profile of outer rotor, curved surface ∑22As a spline profile of the outer rotor. Curved surface sigma21Sum-sigma22The connection forms a tooth surface of the outer rotor, and then the complete tooth surface of the outer rotor (outer rotor tooth number Z) can be obtained through mirroring2＝Z1+1). As shown in fig. 5, the outer rotor cogging profile Σ is solved by the space engagement relationship22Conjugate curved surface (curved surface Σ)12) Curved surface Σ12As a spline profile for the inner rotor. Curved surface sigma11Sum-sigma12The inner rotor is connected to form a tooth surface of the inner rotor, then a complete inner rotor profile can be obtained through mirroring, and then an inner rotor entity is further generated. As shown in fig. 6, the inner and outer rotors can be properly engaged with each other, and the inner and outer rotors rotate in the same direction, so that the gas is sucked from the large end and discharged from the small end. As shown in fig. 7, the inner and outer rotors can achieve a correct meshing relationship with each other as the inner and outer rotors rotate, and the volume of the element gradually decreases from the large end to the small end to complete internal compression.
Referring to FIG. 1, the bottom radius R of the inner rotor pitch cone1Angle of taper delta1Radius R of the bottom surface of the outer rotor pitch cone2Angle of taper delta2Satisfies the following conditions:
Figure BDA0003158711050000061
θ＝δ2-δ1
from a coordinate system OX1Y1Z1Transformation to the coordinate System OX2Y2Z2Is M12，M12The solving expression of (1) is as follows:
Figure BDA0003158711050000062
see (a) and (b) of fig. 2, from the coordinate system ox1y1z1Transformation to the coordinate System OX1Y1Z1Is Mm1From the coordinate system OX2Y2Z2Transformation to coordinate system ox2y2z2Is M2m，Mm1And M2mThe solving expressions of (a) are respectively as follows:
Figure BDA0003158711050000071
Figure BDA0003158711050000072
referring to fig. 3, the epicycloid equation is:
Figure BDA0003158711050000073
inner rotor tooth top profile sigma11The equation is:
Figure BDA0003158711050000074
namely:
Figure BDA0003158711050000075
wherein, γ1Is the helix angle of the inner rotor and p is the pitch of the inner rotor. Radius of generating circle of cycloid R edgeChanges occur in the axial direction, namely:
Figure BDA0003158711050000076
the radius R of the rolling circle is always equal to 1/Z of R1。
The tooth top profile of the inner rotor is formed11Equation follows coordinate system ox through coordinate transformation1y1z1Conversion to a moving coordinate system ox2y2z2And obtaining the conjugate surface family sigma (phi). The coordinates are:
Figure BDA0003158711050000077
namely:
Figure BDA0003158711050000078
where Φ is Φ1，Φ1，Φ2Satisfies the following conditions:
Figure BDA0003158711050000081
therefore, the method comprises the following steps:
Figure BDA0003158711050000082
determining a parameter phi by using a meshing equation of space meshing so as to determine a conjugate curved surface of the tooth top profile of the inner rotor, wherein the meshing equation is as follows:
Figure BDA0003158711050000083
the equation of the tooth surface of the outer rotor can be obtained by combining the sigma (phi) equation of the conjugate surface family of the tooth top profile of the inner rotor and the meshing equation.
Tooth top profile sigma of outer rotor21The equation of (a) is:
Figure BDA0003158711050000084
outer rotor gullet profile sigma22The equation of (a) is:
Figure BDA0003158711050000085
then using the same method to form the outer rotor tooth groove profile sigma22The equation of (A) obtains the tooth space profile sigma of the inner rotor12The equation of (a) is:
Figure BDA0003158711050000086
in fig. 4 (a) and (b) and fig. 5, the number of teeth Z of the outer rotor2Number of teeth Z of inner rotor1Mostly 1, helix angle γ of outer rotor1With helix angle gamma of the inner rotor2Satisfies the following conditions:
Figure BDA0003158711050000087
referring to fig. 6, the inner and outer rotors rotate in the same direction, and the angular velocity ω of the inner rotor1And angular velocity ω of outer rotor2Satisfies the following conditions:
Figure BDA0003158711050000088
referring to fig. 7, as the inner and outer rotors rotate, the volume of the element is gradually reduced from the large end to the small end, so as to realize the inner compression process, and the compressed fluid is sucked from the large end and discharged from the small end.
The independent variables in the above solving process are: independent variable of inner rotor tooth tip profile (inner rotor tooth number Z)1Radius R of the bottom surface of the pitch cone of the inner rotor1And the circleCone angle delta1) Independent variables from the helical scan (pitch p of the inner rotor and helix angle gamma1). In the specific design process, the independent variables can be adjusted according to different working condition requirements.
