CN102678542A - Screw pump - Google Patents
Screw pump Download PDFInfo
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- CN102678542A CN102678542A CN2012100601911A CN201210060191A CN102678542A CN 102678542 A CN102678542 A CN 102678542A CN 2012100601911 A CN2012100601911 A CN 2012100601911A CN 201210060191 A CN201210060191 A CN 201210060191A CN 102678542 A CN102678542 A CN 102678542A
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- rotor
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- screw pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/084—Toothed wheels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2220/00—Application
- F04C2220/10—Vacuum
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a screw pump. A first rotor and a second rotor have helical teeth each including a dedendum portion, an addendum portion, and an addendum tip portion. Profiles of the addendum portions of the first and second rotors are formed by cycloidal curves. Profiles of the dedendum portions of the first and second rotors are formed by trochoidal curves. A pitch circle of the second rotor is larger than that of the first rotor. The number of teeth of the second rotor is larger than that of the first rotor. A width angle of the first rotor is not less than a minimum angle at which the addendum tip portions of the first rotor are in line contact with an outer circle of the first rotor, and not more than an angle at which a discharge volume ratio is approximately equal to that at the minimum angle.
Description
Technical field
The present invention relates to screw pump.
Background technique
Screw pump possesses the first rotor and second rotor with spiral helicine tooth.Intermesh through the first rotor and second rotor and to form the working room.Screw pump through the rotation of the first rotor and second rotor with in the fluid-filled working room, and from suction port to the exhaust port conveyance fluid.For screw pump, the known situation that the transfer efficiency of fluid is descended because of pore (blow hole) etc.Therefore, for example as TOHKEMY 2001-73959 communique, the raising that comes implementation efficiency through the shape of improving rotor.
In TOHKEMY 2001-73959 communique, disclose power rotor (the first rotor) and meshed and be arranged to rotate screw pump freely with driven rotor (second rotor).In the disclosed screw pump of TOHKEMY 2001-73959 communique, the main profile of tooth of power rotor is the cycloid that the crown end points of driven rotor is described.The main profile of tooth of driven rotor is the trochoid that the crown end points of power rotor is described.Thus, can prevent to produce leakage (pore).
Yet, in the disclosed screw pump of TOHKEMY 2001-73959 communique,, therefore have following problem: when aspect manufacturing procedure and quality are guaranteed, quite taking a lot of work because the crown end points of driven rotor is an acute angle.And generally there be the volumetric efficiency problem more such than Roots pump difference in screw pump.With respect to the volume that holds rotor, the shared volume of rotor is big, and it is little to discharge volume.Therefore, compare with Roots pump with identical discharge volume etc., the build of screw pump is big.
Summary of the invention
The object of the present invention is to provide a kind of acute angle portion and high screw pump of discharge plot ratio that reduces rotor.
In a viewpoint, the present invention provides a kind of screw pump, and this screw pump possesses: housing, and this housing is formed with suction port and exhaust port; The first rotor, this first rotor has spiral helicine tooth, and the rotation be contained in freely in the said housing, wherein this tooth comprises the first tooth root portion, the first crown portion and the first crown end that contacts with said housing; Second rotor; This second rotor has spiral helicine tooth; And to be contained in the said housing with the synchronous rotation of said the first rotor mode freely; Wherein this tooth comprises the second tooth root portion, the second crown portion and the second crown end that contacts with said housing; And the said tooth engagement of this tooth and said the first rotor; The profile of said first crown portion and the said second crown portion is formed by cycloidal curve, and the profile of said first tooth root portion and the said second tooth root portion forms by trochoid curves, and the pitch circle of said second rotor is greater than the pitch circle of said the first rotor; The number of said second rotor is more than the number of said the first rotor, and the width angle of said the first rotor is that the minimum angles that contact with the external diameter circle line of said the first rotor of the said first crown end is above and below the basic angle same of discharge plot ratio when making discharge plot ratio and said minimum angles.
