CN1961153A - Screw rotor and screw type fluid machine - Google Patents
Screw rotor and screw type fluid machine Download PDFInfo
- Publication number
- CN1961153A CN1961153A CNA2005800168891A CN200580016889A CN1961153A CN 1961153 A CN1961153 A CN 1961153A CN A2005800168891 A CNA2005800168891 A CN A2005800168891A CN 200580016889 A CN200580016889 A CN 200580016889A CN 1961153 A CN1961153 A CN 1961153A
- Authority
- CN
- China
- Prior art keywords
- curve
- helical rotor
- tooth
- peripheral part
- tooth bottom
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- 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
- F04C18/14—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 toothed rotary pistons
- F04C18/16—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 toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/082—Details specially related to intermeshing engagement type machines or engines
- F01C1/084—Toothed wheels
-
- 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
- F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
- F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
A screw type fluid machine so designed that the leakage from the screw type fluid machine is always constant during operation, that is, the gap in an exhaust chamber is always kept substantially constant. Thus, in a screw type fluid machine, the axis-orthogonal sectional shape (805) of the tooth form of a screw rotor is formed by curved lines including an arc (1) constituting the tooth bottom, an arc (3) constituting the outer periphery, and two curved lines that connect the outer periphery with the tooth bottom, wherein one (5) of the two curved lines is a trochoidal curved line generated by points on the outer periphery of a mating screw rotor, while the other of the two curved lines is bisected by the pitch circle into two portions, one from the pitch circle to the outer periphery, and the other from the pitch circle to the tooth bottom; the portion from the pitch circle to the tooth bottom (7) is formed by a predetermined curved line, while the portion from the pitch circle to the outer periphery (9) is formed by the curved line, generated by the bisected predetermined curved line, of the mating screw rotor to complete a tooth form shape.
Description
Technical field
The present invention relates to the helical rotor of screw compressor or rotary fluid machineries such as spiral vacuum pump, spiral decompressor, particularly its tooth curve.
Background technique
In the past, as rotary fluid machinery (below, the screw type dry vacuum pump is described as an example), for example has following screw type dry vacuum pump: by bearing fixing in the enclosure with a pair of helical rotor, utilize a side of this helical rotor of motor driven, by be fixed on this helical rotor timing gear and with the timing gear of the opposing party's helical rotor that is fixed on the timing gear engagement on this side helical rotor, two helical rotors are rotated uninterruptedly, intakeport from the shell of the running shaft tip side that is formed at two helical rotors sucks and discharges gas thus, and will discharge gas and be transplanted on the ejiction opening on the shell of the other end side that is formed at two helical rotors and spray.Two helical rotors as this screw type dry vacuum pump have various combinations, illustrate that in the present invention the sectional shape perpendicular to axle is identical shaped situation.The tooth curve of the helical rotor of this screw type dry vacuum pump, for example, employing will be by two helical rotors and to accommodate space that the shell of these two helical rotors forms airtight and form transfer chamber shown in the helical rotor tooth curve of documents 1, and seek to improve sealing effect profile of tooth.
The sectional shape perpendicular to running shaft of the helical rotor profile of tooth shown in the documents 1, by with the rotating center of helical rotor as the peripheral part of the circular arc at center, with the rotating center of helical rotor as the tooth bottom of the circular arc at center and connect peripheral part and 2 curve parts of tooth bottom form.One bar curve part is by the trochoid curves decision of 1 A institute generate on the periphery of opposite side helical rotor.Another curve part is by sinusoidal curve or 2 involute curve decisions.
Patent documentation 1: the spy opens flat 8-277790 communique
But, in the profile of tooth of the helical rotor that in existing screw type dry vacuum pump, uses, only be designed to the curve of available specific function representation such as sinusoidal curve, 2 involute curves, in the profile of tooth of using these curves, have the mesh phase that produces the interference between helical rotor, can not in whole mesh phases, make play become 0 or a certain uniform play.That is, owing to the angle of swing difference according to rotor, the gap changes, thereby produces the big part of this gap change, thus the problem that the discharge gas in transferring leaks in large quantities from this big gap.Therefore, many to the discharge gas quantitative change that the exhaust cavity side flows backwards, thus be difficult to improve exhaust velocity.
Summary of the invention
The present invention proposes in view of the problems referred to above of prior art, can suppress discharge gas leakage in the handover of rotary fluid machinery and the amount that flows backwards to suction side as far as possible.That is, its purpose is to provide a kind of rotary fluid machinery, and it is certain that the gap of the transfer chamber in the exhaust chamber during running always roughly keeps.
