CN110242561B - High-flow screw rotor of double-screw pump and design method thereof - Google Patents

High-flow screw rotor of double-screw pump and design method thereof Download PDF

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Publication number
CN110242561B
CN110242561B CN201910670831.2A CN201910670831A CN110242561B CN 110242561 B CN110242561 B CN 110242561B CN 201910670831 A CN201910670831 A CN 201910670831A CN 110242561 B CN110242561 B CN 110242561B
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arc
end surface
screw rotor
molded line
tooth
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CN110242561A (en
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王君
赵胜
李祥艳
奚周瑾
李雪琴
李宏鑫
陈少华
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China University of Petroleum East China
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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps 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
    • F04C2/16—Rotary-piston machines or pumps 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
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • 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

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • General Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Theoretical Computer Science (AREA)
  • Computational Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Mathematical Analysis (AREA)
  • Mathematical Optimization (AREA)
  • Pure & Applied Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
  • Rotary Pumps (AREA)

Abstract

The invention discloses a high-flow screw rotor of a double-screw pump and a design method thereof, wherein a left end surface molded line (101) of a left screw rotor (1) consists of 4 sections of curves and 1 point: 1 section of short epicycloidal equidistant curve, 1 section of variable speed spiral line and 2 sections of circular arcs, wherein no acute sharp point exists in the molded line; the right end surface molded line (201) of the right screw rotor (2) consists of 10 sections of curves: 2 sections of long epicycloids, 2 sections of variable speed spiral enveloping lines and 6 sections of circular arcs, and in the different-direction double-rotation motion with the transmission ratio of the left screw rotor (1) to the right screw rotor (2) being 2 to 1, the left end surface molded line (101) and the right end surface molded line (201) can be meshed correctly. Compared with the traditional screw rotor, the high-flow screw rotor has the advantages that the flow is improved by 15% -25% under the same shell size, the flow requirement under miniaturized manufacturing is met, the structure is more compact, and the sealing and stress performances are good.

Description

High-flow screw rotor of double-screw pump and design method thereof
Technical Field
The invention relates to a double-screw pump, in particular to a high-flow screw rotor suitable for the double-screw pump.
Background
The double-screw pump is a positive displacement liquid pump, a plurality of closed cavities are formed in a pump body through two mutually meshed screw rotors, a pair of screw rotors are driven by a gear to do different-direction double-rotation motion in the pump cavity, the closed cavities continuously move from an inlet of the pump to an outlet of the pump, the processes of medium suction, pressurization and discharge are completed, and liquid delivery is realized. The double-screw pump has the remarkable characteristics of no pulsation, small vibration, high reliability, good stability and strong self-priming capability, and is widely applied to the fields of oil fields, shipbuilding industry, petrochemical industry and food industry at present.
In the design and manufacturing process of the screw pump, the design of the end surface molded line of the screw rotor has a great influence on the performance of the pump. The end surface molded lines of the common double screw pump consist of cycloids and involute curves, and most of the molded lines are driven by 1 to 1. In order to improve the performance of the common double-screw rotor, chinese patent (patent number CN 201720524780.9) proposes a full-smooth double-screw pump screw rotor, which adopts two sections of circular arcs and envelope curves thereof to replace common point meshing cycloid, so that the abrasion problem at the sharp point is relieved, smooth connection is formed between curves, the molded lines are completely and correctly meshed, and the double-screw pump screw rotor has the advantages of good sealing performance and good stress characteristic, but causes the problems of low volume utilization rate and small flow. With the social development, the demand for small-sized screw pumps is increasing, and most of traditional double-screw pumps are applied to high-flow occasions and have complex structures. How to meet the flow requirements and ensure good sealing and stressing properties at the time of miniaturized manufacturing is critical.
Disclosure of Invention
The invention provides a high-flow screw rotor of a double-screw pump for improving the flow of the double-screw pump and enriching the types of end surface molded lines of the screw rotor of the double-screw pump. The radii of the top circle and the root circle of the two screws are equal, the transmission ratio of the left screw rotor to the right screw rotor is 2 to 1, the flow is improved by 15 to 25 percent compared with the original double-screw pump under the same shell size, and the structure is simpler and more compact than the original double-screw pump under the same flow. The gear change spiral line is adopted to be connected with the tooth top arc and the tooth root arc in the left end face molded line smoothly, the conjugate curve of the gear change spiral line is obtained under the condition that the transmission ratio is 2 to 1, the arc is adopted to mesh with the short-amplitude epicycloid equidistant curve, the smooth connection of the tooth top arc and the tooth root arc is realized on the right end face molded line, and the long-amplitude epicycloid is combined to form a symmetrical structure. The flow of the double-screw pump is increased, the stress condition of the screw rotor is improved, the performance of the double-screw pump is improved, and the double-screw pump has important significance for enriching the types of molded lines of the end faces of the screw rotor of the double-screw pump and improving the working performance of the double-screw pump.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
a high flow screw rotor for a twin screw pump comprising: a left screw rotor and a right screw rotor; the left end face molded line of the left screw rotor consists of 4 sections of curves and 1 point, and the left end face molded line sequentially comprises the following parts in the clockwise direction: a short epicycloidal equidistant curve AB, a point B, an addendum arc BC, a variable speed spiral line CD and a dedendum arc DA; the variable speed spiral line CD in the left end surface molded line is smoothly connected with the tooth top arc BC and the tooth root arc DA, and no acute angle sharp point exists;
the right end face molded line of the right screw rotor consists of 10 sections of curves, and the molded line comprises the following components in turn in the anticlockwise direction: the first long-amplitude epicycloid ab, a first tooth root arc bc, a first speed change spiral conjugate curve cd, a first tooth top arc de, a first tooth tip arc ef, a second long-amplitude epicycloid fg, a second tooth root arc gh, a second speed change spiral conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja; right-hand face profile about its centre of rotation O 2 Is centrosymmetric, i.e. about the centre of rotation O 2 The right end surface molded line is rotated 180 degrees for the center and then coincides with the right end surface molded line.
The high-flow screw rotor of the double-screw pump can realize correct meshing in the different-direction double-rotation motion with the transmission ratio of 2 to 1 of the left screw rotor and the right screw rotor, and the meshing relationship is as follows: the point B of the left end surface molded line is meshed with the first long-amplitude epicycloid ab and the second long-amplitude epicycloid fg of the right end surface molded line; the short epicycloidal equidistant curve AB of the left end surface molded line is meshed with the first tooth tip arc ef and the second tooth tip arc ja of the right end surface molded line; the tooth top arc BC of the left end surface molded line is meshed with the first tooth root arc BC and the second tooth root arc gh of the right end surface molded line; the speed change spiral line CD of the left end surface molded line is meshed with the first speed change spiral line conjugate curve CD and the second speed change spiral line conjugate curve hi of the right end surface molded line; the tooth root arc DA of the left end surface molded line is meshed with the first tooth top arc de and the second tooth top arc ij of the right end surface molded line.
The design method of the high-flow screw rotor of the double-screw pump comprises the following steps:
1) The following parameters were given: left pitch radius R 1 The method comprises the steps of carrying out a first treatment on the surface of the Radius of root circle R 2 The method comprises the steps of carrying out a first treatment on the surface of the Radius of addendum circle R 3 The method comprises the steps of carrying out a first treatment on the surface of the The center angle theta of the variable speed spiral line CD; the center angle alpha of the short epicycloidal equidistant curve AB; first tooth pointThe radius r of the arc; the right pitch circle radius R is obtained according to the following relation 4 Radius of first addendum circle R 5 Radius of first root circle R 6 ：R 4 ＝2R 1 ；R 5 ＝R 3 ；R 6 ＝R 2 ；
2) With centre of rotation O of left screw rotor 1 Establishing a coordinate system for an origin, and determining a tooth root circular arc DA according to the following equation:
wherein: t is an angle parameter, rad;
3) The addendum arc BC is determined according to the following equation:
4) The short-amplitude epicycloidal equidistant curve AB is determined according to the following equation:
wherein:
wherein: m is M AB For rotation of the transformation matrix, beta is the rotation angle,is an initial short-amplitude epicycloidal equidistant curve equation, L is the rotor center distance, and L=R 1 +R 4 ；
5) The variable speed spiral CD is determined as follows:
6) With centre of rotation O of right screw rotor 2 Establishing a coordinate system for the origin, and determining a first root arc bc according to the following equation:
7) The first addendum arc de is determined according to the following equation:
8) The first variable speed helix conjugate curve cd is determined according to the following equation:
wherein:for the first intermediate variable, it is determined by the following equation:
9) The first long epicycloidal ab is determined according to the following equation:
10 Determining a first tip arc ef) according to the following equation:
wherein: x is X ef 、Y ef Respectively the abscissa and the ordinate of the circle center of the arc of the tooth tip;
11 Respectively using the first long epicycloid ab, the first tooth root arc bc, the first variable speed spiral conjugate curve cd, the first tooth top arc de and the first tooth tip arc ef as a rotation center O 2 The second long epicycloid fg, a second tooth root arc gh, a second variable speed spiral conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja are obtained for rotating the center by 180 degrees;
12 The left end surface molded line is axially and spirally unfolded along a left spiral line to generate a left screw rotor; the obtained right end surface molded line is axially and spirally unfolded along a right spiral line to generate a right screw rotor; wherein the pitch of the right screw rotor is 2 times that of the left screw rotor.
The beneficial effects of the invention are as follows:
(1) the radii of the top circles and the root circles of the two screws are equal, the transmission ratio of the left screw rotor to the right screw rotor is 2 to 1, the flow is improved by 15 to 25 percent compared with the original double-screw pump with the transmission ratio of 1 to 1 under the same shell size, the structure is simpler and more compact than the original double-screw pump under the same flow, and the miniaturized manufacturing requirement is met under the premise of ensuring the flow.
(2) The meshing mode of the arc and the short epicycloidal curve is adopted, so that an acute sharp point does not exist in the end surface molded line, the stress characteristic of the screw rotor is improved, and the service life of the screw rotor is prolonged.
(3) Enriches the types of molded lines of the end faces of the screw rotors of the double-screw pump.
Drawings
Fig. 1 is a left end surface profile of the left screw rotor (1).
Fig. 2 is a right end surface profile of the right screw rotor (2).
Fig. 3 is a line mesh of two screw rotors at the end faces.
Fig. 4 is a graph of moments when the variable speed spiral is meshed with the conjugate curve of the first variable speed spiral.
Fig. 5 is a timing chart when a root arc is engaged with a first tip arc.
Fig. 6 is a graph of the moment when a short epicycloidal equidistant curve engages a circular arc of the first tooth tip.
Fig. 7 is a timing chart when the addendum arc is meshed with the first dedendum arc.
Fig. 8 is a three-dimensional view of the left screw rotor (1).
Fig. 9 is a three-dimensional view of the right screw rotor (2).
Fig. 10 is a diagram of a two screw rotor engagement.
In the figure: 1-left screw rotor; 2-right screw rotor; 101-left end face molded line; 201-right end face molded line; r is R 1 -left pitch radius; r is R 2 -root circle radius; r is R 3 -addendum circle radius; r is R 4 -right pitch radius; r is R 5 -a first addendum circle radius; r is R 6 -a first root circle radius; r—the radius of the arc of the first tooth tip; alpha-short epicycloidal equidistant curve central angle; θ—variable speed helix central angle; beta-rotation angle.
Detailed Description
The invention will be further described with reference to the drawings and examples.
As shown in fig. 1, a left end surface profile of the left screw rotor 1 is shown, wherein a left end surface profile 101 of the left screw rotor 1 is composed of 4 sections of curves and 1 point, and the following steps are sequentially performed in a clockwise direction: a short epicycloidal equidistant curve AB, a point B, an addendum arc BC, a variable speed spiral line CD and a dedendum arc DA; the variable speed spiral line CD in the left end surface molded line 101 is connected with the tooth top arc BC and the tooth root arc DA smoothly, and no acute sharp point exists; the molded line is formed as follows:
1) The following parameters were given: left pitch radius R 1 The method comprises the steps of carrying out a first treatment on the surface of the Radius of root circle R 2 The method comprises the steps of carrying out a first treatment on the surface of the Radius of addendum circle R 3 The method comprises the steps of carrying out a first treatment on the surface of the The center angle theta of the variable speed spiral line CD; the center angle alpha of the short epicycloidal equidistant curve AB; the arc radius r of the first tooth tip; the right pitch circle radius R is obtained according to the following relation 4 Radius of first addendum circle R 5 Radius of first root circle R 6 ：R 4 ＝2R 1 ；R 5 ＝R 3 ；R 6 ＝R 2 ；
2) With the rotation center O of the left screw rotor 1 1 Establishing a coordinate system for the origin, as followsCheng Queding root arc DA:
wherein: t is an angle parameter, rad;
3) The addendum arc BC is determined according to the following equation:
4) The short-amplitude epicycloidal equidistant curve AB is determined according to the following equation:
wherein:
wherein: m is M AB For rotation of the transformation matrix, beta is the rotation angle,is an initial short-amplitude epicycloidal equidistant curve equation, L is the rotor center distance, and L=R 1 +R 4 ；
5) The variable speed spiral CD is determined as follows:
as shown in fig. 2, a right end surface profile of the right screw rotor 2 is shown, and a right end surface profile 201 of the right screw rotor 2 is formed by 10 sections of curves, which are sequentially in a counterclockwise direction:the first long-amplitude epicycloid ab, a first tooth root arc bc, a first speed change spiral conjugate curve cd, a first tooth top arc de, a first tooth tip arc ef, a second long-amplitude epicycloid fg, a second tooth root arc gh, a second speed change spiral conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja; right end surface profile 201 is about its center of revolution O 2 Is centrosymmetric, i.e. about the centre of rotation O 2 The center is rotated 180 degrees and then coincides with the center; the molded line is formed as follows:
1) The following parameters were given: left pitch radius R 1 The method comprises the steps of carrying out a first treatment on the surface of the Radius of root circle R 2 The method comprises the steps of carrying out a first treatment on the surface of the Radius of addendum circle R 3 The method comprises the steps of carrying out a first treatment on the surface of the The center angle theta of the variable speed spiral line CD; the center angle alpha of the short epicycloidal equidistant curve AB; the arc radius r of the first tooth tip; the right pitch circle radius R is obtained according to the following relation 4 Radius of first addendum circle R 5 Radius of first root circle R 6 ：R 4 ＝2R 1 ；R 5 ＝R 3 ；R 6 ＝R 2 ；
2) With the rotation center O of the right screw rotor 2 2 Establishing a coordinate system for the origin, and determining a first root arc bc according to the following equation:
3) The first addendum arc de is determined according to the following equation:
4) The first variable speed helix conjugate curve cd is determined according to the following equation:
wherein:for the first intermediate variable, it is determined by the following equation:
5) The first long epicycloidal ab is determined according to the following equation:
6) The first tooth tip arc ef is determined according to the following equation:
wherein: x is X ef 、Y ef Respectively the abscissa and the ordinate of the circle center of the arc of the tooth tip;
7) The first long epicycloid ab, the first tooth root arc bc, the first variable speed spiral conjugate curve cd, the first tooth top arc de and the first tooth tip arc ef are respectively set at the rotation center O 2 The second long epicycloid fg, a second tooth root arc gh, a second variable speed spiral conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja are obtained for rotating the center by 180 degrees;
as shown in fig. 3, which is a two-screw rotor end surface molded line meshing diagram, the left end surface molded line 101 and the right end surface molded line 201 can realize correct meshing in the different-direction double-rotation motion with the transmission ratio of 2 to 1 of the left screw rotor 1 and the right screw rotor 2; the meshing relationship is as follows: the point B of the left end surface molded line 101 is meshed with a first long-amplitude epicycloid ab and a second long-amplitude epicycloid fg of the right end surface molded line 201; the short epicycloidal equidistant curve AB of the left end surface molded line 101 is meshed with the first tooth tip arc ef and the second tooth tip arc ja of the right end surface molded line 201; the tooth top arc BC of the left end surface molded line 101 is meshed with the first tooth root arc BC and the second tooth root arc gh of the right end surface molded line 201; the speed change spiral line CD of the left end surface molded line 101 is meshed with a first speed change spiral line conjugate curve CD and a second speed change spiral line conjugate curve hi of the right end surface molded line 201; the root arc DA of the left face line 101 meshes with the first addendum arc de and the second addendum arc ij of the right face line 201.
As shown in fig. 4, to illustrate the timing of the meshing of the shift helix with the first shift helix conjugate curve, the shift helix is properly meshed with the first shift helix conjugate curve.
As shown in fig. 5, the tooth root arc is drawn to mesh with the first tooth tip arc, and the tooth root arc is properly meshed with the first tooth tip arc.
As shown in fig. 6, the short epicycloidal equidistant curve is meshed with the first tooth point arc correctly.
As shown in fig. 7, the tooth top arc is meshed with the first tooth root arc to form a pattern at the time of meshing the tooth top arc with the first tooth root arc.
As shown in fig. 8, a three-dimensional view of the left screw rotor 1 is shown, the left end surface molded line 101 is axially and spirally unfolded along a left spiral line to generate the left screw rotor 1, and the left screw rotor 1 is a single-head fixed-pitch screw.
As shown in fig. 9, a three-dimensional view of the right screw rotor 2 is shown, the obtained right end surface profile 102 is axially and spirally unfolded along a right spiral line to generate the right screw rotor 2, and the right screw rotor 2 is a double-end fixed-pitch screw.
As shown in fig. 10, there is a two screw rotor meshing diagram in which the pitch of the right screw rotor 2 is 2 times the pitch of the left screw rotor 1. The two screw rotors can realize correct engagement in the different-direction double-rotation motion with the transmission ratio of 2 to 1, and no interference or no engagement part exists.
While the foregoing description of the embodiments of the present invention has been presented in conjunction with the drawings, it should be understood that it is not intended to limit the scope of the invention, but rather, it is intended to cover all modifications or variations within the scope of the invention as defined by the claims of the present invention.

