CN111828315A - Double-tooth claw type pump rotor molded line - Google Patents

Double-tooth claw type pump rotor molded line Download PDF

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Publication number
CN111828315A
CN111828315A CN202010720519.2A CN202010720519A CN111828315A CN 111828315 A CN111828315 A CN 111828315A CN 202010720519 A CN202010720519 A CN 202010720519A CN 111828315 A CN111828315 A CN 111828315A
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arc
point
tooth
rotor
meshing
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CN111828315B (en
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贺雪强
甘露
黄魏
孟婵君
朱小飞
苗纯正
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Cssc Southwest Equipment Research Institute Co ltd
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Cssc Southwest Equipment Research Institute Co ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • 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
    • 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)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

The invention relates to a double-tooth claw type pump rotor profile, a rotor 1 and a rotor 2 are around a rotor shaft rotation center O1And O2Symmetrical, rotor profile of the upper half of the rotor 1 comprises point-meshing cycloids a1b1Tip to tip rolling arc b1c1C, transition arc1d1Line d1e1Transition arc e1f1Pin tooth arc f1g1Arc g of contact with tooth bottom1a1The upper half of the rotor profile of the rotor 2 comprises point-meshing cycloids a2b2Round arc b with pairs of tooth bottoms2c2Arc envelope c2d2Linear envelope d2e2Arc envelope e2f2Pin tooth arc f2g2And tooth crest pair rolling arc g2a2(ii) a Point meshing cycloid a1b1And point a2Mesh, point b1Cycloidal a engaged with point2b2Meshing, tooth tip to rolling arc b1c1Arc b of contact with tooth bottom2c2Engaging, transition arc c1d1And the arc envelope c2d2Engagement, straight line d1e1And the linear envelope d2e2Engaging, transition arc e1f1And arc envelope e2f2Meshing, pin tooth arc f1g1Arc f of pin tooth2g2Meshing, bottom of tooth pair rolling arc g1a1Arc g of rolling circle with tooth top2a2Meshing; the correct meshing of the rotor pairs can be realized and the effect of gas compression is ensured.

Description

Double-tooth claw type pump rotor molded line
Technical Field
The invention relates to the technical field of mechanical engineering, in particular to a double-tooth claw type pump rotor profile.
Background
A claw pump is widely used in various fields such as food, medicine, and chemical industry as a rotary vacuum compressor, and particularly, attention has been paid to a double-tooth claw pump because of its excellent performance in a hydrogen recirculation system of a fuel cell in recent years. The claw pump has the advantages of simple structure, convenient processing, reliable operation, low noise and the like, and does not need vulnerable parts such as a suction valve, an exhaust valve and the like, so that the mechanical service life is long, and the claw pump has good application prospect in low-pressure gas delivery.
The claw type pump completes the processes of air suction, compression and air exhaust by a pair of synchronous opposite-direction double rotation of mutually meshed rotors and an 8-shaped compression cavity, so that the inherent compression performance of the claw type pump is directly determined by the molded line composition and the meshing performance of the rotors. The meshed double-tooth rotor profile is composed of multiple sections of curves, each section of curve is correspondingly meshed in the synchronous and opposite-direction rotation process, and the profile of each rotor is divided into an upper part and a lower part which are symmetrical about a rotation center. Compared with a single-tooth claw pump, the double-tooth claw pump runs more stably, and the tooth surface stress and the gas transmission capacity are better. Therefore, the rotor profile of the double-tooth claw pump which can be correctly meshed is designed to ensure gas compression, improve the volume utilization coefficient and further improve the pumping speed of the claw pump.
Disclosure of Invention
To the not enough of above-mentioned prior art, the technical problem that this patent application will solve is how to provide a double tooth claw formula pump rotor molded lines that can mesh correctly to guarantee gas compression, improve the volume utilization coefficient, further improve claw formula pump's pumping speed.
