CN210218092U - High-flow screw rotor of double-screw pump - Google Patents
High-flow screw rotor of double-screw pump Download PDFInfo
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- CN210218092U CN210218092U CN201921170472.6U CN201921170472U CN210218092U CN 210218092 U CN210218092 U CN 210218092U CN 201921170472 U CN201921170472 U CN 201921170472U CN 210218092 U CN210218092 U CN 210218092U
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Abstract
The utility model discloses a large-traffic screw rotor of two screw pumps, left end face molded lines (101) of its left screw rotor (1) are by 4 sections curves and 1 some constitution: 1 section of short-amplitude epicycloid equidistant curve, 1 section of speed-changing spiral line and 2 sections of circular arc, and acute-angle sharp points do not exist in molded lines; the right end face profile line (201) of the right screw rotor (2) consists of 10 sections of curves: 2 sections of long epicycloids, 2 sections of envelope lines of variable speed spirals and 6 sections of circular arcs, and in the anisotropic double-rotation movement with the transmission ratio of 2 to 1 of the left screw rotor (1) and the right screw rotor (2), the left end surface molded line (101) and the right end surface molded line (201) can be correctly meshed. Compared with the traditional screw rotor, the flow of the high-flow screw rotor is improved by 15-25% under the same casing size, the flow requirement under the condition of miniaturization manufacturing is met, the structure is more compact, and the sealing and stress performance is good.
Description
Technical Field
The utility model relates to a twin-screw pump, in particular to large-traffic screw rotor who is applicable to the twin-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, under the driving of a gear, a pair of screw rotors do incongruous double-rotation motion in a pump cavity, the sealed cavities continuously move from an inlet of the pump to an outlet of the pump, the processes of sucking, pressurizing and discharging media are completed, and the liquid is conveyed. 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 molded line of the end face of the screw rotor has great influence on the performance of the pump. The end face molded line of a commonly used double-screw pump consists of a cycloid and an involute, and the transmission is mostly 1 to 1. In order to improve the performance of a commonly used double-screw rotor, a Chinese patent (patent No. CN201720524780.9) provides a full-smooth double-screw pump screw rotor, the rotor adopts two sections of circular arcs and envelope lines thereof to replace a commonly used point meshing cycloid, the abrasion problem at a sharp point is relieved, curves are smoothly connected, molded lines are completely and correctly meshed, the full-smooth double-screw pump screw rotor has the advantages of good sealing performance and good stress characteristic, but the problems of low volume utilization rate and small flow rate are caused. Along with social development, the demand of small-size screw pumps is increasing day by day, and most of the traditional double-screw pumps are applied to large-flow occasions and have complex structures. How to meet the flow requirement and ensure good sealing and stress performance becomes the key of the problem in the miniaturization manufacturing.
Disclosure of Invention
The utility model discloses an improve the flow of twin-screw pump, simultaneously for richening twin-screw pump screw rotor terminal surface molded lines type, the invention provides a large-traffic screw rotor of twin-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 and the right screw rotor is 2 to 1, the flow rate is improved by 15 to 25 percent compared with the original double-screw pump under the same shell size, and the double-screw pump is simpler and more compact in structure compared with the original double-screw pump under the same flow rate condition. According to the invention, the tooth top circular arc and the tooth root circular arc in the left end face molded line are smoothly connected by adopting the speed change spiral line, the conjugate curve of the speed change spiral line is obtained under the condition that the transmission ratio is 2 to 1, the circular arc meshing short-amplitude epicycloid equidistant curve is adopted, the smooth connection of the tooth top circular arc and the tooth root circular arc is realized on the right end face molded line, and the long-amplitude epicycloid is combined to form a symmetrical structure. The double-screw pump has the advantages that 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 face of the screw rotor of the double-screw pump and improving the working performance of the screw rotor of the double-screw pump.