Invention according to technological scheme 1, a kind of helical rotor, profile of tooth perpendicular to the sectional shape of axle by the circular arc that constitutes the tooth bottom, constitute the circular arc of peripheral part and connect peripheral part and 2 curves formations of tooth bottom, it is characterized in that, the serve as reasons trochoid curves of the some institute generate on the periphery of engagement opposite side helical rotor of a curve in 2 curves of above-mentioned connection peripheral part and tooth bottom, another curve is second-class be divided into pitch circle to peripheral part and pitch circle to the tooth bottom, side after this is halved is formed by the predetermined curve of regulation, the opposing party serves as reasons the predetermined curve of a side regulation after the bisection of another helical rotor at the curve of engagement time institute's generate, thereby constitutes the sectional shape perpendicular to axle of profile of tooth.
Another curve in 2 curves of above-mentioned connection peripheral part and tooth bottom also can following formation flute profile shape: helical rotor perpendicular to the cross section of running shaft on peripheral part and tooth bottom between along radial direction uniformly-spaced to be divided into even number part, half after this even number is cut apart part is formed by the predetermined curve of regulation, and second half fractional part is formed by the curve of the predetermined curve institute generate of this regulation of opposite side helical rotor.
Invention according to technological scheme 2, a kind of helical rotor, profile of tooth perpendicular to the sectional shape of axle by the circular arc that constitutes the tooth bottom, constitute the circular arc of peripheral part and connect peripheral part and 2 flute profile curves formations of tooth bottom, it is characterized in that, a flute profile curve in 2 flute profile curves of above-mentioned connection peripheral part and tooth bottom is not interfere with the mate of another helical rotor, and can form the flute profile curve of the transfer chamber that separates with other spaces, another flute profile curve is second-class be divided into pitch circle to peripheral part and pitch circle to the tooth bottom, side after this is halved is formed by the predetermined curve of regulation, the opposing party serves as reasons the predetermined curve of a side regulation after the bisection of another helical rotor at the curve of engagement time institute's generate, thereby constitutes the sectional shape perpendicular to axle of profile of tooth.
As a flute profile curve in 2 flute profile curves of above-mentioned connection peripheral part and tooth bottom, particularly be used as under the situation of spiral vacuum pump, selection is best suited for by the trochoid curves of the some generate on the periphery of engagement opposite side helical rotor, but is not limited thereto.Another flute profile curve also can following formation flute profile shape: helical rotor perpendicular to the cross section of running shaft on peripheral part and tooth bottom between along radial direction uniformly-spaced to be divided into even number part, half after this even number is cut apart part is formed by the predetermined curve of regulation, and second half fractional part is formed by the curve of the predetermined curve institute generate of this regulation of opposite side helical rotor.
Invention according to technological scheme 3 is characterized in that, the predetermined curve part of a regulation after the above-mentioned bisection is formed by circular arc and straight line.If can select configuration and arrangement, make the circular arc that constitutes a side after the above-mentioned bisection and straight line bottom tooth or peripheral part be connected smoothly, and also be connected smoothly with the tooth of the opposing party after the above-mentioned bisection, the number of combinations of circular arc and straight line just without limits.And, not only be defined in circular arc and straight line.
Invention according to technological scheme 4 is characterized in that, the predetermined curve part of afore mentioned rules is formed by sinusoidal curve.If this sinusoidal curve can be selected configuration and arrange, make a side after the above-mentioned bisection bottom tooth or peripheral part be connected smoothly, and also be connected smoothly with the opposing party's tooth after the above-mentioned bisection, the sinusoidal curve number is with regard to without limits.And, not only be defined in sinusoidal curve.But, make simple when only halving back one side's profile of tooth by 1 curve formation for the manufacturing of profile of tooth.
According to the invention of technological scheme 5, a kind of rotary fluid machinery comprises: the pump casing with intakeport and relief opening; Rotate with being meshing with each other, can be contained in a pair of helical rotor in the said pump shell respectively with rotating freely, between said pump shell and each helical rotor, be formed with a plurality of transfer chamber, described transfer chamber is divided by the mate of two helical rotors and is formed, and deliver to exhaust side from the intakeport sidesway by the rotation of two helical rotors, it is characterized in that, the helical rotor profile of tooth perpendicular to the sectional shape of axle by the circular arc that constitutes the tooth bottom, constitute the circular arc of peripheral part and connect peripheral part and 2 curves formations of tooth bottom, a curve in 2 curves of this connection peripheral part and tooth bottom is the trochoid curves by the some institute generate on the periphery of opposite side helical rotor, another curve by pitch circle second-class be divided into pitch circle to peripheral part and pitch circle to tooth the bottom, one side is formed by the predetermined curve of regulation, the opposing party serves as reasons the predetermined curve of a side regulation after the bisection of another helical rotor at the curve of engagement time institute's generate, thereby constitutes the flute profile shape.