In the present invention, form the profile of the first crown portion, form the profile of the first tooth root portion by trochoid curves by cycloidal curve.Therefore the facewidth of the first rotor is little, thereby reduces the ratio that is the rotor occupancy of rotor volumes with respect to the cylinder volume.Therefore can improve the discharge plot ratio of screw pump.And then, owing to form the obtuse angle part, therefore compare with existing screw pump in the second crown end of second rotor, can reduce acute angle portion.Discharge plot ratio and be with by with the caused volumetric efficiency in the gap of rotor housing, multiply by theoretical ratio that is the theoretical resulting value of plot ratio of discharging of discharging volume with respect to the cylinder volume.
On the intermeshing pitch circle of said tooth of the said tooth of said the first rotor and said second rotor; The cycloidal curve of the said first crown portion changes to the trochoid curves of the said first tooth root portion, and the cycloidal curve of the said second crown portion changes to the trochoid curves of the said second tooth root portion.
Angle when the width angle of said the first rotor and said discharge plot ratio are maximum differs in 4 degree.And the width angle of said the first rotor is more than the said minimum angles and below the angle than big 9 degree of said minimum angles.
The interval of the axis of rotation of said the first rotor and the axis of rotation of said second rotor is with respect to the ratio of the external diameter diameter of a circle of said the first rotor, for more than the minimum value of setting up boundary and than in the scope below the value of said minimum value big 0.02.
The first rotor can have 3 teeth, and second rotor can have 4 teeth.
In other viewpoint, the present invention provides a kind of screw pump, and this screw pump possesses: housing, and this housing is formed with suction port and exhaust port; The first rotor, this first rotor has spiral helicine tooth, and the rotation be contained in freely in the said housing, wherein this tooth comprises the first tooth root portion, the first crown portion and the first crown end that contacts with said housing; And second rotor; This second rotor has spiral helicine tooth; And to be contained in the said housing with the synchronous rotation of said the first rotor mode freely; Wherein this tooth comprises the second tooth root portion, the second crown portion and the second crown end that contacts with said housing, and the said tooth engagement of this tooth and said the first rotor, and the profile of the said first crown portion is formed by cycloidal curve; And the profile of the said first tooth root portion is formed by involute curve; The profile of the said second crown portion is formed by involute curve, and the profile of the said second tooth root portion forms by trochoid curves, and the pitch circle of said second rotor is greater than the pitch circle of said the first rotor; The number of said second rotor is more than the number of said the first rotor, and the width angle of said the first rotor is that the minimum angles that contact with the external diameter circle line of said the first rotor of the said first crown end is above and below the basic angle same of discharge plot ratio when making discharge plot ratio and said minimum angles.
In the present invention, the profile of the first crown portion is formed by cycloidal curve, and the profile of the first tooth root portion is formed by involute curve, and the profile of the second crown portion is formed by involute curve, and the profile of the second tooth root portion is formed by trochoid curves.Therefore the facewidth of the first rotor is little, thereby reduces the rotor occupancy.Therefore can improve the discharge plot ratio of screw pump.And then, form the obtuse angle part in the second crown end of second rotor, thereby compare with existing screw pump, can reduce acute angle portion.
Can understand the present invention more fully through following description and to the explanation of respective drawings, and these descriptions and the explanation should not be regarded as limitation of the present invention.
Detailed description according to after this can make embodiment of the present invention become clear.Yet; Although show the preferred implementation of invention; Also only being to be understood as is detailed description and the object lesson that carries out through diagram; Because according to so detailed description, to those skilled in the art, obviously can in purport of the present invention and scope, carry out various changes and modification.
Description of drawings
Fig. 1 is the vertical view cutaway drawing of the related screw pump of this mode of execution.
Fig. 2 is the sectional view of the related the first rotor of this mode of execution and second rotor.
Fig. 3 illustrates the first rotor that is used to simulate and the sectional view of second rotor.
Fig. 4 is the figure that analog result is shown.
Fig. 5 is the figure that analog result is shown.
Fig. 6 is the figure that analog result is shown.
Fig. 7 is the figure that analog result is shown.