In order to achieve the above purpose, the utility model 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 comprise the following steps in the clockwise direction: a short-amplitude epicycloid equidistant curve AB, a point B, an addendum arc BC, a speed-changing spiral line CD and a dedendum arc DA; the variable speed spiral line CD in the left end face 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 profile line of the right screw rotor consists of 10 sections of curves, and the right end face profile line sequentially comprises the following curves in the anticlockwise direction: the first long epicycloid ab, the first tooth root arc bc, the first speed change spiral line conjugate curve cd, the first tooth crest arc de, the first tooth tip arc ef, the second long epicycloid fg, the second tooth root arc gh, the second speed change spiral line conjugate curve hi, the second tooth top arc ij and the second tooth tip arc ja; right end profile about its centre of revolution O2Is centrosymmetric, i.e. about the centre of rotation O2The right end surface profile is rotated by 180 degrees as the center and then is coincided with the right end surface profile.
According to the large-flow screw rotor of the double-screw pump, the left end face molded line and the right end face molded line can be correctly meshed in the incongruous double-rotation motion with the transmission ratio of 2 to 1 between the left screw rotor and the right screw rotor, and the meshing relationship is as follows: a point B of the left end face molded line is meshed with a first prolate epicycloid ab and a second prolate epicycloid fg of the right end face molded line; a short-amplitude epicycloid equidistant curve AB of the left end face molded line is meshed with a first tooth tip arc ef and a second tooth tip arc ja of the right end face molded line; the addendum arc BC of the left end face molded line is meshed with the first dedendum arc BC and the second dedendum arc gh of the right end face molded line; the speed-changing spiral line CD of the left end face molded line is meshed with the first speed-changing spiral line conjugate curve CD and the second speed-changing spiral line conjugate curve hi of the right end face molded line; and the tooth root circular arc DA of the left end face molded line is meshed with the first tooth top circular arc de and the second tooth top circular arc ij of the right end face molded line.
The high-flow screw rotor of the double-screw pump uses the rotation center O of the left screw rotor1Establishing a coordinate system for the origin, wherein the equation of the tooth root circular arc DA is as follows:
in the formula: t is an angle parameter, rad;
the equation of the addendum arc BC is as follows:
the equation of the short-amplitude epicycloid equidistant curve AB is as follows:
wherein:
in the formula: mABTo rotate the transformation matrix, βIs the angle of rotation,
is an initial short-amplitude epicycloid equidistant curve equation, L is the center distance of the rotor, and L is equal to R1+R4；
The equation of the speed change spiral CD is as follows:
using the rotation center O of the right screw rotor2Establishing a coordinate system for an origin, wherein the equation of the first tooth root circular arc bc is as follows:
the equation of the first addendum arc de is as follows:
the equation of the conjugate curve cd of the first speed-changing spiral line is as follows:
in the formula:
for the first intermediate variable, it is determined by the following equation:
the equation of the first prolate epicycloid ab is as follows:
the equation of the first tooth tip circular arc ef is as follows:
in the formula: xef、YefRespectively the abscissa and the ordinate of the circular arc center of the tooth tip;
the method comprises the following steps: r1Is the radius of the left pitch circle; r2Is the root circle radius; r3Is the radius of addendum circle, theta is the central angle of speed-changing spiral line CD, α is the central angle of short-amplitude epicycloid equidistant curve AB, R is the radius of first tooth tip arc, R is4Is the radius of the right pitch circle; r5Is a first tip circle radius; r6Is a first root circle radius; r4＝2R1；R5＝R3；R6＝R2；
Respectively using the first long-amplitude epicycloid ab, the first tooth root circular arc bc, the first speed-changing spiral line conjugate curve cd, the first tooth crest circular arc de and the first tooth tip circular arc ef to rotate by the center O2Rotating the center by 180 degrees to obtain a second long-amplitude epicycloid fg, a second tooth root arc gh, a second speed change spiral line conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja;
the left end face molded line (101) is axially and spirally expanded along a left spiral line to generate a left screw rotor (1); the obtained right end face molded line (102) is axially and spirally expanded along a right spiral line to generate a right screw rotor (2); wherein the pitch of the right screw rotor (2) is 2 times of the pitch of the left screw rotor (1).
The utility model has the advantages that:
① the radius of the top circle and the root circle of the two screws are equal, the transmission ratio of the left screw rotor and the right screw rotor is 2 to 1, the flow rate is improved by 15% -25% 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 compared with the original double screw pump under the same flow rate condition, and the requirement of miniaturization manufacturing is met under the premise of ensuring the flow rate.