Another curve in 2 curves of above-mentioned connection peripheral part and tooth bottom also can following formation flute profile shape: helical rotor perpendicular to the cross section of running shaft on peripheral part and tooth bottom between along radial direction uniformly-spaced to be divided into even number part, half after this even number is cut apart part is formed by the predetermined curve of regulation, and second half fractional part is formed by the curve of the predetermined curve institute generate of this regulation of opposite side helical rotor.
According to the invention of technological scheme 6, a kind of rotary fluid machinery comprises: the pump casing with intakeport and relief opening; Rotate with being meshing with each other, can be contained in a pair of helical rotor in the said pump shell respectively with rotating freely, between said pump shell and each helical rotor, be formed with a plurality of transfer chamber, described transfer chamber is divided by the mate of two helical rotors and is formed, and deliver to exhaust side from the intakeport sidesway by the rotation of two helical rotors, it is characterized in that, the helical rotor profile of tooth perpendicular to the sectional shape of axle by the circular arc that constitutes the tooth bottom, constitute the circular arc of peripheral part and connect peripheral part and 2 flute profile curves formations of tooth bottom, a flute profile curve in 2 curves of this connection peripheral part and tooth bottom is not interfere with the mate of opposite side helical rotor, and the flute profile curve that above-mentioned each transfer chamber and adjacent other transfer chamber are separated, another flute profile curve negotiating pitch circle is second-class be divided into pitch circle to peripheral part and pitch circle to the tooth bottom, one side is formed by the predetermined curve of regulation, the opposing party is by the predetermined curve of the regulation of a side after the bisection of the opposite side helical rotor curve at engagement time institute's generate, thereby constitutes the flute profile shape.
As a flute profile curve in 2 flute profile curves of above-mentioned connection peripheral part and tooth bottom, particularly be used as under the situation of spiral vacuum pump, selection is best suited for by the trochoid curves of the some generate on the periphery of engagement opposite side helical rotor, but is not limited thereto.Another flute profile curve also can following formation flute profile shape: helical rotor perpendicular to the cross section of running shaft on peripheral part and tooth bottom between along radial direction uniformly-spaced to be divided into even number part, half after this even number is cut apart part is formed by the predetermined curve of regulation, and second half fractional part is formed by the curve of the predetermined curve institute generate of this regulation of opposite side helical rotor.
Invention according to technological scheme 7 is characterized in that, the predetermined curve part of a regulation after the above-mentioned bisection is formed by circular arc and straight line.If can select configuration and arrangement, make the circular arc that constitutes a side after the above-mentioned bisection and straight line bottom tooth or peripheral part be connected smoothly, and also be connected smoothly with the tooth of the opposing party after the above-mentioned bisection, the number of combinations of circular arc and straight line just without limits.And, not only be defined in circular arc and straight line.
Invention according to technological scheme 8 is characterized in that, the predetermined curve part of afore mentioned rules is formed by sinusoidal curve.If this sinusoidal curve can be selected configuration and arrange, make a side after the above-mentioned bisection bottom tooth or peripheral part be connected smoothly, and also be connected smoothly with the opposing party's tooth after the above-mentioned bisection, the sinusoidal curve number is with regard to without limits.And, not only be defined in sinusoidal curve.But, make simple when only halving back one side's profile of tooth by 1 curve formation for the manufacturing of profile of tooth.
The invention effect
According to the invention of technological scheme 1, can easily form the flute profile of helical rotor, make helical rotor engagement and during rotation, and angle of swing always makes irrespectively the gap between the helical rotor remain unchanged.
According to the invention of technological scheme 2, can easily form the flute profile of helical rotor, make helical rotor engagement and during rotation, and angle of swing always makes irrespectively the gap between the helical rotor remain unchanged.
According to the invention of technological scheme 3, use circular arc with the tooth bottom or the peripheral part engaging portion of side's flute profile after halving by pitch circle, can form easily thus and the flute profile of the helical rotor of connection joining part smoothly.
Invention according to technological scheme 4, can easily constitute by a curve after the predetermined pitch circle bisection of regulation by minimum 1 curve, can form the joining portion and be connected to bottom the tooth easily and smoothly or the flute profile of the helical rotor of the anastomosis part of peripheral part.
According to the invention of technological scheme 5, can easily constitute rotary fluid machinery, it has the helical rotor of making engagement and during rotation, and angle of swing irrespectively always makes the flute profile of the helical rotor that the gap between the helical rotor remains unchanged.
According to the invention of technological scheme 6, can easily constitute rotary fluid machinery, it has the helical rotor of making engagement and during rotation, and angle of swing irrespectively always makes the flute profile of the helical rotor that the gap between the helical rotor remains unchanged.
According to the invention of technological scheme 7, use circular arc with the tooth bottom or the peripheral part engaging portion of side's flute profile after halving by pitch circle, can constitute thus and have easily and the rotary fluid machinery of the helical rotor flute profile of connection joining part smoothly.