Fig. 8 is the sectional view of the rotor of the related screw pump of the variation of this mode of execution.
Embodiment
Below, with reference to accompanying drawing preferred implementation of the present invention is elaborated.Wherein, in explanation, same parts or parts with identical function are used same numeral, and the explanation that will repeat omission.
As shown in Figure 1, screw pump 10 is screw pumps of horizontal arrangement type.Screw pump 10 for example is used as the vacuum pump of exempting to refuel.The formation of the housing of screw pump 10 comprises: rotor housing 11; Front end shell 12, this front end shell 12 engages with the front end of rotor housing 11; And rear end housing 13, this rear end housing 13 engages with the rearward end of rotor housing 11.Space portion in housing accommodates the intermeshing the first rotor 20 and second rotor 30.
Be formed with in one distolateral (left side of Fig. 1) of rotor housing 11 fluid is drawn into the suction port 14 in the housing.Be formed with the exhaust port 15 that the fluid in the housing is discharged to the outside on rotor housing 11 another distolateral (right side of Fig. 1).Suction port 14 openings are general square shape, and near 30 configurations of second rotor.Suction port 14 is in the face of two rotor 20,30 position engaged.Exhaust port 15 is at second rotor, 30 side openings.The opening area of exhaust port 15 is configured to the opening area less than suction port 14.
Connect the first rotor 20 for first 21 and be fixed in the first rotor 20.Connect second rotor 30 for second 31 and be fixed in second rotor 30.The axis of rotation A2 of the axis of rotation A1 of the first rotor 20 and second rotor 30 is with interval L parallel configuration.An end of first 21 (left side of Fig. 1) is inserted and is led among the axis hole 12A that is formed at front end shell 12, is supported on front end shell 12 via bearing 18.The other end of first 21 (right side of Fig. 1) is inserted and is led among the axis hole 13A that is formed at rear end housing 13, is supported on rear end housing 13 via bearing 18.
An end of second 31 (left side of Fig. 1) is inserted and is led among the axis hole 12B that is formed at front end shell 12, is supported on front end shell 12 via bearing 18.The other end of second 31 (right side of Fig. 1) is inserted and is led among the axis hole 13B that is formed at rear end housing 13, is supported on rear end housing 13 via bearing 18.That is, the first rotor 20 by the first spool 21 center impeller type ground axle suspension outstanding from two ends in housing.The second 31 center impeller type ground axle suspension that second rotor, 30 quilts are given prominence to from two ends is in housing.
Across rear end housing 13 and opposition side rotor housing 11, gear-box 40 engages with rear end housing 13.Gear-box 40 is with rear end housing formative gear chambers 41 13.The other end of first 21 connects rear end housing 13, at gear-box 40 internal fixation in actuation gear 42.The other end of second 31 connects rear end housing 13, at gear-box 40 internal fixation in driven gear 43.In gear-box 40, dispose the motor 45 as driving source, the output shaft 46 of motor 45 links via the other end of coupling 47 and first 21.Through the engagement of actuation gear 42 with driven gear 43, first 21 rotation is passed to second 31 via actuation gear 42 and driven gear 43, thereby the first rotor 20 and second rotor 30 rotate synchronously.
Next, based on Fig. 2 the shape of the first rotor 20 and second rotor 30 is described.
The first rotor 20 is external rotors of three teeth.The first rotor 20 has the axle side face of representing with internal diameter circle 20B1.The first rotor 20 possesses a plurality of teeth (being 3 teeth) 20A in this mode of execution, these a plurality of tooth 20A from the axle side face radially with radial extension and shape in the shape of a spiral.Internal diameter circle 20B1 is to be the circle at center with first 21 axis of rotation A1.As shown in Figure 2, on the cross section of the first rotor 20, each tooth 20A is respectively with uniformly-spaced configuration.