Claims (3)

1. A high flow screw rotor for a twin screw pump comprising: a left screw rotor (1) and a right screw rotor (2); the method is characterized in that: the left end face molded line (101) of the left screw rotor (1) consists of 4 sections of curves and 1 point, and is sequentially as follows in the clockwise direction: a short epicycloidal equidistant curve AB, a point B, an addendum arc BC, a variable speed spiral line CD and a dedendum arc DA; the variable speed spiral line CD in the left end surface molded line (101) is smoothly connected with the tooth top arc BC and the tooth root arc DA, and no acute sharp point exists;
the right end face molded line (201) of the right screw rotor (2) consists of 10 sections of curves, and the curves are sequentially as follows in the anticlockwise direction: the first long-amplitude epicycloid ab, a first tooth root arc bc, a first speed change spiral conjugate curve cd, a first tooth top arc de, a first tooth tip arc ef, a second long-amplitude epicycloid fg, a second tooth root arc gh, a second speed change spiral conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja; right end surface profile (201) about its centre of rotation O 2 Is centrosymmetric, i.e. about the centre of rotation O 2 The right end surface molded line (201) is rotated 180 degrees for the center and then coincides with the right end surface molded line.
2. A high flow screw rotor for a twin screw pump as defined in claim 1, wherein: the left end surface molded line (101) and the right end surface molded line (201) can realize correct meshing in the different-direction double-rotation motion with the transmission ratio of 2 to 1 of the left screw rotor (1) and the right screw rotor (2), and the meshing relationship is as follows: the point B of the left end surface molded line (101) is meshed with a first long-amplitude epicycloid ab and a second long-amplitude epicycloid fg of the right end surface molded line (201); the short epicycloidal equidistant curve AB of the left end surface molded line (101) is meshed with the first tooth tip arc ef and the second tooth tip arc ja of the right end surface molded line (201); the tooth top arc BC of the left end surface molded line (101) is meshed with the first tooth root arc BC and the second tooth root arc gh of the right end surface molded line (201); the speed change spiral line CD of the left end surface molded line (101) is meshed with a first speed change spiral line conjugate curve CD and a second speed change spiral line conjugate curve hi of the right end surface molded line (201); the tooth root arc DA of the left end surface molded line (101) is meshed with the first tooth top arc de and the second tooth top arc ij of the right end surface molded line (201).
3. A method of designing a high flow screw rotor for a twin screw pump as defined in claim 1, wherein: the method comprises the following steps:
1) The following parameters were given: left pitch radius R 1 The method comprises the steps of carrying out a first treatment on the surface of the Radius of root circle R 2 The method comprises the steps of carrying out a first treatment on the surface of the Radius of addendum circle R 3 The method comprises the steps of carrying out a first treatment on the surface of the The center angle theta of the variable speed spiral line CD; the center angle alpha of the short epicycloidal equidistant curve AB; the arc radius r of the first tooth tip; the right pitch circle radius R is obtained according to the following relation 4 Radius of first addendum circle R 5 Radius of first root circle R 6 ：R 4 ＝2R 1 ；R 5 ＝R 3 ；R 6 ＝R 2 ；
2) With the rotation center O of the left screw rotor (1) 1 Establishing a coordinate system for an origin, and determining a tooth root circular arc DA according to the following equation:
wherein: t is an angle parameter, rad;
3) The addendum arc BC is determined according to the following equation:
4) The short-amplitude epicycloidal equidistant curve AB is determined according to the following equation:
wherein:
wherein: m is M AB To rotate the transformation matrix betaAs the rotation angle of the rotation,is an initial short-amplitude epicycloidal equidistant curve equation, L is the rotor center distance, and L=R 1 +R 4 ；
5) The variable speed spiral CD is determined as follows:
6) With the rotation center O of the right screw rotor (2) 2 Establishing a coordinate system for the origin, and determining a first root arc bc according to the following equation:
7) The first addendum arc de is determined according to the following equation:
8) The first variable speed helix conjugate curve cd is determined according to the following equation:
wherein:for the first intermediate variable, it is determined by the following equation:
9) The first long epicycloidal ab is determined according to the following equation:
10 Determining a first tip arc ef) according to the following equation:
wherein: x is X ef 、Y ef Respectively the abscissa and the ordinate of the circle center of the arc of the tooth tip;
11 Respectively using the first long epicycloid ab, the first tooth root arc bc, the first variable speed spiral conjugate curve cd, the first tooth top arc de and the first tooth tip arc ef as a rotation center O 2 The second long epicycloid fg, a second tooth root arc gh, a second variable speed spiral conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja are obtained for rotating the center by 180 degrees;
12 The left end surface molded line (101) is axially and spirally unfolded along a left spiral line to generate a left screw rotor (1); the obtained right end surface molded line (201) is axially spirally unfolded along a right spiral line to generate a right screw rotor (2); wherein the screw pitch of the right screw rotor (2) is 2 times of the screw pitch of the left screw rotor (1).
CN201910670831.2A 2019-07-24 2019-07-24 High-flow screw rotor of double-screw pump and design method thereof Active CN110242561B (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001073959A (en) * 1999-08-31 2001-03-21 Shigeyoshi Osada Screw pump
CN1743678A (en) * 2005-09-30 2006-03-08 浙江大学 Screw profile for high flow high-pressure dual-screw pump
CN205388011U (en) * 2015-11-09 2016-07-20 中国石油大学(华东) Screw rotor of no acute angle cusp and twin screw vacuum pump thereof
CN108930650A (en) * 2018-07-02 2018-12-04 西安交通大学 A kind of double end claw pump rotor and its molded line
CN210218092U (en) * 2019-07-24 2020-03-31 中国石油大学(华东) High-flow screw rotor of double-screw pump

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001073959A (en) * 1999-08-31 2001-03-21 Shigeyoshi Osada Screw pump
CN1743678A (en) * 2005-09-30 2006-03-08 浙江大学 Screw profile for high flow high-pressure dual-screw pump
CN205388011U (en) * 2015-11-09 2016-07-20 中国石油大学(华东) Screw rotor of no acute angle cusp and twin screw vacuum pump thereof
CN108930650A (en) * 2018-07-02 2018-12-04 西安交通大学 A kind of double end claw pump rotor and its molded line
CN210218092U (en) * 2019-07-24 2020-03-31 中国石油大学(华东) High-flow screw rotor of double-screw pump

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