Invention according to technological scheme 8, can constitute the fluid machinery of the flute profile with following helical rotor: can easily constitute by the binary curve of stipulating of predetermined pitch circle by minimum 1 curve, the joining portion is connected to the anastomosis part of tooth bottom or peripheral part easily and smoothly.
Description of drawings
Fig. 1 represents screw type dry vacuum pump of the present invention.
Fig. 2 represents the sectional shape perpendicular to running shaft of helical rotor of the present invention.
Fig. 3 represents to form first process perpendicular to the sectional shape of running shaft of helical rotor of the present invention.
Fig. 4 represents to form second process perpendicular to the sectional shape of running shaft of helical rotor of the present invention.
Fig. 5 represents to form the 3rd process perpendicular to the sectional shape of running shaft of helical rotor of the present invention.
Fig. 6 represents to form the 4th process perpendicular to the sectional shape of running shaft of helical rotor of the present invention.
Fig. 7 represents to form the 5th process perpendicular to the sectional shape of running shaft of helical rotor of the present invention.
Fig. 8 represents to form the 6th process perpendicular to the sectional shape of running shaft of helical rotor of the present invention.
Fig. 9 represents to form the 7th process perpendicular to the sectional shape of running shaft of helical rotor of the present invention.
Figure 10 represents to form the 8th process perpendicular to the sectional shape of running shaft of helical rotor of the present invention.
Label declaration
100 screw type dry vacuum pumps
101 shells
101,102
111,112,113,114 bearings
103,104 helical rotors
106,115 timing gears
107 intakepories
108 exhaust ports
109 exhaust side flanges
116,117,118,119 shaft sealings
201 pitch circles
Embodiment
The following describes embodiments of the present invention.
Embodiment 1
Fig. 1 is to use the embodiment of the screw type dry vacuum pump 100 of helical rotor of the present invention.
As shown in Figure 1,100,2 parallel axles 101,102 of screw type dry vacuum pump are supported in the shell 110 by bearing 111,112,113 and 114 respectively, are fixed with the intermeshing spiral fluted helical rotor 103,104 that has on described axle.An axle 101 is rotated driving by motor 105, and this rotation is by being fixed on the timing gear 106 of axle on 101 and passing to 106 engagements of this timing gear and being fixed on another timing gear 115 on 102.That is, helical rotor 103 and 104 rotates synchronously by timing gear 106 and 115.Shell 110 comprises the exhaust port 108 that is used for that the discharge gas in the not shown exhaust cavity sucked the intakeport 107 in the exhaust chamber and is used for discharging the discharge gas of sending here from intakeport 107 sidesways in exhaust chamber.By above structure, helical rotor 103 and 104 is reversed synchronously, thereby make sealing go into the discharge gas of the transfer chamber in the exhaust chamber that forms by helical rotor 103,104 and shell 110, axially move by the rotation of helical rotor 103 and 104 and discharge.
The effect of this screw type dry vacuum pump is by the suction process that sucks gas from intakeport 107 in exhaust chamber, in the handover process of the inner handover of exhaust chamber gas and the ejection process realization that sprays gases from exhaust port 108.
At this, intakeport 107 can be configured on the shell upper-end surface as illustrated in fig. 1, and intakeport also can be configured in the side of shell, be configured in when observing perpendicular to the direction of axle and the helical rotor position overlapped on.About relief opening, in the end, make between the gap and two helical rotors of exhaust side flange 109 upper surfaces and helical rotor exhaust side end face, when the gap between two helical rotor sides and the shell similarly narrows down, can regulate transfer chamber and discharge connect hours between the side extraneous gas by the position, the size that change relief opening, can change the head pressure of discharging gas.And, under the situation that the side end exhaust port of above-mentioned shell is opened, can increase exhaust passageway and relief opening, the against vacuum pump can improve maintainability.
And, in semiconductor-fabricating device etc. does not allow device that impurity sneaks into, use under the situation of spiral interference vacuum pump, exhaust chamber side between axle and shell is provided with shaft sealing 116,117,118 and 119, makes the lubricated wet goods be used for lubricating bearings 111,112,113 and 114, timing gear 106 and 115 can not leak in the exhaust chamber.
In above-mentioned exhaust chamber, by a pair of helical rotor and the airtight transfer chamber of shell, bar number and volume number according to helical rotor are formed with a plurality of chambers, to seal in this transfer chamber from the discharge gas that above-mentioned intakeport 107 sucks, to discharge gas according to the rotation of helical rotor and transfer, and discharge gas from these exhaust port 108 ejections to exhaust port 108.