The 20A2 of crown portion that the tooth 20A of the first rotor 20 has the 20A1 of tooth root portion that is positioned at axis of rotation A1 side and is positioned at the outer circumferential side of the 20A1 of tooth root portion.The border of 20A1 of tooth root portion and the 20A2 of crown portion is arranged on the pitch circle of the first rotor of representing with footpath circle 2,0B2 20.Tooth 20A has the crown end 20A3 that representes with external diameter circle 20B3 at the front end radially of the 20A2 of crown portion.As shown in Figure 2, the 20A1 of tooth root portion justifies the position between 20B1 and the middle footpath circle 20B2 at internal diameter diametrically.The 20A2 of crown portion justifies the position between 20B2 and the external diameter circle 20B3 in middle footpath diametrically.The diameter of middle footpath circle 20B2 is set the diameter greater than internal diameter circle 20B1 for.The diameter of external diameter circle 20B3 is set the diameter greater than middle footpath circle 20B2 for.The part of the inner peripheral surface of rotor housing 11 forms in the position along external diameter circle 20B3.Crown end 20A3 contacts with the inner peripheral surface of rotor housing 11 on external diameter circle 20B3.Because the tooth 20A of the first rotor 20 forms helical, so crown end 20A3 is with respect to the internal surface line contact of rotor housing 11.
The 30A2 of crown portion that the tooth 30A of second rotor 30 has the 30A1 of tooth root portion that is positioned at axis of rotation A2 side and is positioned at the outer circumferential side of the 30A1 of tooth root portion.The border of 30A1 of tooth root portion and the 30A2 of crown portion is arranged on the pitch circle of second rotor of representing with footpath circle 3,0B2 30.Tooth 30A has the crown end 30A3 that representes with external diameter circle 30B3 at the front end radially of the 30A2 of crown portion.As shown in Figure 2, the 30A1 of tooth root portion justifies the position between 30B1 and the middle footpath circle 30B2 at internal diameter diametrically.The 30A2 of crown portion justifies the position between 30B2 and the external diameter circle 30B3 in middle footpath diametrically.Crown end 30A3 forms circular-arc with the mode along external diameter circle 30B3.The diameter of middle footpath circle 30B2 is set the diameter greater than internal diameter circle 30B1 for.The diameter of external diameter circle 30B3 is set the diameter greater than middle footpath circle 30B2 for.In this mode of execution, the external diameter of the first rotor 20 circle 20B3 forms with identical diameter with the external diameter circle 30B3 of second rotor 30.The part of the inner peripheral surface of rotor housing 11 is formed on along the position of external diameter circle 30B3.Crown end 30A3 contacts with the inner peripheral surface of constant face with rotor housing 11 on external diameter circle 30B3.
The profile of the 20A1 of tooth root portion of the first rotor 20 is formed by trochoid curves based on the external diameter circle 30B3 of second rotor 30.That is to say that the profile of the 20A1 of tooth root portion forms with the mode that a bit is arranged in arbitrarily on the trochoid curves that begins to describe from certain point as the footpath circle 20B2 of the pitch circle of the first rotor 20 on the external diameter of the second rotor 30 circle 30B3.In this mode of execution, the profile of the 20A1 of tooth root portion all forms time pendulum curve.The profile of the 20A2 of crown portion of the first rotor 20 is formed by cycloidal curve based on the middle footpath circle 30B2 of second rotor 30.That is to say that the profile of the 20A2 of crown portion forms with the mode that a bit is arranged in arbitrarily on the cycloidal curve that begins to describe from certain point as the footpath circle 20B2 of the pitch circle of the first rotor 20 on the middle footpath circle 30B2 of second rotor 30.Article two, cycloidal curve intersects at crown end 20A3 (on the external diameter circle 20B3).The profile of the 20A2 of crown portion all forms cycloidal curve.