In order to solve the technical problems, the invention adopts the following technical scheme:
a double-tooth claw type pump rotor profile comprises a rotor 1 and a rotor 2, wherein the rotor 1 and the rotor 2 are both relative to the rotation center O of a rotor shaft of the rotor 1 and the rotor 21And the rotor shaft rotation center O2Symmetrically, the rotor profile of the upper half part of the rotor 1 comprises point meshing cycloids a1b1Tip to tip rolling arc b1c1C, transition arc1d1Line d1e1Transition arc e1f1Pin tooth arc f1g1Arc g of contact with tooth bottom1a1The upper half rotor profile of the rotor 2 comprises point meshing cycloids a2b2Round arc b with pairs of tooth bottoms2c2Arc envelope c2d2Linear envelope d2e2Arc envelope e2f2Pin tooth arc f2g2And tooth crest pair rolling arc g2a2；
Rotor 1 and rotor 2 each rotate around rotor shaft rotation center O1And a center O2Mid-point meshing cycloid a in synchronous and heterodromous rotation process1b1And point a2Mesh, point b1Cycloidal a engaged with point2b2Meshing, tooth tip to rolling arc b1c1Arc b of contact with tooth bottom2c2Engaging, transition arc c1d1And the arc envelope c2d2Engagement, straight line d1e1And the linear envelope d2e2Engaging, transition arc e1f1And arc envelope e2f2Meshing, pin tooth arc f1g1Arc f of pin tooth2g2Meshing, bottom of tooth pair rolling arc g1a1Arc g of rolling circle with tooth top2a2Meshing;
the point b1Point a2Is a sharp point, point a1Point c1Point d1Point e1Point f1Point g1Point b2Point c2Point d2Point e2Point f2Point g2Are common tangent points of two adjacent curves.
Wherein the pitch circle radius r of the rotor 11Radius r of pitch circle of rotor 22The pitch circle radiuses of the rotor 1 and the rotor 2 are equal, and the meshing parameter transmission ratio i is equal to r1/r21, center distance A r1+r2＝2r1。
Wherein the points mesh with cycloids a1b1And point-meshing cycloid a2b2If symmetrical about the x-axis in the same coordinate system, the center point thereof engages the cycloid a1b1And point a2Meshing; point b1Cycloidal a engaged with point2b2Meshing;
point meshing cycloid a1b1Satisfies the following formula:
xab1＝acostab-bcos2tab
yab1＝-(asintab-bsin2tab)
point meshing cycloid a2b2Satisfies the following formula:
xab2＝acostab-bcos2tab
yab2＝asintab-bsin2tab
wherein,
Figure BDA0002599810060000031
point meshing cycloid a1b1Is characterized in that the radius of the base circle is equal to the radius of the pitch circle 1, namely R ═ R1The radius of the rolling circle is equal to the radius of the pitch circle 2, i.e. r＝r2The distance a between the center of the rolling circle and the center of the base circle is R + R, A, the center distance A is known, and the swing diameter b is Rh，RhIs known wherein RhIs addendum circle radius, point meshing cycloid a2b2The parameter calculation method is the same.