② adopts the engagement mode of circular arc and short epicycloid equidistant curve, so that there is no sharp point in the end face profile, improving the stress characteristic of screw rotor and prolonging the service life of screw rotor.
③ enrich the profile types of the screw rotor end faces of the twin-screw pump.
Drawings
Fig. 1 is a left end surface profile view of the left screw rotor (1).
Fig. 2 is a right end face line drawing of the right screw rotor (2).
Fig. 3 is a meshing diagram of end face profiles of two screw rotors.
Fig. 4 is a timing chart of the engagement of the gear change helix with the conjugate curve of the first gear change helix.
FIG. 5 is a timing diagram of the engagement of the dedendum arc with the first addendum arc.
Fig. 6 is a timing diagram of the meshing of a short-amplitude epicycloid equidistant curve and a first tooth tip circular arc.
FIG. 7 is a timing diagram of the engagement of the addendum arc 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 view of the engagement of two screw rotors.
In the figure: 1-left screw rotor; 2-right screw rotor; 101-left end profile; 201-right end profile; r1-left pitch circle radius; r2-root circle radius; r3-addendum circle radius; r4-right pitch circle radius; r5-a first tip circle radius; r6The radius of a first tooth root circle, r, the radius of a first tooth tip arc, α, the central angle of a short-amplitude epicycloid equidistant curve, theta, the central angle of a speed-changing spiral line and β, the rotation angle.
Detailed Description
The present invention will be further explained with reference to the accompanying drawings and examples.
As shown in fig. 1, which is a left end profile diagram of the left screw rotor 1, the left end profile 101 of the left screw rotor 1 is composed of 4 segments of curves and 1 point, and the curves are sequentially in the clockwise direction: a short-amplitude epicycloid equidistant curve AB, a point B, an addendum arc BC, a speed-changing spiral line CD and a dedendum arc DA; the variable speed spiral line CD in the left end face molded line 101 is smoothly connected with the tooth top circular arcBC and a tooth root circular arc DA, and no sharp point exists; using the rotation center O of the left screw rotor 11Establishing a coordinate system for the origin, wherein the equation of the tooth root circular arc DA is as follows:
in the formula: t is an angle parameter, rad;
the equation of the addendum arc BC is as follows:
the equation of the short-amplitude epicycloid equidistant curve AB is as follows:
wherein:
in the formula: mABFor the rotation transformation matrix, β is the rotation angle,
is an initial short-amplitude epicycloid equidistant curve equation, L is the center distance of the rotor, and L is equal to R1+R4；
The equation of the speed change spiral CD is as follows:
the method comprises the following steps: r1Is the radius of the left pitch circle; r2Is the root circle radius; r3Is the radius of addendum circle, theta is the central angle of speed-changing spiral line CD, α is short-amplitude outerThe central angle of a cycloid equidistant curve AB; r is the arc radius of the first tooth tip; r4Is the radius of the right pitch circle; r5Is a first tip circle radius; r6Is a first root circle radius; r4＝2R1；R5＝R3；R6＝R2。
As shown in fig. 2, which is a right end face profile of the right screw rotor 2, a right end face profile 201 of the right screw rotor 2 is composed of 10 segments of curves, which are sequentially in the counterclockwise direction: the first long epicycloid ab, the first tooth root arc bc, the first speed change spiral line conjugate curve cd, the first tooth crest arc de, the first tooth tip arc ef, the second long epicycloid fg, the second tooth root arc gh, the second speed change spiral line conjugate curve hi, the second tooth top arc ij and the second tooth tip arc ja; the right end profile 201 is about its centre of revolution O2Is centrosymmetric, i.e. about the centre of rotation O2The center is rotated by 180 degrees and then is superposed with the self; with the rotation center O of the right screw rotor 22Establishing a coordinate system for an origin, wherein the equation of the first tooth root circular arc bc is as follows:
the equation of the first addendum arc de is as follows:
the equation of the conjugate curve cd of the first speed-changing spiral line is as follows:
in the formula:
for the first intermediate variable, it is determined by the following equation:
the equation of the first prolate epicycloid ab is as follows:
the equation of the first tooth tip circular arc ef is as follows:
in the formula: xef、YefRespectively the abscissa and the ordinate of the circular arc center of the tooth tip;