The facewidth of each tooth 20A of the first rotor 20 is stipulated with width angle θ shown in Figure 2.Width angle θ be from the axis of rotation A1 of the first rotor 20 with tooth 20A width on the circle 20B2 of footpath formed angle when linking.In the first rotor 20, form each the tooth 20A in 3 teeth with identical width angle θ.As width angle θ during greater than angle shown in Figure 2, crown end 20A3 is to widen with 11 modes that contact of rotor housing on external diameter circle 20B3.As width angle θ during less than angle shown in Figure 2, crown end 20A3 is positioned at radially inner side, thereby does not contact with rotor housing 11.Therefore because fluid can be from clearance leakage, thereby screw pump 10 becomes and can't bring into play function as pump.As shown in Figure 2, the width angle θ when crown end 20A3 contacts with the internal surface line of rotor housing 11 on external diameter circle 20B3 is the minimum angles of width angle θ.That is the width angle θ when, crown end 20A3 contacts with external diameter circle 20B3 line is the minimum angles of width angle θ.In this mode of execution, the width angle θ of the first rotor 20 is set at this minimum angles.
The profile of the 30A1 of tooth root portion of second rotor 30, round 20B3 is formed by trochoid curves based on the external diameter of the first rotor 20.That is to say that the profile of the 30A1 of tooth root portion forms with the mode that a bit is arranged in arbitrarily on the trochoid curves that begins to describe from certain point as the footpath circle 30B2 of the pitch circle of second rotor 30 on the external diameter of the first rotor 20 circle 20B3.In this mode of execution, the profile of the 30A1 of tooth root portion all forms trochoid curves.The profile of the 30A2 of crown portion of second rotor 30 is formed by cycloidal curve based on the middle footpath circle 20B2 of the first rotor 20.That is to say that the profile of the 30A2 of crown portion forms with the mode that a bit is arranged in arbitrarily on the cycloidal curve that begins to describe from certain point as the footpath circle 30B2 of the pitch circle of second rotor 30 on the middle footpath circle 20B2 of the first rotor 20.In this mode of execution, the trochoid curves of the 30A1 of tooth root portion contacts with the internal diameter circle 30B1 of second rotor 30.That is to say that adjacent tooth 30A forms the 30A1 of tooth root portion by a trochoid curves.The part of the internal surface of the arrival rotor housing 11 of the 30A2 of crown portion (external diameter circle 30B3) is formed by cycloidal curve.
The analog result of the theory of the width angle θ of the first rotor 20 and screw pump 10 being discharged plot ratio is described here.Fig. 3 is the figure in cross section that is illustrated in this simulation the first rotor 20 and second rotor 30 of the screw pump 10 that uses.In this simulation, the diameter of the external diameter of the first rotor 20 being justified 20B3 is made as 100 millimeters.Interval L between the axis of rotation A2 of the axis of rotation A1 of the first rotor 20 and second rotor 30 is made as 70 millimeters.The first rotor 20 possesses 3 teeth, and number is 3.Second rotor 30 possesses 4 teeth, and number is 4.In the first rotor 20 and second rotor 30, the profile of the 20A1 of tooth root portion, 30A1 is formed by trochoid curves.The profile of the 20A2 of crown portion, 30A2 is formed by cycloidal curve.
The theory of the screw pump 10 when the width angle θ that Fig. 4 shows the first rotor 20 that makes Fig. 3 changes is discharged the variation of plot ratio.Utilize the theoretical plot ratio of discharging of following formula (1) definition here.
Theoretical plot ratio=the theory of discharging is discharged volume/cylinder volume ... (1)
Theoretical discharge volume is that the first rotor 20 revolves the discharge volume when turning around.The cylinder volume is the volume that holds the rotor housing 11 of the first rotor 20 and second rotor 30.
As shown in Figure 4, the width angle θ of the first rotor 20 is set to 51 degree, 60 degree, 70 degree, 80 degree respectively and simulates.Its result, when the width angle θ of the first rotor 20 increased, the theoretical plot ratio of discharging reduced.In analog result, when width angle θ is 51 when spending, the theoretical plot ratio of discharging is maximum, is about 0.50.Therefore the width angle θ of the first rotor 20 is preferably less.Under these simulated conditions, the minimum angles of the width angle θ of the first rotor 20 is 51 degree.That is to say, when width angle θ being set at when spending less than 51, because of the first rotor 20 and the internal surface of rotor housing 11 between have the gap and increase escape of liquid, thereby the efficient of screw pump 10 significantly reduces.
Illustrated among Fig. 4 crown end 20A3 and crown end 30A3 external diameter circle 20B3,30B3 is last with the inner peripheral surface state of contact of rotor housing 11 under; And when the width angle θ that makes the first rotor 20 changed, the theory of screw pump 10 was discharged the analog result of the variation of plot ratio.Yet, when reality is made screw pump 10, because the relation of surface friction drag and manufacturing tolerances, needing the gap respectively between the crown end 20A3 of the first rotor 20 and the rotor housing 11 and between the crown end 30A3 of second rotor 30 and the rotor housing 11.Because volumetric efficiency changes because of these gaps, therefore utilize following formula (2) to define actual discharge plot ratio.
Discharge plot ratio=theory and discharge plot ratio * volumetric efficiency ... (2)
Fig. 5 shows under the situation of in the build of screw pump 10, having set general gap and when the width angle θ of the first rotor 20 of Fig. 3 is changed, the variation of the discharge plot ratio of screw pump 10.As shown in Figure 5, the width angle θ of the first rotor 20 is set at 51 degree, 60 degree, 70 degree, 80 degree respectively and simulates.Its result when the width angle θ of the first rotor 20 increases, discharges plot ratio and after increasing, reduces.In analog result, when width angle θ is 51 when spending, discharge plot ratio and be about 0.461, when width angle θ is 60 when spending, discharge plot ratio and be about 0.460.The details of the discharge plot ratio when width angle θ being set at the angle of 51 degree between spending with 60 is simulated.When width angle θ is 55 when spending, it be maximum discharging plot ratio, after this if width angle θ spends greater than 55, then discharges plot ratio and reduces.Discharge plot ratio and width angle θ in width angle θ is the scope of 59 degree is that 51 discharge plot ratio when spending are basic identical.Even under this simulated conditions, the minimum angles of the width angle θ of the first rotor 20 also is 51 degree.
Next, based on Fig. 6 other analog result is described.These simulated conditions are identical with the simulated conditions of Fig. 4.That is to say that the diameter of external diameter being justified 20B3 is made as 100 millimeters, L is made as 70 millimeters at interval.And then, the number of number and second rotor 30 of the first rotor 20 is changed respectively and measure theoretical discharge plot ratio.The width angle θ of the first rotor 20 is set at, even number changes, the width angle θ of the first rotor 20 also is always minimum angles.
As shown in Figure 6, be under 3 the situation in the number of the first rotor 20, be to compare in 4 o'clock with the number of second rotor 30, it is low that the number of second rotor 30 is that 5 o'clock theory is discharged plot ratio.Being under 4 the situation in the number of the first rotor 20, is to compare in 5 o'clock with the number of second rotor 30, and it is low that the number of second rotor 30 is that 6 o'clock theory is discharged plot ratio.Thus, can know about the number of the first rotor 20 and second rotor 30, when the difference of the number of the number of the first rotor 20 and second rotor 30 hour, can increase the theoretical plot ratio of discharging.Under the condition of this simulation, when the number of the first rotor 20 is 5, can't form number and be 7 second rotor 30.
And then as shown in Figure 6, the number that is accompanied by the first rotor 20 increases the rising of theoretical discharge plot ratio from 3 to 4,5.Can know that according to this Simulation result when the number of the first rotor 20 is the number of 5 and second rotor 30 when being 6, the theoretical plot ratio of discharging is the highest, is about 0.535.
Next, based on Fig. 7 other analog result is described.In this simulation, the width angle θ with the first rotor 20 is made as minimum angles all the time.The diameter of external diameter circle 20B3 is 100 millimeters.And then when the number that makes the first rotor 20 and second rotor 30 changed, the variation of the theory discharge plot ratio under the situation that the interval L of the axis of rotation A1 that makes the first rotor 20 and the axis of rotation A2 of second rotor 30 is changed was measured.The number of second rotor 30 is set at greater than the number of the first rotor 20 and both differences are reduced.That is to say that the number of second rotor 30 is bigger by 1 than the number of the first rotor 20.