Wherein, a double tooth claw type pump rotor molded lines, characterized in that, the addendum is to rolling arc b1c1With the center point at the center point O1(ii) a Round arc b of gear bottom pair rolling2c2With the center point at the center point O2；
Tooth tip to rolling arc b1c1Satisfies the following formula:
xbc1＝rbccostbc
ybc1＝rbcsintbc
round arc b of gear bottom pair rolling2c2Satisfies the following formula:
xbc2＝(A-rbc)costbc
ybc2＝(A-rbc)sintbc
wherein, tbc∈(0,α1)；α1Is formed by rolling a circular arc b on the tooth crest1c1Arc of a circle, alpha1The method comprises the following steps of (1) knowing; tooth tip to rolling arc b1c1Radius of arc rbc＝Rh。
Wherein the pair of tooth bottoms roll a circular arc g1a1With the center point at the center point O1(ii) a The tooth crest pair rolling arc g2a2With the center point at the center point O2；
Tooth bottom pair rolling arc g1a1Satisfies the following formula:
xga1＝rgacostga
yga1＝rgasintga
tooth tip pair rolling arc g2a2Satisfies the following formula:
xga2＝(A-rga)costga
yga2＝(A-rga)sintga
wherein, tga∈(π-α5，π)；α5For the tooth bottom to roll the circular arc g1a1Arc radians, known; tooth bottom pair rolling arc g1a1Radius of arc rga＝2r1-Rh。
Wherein the pin tooth arc f1g1Center of circle is O1g1Intersection point O with pitch circle 1fg(ii) a Pin tooth arc f2g2Center of circle is O2h2The intersection with the pitch circle 2;
pin tooth arc f1g1Satisfies the following formula:
xfg1＝-r1cosα5+rfgcostfg
yfg1＝r1sinα5+rfgsintfg
pin tooth arc f2g2Satisfies the following formula:
xfg2＝-r1cosα5-rfgcos(tfg+2α5)
yfg2＝r1sinα5+rfgsin(tfg+2α5)
wherein, tfg∈(-α5，α4-α5)；α4Is a pin tooth arc f1g1Arc of a circle, alpha4The method comprises the following steps of (1) knowing; pin tooth arc f1g1Radius of arc rfg＝Rh-r1。
Wherein the transition arc e1f1The center of the circle is at y1Shaft and Ofgf1Intersection point O of extension linesefThe starting point of the arc is y1On-axis, i.e. the radian of the starting point of the arc is pi/2; circular arc envelope e2f2；
Transition arc e1f1Satisfies the following formula:
xef1＝refcostef
Figure BDA0002599810060000051
circular arc envelope e2f2Satisfies the following formula:
Figure BDA0002599810060000052
Figure BDA0002599810060000053
Figure BDA0002599810060000054
wherein, tef∈(π/2,α3+ π/2); transition arc e1f1Arc radian alpha3＝∠O1OfgOef+∠OfgO1Oef＝α4+π/2-α5(ii) a From Delta O1OefOfgSine theorem and related line segment and transition arc e1f1Radius of arc refThe relationship between them is known:
Figure BDA0002599810060000055
wherein the transition arc c1d1The center of the circle is O1c1The radian of the end point of the arc is pi/2; circular arc envelope c2d2；
Transition arc c1d1Satisfies the following formula:
xcd1＝(rbc-rcd)cosα1+rcdcostcd
ycd1＝(rbc-rcd)sinα1+rcdsintcd
circular arc envelope c2d2Satisfies the following formula:
Figure BDA0002599810060000061
Figure BDA0002599810060000062
Figure BDA0002599810060000063
wherein, tcd∈(α1，π/2)；α2Is c1d1Arc radian; from Delta O1OefOfgSine theorem and line segment relation of1e1|＝|m1d1L where m1Is d1OcdExtension line and x1At the intersection of the axes, i.e.
Figure BDA0002599810060000064
Get solution of c1d1Radius of arc
Figure BDA0002599810060000065
Wherein the straight line d1e1And the transition arc c1d1And a transition arc e1f1Are all tangent, and the slope is 0; linear envelope d2e2；
Straight line d1e1Satisfies the following formula:
xde1＝tde
yde1＝n
linear envelope d2e2Satisfies the following formula:
Figure BDA0002599810060000066
Figure BDA0002599810060000071
Figure BDA0002599810060000072
wherein, tdeE (0, l); set point d1The coordinate is (m, n), then m is 0, n is | O1Oef|+refWherein by Δ O1OefOfgThe sine theorem of (a) knows that,
Figure BDA0002599810060000073
therefore, it is not only easy to use
Figure BDA0002599810060000074
d1e1Length of straight line segment
Figure BDA0002599810060000075
The invention has the beneficial effects that:
the double-tooth claw type pump rotor disclosed by the patent application has a simple profile structure and a reasonable design, can realize the correct meshing of the rotor pairs to ensure the gas compression, improves the volume utilization coefficient of the pump compared with the existing single-tooth claw type pump rotor, is more stable to operate, further improves the pumping speed of the claw type pump, and has stronger practicability; meanwhile, the method has important significance for enriching the types of the rotor profiles of the claw type pump and promoting the development of the claw type pump.
Drawings
Fig. 1 is a schematic structural diagram of a rotor profile of a double-tooth claw pump according to the present invention.
Fig. 2(a) is a schematic view of a double-tooth claw pump rotor profile meshing motion state 1 according to the present invention.
Fig. 2(b) is a schematic view of a double-tooth claw pump rotor profile meshing motion state 2 according to the present invention.
Fig. 2(c) is a schematic view of a double claw pump rotor profile meshing state 3 according to the present invention.
Fig. 2(d) is a schematic view of a double-tooth claw pump rotor profile meshing motion state 4 according to the present invention.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings. In the description of the present invention, it is to be understood that the orientation or positional relationship indicated by the orientation words such as "upper, lower" and "top, bottom" etc. are usually based on the orientation or positional relationship shown in the drawings, and are only for convenience of description and simplicity of description, and in the case of not making a reverse description, these orientation words do not indicate and imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore, should not be interpreted as limiting the scope of the present invention; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.
As shown in figure 1, the rotor profile of the double-tooth claw type pump comprises a rotor 1 and a rotor 2, wherein the rotor 1 and the rotor 2 are both relative to the rotation center O of the rotor shaft of the rotor 1 and the rotor 21And the rotor shaft rotation center O2Symmetrically, the rotor profile of the upper half part of the rotor 1 comprises point meshing cycloids a1b1Tip to tip rolling arc b1c1C, transition arc1d1Line d1e1Transition arc e1f1Pin tooth arc f1g1Arc g of contact with tooth bottom1a1The upper half rotor profile of the rotor 2 comprises point meshing cycloids a2b2Round arc b with pairs of tooth bottoms2c2Arc envelope c2d2Linear envelope d2e2Arc envelope e2f2Pin tooth arc f2g2And tooth crest pair rolling arc g2a2；
Rotor 1 and rotor 2 each rotate around rotor shaft rotation center O1And a center O2Mid-point meshing cycloid a in synchronous and heterodromous rotation process1b1And point a2Mesh, point b1Cycloidal a engaged with point2b2Meshing, tooth tip to rolling arc b1c1Arc b of contact with tooth bottom2c2Engaging, transition arc c1d1And the arc envelope c2d2Engagement, straight line d1e1And the linear envelope d2e2Engaging, transition arc e1f1And arc envelope e2f2Meshing, pin tooth arc f1g1Arc f of pin tooth2g2Meshing, bottom of tooth pair rolling arc g1a1Arc g of rolling circle with tooth top2a2Meshing;
the point b1Point a2Is a sharp point, point a1Point c1Point d1Point e1Point f1Point g1Point b2Point c2Point d2Point e2Point f2Point g2Are common tangent points of two adjacent curves.
Wherein the pitch circle radius r of the rotor 11Radius r of pitch circle of rotor 22The pitch circle radiuses of the rotor 1 and the rotor 2 are equal, and the meshing parameter transmission ratio i is equal to r1/r21, center distance A r1+r2＝2r1。
Wherein the points mesh with cycloids a1b1And point-meshing cycloid a2b2If symmetrical about the x-axis in the same coordinate system, the center point thereof engages the cycloid a1b1And point a2Mesh, point b1Cycloidal a engaged with point2b2Meshing;
point meshing cycloid a1b1Satisfies the following formula:
xab1＝acostab-bcos2tab
yab1＝-(asintab-bsin2tab)
point meshing cycloid a2b2Satisfies the following formula:
xab2＝acostab-bcos2tab
yab2＝asintab-bsin2tab
wherein,
Figure BDA0002599810060000091
point meshCycloid a1b1Is characterized in that the radius of the base circle is equal to the radius of the pitch circle 1, namely R ═ R1The radius of the rolling circle is equal to the radius of the pitch circle 2, i.e. r is equal to r2The distance a between the center of the rolling circle and the center of the base circle is R + R, A, the center distance A is known, and the swing diameter b is Rh，RhIs known wherein RhIs the addendum circle radius; point meshing cycloid a2b2The parameter calculation method is the same.
