CN102808772B - Single-head varying pitch screw rotor with uniform tooth top width - Google Patents

Abstract

A single-head varying pitch screw rotor with uniform tooth top width consists of a tooth root face, an oblique tooth face, a tooth top face and a transitional tooth face that are sequentially connected, wherein a rotor helical lead is linearly increased from an exhaust end to a suction end along with a helical angle of spread, so that the axial width of the oblique tooth face is gradually increased correspondingly, and the width of the tooth top face remains unchanged. Compared with the existing single-head varying pitch screw rotors, the molded line rotor has a relatively small tooth top face width at the suction end, so that a bigger interstage suction volume is formed, and the molded line rotor has the relatively big volume utilization rate, so that the bigger theoretic pumping speed is achieved under the same structural parameters; in contrary, the molded line rotor has the relatively bigger tooth top width at the exhaust end, has stronger interstage leakage resistance and can reduce the gas interstage leakage backflow rate, so that the improvement of the limit vacuum degree and the actual effective pumping speed of the vacuum pump are facilitated.

Description

A kind of single head varying pitch screw rotor waiting tooth top width

Technical field

The present invention relates to screw type oil-free vacuum pump technical field, particularly a kind of single head varying pitch screw rotor waiting tooth top width.

Background technique

Oil free screw pump has pumping speed wide ranges, simple and compact for structure, pumping chamber element without friction, the life-span is long, energy consumption is low, without features such as oil pollutions, be widely used in the industrial fields such as semiconductor, medicine, food, chemical industry.Screw rotor is the pumping section of most critical in screw vacuum pump, directly decides service behaviour and the working life of pump, and its manufacturing cost accounts for the nearly half of whole screw pump overall cost.The Profile Design of screw rotor is then the most critical technology in the design of whole screw pump.The wherein screw rotor of single head variable pitch, because it has inner precompressed exhaust mode, compared with constant lead screw rotor, has outstanding energy-saving and noise-reducing advantage, therefore enjoys the artificer of rotors for dry double-screw vacuum pump and the favor of user.Existing many technician have devised the single head varying pitch screw molded lines of rotor of various structures form.

Although the Structure composing of existing single head varying pitch screw molded lines of rotor is varied, but its common structure characteristic is: in the process diminished gradually to exhaust end by suction end along with the helical pitch (pitch) of screw rotor, the tooth top width (and the tooth root of correspondence is wide) in rotor flute profile also narrows to equal proportion gradually thereupon.Because the gap between rotor tooth end face and pump housing internal surface is the main leakage way that in rotor exhaust process, gas inter-stage backflows, the tooth top width of rotor flute profile is then equivalent to the degree of depth of this leakage way, tooth top width is wider, leakage way is darker, the blocking capability leaked inter-stage is stronger, then the gas backflow amount between adjacent two-stage is less.The tooth top width of existing single head varying pitch screw molded lines of rotor is narrowed to exhaust end gradually by suction end, then more and more weak to the blocking capability of inter-stage leakage.And screw vacuum pump is in the course of the work, the closer to exhaust end, gas pressure and interstage pressure difference larger, result appears at suction end interstage pressure poor hour, and flute profile tooth top width unnecessarily very greatly, causes the volumetric efficiency of pump less than normal on the contrary; And when exhaust end interstage pressure difference is very large, instead flute profile tooth top width diminishes the unreasonable situation causing gas backflow amount to increase.This directly causes, and the aspirated volume utilization factor of screw vacuum pump is little and leakage rate of totally backflowing is large, thus causes the consequence that main performance index ultimate vacuum reduces and the actual speed of exhaust declines of screw vacuum pump.

If in screw rotor Profile Design process, have a mind to keep rotor flute profile tooth top width constant all the time, then effectively can avoid the appearance of the problems referred to above, thus improve the pumping performance index of screw vacuum.