The exhaust performance of the screw type dry vacuum pump during running is because of being formed at the bigger variation of leak tightness of the transfer chamber in the exhaust chamber.That is, flow from high side to low side, thereby leak tightness is when bad owing to discharge gas, from intakeport 107 to exhaust port 108 transfer discharge gases during, the discharge gas that is enclosed in this transfer chamber goes out to intakeport 107 side leakages, thus the exhaust performance variation.
This transfer chamber airtight is between the peripheral part and shell by two helical rotors, between the peripheral part of the tooth bottom of a helical rotor and another helical rotor and connect between 2 curves of the peripheral part of each helical rotor and tooth bottom and form potted line.
At this, use Fig. 2 that the sectional shape perpendicular to running shaft of above-mentioned helical rotor is described.In Fig. 2, peripheral part is represented in expression tooth bottom between AB between CD, between BC with AD between expression is connected 2 curves bottom peripheral part and the tooth.Form with trochoid curves between BC, between AD, with pitch circle 201 as the border, tooth bottom side 203 is formed by the curve of combination circular arc and straight line, outer circumferential side 205 forms by formation curve, wherein, described pitch circle 201 have the diameter of the centre of circular arc at the bottom of periphery circular arc and the tooth and with the running shaft O of helical rotor as the center.
When having the big part in gap on above-mentioned potted line, the discharge gas of transfer chamber reduces exhaust efficiency from this clearance leakage.Along the gap of sealing line, can form between the peripheral part CD of two helical rotors and between the shell, between the peripheral part of the tooth bottom of a helical rotor and another helical rotor and connect the profile of tooth that always can keep certain clearance between the trochoid curves portion of the peripheral part of helical rotor and tooth bottom and turn round.But, connect engaging piece between the AD of peripheral part and tooth bottom in existing design, the angle of swing difference of two helical rotors during because of running, the gap changes.Therefore, with the part of gap minimum as benchmark, make under the situation identical of this minimum gap with the gap of above-mentioned other certain clearance parts, can produce the part in big gap at another curve part, discharge gas in the transfer chamber flows backwards from this part leakage and to air-breathing oral-lateral, thereby make the exhaust efficiency variation, but as the embodiment of the invention, for this part, with pitch circle 201 as the border, curve with combination circular arc and straight line forms tooth bottom side 203, and by generate curve formation outer circumferential side 205, therefore have degrees of freedom at this generate curve part, the gap of this engaging piece always keeps identical profile of tooth with the gap of other parts in the time of can forming running, can constitute to have the very screw type dry vacuum pump of excellent sealing performance.
Then use Fig. 3 to Figure 10 that the forming process of the screw serrated form of present embodiment is described.
At first, expression is that the circular arc at center forms the tooth bottom between AB by the running shaft O with helical rotor in Fig. 3, by the running shaft O with helical rotor is that the circular arc at center forms the peripheral part between CD, form between BC by trochoid curves, and the sectional shape perpendicular to running shaft of the helical rotor before the profile of tooth that forms between AD.
Then at Fig. 4, configuration will be with pitch circle 201 as the border, circumscribed in tooth bottom side 203 with circular arc at the bottom of the tooth, and circle 301 with the diameter that equates with the difference of circular arc at the bottom of periphery circular arc and the tooth, wherein, described pitch circle 201 has the diameter of the centre of circular arc at the bottom of periphery circular arc and the tooth and is the center with the running shaft O of helical rotor.
As shown in Figure 5, form by intersection point P, and at the tangent line part 403 of tooth bottom side and above-mentioned circle 301, wherein, described intersection point P is the intersection point of straight line L and pitch circle, described straight line L is the central shaft O and this circle 301 and the straight line at the point of contact of circular arc at the bottom of the tooth and the middle separated time of formed angle 2 θ of the straight line of the end points D of central shaft O that is connected helical rotor and peripheral part that connects helical rotor, as shown in Figure 6, by at the bottom of the tooth of above-mentioned circle 301 with the tangent part of line part 403 and from pitch circle 201 to forming the profile of tooth of tooth bottom side 203 with the tangent line part 403 of circle 301.
Then as shown in Figure 7, with respect to helical rotor 701, on the position of leaving pitch circle 201 diameter distances, depart from 180 ° of phase places and dispose another identical shaped helical rotor 703.
Then as shown in Figure 8, fix a helical rotor 701, make the position relation of another helical rotor 703 according to two helical rotors under the operating condition, around a helical rotor 701, rotation when departing from mesh phase.
At this moment, as shown in Figure 9, form the outer circumferential side profile of tooth by the generate curve that forms at the outermost line that connects the tooth bottom side tooth 903 of the opposing party's helical rotor between P to D, make at the outer circumferential side tooth portion 901 of the next helical rotor 701 of each phase place and the tooth bottom side interference of tooth of another helical rotor.