respectively using the first long-amplitude epicycloid ab, the first tooth root circular arc bc, the first speed-changing spiral line conjugate curve cd, the first tooth crest circular arc de and the first tooth tip circular arc ef to rotate by the center O2Rotating the center by 180 degrees to obtain a second long-amplitude epicycloid fg, a second tooth root arc gh, a second speed change spiral line conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja;
the method comprises the following steps: r1Is the radius of the left pitch circle; r2Is the root circle radius; r3Is the radius of addendum circle, theta is the central angle of speed-changing spiral line CD, α is the central angle of short-amplitude epicycloid equidistant curve AB, R is the radius of first tooth tip arc, R is4Is the radius of the right pitch circle; r5Is a first tip circle radius; r6Is a first root circle radius; r4＝2R1；R5＝R3；R6＝R2。
As shown in fig. 3, which is a diagram of meshing of end-face profiles of two screw rotors, the left end-face profile 101 and the right end-face profile 201 can be correctly meshed in a counter-rotating movement in which the transmission ratio of the left screw rotor 1 and the right screw rotor 2 is 2 to 1; the meshing relation is as follows: a point B of the left end face molded line 101 is meshed with a first prolate epicycloid ab and a second prolate epicycloid fg of the right end face molded line 201; a short-amplitude epicycloid equidistant curve AB of the left end face molded line 101 is meshed with a first tooth tip arc ef and a second tooth tip arc ja of the right end face molded line 201; an addendum arc BC of the left end face molded line 101 is meshed with a first dedendum arc BC and a second dedendum arc gh of the right end face molded line 201; the speed change spiral line CD of the left end face molded line 101 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 face molded line 201; the root arc DA of the left end face molded line 101 meshes with the first addendum arc de and the second addendum arc ij of the right end face molded line 201.
As shown in fig. 4, the timing diagram of the engagement of the shift helix with the first shift helix conjugate curve is shown, and the shift helix is correctly engaged with the first shift helix conjugate curve.
As shown in fig. 5, it is a timing diagram of the engagement of the dedendum arc with the first addendum arc, and the dedendum arc is correctly engaged with the first addendum arc.
As shown in fig. 6, the graph is a time chart of the meshing of the short-amplitude epicycloid equidistant curve and the first tooth tip circular arc, and the short-amplitude epicycloid equidistant curve is correctly meshed with the first tooth tip circular arc.
As shown in fig. 7, the timing diagram is the engagement of the addendum arc with the first dedendum arc, and the addendum arc and the first dedendum arc are correctly engaged.
As shown in fig. 8, which is a three-dimensional view of the left screw rotor 1, the left end face molded line 101 is axially and spirally expanded 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, which is a three-dimensional view of the right screw rotor 2, the right end face profile 102 is axially and spirally expanded along a right spiral line to generate the right screw rotor 2, and the right screw rotor 2 is a double-head fixed-pitch screw.
As shown in FIG. 10, the two screw rotors are meshed, wherein 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 meshing in the incongruous double-rotation motion with the transmission ratio of 2 to 1, and no interference or meshing part exists.
Although the present invention has been described with reference to the accompanying drawings, it is not intended to limit the scope of the present invention, and those skilled in the art should understand that various modifications or variations that can be made by those skilled in the art without inventive work are still within the scope 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 the curves and the points are sequentially in the clockwise direction: a short-amplitude epicycloid equidistant curve AB, a point B, an addendum arc BC, a speed-changing spiral line CD and a dedendum arc DA; the variable speed spiral line CD in the left end face molded line (101) 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 profile line (201) of the right screw rotor (2) consists of 10 sections of curves, and the curves are sequentially in the anticlockwise direction: the first long epicycloid ab, the first tooth root arc bc, the first speed change spiral line conjugate curve cd, the first tooth crest arc de, the first tooth tip arc ef, the second long epicycloid fg, the second tooth root arc gh, the second speed change spiral line conjugate curve hi, the second tooth top arc ij and the second tooth tip arc ja; the right end face profile (201) is about the centre of revolution O thereof2Is centrosymmetric, i.e. about the centre of rotation O2The right end face molded line (201) is rotated by 180 degrees as a center and then is coincided with the right end face molded line.