Summary of the invention

For prior art Problems existing, the object of this invention is to provide a kind of single head varying pitch screw rotor waiting tooth top width, ensure in the process linearly increased with the spiral angle of spread by the minimum value of exhaust end in rotor helical pitch, the tooth top width of rotor remains constant, to make rotor, there is stronger inter-stage and leak blocking capability, reduce gas inter-stage and leak regurgitation volume, thus reach and be conducive to improving the ultimate vacuum of vacuum pump and the object of actual effective pumping speed.

Technological scheme of the present invention is achieved in that a kind of single head varying pitch screw rotor waiting tooth top width, connected and composed successively by tooth flank, pitch face, Topland and the transition flank of tooth, rotor helical-screw helical pitch with the spiral angle of spread by exhaust end to the linear increase of suction end, the axial width of pitch face becomes large thereupon gradually, and the width of Topland remains constant.

Described tooth flank, pitch face, Topland and the transition flank of tooth are that the profile connected and composed successively by root circle curve, involute curve, top circle curve and changeover portion curve is done variable-pitch auger expansion and generates.

Using the axle center of screw rotor exhaust end face as true origin, rotor suction extreme direction is pointed to for Z axis forward with rotor axis, set up the rectangular coordinate system Oxyz describing molded lines of rotor, root circle curve of the present invention, involute curve, top circle curve and changeover portion curve meet following condition:

Described root circle section curve, meets following formula:

$\begin{array}{c}x=\frac{d}{2}\cos (t_1+\mathrm{\τ})\\ y=\frac{d}{2}\sin (t_1+\mathrm{\τ})\end{array}---\left(1\right)$

In formula, x is abscissa, and y is y coordinate, and d is root diameter, and τ is the spiral angle of spread, t ₁for formal parameter.

Described involute curve, meets following formula:

$\begin{array}{c}x=\frac{a\left(\mathrm{\τ}\right)}{2}\·[\cos (t_2+\mathrm{\τ})+t_2\·\sin (t_2+\mathrm{\τ})]\\ y=\frac{a\left(\mathrm{\τ}\right)}{2}\·[\sin (t_2+\mathrm{\τ})-t_2\·\cos (t_2+\mathrm{\τ})]\end{array}---\left(2\right)$

In formula, a (τ) is involute base circle diameter (BCD), t ₂for formal parameter.

Described top circle curve, meets following formula:

$\begin{array}{c}x=\frac{D}{2}\cos (t_3+\mathrm{\τ})\\ y=\frac{D}{2}\sin (t_3+\mathrm{\τ})\end{array}---\left(3\right)$

In formula, D is tip diameter, t ₃for formal parameter.

Described changeover portion curve, refers to any one curve of connection top circle and the root circle had from meshing characteristic, and the optimal case that this transition curve is selected is single cycloid transition curve or double cycloid transition curve, wherein,

Described single cycloid transition curve, meets following formula:

$\begin{array}{c}x=\frac{d+D}{2}\cos (t_{41}+\mathrm{\τ})-\frac{D}{2}\cos (2t_{41}+\mathrm{\τ})\\ y=\frac{d+D}{2}\sin (t_{41}+\mathrm{\τ})-\frac{D}{2}\sin (2t_{41}+\mathrm{\τ})\end{array}---\left(4\right)$

In formula, t ₄₁for formal parameter.

Described double cycloid transition curve, comprises hypocycloid and epicycloid, and wherein, hypocycloid, meets following formula:

$\begin{array}{c}x=\frac{d+D}{2}\cos (t_{421}+{\mathrm{\β}}_{421}+\mathrm{\τ})-\frac{D}{2}\cos (2t_{421}+{\mathrm{\β}}_{421}+\mathrm{\τ})\\ y=\frac{d+D}{2}\sin (t_{421}+{\mathrm{\β}}_{421}+\mathrm{\τ})-\frac{D}{2}\cos (2t_{421}+{\mathrm{\β}}_{421}+\mathrm{\τ})\end{array}---\left(5\right)$

In formula, t ₄₂₁for formal parameter, β ₄₂₁for regulating angle.