As mentioned above, helical rotor 805 can have the profile of tooth perpendicular to the sectional shape of running shaft as shown in figure 10, can be formed on the complete profile of tooth that play under any phase place all is roughly 0mm.But, under the situation with the running of no oil condition, owing to the friction between two helical rotors, discharge the compression of gas etc., thermal expansion takes place on the direction perpendicular to helical tooth flank, thereby certain play (0.05～0.3mm) need be set.In this case, the complete flute profile that is roughly 0mm with above-mentioned play is as benchmark, along the adjustment in direction perpendicular to the helical tooth flank of each helical rotor a certain amount of (0.025～0.15mm), just can in whole mesh phases, obtain uniform play.
If existing profile of tooth, because of the part that makes the gap minimum that interferes consistent with the gap design minimum value of determining by thermal expansion etc., thereby the generation gap becomes big phase place, but if having the screw type dry vacuum pump of the helical rotor of present embodiment, the gap is a certain value with respect to phase place, can consider the optimal design of exhaust efficiency, thermal expansion etc.Thus, can suppress the leakage that the gap causes in inferior limit ground, can improve exhaust efficiency, realize consuming the minimizing of electric power.
Claims (8)
1. helical rotor, profile of tooth perpendicular to the sectional shape of axle by the circular arc that constitutes the tooth bottom, constitute the circular arc of peripheral part and connect peripheral part and 2 curves formations of tooth bottom, it is characterized in that, the serve as reasons trochoid curves of the some institute generate on the periphery of engagement opposite side helical rotor of a curve in 2 curves of described connection peripheral part and tooth bottom, another curve is second-class be divided into pitch circle to peripheral part and pitch circle to the tooth bottom, side after this is halved is formed by the predetermined curve of regulation, the opposing party serves as reasons the predetermined curve of a side regulation after the bisection of another helical rotor at the curve of engagement time institute's generate, thereby constitutes the sectional shape perpendicular to axle of profile of tooth.
2. helical rotor, profile of tooth perpendicular to the sectional shape of axle by the circular arc that constitutes the tooth bottom, constitute the circular arc of peripheral part and connect peripheral part and 2 flute profile curves formations of tooth bottom, it is characterized in that, a flute profile curve in 2 flute profile curves of described connection peripheral part and tooth bottom is not interfere with the mate of another helical rotor, and can form the flute profile curve of the transfer chamber that separates with other spaces, another flute profile curve is second-class be divided into pitch circle to peripheral part and pitch circle to the tooth bottom, side after this is halved is formed by the predetermined curve of regulation, the opposing party serves as reasons the predetermined curve of a side regulation after the bisection of another helical rotor at the curve of engagement time institute's generate, thereby constitutes the sectional shape perpendicular to axle of profile of tooth.
3. helical rotor according to claim 1 and 2 is characterized in that, the predetermined curve part of a regulation after the described bisection is formed by circular arc and straight line.
4. helical rotor according to claim 1 and 2 is characterized in that, the predetermined curve part of described regulation is formed by sinusoidal curve.
5. a rotary fluid machinery comprises: the pump casing with intakeport and relief opening; Rotate with being meshing with each other, can be contained in a pair of helical rotor in the described pump casing respectively with rotating freely, between described pump casing and each helical rotor, be formed with a plurality of transfer chamber, described transfer chamber is divided by the mate of two helical rotors and is formed, and deliver to exhaust side from the intakeport sidesway by the rotation of two helical rotors, it is characterized in that, the helical rotor profile of tooth perpendicular to the sectional shape of axle by the circular arc that constitutes the tooth bottom, constitute the circular arc of peripheral part and connect peripheral part and 2 curves formations of tooth bottom, a curve in 2 curves of this connection peripheral part and tooth bottom is the trochoid curves by the some institute generate on the periphery of opposite side helical rotor, another curve by pitch circle second-class be divided into pitch circle to peripheral part and pitch circle to tooth the bottom, one side is formed by the predetermined curve of regulation, the opposing party is by the predetermined curve of the regulation of a side after the bisection of the opposite side helical rotor curve at engagement time institute's generate, thereby constitutes the flute profile shape.
6. a rotary fluid machinery comprises: the pump casing with intakeport and relief opening; Rotate with being meshing with each other, can be contained in a pair of helical rotor in the described pump casing respectively with rotating freely, between described pump casing and each helical rotor, be formed with a plurality of transfer chamber, described transfer chamber is divided by the mate of two helical rotors and is formed, and deliver to exhaust side from the intakeport sidesway by the rotation of two helical rotors, it is characterized in that, the helical rotor profile of tooth perpendicular to the sectional shape of axle by the circular arc that constitutes the tooth bottom, constitute the circular arc of peripheral part and connect peripheral part and 2 flute profile curves formations of tooth bottom, a flute profile curve in 2 curves of this connection peripheral part and tooth bottom is not interfere with the mate of opposite side helical rotor, and the flute profile curve that described each transfer chamber and adjacent other transfer chamber are separated, another flute profile curve negotiating pitch circle is second-class be divided into pitch circle to peripheral part and pitch circle to the tooth bottom, one side is formed by the predetermined curve of regulation, the opposing party is by the predetermined curve of the regulation of a side after the bisection of the opposite side helical rotor curve at engagement time institute's generate, thereby constitutes the flute profile shape.