2. A high flow screw rotor for a twin screw pump according to claim 1, wherein: the left end face molded line (101) and the right end face molded line (201) can be correctly meshed in the incongruous 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: a point B of the left end face molded line (101) is meshed with a first prolate epicycloid ab and a second prolate epicycloid fg of the right end face molded line (201); a short-amplitude epicycloid equidistant curve AB of the left end face molded line (101) is meshed with a first tooth tip arc ef and a second tooth tip arc ja of the right end face molded line (201); an addendum arc BC of the left end face molded line (101) is meshed with a first dedendum arc BC and a second dedendum arc gh of the right end face molded line (201); the speed change spiral line CD of the left end face 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 face molded line (201); the tooth root circular arc DA of the left end face molded line (101) is meshed with the first tooth top circular arc de and the second tooth top circular arc ij of the right end face molded line (201).
3. A high flow screw rotor for a twin screw pump according to claim 1, characterized by: using the rotation center O of the left screw rotor (1)1Establishing a coordinate system for the origin, wherein the equation of the tooth root circular arc DA is as follows:
in the formula: t is an angle parameter, rad;
the equation of the addendum arc BC is as follows:
the equation of the short-amplitude epicycloid equidistant curve AB is as follows:
wherein:
in the formula: mABFor the rotation transformation matrix, β is the rotation angle,
is an initial short-amplitude epicycloid equidistant curve equation, L is the center distance of the rotor, and L is equal to R1+R4；
The equation of the speed change spiral CD is as follows:
using the rotation center O of the right screw rotor (2)2Establishing a coordinate system for an origin, wherein the equation of the first tooth root circular arc bc is as follows:
the equation of the first addendum arc de is as follows:
the equation of the conjugate curve cd of the first speed-changing spiral line is as follows:
in the formula:
for the first intermediate variable, it is determined by the following equation:
the equation of the first prolate epicycloid ab is as follows:
the equation of the first tooth tip circular arc ef is as follows:
in the formula: xef、YefRespectively the abscissa and the ordinate of the circular arc center of the tooth tip;
the above：R1Is the radius of the left pitch circle; r2Is the root circle radius; r3Is the radius of addendum circle, theta is the central angle of speed-changing spiral line CD, α is the central angle of short-amplitude epicycloid equidistant curve AB, R is the radius of first tooth tip arc, R is4Is the radius of the right pitch circle; r5Is a first tip circle radius; r6Is a first root circle radius; r4＝2R1；R5＝R3；R6＝R2；
Respectively using the first long-amplitude epicycloid ab, the first tooth root circular arc bc, the first speed-changing spiral line conjugate curve cd, the first tooth crest circular arc de and the first tooth tip circular arc ef to rotate by the center O2Rotating the center by 180 degrees to obtain a second long-amplitude epicycloid fg, a second tooth root arc gh, a second speed change spiral line conjugate curve hi, a second tooth top arc ij and a second tooth tip arc ja;
the left end face molded line (101) is axially and spirally expanded along a left spiral line to generate a left screw rotor (1); the obtained right end face molded line (201) is axially and spirally expanded along a right spiral line to generate a right screw rotor (2); wherein the pitch of the right screw rotor (2) is 2 times of the pitch of the left screw rotor (1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921170472.6U CN210218092U (en) | 2019-07-24 | 2019-07-24 | High-flow screw rotor of double-screw pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921170472.6U CN210218092U (en) | 2019-07-24 | 2019-07-24 | High-flow screw rotor of double-screw pump |
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| Publication Number | Publication Date |
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| CN210218092U true CN210218092U (en) | 2020-03-31 |
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| CN201921170472.6U Withdrawn - After Issue CN210218092U (en) | 2019-07-24 | 2019-07-24 | High-flow screw rotor of double-screw pump |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110242561A (en) * | 2019-07-24 | 2019-09-17 | 中国石油大学(华东) | A kind of the big flow screw rotor and its design method of Quimby pump |
-
2019
- 2019-07-24 CN CN201921170472.6U patent/CN210218092U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110242561A (en) * | 2019-07-24 | 2019-09-17 | 中国石油大学(华东) | A kind of the big flow screw rotor and its design method of Quimby pump |
| CN110242561B (en) * | 2019-07-24 | 2023-10-24 | 中国石油大学(华东) | High-flow screw rotor of double-screw pump and design method thereof |
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