Epicycloid equation

$\begin{array}{c}x=\frac{d+D}{2}\cos (t_{422}+\mathrm{\τ})-\frac{D+d}{4}\cos (2t_{422}+\mathrm{\τ})\\ y=\frac{d+D}{2}\sin (t_{422}+\mathrm{\τ})-\frac{D+d}{4}\cos (2t_{422}+\mathrm{\τ})\end{array}---\left(6\right)$

In formula, t ₄₂₂for formal parameter.

The formula of the above-mentioned molded line adopting cylindrical-coordinate system or other form system of coordinates to state also belongs to the row of the present invention.

Described profile is in variable pitch expansion process, the base circle diameter (BCD) of involute curve by exhaust end to suction end in diminishing gradually, angle occupied by involute curve increases gradually, and the angle that top circle curve and root circle Curves occupy reduces gradually, when rotor lead of screw with the spiral angle of spread be directly proportional change, the tooth top width in rotor tooth form face and tooth root wide constant all the time.

Root circle curve, involute curve, top circle curve and changeover portion curve are in axial screw expansion process, and axial coordinate all meets following formula:

$z=\frac{p_0}{2\mathrm{\π}}(\mathrm{\τ}+{\mathrm{\λ\τ}}^2)---\left(7\right)$

Relation between described lead of screw p and spiral angle of spread τ meets:

p=p ₀(1+2λτ) （8）

Involute curve in profile is connected between root circle curve and top circle curve, and the generation circular diameter a (τ) of this involute curve is diminished with spiral angle of spread τ to suction end gradually by exhaust end, and formula is as follows:

$\begin{array}{c}\arctan \sqrt{{\left(\frac{D}{\mathrm{\α}\left(\mathrm{\τ}\right)}\right)}^2-1}-\arctan \sqrt{{\left(\frac{e}{a\left(\mathrm{\τ}\right)}\right)}^2-1}-\sqrt{{\left(\frac{D}{a\left(\mathrm{\τ}\right)}\right)}^2-1}+\sqrt{{\left(\frac{e}{a\left(\mathrm{\τ}\right)}\right)}^2-1}\\ =3\mathrm{\π}-\mathrm{\τ}-\frac{1}{2\mathrm{\λ}}+\frac{1}{2\mathrm{\λ}}\sqrt{1-\frac{8\mathrm{\πB\λ}}{p_0}+4\mathrm{\λ\τ}+4{\mathrm{\λ}}^2{\mathrm{\τ}}^2}\end{array}---\left(9\right)$

In formula, e is rotor pitch diameter, and B is tooth top width, and λ is variable pitch coefficient, p ₀for being vented the initial helical pitch of rotor of end.

Described rotor helical-screw expansion direction is left-handed or dextrorotation;

Beneficial effect of the present invention: the single head varying pitch screw rotor structure that flute profile tooth top width proposed by the invention is constant, at the minimum value p of rotor helical pitch by exhaust end ₀in the process linearly increased with the spiral angle of spread, the tooth top width of rotor remains constant.Compared with existing various single head varying pitch screw rotor, this molded line rotor is relatively little at the addendum width of suction end, thus form larger inter-stage aspirated volume, there is larger volumetric efficiency, therefore there is under identical structural parameter larger theoretical pumping speed; Otherwise this molded line rotor is relatively large at the addendum width of exhaust end, there is stronger inter-stage and leak blocking capability, gas inter-stage can be made to leak regurgitation volume and reduce, thus be conducive to improving the ultimate vacuum of vacuum pump and actual effective pumping speed.

Accompanying drawing explanation

The exhaust end profile view waiting tooth top width single head varying pitch screw rotor that Fig. 1 is is transition curve with single cycloid;

Fig. 2 is the screw rotor plan view generated according to rotor end-face molded line shown in Fig. 1;

Fig. 3 is the exhaust end profile view of the rotor such as varying pitch screw such as single head such as tooth top width such as grade taking double cycloid as transition curve;

Fig. 4 is the screw rotor plan view generated according to rotor end-face molded line shown in Fig. 3;

In figure, 1. root circle curve; 2. involute curve; 3. top circle curve; 4. the transition curve of single cycloid formation; 5. tooth flank; 6. pitch face; 7. Topland; 8. the recessed flank of tooth; 9. the transition curve of double cycloid formation; 10. straight-sided flank.

Embodiment

Below in conjunction with accompanying drawing, one step detailed description is done to embodiments of the present invention.

Embodiment one:

Present embodiment provides and a kind ofly waits the single head varying pitch screw rotor of tooth top width, its a certain cross-section profile as shown in Figure 1.Curve abc section is root circle curve 1, curve cde section is involute curve 2, curve efg section is top circle curve 3, curve gha section is the transition curve 4 be made up of single cycloid, four sections of curves connect (as the end c of root circle curve abc is connected with the starting point c of involute curve cde in order, the end e of involute curve cde is connected with the starting point e of top circle curve efg, the starting point g of the transition curve gha that end g and the single cycloid of top circle curve efg are formed is connected, the end of the transition curve gha that single cycloid is formed is connected with the starting point a of root circle curve abc, form profile).

The structural drawing of the rotor such as varying pitch screw such as single head such as tooth top width such as grade that dextrorotation variable-pitch auger launches to generate is made as shown in Figure 2 based on this profile.As can be seen from Fig. 2, the Profile of AT of this screw rotor comprises the fillet surface that tooth flank 5, pitch face 6, Topland 7 and recessed flank of tooth 8(are generated by single cycloid) 8.The lead of screw (pitch) of rotor by right side exhaust end to the left suction end become large gradually, P3 > P2 > P1, is directly proportional to the spiral angle of spread as shown in Figure 2; But the width B of its Topland 7 is constant all the time, as shown in Figure 2 B3=B2=B1=B; Axial length occupied by pitch face 6 is then more and more longer, as shown in Figure 2 L3 > L2 > L1.

According to the formula of formula (1) ~ formula (9), the structural parameter that the present embodiment provides the rotor such as varying pitch screw such as single head such as tooth top width such as grade of certain model rotors for dry double-screw vacuum pump are as follows: tip diameter D=186mm; Root diameter d=62mm; Pitch diameter e=(d+D)/2=124mm; The initial helical pitch p of rotor of exhaust end ₀=80mm; Variable pitch coefficient lambda=0.0198944; Tooth top width B=28mm; Working rotor district total length L=480mm.As shown in Figure 2, its spiral number of turns is 4 circles to its structural drawing.

Embodiment two:

Present embodiment provides a kind of single head varying pitch screw rotor waiting tooth top width, its a certain cross-section profile as shown in Figure 3, curve abc section is root circle curve 1, curve cde section is involute curve 2, curve efg section is top circle curve 3, curve gha section is the transition curve 9 that double cycloid is formed, four sections of curves connect (as the end c of root circle curve abc is connected with the starting point c of involute curve cde in order, the end e of involute curve cde is connected with the starting point e of top circle curve efg, the starting point g of the transition curve gha that end g and the single cycloid of top circle curve efg are formed is connected, the end of the transition curve gha that single cycloid is formed is connected with the starting point a of root circle curve abc, form profile).

The structural drawing of the rotor such as varying pitch screw such as single head such as tooth top width such as grade that left-handed variable-pitch auger launches to generate is made as shown in Figure 4 based on this profile.As can be seen from Fig. 4, the Profile of AT of this screw rotor comprises tooth flank 5, pitch face 6, Topland 7 and straight-sided flank (fillet surface that the transition curve be made up of double cycloid generates) 10.The lead of screw (pitch) of rotor by right side exhaust end to the left suction end become large gradually, P3 > P2 > P1, is directly proportional to the spiral angle of spread as shown in Figure 4; But the width B of its Topland 7 is constant all the time, as shown in Figure 2 B4=B3=B2=B1=B; Axial length occupied by pitch face 6 is then more and more longer, as shown in Figure 2 L4 > L3 > L2 > L1.