7. according to claim 5 or 6 described helical rotors, it is characterized in that the predetermined curve part of a regulation after the described bisection is formed by circular arc and straight line.
8. according to claim 5 or 6 described helical rotors, it is characterized in that the predetermined curve part of described regulation is formed by sinusoidal curve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP153957/2004 | 2004-05-24 | ||
| JP2004153957 | 2004-05-24 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1961153A true CN1961153A (en) | 2007-05-09 |
Family
ID=35428448
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2005800168891A Pending CN1961153A (en) | 2004-05-24 | 2005-05-24 | Screw rotor and screw type fluid machine |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20080193317A1 (en) |
| EP (1) | EP1750011A1 (en) |
| JP (1) | JPWO2005113984A1 (en) |
| KR (1) | KR20070027558A (en) |
| CN (1) | CN1961153A (en) |
| TW (1) | TW200607926A (en) |
| WO (1) | WO2005113984A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105485015A (en) * | 2016-01-11 | 2016-04-13 | 巫修海 | Screw rotor end face molded line of dry screw vacuum pump |
| CN107084131A (en) * | 2017-06-08 | 2017-08-22 | 中国石油大学(华东) | A kind of complete smooth screw rotor based on eccentric circle involute |
| CN107110156A (en) * | 2015-01-05 | 2017-08-29 | 株式会社爱发科 | Screw vacuum pump |
| CN112746958A (en) * | 2021-01-04 | 2021-05-04 | 西安交通大学 | Double-screw compression and expansion integrated machine for fuel cell |
| CN114876795A (en) * | 2022-04-25 | 2022-08-09 | 江阴全玉节能环保真空设备制造有限公司 | Energy-saving backflow-preventing variable-pitch screw vacuum pump |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5024750B2 (en) * | 2006-08-20 | 2012-09-12 | 秀隆 渡辺 | Rotary thermal fluid equipment |
| US7798794B2 (en) | 2006-09-05 | 2010-09-21 | Kabushiki Kaisha Toyota Jidoshokki | Screw pump and screw rotor |
| CN100432434C (en) * | 2006-09-29 | 2008-11-12 | 中国船舶重工集团公司第七一一研究所 | Noval tooth-type screw rod |
| CN102465871B (en) * | 2010-11-17 | 2014-11-26 | 上海格什特螺杆科技有限公司 | Screw rotor end face tooth type |
| CN104776027B (en) * | 2013-04-26 | 2016-10-26 | 巫修海 | Strict seal type dry screw vacuum pump screw rotor |
| CN106438357B (en) * | 2016-11-28 | 2018-07-06 | 浙江创为真空设备股份有限公司 | A kind of screw vacuum pump |
| CN107989792B (en) * | 2018-01-22 | 2023-09-12 | 中国石油大学(华东) | Full smooth screw rotor |
| CN108757438B (en) * | 2018-07-25 | 2023-08-18 | 中国石油大学(华东) | Full-smooth screw rotor with small enclosed volume and design method thereof |
| CN110360113B (en) * | 2019-07-18 | 2021-03-02 | 合肥工业大学 | Double-end symmetrical rotor profile based on single-end screw rotor profile design |
| CN110645172B (en) * | 2019-11-01 | 2021-01-19 | 西安交通大学 | Screw vacuum pump rotor and screw vacuum pump |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3472445A (en) * | 1968-04-08 | 1969-10-14 | Arthur E Brown | Rotary positive displacement machines |
| US4088427A (en) * | 1974-06-24 | 1978-05-09 | Atlas Copco Aktiebolag | Rotors for a screw rotor machine |
| JPS5746083A (en) * | 1980-09-01 | 1982-03-16 | Shigeyoshi Osada | Improved quimby pump |
| JPS6415485A (en) * | 1987-07-07 | 1989-01-19 | Fuji Heavy Ind Ltd | Root's blower |
| KR0133154B1 (en) * | 1994-08-22 | 1998-04-20 | 이종대 | Screw pump |
| JP2924997B2 (en) * | 1995-01-11 | 1999-07-26 | 株式会社荏原製作所 | Screw machine |
| JP2904719B2 (en) * | 1995-04-05 | 1999-06-14 | 株式会社荏原製作所 | Screw rotor, method for determining cross-sectional shape of tooth profile perpendicular to axis, and screw machine |
| US6244844B1 (en) * | 1999-03-31 | 2001-06-12 | Emerson Electric Co. | Fluid displacement apparatus with improved helical rotor structure |
| JP4282867B2 (en) * | 2000-03-15 | 2009-06-24 | ナブテスコ株式会社 | Screw rotor and screw machine |
