CN112032050B - Screw pump rotor molded lines and have screw pump of this screw pump rotor molded lines - Google Patents

Screw pump rotor molded lines and have screw pump of this screw pump rotor molded lines Download PDF

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CN112032050B
CN112032050B CN202010502539.2A CN202010502539A CN112032050B CN 112032050 B CN112032050 B CN 112032050B CN 202010502539 A CN202010502539 A CN 202010502539A CN 112032050 B CN112032050 B CN 112032050B
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line segment
denotes
screw pump
coordinate
transition arc
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CN112032050A (en
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张炯焱
卢阳
王立光
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Ningbo Baosi Energy Equipment Co Ltd
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Ningbo Baosi Energy Equipment Co Ltd
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08Rotary-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
    • F04C18/12Rotary-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
    • F04C18/14Rotary-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
    • F04C18/16Rotary-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
    • GPHYSICS
    • G06COMPUTING; CALCULATING OR COUNTING
    • G06FELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00Computer-aided design [CAD]
    • G06F30/10Geometric CAD
    • G06F30/17Mechanical parametric or variational design
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/20Rotors

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  • Mechanical Engineering (AREA)
  • Rotary Pumps (AREA)

Abstract

The invention discloses a screw pump rotor profile and a screw pump with the same, wherein the rack profiles of the screw pump rotor profile are symmetrical about an axis, and a half of the rack profiles comprise a first line section AB, a first transition arc BC, a second line section CD, a second transition arc DE and a third line section EF; the other half of the rack profile is obtained by symmetrically obtaining the one half of the rack profile. The screw pump with the screw pump rotor profile and the screw pump with the screw pump rotor profile are simple in structure and easy to machine, the number of teeth and the structure of the profile can be flexibly adjusted according to working conditions, and the rotor profile is symmetrical about the center.

Description

Screw pump rotor molded lines and have screw pump of this screw pump rotor molded lines
Technical Field
The invention belongs to the field of mechanical engineering design, and particularly relates to a screw pump rotor profile and a screw pump with the same.
Background
The twin-screw pump is an oil-free rotary machine, and has the advantages of simple and compact structure, stable operation, low mechanical vibration noise, easy maintenance and the like of the twin-screw machine. The core component in the double-screw pump is a pair of meshed rotors with opposite rotation directions, the driving rotor is connected with a motor, and the driven rotor is driven to rotate in the cylinder through a synchronous gear. The rotor completes the air suction and exhaust process in the rotation process. The rotor profile is the main factor influencing the pump performance, and the development of the high-performance screw pump can effectively save energy and prolong the service life of the pump.
The design hope of the novel line suitable for the screw pump is satisfied: 1) the structure is simple and easy to process; 2) the tooth number and the structure of the molded line can be flexibly adjusted according to the working conditions; 3) the rotor profile is symmetrical about the center.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a screw pump rotor profile, the screw pump rotor profile rotor has a simple structure and is easy to process, the number of profile teeth and the structure can be flexibly adjusted according to working conditions, and the rotor profiles are symmetrical about the center.
The technical scheme of the invention is that a screw pump rotor profile with the following structure is provided, wherein the rack profiles of the screw pump rotor profile are symmetrical about an axis, and one half of the rack profiles comprise a first profile AB, a first transition arc BC, a second profile CD, a second transition arc DE and a third profile EF; the other half of the rack profile is obtained by symmetrically obtaining the one half of the rack profile.
After adopting the structure, compared with the prior art, the screw pump rotor profile has the following advantages:
the rack profile of the screw pump rotor profile comprises a straight line and an arc. The screw pump designed by the rack has the advantages that the molded line is completely conjugated, the meshing condition is met, and the tooth number combination and the tooth top gap belt length, the tooth top length, the tooth bottom length and the tooth thickness can be conveniently and flexibly changed. The rotor designed by the molded line is simple to process, and the cost is saved. The twin-screw hydrogen pump using the rotor has better air tightness and volume efficiency.
As an improvement, the center distance A of a molded line is defined, the tooth top height is rad, the tooth root height is rde, and the tooth numbers of a driving rotor and a driven rotor of the screw pump are respectively z1 and z 2; thus, the pitch circle radius of the male and female rotors is respectively r1w ═ A · z1/(z1+ z2) and r2w ═ A · z2(z1+ z2), and the total rack length l ═ 2 · pi · r1w/z1 ═ 2 · pi · r2w/z2 can be obtained; the rectangular coordinate parameter equation of the first line segment AB is as follows:
Figure GDA0003703591360000021
where xab denotes the X coordinate of the first line segment, yab denotes the Y coordinate of the first line segment, tab denotes the range of the first line segment, and l1 denotes the length of the first line segment.
As an improvement, the rectangular coordinate parameter equation of the first transition arc BC is:
Figure GDA0003703591360000022
wherein xbc denotes an X coordinate of the first transition circular arc, ybc denotes a Y coordinate of the first transition circular arc, and tbc denotes a rotation angle range of the first transition circular arc; the first transition arc is tangent to the first line segment at the point B; r represents the radius of the first transition arc, and α represents the angular range of the first transition arc; l1 denotes the length of the first line segment.
As an improvement, the rectangular coordinate parameter equation of the second line segment CD is:
Figure GDA0003703591360000023
wherein xcd represents the X coordinate of the second segment, ycd represents the Y coordinate of the second segment, and tcd represents the range of the second segment; xbc (1) represents the starting point X coordinate of the first transition circular arc, xbc (end) represents the ending point X coordinate of the first transition circular arc, and h ═ xbc (end) -xbc (1); bcd can be found from the coordinates of the end point of the second transition arc, the second line segment being tangent to the first transition arc BC at point C.
As an improvement, the right-angle parameter equation of the second transition arc DE is:
Figure GDA0003703591360000024
wherein xde denotes an X coordinate of the second transition arc, yde denotes a Y coordinate of the second transition arc, and tde denotes a rotation angle range of the second transition arc; r represents the radius of the second transition arc, and α represents the angle range of the second transition arc; l2 denotes the length of the third line segment; the second transition arc is tangent to the second line segment at point D.
As an improvement, the rectangular coordinate parameter equation of the third line segment EF is:
Figure GDA0003703591360000031
where xef denotes the X coordinate of the third line segment, yef denotes the Y coordinate of the third line segment, tef denotes the range of the third line segment, and l2 denotes the length of the third line segment.
Another technical problem to be solved by the present invention is to provide a screw pump, which has a simple structure and is easy to process, and the number of teeth and the structure of the molded lines can be flexibly adjusted according to the working conditions, and the molded lines of the rotor are symmetrical about the center.
The technical scheme is that the screw pump with the following structure is provided, and the screw pump comprises a driving rotor and a driven rotor, wherein the driving rotor is meshed with the driven rotor, and the molded line of the driving rotor or the molded line of the driven rotor is the molded line of the screw pump rotor.
After adopting the structure, compared with the prior art, the screw pump has the following advantages:
the rack profile of the screw pump rotor profile comprises a straight line and an arc. The screw pump designed by the rack has the advantages that the molded line is completely conjugated, the meshing condition is met, and the tooth number combination and the tooth top gap belt length, the tooth top length, the tooth bottom length and the tooth thickness can be conveniently and flexibly changed. The rotor designed by the molded line is simple to process, and the cost is saved. The twin-screw hydrogen pump using the rotor has better air tightness and volume efficiency.
Drawings
FIG. 1 is a schematic view of a profile of a screw pump rotor of the present invention.
FIG. 2 is an example of a screw pump 2/2 tooth rotor profile of the present invention.
FIG. 3 is an example of a screw pump 3/3 tooth rotor profile of the present invention.
FIG. 4 is an example of a screw pump 4/4 tooth rotor profile of the present invention.
Fig. 5 is an example of profile of a single-tooth rotor of a screw pump according to the invention.
Detailed Description
For a better understanding of the present application, various aspects of the present application will be described in more detail with reference to the accompanying drawings. It should be understood that the detailed description is merely illustrative of exemplary embodiments of the present application and does not limit the scope of the present application in any way.
Referring to fig. 1 to 5, the invention discloses a screw pump rotor profile, wherein a rack profile of the screw pump rotor profile is symmetrical about an axis, and a half of the rack profile comprises a first line section AB, a first transition arc BC, a second line section CD, a second transition arc DE and a third line section EF; and the other half of the rack profile is obtained by symmetrically obtaining the half of the rack profile.
The center distance A of the defined profile is 60mm, the tooth top height is rad 14mm, the tooth root height is rde 14mm, and the tooth number of the driving rotor and the driven rotor is z1 z2 2 respectively. The total rack length l is 94mm, the length l1 of the first line segment is 1.8mm, the radii r of the first transition arc and the second transition arc are 6mm, and the angle range α is 0.2 · pi.
The first line segment AB rectangular coordinate parameter equation is:
Figure GDA0003703591360000041
the first transition arc BC rectangular coordinate parameter equation is as follows:
Figure GDA0003703591360000042
the second line segment CD rectangular coordinate parameter equation is as follows:
Figure GDA0003703591360000043
the second transition arc DE right angle parameter equation is:
Figure GDA0003703591360000044
the third segment EF rectangular coordinate parameter equation is:
Figure GDA0003703591360000045
given the 2/2 rotor profile of the rotor combination, the same rack can be used to generate rotors with different tooth number combinations, as shown in fig. 3 and 4. The single tooth rotor profile can be generated by modifying the rack parameters, as shown in fig. 5.
The invention also discloses a screw pump, which comprises a driving rotor and a driven rotor, wherein the driving rotor is meshed with the driven rotor, and the molded line of the driving rotor or the molded line of the driven rotor is the molded line of the screw pump rotor.