According to the formula of formula (1) ~ formula (9), the structural parameter that present embodiment provides the rotor such as varying pitch screw such as single head such as tooth top width such as grade of certain model rotors for dry double-screw vacuum pump are as follows: tip diameter D=188mm; Root diameter d=62mm; Pitch diameter e=(d+D)/2=125mm; The initial helical pitch p of rotor of exhaust end ₀=80mm; Variable pitch coefficient lambda=0.0198944; Tooth top width B=28mm; Working rotor district total length L=562.5mm.As shown in Figure 4, its spiral number of turns is 4.5 circles to its structural drawing.

Although the foregoing describe the specific embodiment of the present invention, one skilled in the art should be appreciated that these only illustrate, can make various changes or modifications, and do not deviate from principle of the present invention and essence to these mode of executions.Scope of the present invention is only defined by the appended claims.

Claims (4)

1. one kind is waited the single head varying pitch screw rotor of tooth top width, the Profile of AT of this screw rotor is connected and composed successively by tooth flank (5), pitch face (6), Topland (7) and the transition flank of tooth (8), described tooth flank (5), pitch face (6), Topland (7) and the transition flank of tooth (8) are that the profile connected and composed successively by root circle curve (abc), involute curve (cde), top circle curve (efg) and changeover portion curve (gha) is done variable-pitch auger expansion and generates; It is characterized in that: rotor helical-screw helical pitch (P1, P2, P3) with the spiral angle of spread by exhaust end to the linear increase of suction end, axial width (the L1 of pitch face (6), L2, L3) become large gradually thereupon, and the width of Topland (7) (B1, B2, B3) remain constant;

Described profile is in variable pitch expansion process, the base circle diameter (BCD) of involute curve (cde) by exhaust end to suction end in diminishing gradually, angle occupied by involute curve (cde) increases gradually, and top circle curve (efg) and the angle occupied by root circle curve (abc) reduce gradually, when rotor lead of screw with the spiral angle of spread be directly proportional change, the tooth top width of rotor tooth profile and tooth root wide constant all the time;

Involute curve (cde) in profile is connected between root circle curve (abc) and top circle curve (efg), this involute base circle diameter (BCD) a (τ) is diminished with spiral angle of spread τ to suction end gradually by exhaust end, meets following formula:

$\begin{array}{c}\arctan \sqrt{{\left(\frac{D}{a\left(\mathrm{\τ}\right)}\right)}^2-1}-\arctan \sqrt{{\left(\frac{e}{a\left(\mathrm{\τ}\right)}\right)}^2-1}-\sqrt{{\left(\frac{D}{a\left(\mathrm{\τ}\right)}\right)}^2-1}+\sqrt{{\left(\frac{e}{a\left(\mathrm{\τ}\right)}\right)}^2-1}\\ =3\mathrm{\π}-\mathrm{\τ}-\frac{1}{2\mathrm{\λ}}+\frac{1}{2\mathrm{\λ}}\sqrt{1-\frac{8\mathrm{\πB\λ}}{p_0}+4\mathrm{\λ\τ}+4{\mathrm{\λ}}^2{\mathrm{\τ}}^2}\end{array}$

In formula: D is rotor tooth outside diameter circle, e is rotor pitch diameter; B is tooth top width, and α (τ) is involute base circle diameter (BCD); λ is variable pitch coefficient, p ₀for being vented the initial helical pitch of rotor of end, τ is the spiral angle of spread.

2. the single head varying pitch screw rotor waiting tooth top width according to claim 1, is characterized in that: the relation between described lead of screw p and spiral angle of spread τ meets following formula:

p＝p ₀(1+2λτ)。

3. the single head varying pitch screw rotor waiting tooth top width according to claim 1, is characterized in that: connect the changeover portion curve (gha) of top circle curve (efg) and root circle curve (abc) in profile for having the arbitrary curve from meshing characteristic.

4. the single head varying pitch screw rotor waiting tooth top width according to claim 1, is characterized in that: rotor helical-screw expansion direction is left-handed or dextrorotation.