The space inner meshing conical double-screw compressor rotor driven by the intersecting shaft has a good application prospect in the fields of miniaturization, high pressure ratio and low noise. In the case of unsatisfactory effect of the conical screw driven by the parallel shaft, the invention provides a mode of transmission of the intersecting shaft, the transmission of the intersecting shaft belongs to a space meshing range, different from a pitch circle with a fixed size, the pitch cone in space meshing can automatically realize the change of the section shape along the axial direction, and the requirements of different conicity of the conical screw can be realized by changing the size of the cone angle of the pitch cone. It can be seen from the model that a small cone angle allows a large variation of the rotor cross-section. The conical screw driven by the crossed shafts is more compact under the condition of meeting the space meshing, a closed working volume cavity can be realized without using a shell, the leakage area between the tooth top of the externally meshed double-screw rotor and the shell is avoided, the thermal performance of the rotors is favorably improved, and the space utilization rate and the compression ratio of the screw compressor are improved.
Examples
A space internal-meshing conical twin-screw compressor rotor driven by intersecting shafts is characterized in that the tooth top profile of the inner rotor is sigma11External rotor tooth top profile Σ21Tooth-groove profile Σ22All-inner rotor tooth top profile sigma11Conjugate curved surface of (2), inner rotor gullet profile Σ12For outer rotor gullet profile sigma22The conjugate curved surface of (2). With independent parameters of number of teeth Z of inner rotor1Radius R of the bottom surface of the pitch cone of the inner rotor1Angle delta to the cone1Pitch p of inner rotor, helix angle gamma1. The design process is as follows:
1) inner rotor tooth number Z is optimized according to volume size and air pumping speed1Radius R of the bottom surface of the pitch cone of the inner rotor1Angle delta to the cone1Pitch p of inner rotor, helix angle gamma1Taking the number of teeth Z of the inner rotor as shown in FIG. 11Is the number of 2, and the number of the second,bottom radius R of inner rotor pitch cone140mm, cone angle delta of the pitch cone of the inner rotor1At 4 deg., the pitch p of the inner rotor is 40 mm.
2) The inner rotor helix angle gamma is preferably selected according to the requirements of gas tightness, stress performance and the like1Is 3 pi (540 deg.).
3) Solving the rotor profile by using the optimal parameters;
the following equation is utilized:
Figure BDA0003158711050000101
Figure BDA0003158711050000102
determining inner rotor tooth top three-dimensional contour curved surface sigma11。
Figure BDA0003158711050000103
The following equation is utilized:
Figure BDA0003158711050000104
where phi is phi1，Φ1，Φ2Satisfies the following conditions: phi1/Φ2＝Z2/Z1。
Figure BDA0003158711050000105
And determining the three-dimensional contour curved surface of the tooth top and the tooth socket of the outer rotor.
Tooth top profile sigma of outer rotor21The equation of (a) is:
Figure BDA0003158711050000106
outer rotor gullet profile sigma22The equation of (a) is:
Figure BDA0003158711050000107
then using the same method to form the outer rotor tooth groove profile sigma22The equation of (A) obtains the tooth space profile sigma of the inner rotor12I.e.:
Figure BDA0003158711050000108
the double-screw rotor structure can realize the pressurization and transportation process of gas, adopts a space internal engagement mode of intersecting shaft transmission, improves the space utilization rate of the structure, reduces the energy consumption of the compressor, further increases the single-stage compression ratio, avoids a leakage channel between an external engagement double-screw rotor and a shell, and is beneficial to improving the efficiency of the small double-screw compressor. Compared with the conventional double-screw compressor, the double-screw compressor has the advantages of few easily-damaged parts, compact structure, high air extraction rate, no surge, low vibration noise and the like.
The above-mentioned embodiments are only preferred embodiments of the present invention, and are not intended to limit the technical solution of the present invention, and it should be understood by those skilled in the art that the technical solution can be modified and replaced by a plurality of simple modifications and replacements without departing from the spirit and principle of the present invention, and the modifications and replacements also fall into the protection scope covered by the claims.

Claims (8)

1. The utility model provides a crossing shaft drive's space internal gearing toper double screw compressor rotor which characterized in that: the outer rotor tooth surface is a conjugate curved surface of the tooth top profile of the inner rotor, and a complete outer rotor tooth surface is obtained by mirroring one tooth surface of the outer rotor; the tooth space profile of the inner rotor is a conjugate curved surface of the tooth space profile of the outer rotor, one tooth surface of the inner rotor is formed by connecting the tooth top profile of the inner rotor with the tooth space profile of the inner rotor, and the complete tooth surface of the inner rotor is obtained by mirroring one tooth surface of the inner rotor; along with the meshing rotation of the inner rotor and the outer rotor, the volume of the element is gradually reduced from the large end to the small end, the inner compression process is realized, and the compressed fluid is sucked from the large end and is discharged from the small end.
2. The spatially intermeshing conical twin screw compressor rotor of claim 1 in which the pitch cone of the inner rotor has a base radius R1Angle of taper delta1Radius R of the bottom surface of the outer rotor pitch cone2Angle of taper delta2Satisfies the following conditions:
Figure FDA0003158711040000011
θ＝δ2-δ1
Z2number of teeth of outer rotor, Z1The number of teeth of the inner rotor.
3. Spatially intermeshing conical twin-screw compressor rotor according to claim 2 of intersecting shaft drive, characterized by establishing a spatial coordinate system, coordinate system OX1Y1Z1And a coordinate system OX2Y2Z2For a coordinate system fixed to the machine frame, coordinate system OX2Y2Z2Is a coordinate system OX1Y1Z1Around OY1Is generated by rotating theta, and a moving coordinate system ox is respectively established on the inner rotor and the outer rotor1y1z1And ox2y2z2；
From a coordinate system OX1Y1Z1Transformation to the coordinate System OX2Y2Z2Is M12，M12The solving expression of (1) is as follows:
Figure FDA0003158711040000012
from the coordinate system ox1y1z1Transformation to the coordinate System OX1Y1Z1Is Mm1From the coordinate system OX2Y2Z2Transformation to coordinate system ox2y2z2Is M2m，Mm1And M2mThe solving expressions of (a) are respectively as follows:
Figure FDA0003158711040000013
Figure FDA0003158711040000014
4. a spatially intermeshing conical twin-screw compressor rotor according to claim 3 in which the epicycloid has the equation calculated as:
Figure FDA0003158711040000021
wherein R and R are the generating circle radius and the rolling circle radius of the epicycloid respectively.
Inner rotor tooth top profile sigma11The calculation equation of (a) is:
Figure FDA0003158711040000022
namely:
Figure FDA0003158711040000023
wherein, γ1The helix angle of the inner rotor, and p is the pitch of the inner rotor;
the generating circle radius R of the epicycloid changes along the axial direction, namely:
Figure FDA0003158711040000024
the radius R of the rolling circle is always equal to 1/Z of R1。
5. The interleaved shaft driven, spatially intermeshing conical twin screw compressor rotor of claim 4 wherein the internal rotor addendum profile Σ11Is determined by a coordinate transformation of the secondary coordinate system ox1y1z1Conversion to a moving coordinate system ox2y2z2Obtaining a family of conjugate surfaces Σ (Φ) of the inner rotor, and a coordinate equation of the family of conjugate surfaces Σ (Φ) of the inner rotor tooth tip profile Σ 11 is as follows:
Figure FDA0003158711040000025
namely:
Figure FDA0003158711040000026
where phi is phi1，Φ1，Φ2Satisfies the following conditions:
Figure FDA0003158711040000031
therefore, the method comprises the following steps:
Figure FDA0003158711040000032
the meshing equation is:
Figure FDA0003158711040000033
and determining a parameter phi through a meshing equation of space meshing so as to determine a conjugate curved surface of the tooth top profile of the inner rotor.
6. A spatially intermeshing conical twin-screw compressor rotor according to claim 5 in which: tooth top profile sigma of outer rotor21The equation of (a) is:
Figure FDA0003158711040000034
outer rotor gullet profile sigma22The equation of (a) is:
Figure FDA0003158711040000035
inner rotor tooth space profile sigma12The equation of (c) is:
Figure FDA0003158711040000036
7. an intermeshing tapered twin screw compressor rotor in space driven by intersecting shafts as claimed in claim 1, wherein the number of teeth Z of the outer rotor2Number of teeth Z of inner rotor1Mostly 1, helix angle γ of outer rotor1With helix angle gamma of the inner rotor2Satisfies the following conditions:
Figure FDA0003158711040000037
the inner and outer rotors rotate in the same direction, and the angular velocity omega of the inner rotor1And angular velocity of outer rotorDegree omega2Satisfies the following conditions:
Figure FDA0003158711040000038
8. a compressor, characterized by: the rotor adopts a space inner meshing conical twin-screw compressor rotor driven by an intersecting shaft according to any one of claims 1-7.
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