| EP1552150B1 (en) * | 2002-10-04 | 2015-12-23 | Ebara Corporation | Screw pump and method of operating the same |
-
2005
- 2005-05-24 EP EP05743311A patent/EP1750011A1/en not_active Withdrawn
- 2005-05-24 WO PCT/JP2005/009415 patent/WO2005113984A1/en active Application Filing
- 2005-05-24 US US11/569,536 patent/US20080193317A1/en not_active Abandoned
- 2005-05-24 TW TW094116900A patent/TW200607926A/en unknown
- 2005-05-24 JP JP2006513756A patent/JPWO2005113984A1/en not_active Ceased
- 2005-05-24 KR KR1020067024777A patent/KR20070027558A/en not_active Application Discontinuation
- 2005-05-24 CN CNA2005800168891A patent/CN1961153A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107110156A (en) * | 2015-01-05 | 2017-08-29 | 株式会社爱发科 | Screw vacuum pump |
| CN105485015A (en) * | 2016-01-11 | 2016-04-13 | 巫修海 | Screw rotor end face molded line of dry screw vacuum pump |
| CN106762661A (en) * | 2016-01-11 | 2017-05-31 | 台州职业技术学院 | A kind of dry screw vacuum pump screw rotor end face molded line |
| CN107084131A (en) * | 2017-06-08 | 2017-08-22 | 中国石油大学(华东) | A kind of complete smooth screw rotor based on eccentric circle involute |
| CN107084131B (en) * | 2017-06-08 | 2019-05-31 | 中国石油大学(华东) | A kind of complete smooth screw rotor based on eccentric circle involute |
| CN112746958A (en) * | 2021-01-04 | 2021-05-04 | 西安交通大学 | Double-screw compression and expansion integrated machine for fuel cell |
| CN114876795A (en) * | 2022-04-25 | 2022-08-09 | 江阴全玉节能环保真空设备制造有限公司 | Energy-saving backflow-preventing variable-pitch screw vacuum pump |
| CN114876795B (en) * | 2022-04-25 | 2024-05-14 | 江阴全玉节能环保真空设备制造有限公司 | Energy-saving backflow-preventing variable-pitch screw vacuum pump |
Also Published As
| Publication number | Publication date |
|---|---|
| US20080193317A1 (en) | 2008-08-14 |
| EP1750011A1 (en) | 2007-02-07 |
| WO2005113984A1 (en) | 2005-12-01 |
| JPWO2005113984A1 (en) | 2008-03-27 |
| KR20070027558A (en) | 2007-03-09 |
| TW200607926A (en) | 2006-03-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1961153A (en) | Screw rotor and screw type fluid machine | |
| US8827669B2 (en) | Screw pump having varying pitches | |
| CN109642574B (en) | Dry compression type vacuum pump | |
| KR20130037115A (en) | Scroll compressor with supporting member in axial direction | |
| JP4823455B2 (en) | Fluid machine provided with a gear and a pair of engagement gears using the gear | |
| CN1061742C (en) | Fluid mechanism | |
| US3986801A (en) | Screw compressor | |
| CN2821225Y (en) | Rotor pump | |
| CN110307079A (en) | Energy conversion device based on fluid displacement variation | |
| CN1159529C (en) | Scrawl compressor | |
| JP2001304161A (en) | Improved vacuum pump | |
| CN1178004C (en) | Asymmetric whirl compressor | |
| JP2924997B2 (en) | Screw machine | |
| CN1034752C (en) | Fluid pump and rotary machine having said fluid pump | |
| CN110307078A (en) | Energy conversion device and rotary engine based on fluid displacement variation | |
| CN1477310A (en) | Axle sealing structure for vacuum pump | |
| CN110307080A (en) | Energy conversion device and rotary engine based on fluid displacement variation | |
| CN220267946U (en) | Fixed scroll, compressor and refrigeration equipment | |
| CN1080389C (en) | Fluid compressor | |
| CN114198206B (en) | Combined return oil pump of aero-engine and aero-engine comprising same | |
| CN110307081A (en) | Energy conversion device based on fluid displacement variation | |
| US12012962B2 (en) | Fluid transfer device | |
| KR200276901Y1 (en) | Rotary vane vacuum pumps | |
| KR100196920B1 (en) | A dual pump for compressor and motor | |
| CN1492971A (en) | Rotary piston machine for compressible media |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |