阅读说明：本技术 一种双齿爪式泵转子型线 (Double-tooth claw type pump rotor molded line ) 是由 贺雪强 甘露 黄魏 孟婵君 朱小飞 苗纯正 于 2020-07-24 设计创作，主要内容包括：本发明涉及一种双齿爪式泵转子型线,转子1和转子2关于转子轴旋转中心O<Sub>1</Sub>和O<Sub>2</Sub>对称,转子1的上半部分转子型线包括点啮合摆线a<Sub>1</Sub>b<Sub>1</Sub>、齿顶对滚圆弧b<Sub>1</Sub>c<Sub>1</Sub>、过渡圆弧c<Sub>1</Sub>d<Sub>1</Sub>、直线d<Sub>1</Sub>e<Sub>1</Sub>、过渡圆弧e<Sub>1</Sub>f<Sub>1</Sub>、销齿圆弧f<Sub>1</Sub>g<Sub>1</Sub>和齿底对滚圆弧g<Sub>1</Sub>a<Sub>1</Sub>,转子2的上半部分转子型线包括点啮合摆线a<Sub>2</Sub>b<Sub>2</Sub>、齿底对滚圆弧b<Sub>2</Sub>c<Sub>2</Sub>、圆弧包络线c<Sub>2</Sub>d<Sub>2</Sub>、直线包络线d<Sub>2</Sub>e<Sub>2</Sub>、圆弧包络线e<Sub>2</Sub>f<Sub>2</Sub>、销齿圆弧f<Sub>2</Sub>g<Sub>2</Sub>和齿顶对滚圆弧g<Sub>2</Sub>a<Sub>2</Sub>；点啮合摆线a<Sub>1</Sub>b<Sub>1</Sub>与点a<Sub>2</Sub>啮合,点b<Sub>1</Sub>与点啮合摆线a<Sub>2</Sub>b<Sub>2</Sub>啮合,齿顶对滚圆弧b<Sub>1</Sub>c<Sub>1</Sub>与齿底对滚圆弧b<Sub>2</Sub>c<Sub>2</Sub>啮合,过渡圆弧c<Sub>1</Sub>d<Sub>1</Sub>与圆弧包络线c<Sub>2</Sub>d<Sub>2</Sub>啮合,直线d<Sub>1</Sub>e<Sub>1</Sub>与直线包络线d<Sub>2</Sub>e<Sub>2</Sub>啮合,过渡圆弧e<Sub>1</Sub>f<Sub>1</Sub>和圆弧包络线e<Sub>2</Sub>f<Sub>2</Sub>啮合,销齿圆弧f<Sub>1</Sub>g<Sub>1</Sub>与销齿圆弧f<Sub>2</Sub>g<Sub>2</Sub>啮合,齿底对滚圆弧g<Sub>1</Sub>a<Sub>1</Sub>与齿顶对滚圆弧g<Sub>2</Sub>a<Sub>2</Sub>啮合；能实现转子对的正确啮合并保证气体压缩的效果。(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 O 1 And O 2 Symmetrical, rotor profile of the upper half of the rotor 1 comprises point-meshing cycloids a 1 b 1 Tip to tip rolling arc b 1 c 1 C, transition arc 1 d 1 Line d 1 e 1 Transition arc e 1 f 1 Pin tooth arc f 1 g 1 Arc g of contact with tooth bottom 1 a 1 The upper half of the rotor profile of the rotor 2 comprises point-meshing cycloids a 2 b 2 Round arc b with pairs of tooth bottoms 2 c 2 Arc envelope c 2 d 2 Linear envelope d 2 e 2 Arc envelope e 2 f 2 Pin tooth arc f 2 g 2 And tooth crest pair rolling arc g 2 a 2 (ii) a Point meshing cycloid a 1 b 1 And point a 2 Mesh, point b 1 Cycloidal a engaged with point 2 b 2 Meshing, tooth tip to rolling arc b 1 c 1 Arc b of contact with tooth bottom 2 c 2 Engaging, transition arc c 1 d 1 And the arc envelope c 2 d 2 Engagement, straight line d 1 e 1 And the linear envelope d 2 e 2 Engaging, transition arc e 1 f 1 And arc envelope e 2 f 2 Meshing, pin tooth arc f 1 g 1 Arc f of pin tooth 2 g 2 Meshing, bottom of tooth pair rolling arc g 1 a 1 Arc g of rolling circle with tooth top 2 a 2 Meshing; the correct meshing of the rotor pairs can be realized and the effect of gas compression is ensured.)

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:

x_ab1＝acost_ab-bcos2t_ab

y_ab1＝-(asint_ab-bsin2t_ab)

point meshing cycloid a₂b₂Satisfies the following formula:

x_ab2＝acost_ab-bcos2t_ab

y_ab2＝asint_ab-bsin2t_ab

wherein the content of the first and second substances,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 R_h，R_hIs known wherein R_hIs 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:

x_bc1＝r_bccost_bc

y_bc1＝r_bcsint_bc

round arc b of gear bottom pair rolling₂c₂Satisfies the following formula:

x_bc2＝(A-r_bc)cost_bc

y_bc2＝(A-r_bc)sint_bc

wherein, t_bc∈(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 r_bc＝R_h。

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:

x_ga1＝r_gacost_ga

y_ga1＝r_gasint_ga

tooth tip pair rolling arc g₂a₂Satisfies the following formula:

x_ga2＝(A-r_ga)cost_ga

y_ga2＝(A-r_ga)sint_ga

wherein, t_ga∈(π-α₅，π)；α₅For the tooth bottom to roll the circular arc g₁a₁Arc radians, known; tooth bottom pair rolling arc g₁a₁Radius of arc r_ga＝2r₁-R_h。

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 1_fg(ii) a Pin tooth arc f₂g₂Center of circle is O₂h₂The intersection with the pitch circle 2;

pin tooth arc f₁g₁Satisfies the following formula:

x_fg1＝-r₁cosα₅+r_fgcost_fg

y_fg1＝r₁sinα₅+r_fgsint_fg

pin tooth arc f₂g₂Satisfies the following formula:

x_fg2＝-r₁cosα₅-r_fgcos(t_fg+2α₅)

y_fg2＝r₁sinα₅+r_fgsin(t_fg+2α₅)

wherein, t_fg∈(-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 r_fg＝R_h-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 O_fgf₁Intersection point O of extension lines_efThe 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:

x_ef1＝r_efcost_ef

circular arc envelope e₂f₂Satisfies the following formula：

Wherein, t_ef∈(π/2,α₃+ π/2); transition arc e₁f₁Arc radian alpha₃＝∠O₁O_fgO_ef+∠O_fgO₁O_ef＝α₄+π/2-α₅(ii) a From Delta O₁O_efO_fgSine theorem and related line segment and transition arc e₁f₁Radius of arc r_efThe relationship between them is known:

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:

x_cd1＝(r_bc-r_cd)cosα₁+r_cdcost_cd

y_cd1＝(r_bc-r_cd)sinα₁+r_cdsint_cd

circular arc envelope c₂d₂Satisfies the following formula:

wherein, t_cd∈(α₁，π/2)；α₂Is c₁d₁Arc radian; from Delta O₁O_efO_fgSine theorem and line segment relation of₁e₁|＝|m₁d₁L where m₁Is d₁O_cdExtension line and x₁At the intersection of the axes, i.e.

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:

x_de1＝t_de

y_de1＝n

linear envelope d₂e₂Satisfies the following formula:

wherein, t_deE (0, l); set point d₁The coordinate is (m, n), then m is 0, n is | O₁O_ef|+r_efWherein by Δ O₁O_efO_fgThe sine theorem of (a) knows that,

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:

x_ab1＝acost_ab-bcos2t_ab

y_ab1＝-(asint_ab-bsin2t_ab)

point meshing cycloid a₂b₂Satisfies the following formula:

x_ab2＝acost_ab-bcos2t_ab

y_ab2＝asint_ab-bsin2t_ab

wherein the content of the first and second substances,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 R_h，R_hIs known wherein R_hIs 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:

x_bc1＝r_bccost_bc

y_bc1＝r_bcsint_bc

round arc b of gear bottom pair rolling₂c₂Satisfies the following formula:

x_bc2＝(A-r_bc)cost_bc

y_bc2＝(A-r_bc)sint_bc

wherein, t_bc∈(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 r_bc＝R_h。

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:

x_ga1＝r_gacost_ga

y_ga1＝r_gasint_ga

tooth tip pair rolling arc g₂a₂Satisfies the following formula:

x_ga2＝(A-r_ga)cost_ga

y_ga2＝(A-r_ga)sint_ga

wherein, t_ga∈(π-α₅，π)；α₅For the tooth bottom to roll the circular arc g₁a₁Arc radians, known; tooth bottom pair rolling arc g₁a₁Radius of arc r_ga＝2r₁-R_h。

Wherein the pin tooth arc f₁g₁Center of circle is O₁g₁Intersection point O with pitch circle 1_fg(ii) a Pin tooth arc f₂g₂Center of circle is O₂h₂The intersection with the pitch circle 2;

pin tooth arc f₁g₁Satisfies the following formula:

x_fg1＝-r₁cosα₅+r_fgcost_fg

y_fg1＝r₁sinα₅+r_fgsint_fg

pin tooth arc f₂g₂Satisfies the following formula:

x_fg2＝-r₁cosα₅-r_fgcos(t_fg+2α₅)

y_fg2＝r₁sinα₅+r_fgsin(t_fg+2α₅)

wherein, t_fg∈(-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 r_fg＝R_h-r₁。

Wherein the transition arc e₁f₁The center of the circle is at y₁Shaft and O_fgf₁Intersection point O of extension lines_efThe 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:

x_ef1＝r_efcost_ef

circular arc envelope e₂f₂Satisfies the following formula:

wherein, t_ef∈(π/2,α₃+ π/2); transition arc e₁f₁Arc radian alpha₃＝∠O₁O_fgO_ef+∠O_fgO₁O_ef＝α₄+π/2-α₅(ii) a From Delta O₁O_efO_fgSine theorem and related line segment and transition arc e₁f₁Radius of arc r_efThe relationship between them is known:

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:

x_cd1＝(r_bc-r_cd)cosα₁+r_cdcost_cd

y_cd1＝(r_bc-r_cd)sinα₁+r_cdsint_cd

circular arc envelope c₂d₂Satisfies the following formula:

wherein, t_cd∈(α₁，π/2)；α₂Is c₁d₁Arc radian; from Delta O₁O_efO_fgSine theorem and line segment relation of₁e₁|＝|m₁d₁L where m₁Is d₁O_cdExtension line and x₁At the intersection of the axes, i.e.Get solution of c₁d₁Radius of arc

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:

x_de1＝t_de

y_de1＝n

linear envelope d₂e₂Satisfies the following formula:

wherein, t_deE (0, l); set point d₁The coordinate is (m, n), then m is 0, n is | O₁O_ef|+r_efWherein by Δ O₁O_efO_fgThe sine theorem of (a) knows that,therefore, it is not only easy to used₁e₁Length of straight line segment

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:

x_ab1＝acost_ab-bcos2t_ab

y_ab1＝-(asint_ab-bsin2t_ab)

point meshing cycloid a₂b₂Satisfies the following formula:

x_ab2＝acost_ab-bcos2t_ab

y_ab2＝asint_ab-bsin2t_ab

wherein the content of the first and second substances,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 R_h，R_hIs known wherein R_hIs 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:

x_bc1＝r_bccost_bc

y_bc1＝r_bcsint_bc

round arc b of gear bottom pair rolling₂c₂Satisfies the following formula:

x_bc2＝(A-r_bc)cost_bc

y_bc2＝(A-r_bc)sint_bc

wherein, t_bc∈(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 r_bc＝R_h。

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:

x_ga1＝r_gacost_ga

y_ga1＝r_gasint_ga

tooth tip pair rolling arc g₂a₂Satisfies the following formula:

x_ga2＝(A-r_ga)cost_ga

y_ga2＝(A-r_ga)sint_ga

wherein, t_ga∈(π-α₅，π)；α₅For the tooth bottom to roll the circular arc g₁a₁Arc radians, known; tooth bottom pair rolling arc g₁a₁Radius of arc r_ga＝2r₁-R_h。

Wherein the pin tooth arc f₁g₁Center of circle is O₁g₁Intersection point O with pitch circle 1_fg(ii) a Pin tooth arc f₂g₂Center of circle is O₂h₂The intersection with the pitch circle 2;

pin tooth arc f₁g₁Satisfies the following formula:

x_fg1＝-r₁cosα₅+r_fgcost_fg

y_fg1＝r₁sinα₅+r_fgsint_fg

pin tooth arc f₂g₂Satisfies the following formula:

x_fg2＝-r₁cosα₅-r_fgcos(t_fg+2α₅)

y_fg2＝r₁sinα₅+r_fgsin(t_fg+2α₅)

wherein, t_fg∈(-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 r_fg＝R_h-r₁。

Wherein the transition arc e₁f₁The center of the circle is at y₁Shaft and O_fgf₁Intersection point O of extension lines_efThe 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:

x_ef1＝r_efcost_ef

circular arc envelope e₂f₂Satisfies the following formula:

wherein, t_ef∈(π/2,α₃+ π/2); transition arc e₁f₁Arc radian alpha₃＝∠O₁O_fgO_ef+∠O_fgO₁O_ef＝α₄+π/2-α₅(ii) a From Delta O₁O_efO_fgSine theorem and related line segment and transition arc e₁f₁Radius of arc r_efThe relationship between them is known:

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:

x_cd1＝(r_bc-r_cd)cosα₁+r_cdcost_cd

y_cd1＝(r_bc-r_cd)sinα₁+r_cdsint_cd

circular arc envelope c₂d₂Satisfies the following formula:

wherein, t_cd∈(α₁，π/2)；α₂Is c₁d₁Arc radian; from Delta O₁O_efO_fgSine theorem and line segment relation of₁e₁|＝|m₁d₁L where m₁Is d₁O_cdExtension line and x₁At the intersection of the axes, i.e.Get solution of c₁d₁Radius of arc

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:

x_de1＝t_de

y_de1＝n

linear envelope d₂e₂Satisfies the following formula:

wherein, t_deE (0, l); set point d₁The coordinate is (m, n), then m is 0, n is | O₁O_ef|+r_efWherein by Δ O₁O_efO_fgThe sine theorem of (a) knows that,

therefore, it is not only easy to used₁e₁Length of straight line segment

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.