Wherein, a double tooth claw type pump rotor molded lines, characterized in that, the addendum is to rolling arc b1c1With the center point at the center point O1(ii) a Round arc b of gear bottom pair rolling2c2With the center point at the center point O2；
Tooth tip to rolling arc b1c1Satisfies the following formula:
xbc1＝rbccostbc
ybc1＝rbcsintbc
round arc b of gear bottom pair rolling2c2Satisfies the following formula:
xbc2＝(A-rbc)costbc
ybc2＝(A-rbc)sintbc
wherein, tbc∈(0,α1)；α1Is formed by rolling a circular arc b on the tooth crest1c1Arc of a circle, alpha1The method comprises the following steps of (1) knowing; tooth tip to rolling arc b1c1Radius of arc rbc＝Rh。
Wherein the pair of tooth bottoms roll a circular arc g1a1With the center point at the center point O1(ii) a The tooth crest pair rolling arc g2a2With the center point at the center point O2；
Tooth bottom pair rolling arc g1a1Satisfies the following formula:
xga1＝rgacostga
yga1＝rgasintga
tooth tip pair rolling arc g2a2Satisfies the following formula:
xga2＝(A-rga)costga
yga2＝(A-rga)sintga
wherein, tga∈(π-α5，π)；α5For the tooth bottom to roll the circular arc g1a1Arc radians, known; tooth bottom pair rolling arc g1a1Radius of arc rga＝2r1-Rh。
Wherein the pin tooth arc f1g1Center of circle is O1g1Intersection point O with pitch circle 1fg(ii) a Pin tooth arc f2g2Center of circle is O2h2The intersection with the pitch circle 2;
pin tooth arc f1g1Satisfies the following formula:
xfg1＝-r1cosα5+rfgcostfg
yfg1＝r1sinα5+rfgsintfg
pin tooth arc f2g2Satisfies the following formula:
xfg2＝-r1cosα5-rfgcos(tfg+2α5)
yfg2＝r1sinα5+rfgsin(tfg+2α5)
wherein, tfg∈(-α5，α4-α5)；α4Is a pin tooth arc f1g1Arc of a circle, alpha4The method comprises the following steps of (1) knowing; pin tooth arc f1g1Radius of arc rfg＝Rh-r1。
Wherein the transition arc e1f1The center of the circle is at y1Shaft and Ofgf1Intersection point O of extension linesefThe starting point of the arc is y1On-axis, i.e. the radian of the starting point of the arc is pi/2; circular arc envelope e2f2；
Transition arc e1f1Satisfies the following formula:
xef1＝refcostef
Figure BDA0002599810060000111
circular arc envelope e2f2Satisfies the following formula:
Figure BDA0002599810060000112
Figure BDA0002599810060000113
Figure BDA0002599810060000114
wherein, tef∈(π/2,α3+ π/2); transition arc e1f1Arc radian alpha3＝∠O1OfgOef+∠OfgO1Oef＝α4+π/2-α5(ii) a From Delta O1OefOfgSine theorem and related line segment and transition arc e1f1Radius of arc refThe relationship between them is known:
Figure BDA0002599810060000121
wherein the transition arc c1d1The center of the circle is O1c1The radian of the end point of the arc is pi/2; circular arc envelope c2d2；
Transition arc c1d1Satisfies the following formula:
xcd1＝(rbc-rcd)cosα1+rcdcostcd
ycd1＝(rbc-rcd)sinα1+rcdsintcd
circular arc envelope c2d2Satisfies the following formula:
Figure BDA0002599810060000122
Figure BDA0002599810060000123
Figure BDA0002599810060000124
wherein, tcd∈(α1，π/2)；α2Is c1d1Arc radian; from Delta O1OefOfgSine theorem and line segment relation of1e1|＝|m1d1L where m1Is d1OcdExtension line and x1At the intersection of the axes, i.e.