Claims (2)

1. A screw pump rotor profile which characterized in that: the rack molded lines of the screw pump rotor molded lines are symmetrical about an axis, and one half of the rack molded lines comprise a first line section AB, a first transition arc BC, a second line section CD, a second transition arc DE and a third line section EF; the other half of the rack profile is obtained by symmetrically obtaining the half of the rack profile;
the central distance A of the molded line is defined, the tooth top height is rad, the tooth root height is rde, and the tooth number of a driving rotor and a driven rotor of the screw pump is z1 and z2 respectively;
thus, the pitch circle radii of the male and female rotors are r1w ═ a · z1/(z1+ z2) and r2w ═ a · z2(z1+ z2), respectively,
the total length l of the rack is 2. pi. r1w/z 1. 2. pi. r2w/z 2;
the rectangular coordinate parameter equation of the first line segment AB is as follows:
Figure FDA0003707480970000011
wherein, xab represents the X coordinate of the first line segment, yab represents the Y coordinate of the first line segment, tab represents the range of the first line segment, and l1 represents the length of the first line segment;
the rectangular coordinate parameter equation of the first transition arc BC is as follows:
Figure FDA0003707480970000012
wherein xbc denotes an X coordinate of the first transition circular arc, ybc denotes a Y coordinate of the first transition circular arc, and tbc denotes a rotation angle range of the first transition circular arc; the first transition arc is tangent to the first line segment at the point B; r represents the radius of the first transition arc, and α represents the angular range of the first transition arc; l1 denotes the length of the first line segment;
the rectangular coordinate parameter equation of the second line segment CD is as follows:
Figure FDA0003707480970000013
wherein xcd represents the X coordinate of the second segment, ycd represents the Y coordinate of the second segment, and tcd represents the range of the second segment; xbc (1) denotes the starting point X coordinate of the first transition circular arc, xbc (end) denotes the ending point X coordinate of the first transition circular arc, h ═ xbc (end) -xbc (1); bcd can be obtained through the terminal point coordinates of the second transition arc, and the second line segment is tangent to the first transition arc BC at the point C;
the right-angle parameter equation of the second transition arc DE is as follows:
Figure FDA0003707480970000021
wherein xde denotes an X coordinate of the second transition arc, yde denotes a Y coordinate of the second transition arc, and tde denotes a rotation angle range of the second transition arc; r represents the radius of the second transition arc, and α represents the angular range of the second transition arc; the second transition arc and the first transition arc have the same radius and angle range; l2 denotes the length of the third line segment; the second transition arc is tangent to the second line segment at point D;
the rectangular coordinate parameter equation of the third line segment EF is as follows:
Figure FDA0003707480970000022
where xef denotes the X coordinate of the third line segment, yef denotes the Y coordinate of the third line segment, tef denotes the range of the third line segment, and l2 denotes the length of the third line segment.
2. A screw pump, including a driving rotor and a driven rotor, said driving rotor engaging said driven rotor, characterized in that: the profile of the driving rotor or the profile of the driven rotor is the profile of a screw pump rotor according to claim 1.
CN202010502539.2A 2020-05-19 2020-06-05 Screw pump rotor molded lines and have screw pump of this screw pump rotor molded lines Active CN112032050B (en)

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CN114607603B (en) * 2020-12-09 2023-07-11 东北大学 Design method of screw vacuum dry pump rotor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1503488A (en) * 1974-03-06 1978-03-08 Svenska Rotor Maskiner Ab Meshing screw rotor fluid maching
CN205172940U (en) * 2015-11-03 2016-04-20 晗森机械(上海)有限公司 Tridentate helical -lobe compressor's rotor terminal surface flute profile
CN207795571U (en) * 2017-11-21 2018-08-31 山东伯仲真空设备股份有限公司 Leafy lobe pump universal line

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1503488A (en) * 1974-03-06 1978-03-08 Svenska Rotor Maskiner Ab Meshing screw rotor fluid maching
CN205172940U (en) * 2015-11-03 2016-04-20 晗森机械(上海)有限公司 Tridentate helical -lobe compressor's rotor terminal surface flute profile
CN207795571U (en) * 2017-11-21 2018-08-31 山东伯仲真空设备股份有限公司 Leafy lobe pump universal line

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
渐开线型罗茨真空泵转子型线的改进研究;李海洋 等;《机床与液压》;20111130(第22期);第37-39页 *
渐开线转子密封用宽顶的型线构造研究;李玉龙 等;《机械传动》;20190715(第7期);第172-176页 *

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