Figure BDA0002599810060000125
Get solution of c1d1Radius of arc
Figure BDA0002599810060000126
Wherein the straight line d1e1And the transition arc c1d1And a transition arc e1f1Are all tangent, and the slope is 0; linear envelope d2e2；
Straight line d1e1Satisfies the following formula:
xde1＝tde
yde1＝n
linear envelope d2e2Satisfies the following formula:
Figure BDA0002599810060000131
Figure BDA0002599810060000132
Figure BDA0002599810060000133
wherein, tdeE (0, l); set point d1The coordinate is (m, n), then m is 0, n is | O1Oef|+refWherein by Δ O1OefOfgThe sine theorem of (a) knows that,
Figure BDA0002599810060000134
therefore, it is not only easy to use
Figure BDA0002599810060000135
d1e1Length of straight line segment
Figure BDA0002599810060000136
Through the verification of the meshing operation states of the rotor profiles of the double-tooth claw pump under different rotation angles of fig. 2(a), fig. 2(b), fig. 2(c) and fig. 2(d), the rotor profile of the proposed double-tooth claw pump is reasonable in design, the correct meshing and the high volume utilization coefficient of the rotor pair in the operation process can be effectively guaranteed, and the performance of the claw pump is improved.
Finally, it should be noted that: various modifications and alterations of this invention may be made by those skilled in the art without departing from the spirit and scope of this invention. Thus, it is intended that the present invention cover the modifications and variations of this invention provided they come within the scope of the appended claims and their equivalents.

Claims (9)

1. A double-tooth claw type pump rotor profile is characterized by comprising a rotor 1 and a rotor 2, wherein the rotor 1 and the rotor 2 are both relative to the rotation center O of a rotor shaft of the rotor 1 and the rotor 21And the rotor shaft rotation center O2Symmetrically, the rotor profile of the upper half part of the rotor 1 comprises point meshing cycloids a1b1Tip to tip rolling arc b1c1C, transition arc1d1Line d1e1Transition arc e1f1Pin tooth arc f1g1Arc g of contact with tooth bottom1a1The upper half rotor profile of the rotor 2 comprises point meshing cycloids a2b2Round arc b with pairs of tooth bottoms2c2Arc envelope c2d2Linear envelope d2e2Arc envelope e2f2Pin tooth arc f2g2And tooth crest pair rolling arc g2a2；
Rotor 1 and rotor 2 each rotate around rotor shaft rotation center O1And a center O2Mid-point meshing cycloid a in synchronous and heterodromous rotation process1b1And point a2Mesh, point b1Cycloidal a engaged with point2b2Meshing, tooth tip to rolling arc b1c1Arc b of contact with tooth bottom2c2Engaging, transition arc c1d1And the arc envelope c2d2Engagement, straight line d1e1And the linear envelope d2e2Engaging, transition arc e1f1And arc envelope e2f2Meshing, pin tooth arc f1g1Arc f of pin tooth2g2Meshing, bottom of tooth pair rolling arc g1a1Arc g of rolling circle with tooth top2a2Meshing;
the point b1Point a2Is a sharp point, point a1Point c1Point d1Point e1Point f1Point g1Point b2Point c2Point d2Point e2Point f2Point g2Are common tangent points of two adjacent curves.
2. A double claw pump rotor profile according to claim 1, characterised in that the pitch circle radius r of the rotor 11Radius r of pitch circle of rotor 22The pitch circle radiuses of the rotor 1 and the rotor 2 are equal, and the meshing parameter transmission ratio i is equal to r1/r21, center distance A r1+r2＝2r1。
3. A double claw pump rotor profile according to claim 1, characterized in that said point meshing cycloid a1b1And point-meshing cycloid a2b2If symmetrical about the x-axis in the same coordinate system, the center point thereof engages the cycloid a1b1And point a2Meshing; point b1Cycloidal a engaged with point2b2Meshing;
point meshing cycloid a1b1Satisfies the following formula:
xab1＝acostab-bcos2tab
yab1＝-(asintab-bsin2tab)
point meshing cycloid a2b2Satisfies the following formula:
xab2＝acostab-bcos2tab
yab2＝asintab-bsin2tab
wherein,
Figure FDA0002599810050000021
point meshing cycloid a1b1Is characterized in that the radius of the base circle is equal to the radius of the pitch circle 1, namely R ═ R1The radius of the rolling circle is equal to the radius of the pitch circle 2, i.e. r is equal to r2The distance a between the center of the rolling circle and the center of the base circle is R + R, A, the center distance A is known, and the swing diameter b is Rh，RhIs known wherein RhIs addendum circle radius, point meshing cycloid a2b2The parameter calculation method is the same.
4. A double claw pump rotor profile according to claim 1, wherein the addendum is rounded to the circular arc b1c1With the center point at the center point O1(ii) a Round arc b of gear bottom pair rolling2c2With the center point at the center point O2；
Tooth top pair rollerArc b1c1Satisfies the following formula:
xbc1＝rbccostbc
ybc1＝rbcsintbc
round arc b of gear bottom pair rolling2c2Satisfies the following formula:
xbc2＝(A-rbc)costbc
ybc2＝(A-rbc)sintbc
wherein, tbc∈(0,α1)；α1Is formed by rolling a circular arc b on the tooth crest1c1Arc of a circle, alpha1The method comprises the following steps of (1) knowing; tooth tip to rolling arc b1c1Radius of arc rbc＝Rh。
5. A double dog rotor profile according to claim 1, wherein said pair of root rolling arcs g1a1With the center point at the center point O1(ii) a Tooth tip pair rolling arc g2a2With the center point at the center point O2；
Tooth bottom pair rolling arc g1a1Satisfies the following formula:
xga1＝rgacostga
yga1＝rgasintga
tooth tip pair rolling arc g2a2Satisfies the following formula:
xga2＝(A-rga)costga
yga2＝(A-rga)sintga
wherein, tga∈(π-α5，π)；α5For the tooth bottom to roll the circular arc g1a1Arc radians, known; tooth bottom pair rolling arc g1a1Radius of arc rga＝2r1-Rh。
6. A double claw pump rotor profile according to claim 1, characterised in thatIn that the pin tooth arc f1g1Center of circle is O1g1Intersection point O with pitch circle 1fg(ii) a Pin tooth arc f2g2Center of circle is O2h2The intersection with the pitch circle 2;
pin tooth arc f1g1Satisfies the following formula:
xfg1＝-r1cosα5+rfgcostfg
yfg1＝r1sinα5+rfgsintfg
pin tooth arc f2g2Satisfies the following formula:
xfg2＝-r1cosα5-rfgcos(tfg+2α5)
yfg2＝r1sinα5+rfgsin(tfg+2α5)
wherein, tfg∈(-α5，α4-α5)；α4Is a pin tooth arc f1g1Arc of a circle, alpha4The method comprises the following steps of (1) knowing; pin tooth arc f1g1Radius of arc rfg＝Rh-r1。
7. A double claw pump rotor profile according to claim 1, characterised in that the transition arc e1f1The center of the circle is at y1Shaft and Ofgf1Intersection point O of extension linesefThe starting point of the arc is y1On-axis, i.e. the radian of the starting point of the arc is pi/2; circular arc envelope e2f2；
Transition arc e1f1Satisfies the following formula:
xef1＝refcostef
Figure FDA0002599810050000041
circular arc envelope e2f2Satisfies the following formula：
Figure FDA0002599810050000042
Figure FDA0002599810050000043
Figure FDA0002599810050000044
Wherein, tef∈(π/2,α3+ π/2); transition arc e1f1Arc radian alpha3＝∠O1OfgOef+∠OfgO1Oef＝α4+π/2-α5(ii) a From Delta O1OefOfgSine theorem and related line segment and transition arc e1f1Radius of arc refThe relationship between them is known:
Figure FDA0002599810050000045
8. a double claw pump rotor profile according to claim 1, characterised in that the transition arc c1d1The center of the circle is O1c1The radian of the end point of the arc is pi/2; circular arc envelope c2d2；
Transition arc c1d1Satisfies the following formula:
xcd1＝(rbc-rcd)cosα1+rcdcostcd
ycd1＝(rbc-rcd)sinα1+rcdsintcd
circular arc envelope c2d2Satisfies the following formula:
Figure FDA0002599810050000051
Figure FDA0002599810050000052
Figure FDA0002599810050000053
wherein, tcd∈(α1，π/2)；α2Is c1d1Arc radian; from Delta O1OefOfgSine theorem and line segment relation of1e1|＝|m1d1L where m1Is d1OcdExtension line and x1At the intersection of the axes, i.e.
Figure FDA0002599810050000054
Get solution of c1d1Radius of arc
Figure FDA0002599810050000055
9. A double claw pump rotor profile according to claim 1, characterized in that the straight line d1e1And the transition arc c1d1And a transition arc e1f1Are all tangent, and the slope is 0; linear envelope d2e2；
Straight line d1e1Satisfies the following formula:
xde1＝tde
yde1＝n
linear envelope d2e2Satisfies the following formula:
Figure FDA0002599810050000061
Figure FDA0002599810050000062
Figure FDA0002599810050000063
wherein, tdeE (0, l); set point d1The coordinate is (m, n), then m is 0, n is | O1Oef|+refWherein by Δ O1OefOfgThe sine theorem of (a) knows that,
Figure FDA0002599810050000064
therefore, it is not only easy to use
Figure FDA0002599810050000065
d1e1Length of straight line segment
Figure FDA0002599810050000066
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113389725A (en) * 2021-07-22 2021-09-14 浙江湖井流体技术有限公司 High stability hydrogen circulating pump
CN114320921A (en) * 2021-12-30 2022-04-12 中船重工(重庆)西南装备研究院有限公司 Double-end claw type pump rotor molded lines
CN115559901A (en) * 2022-12-07 2023-01-03 中核第七研究设计院有限公司 Claw type vacuum pump rotor and vacuum pump

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US20030170135A1 (en) * 2002-01-25 2003-09-11 Kim Jeong Suk Rotor profile for screw compressors
CN105649981A (en) * 2016-01-05 2016-06-08 西安交通大学 Rotor profiles of double-gear compressor
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
CN111120328A (en) * 2019-12-31 2020-05-08 西安交通大学 Rotor tooth form

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US20030170135A1 (en) * 2002-01-25 2003-09-11 Kim Jeong Suk Rotor profile for screw compressors
CN105649981A (en) * 2016-01-05 2016-06-08 西安交通大学 Rotor profiles of double-gear compressor
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
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113389725A (en) * 2021-07-22 2021-09-14 浙江湖井流体技术有限公司 High stability hydrogen circulating pump
CN114320921A (en) * 2021-12-30 2022-04-12 中船重工(重庆)西南装备研究院有限公司 Double-end claw type pump rotor molded lines
CN114320921B (en) * 2021-12-30 2023-08-25 中船重工(重庆)西南装备研究院有限公司 Design method of double-head claw pump rotor molded line
CN115559901A (en) * 2022-12-07 2023-01-03 中核第七研究设计院有限公司 Claw type vacuum pump rotor and vacuum pump
CN115559901B (en) * 2022-12-07 2023-03-24 中核第七研究设计院有限公司 Claw type vacuum pump rotor and vacuum pump

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