As shown in Figure 7, if reduce L at interval, the increase of then theoretical discharge plot ratio since 70 millimeters.Can know according to this Simulation result; In the number of the first rotor 20 is that the number of 3 and second rotor 30 is under 4 the situation; When interval L with respect to the ratio of the round 20B3 of external diameter (diameter of L/ external diameter circle 20B3 at interval) when being 0.62, the theoretical plot ratio of discharging is maximum, is about 0.63.
Be under 3 the situation in the number of the first rotor 20, if at interval L with respect to the ratio of the round 20B3 of external diameter less than 0.62, then the first rotor 20 and second rotor 30 too near.Therefore, can't be false by screw pump 10.That is to say, about the ratio of interval L (62 millimeters) with respect to the round 20B3 of external diameter (100 millimeters), be that the number of 3 and second rotor 30 is that the establishment boundary of screw pump 10 is 0.62 under 4 the situation in the number of the first rotor 20.L is with respect to ratio the getting final product more than 0.62 for the establishment boundary of the round 20B3 of external diameter at interval.Equally, about the ratio of interval L (66 millimeters), be that the number of 4 and second rotor 30 is under 5 the situation in the number of the first rotor 20 with respect to the round 20B3 of external diameter (100 millimeters), be 0.66 as the minimum value of setting up boundary.
About the ratio of interval L (69 millimeters) with respect to the round 20B3 of external diameter (100 millimeters), be that the number of 5 and second rotor 30 is under 6 the situation in the number of the first rotor 20, be 0.69 as the minimum value of setting up boundary.Therefore; Can know according to analog result shown in Figure 7; Preferably, if make L at interval with respect to the ratio of the round 20B3 of external diameter be in from the value of the establishment boundary of the first rotor 20 and second rotor 30 begin, to than in the scope till the value of the value big 0.02 of setting up boundary, then theoretical discharge plot ratio height.
Based on Fig. 4～analog result shown in Figure 7, the shape of the first rotor shown in Figure 2 20 and second rotor 30 is further specified.The number of the first rotor 20 is 3.The number of second rotor 30 is greater than the number of the first rotor 20, for the number difference that makes both little 4.Setting the round 20B3 of the external diameter of the first rotor 20 for diameter is 100 millimeters.Interval L between the axis of rotation A2 of the axis of rotation A1 of the first rotor 20 and second rotor 30 is preferably set to 62 millimeters.The width angle θ of the first rotor 20 preferably sets and is spending to 59 degree from 51.Though width angle θ preferably sets spending from 51 of minimum angles to 59 degree,, be allowed band about 1 degree then if consider manufacturing tolerances.That is to say, if width angle θ to be 51 degree above and 60 degree with interior, can improve the discharge plot ratio.And the angle when the width angle θ of the first rotor 20 and discharge plot ratio are maximum preferably differs in 4 degree.For Fig. 6 and simulation shown in Figure 7, owing to do not relate to rotor housing 11, therefore theoretical increase of discharging plot ratio continues to have influence on the increase of discharging plot ratio.
According to this mode of execution, can obtain following effect.
In the first rotor 20 and second rotor 30 of screw pump 10, the profile of each 20A1 of tooth root portion, 30A1 is formed by trochoid curves, and the profile of each 20A2 of crown portion, 30A2 is formed by cycloidal curve.Thus, can reduce pore, thereby high efficiency screw pump 10 can be provided.
The number of second rotor 30 is greater than the number of the first rotor 20, and the pitch circle of second rotor 30 is set at the pitch circle greater than the first rotor 20.Owing to the width angle θ of the first rotor 20 is set at the angle of the discharge plot ratio that the discharge plot ratio can obtain with crown end 20A3 with minimum angles that external diameter circle 20B3 line contacts the time equates basically, so can improves the discharge plot ratio of screw pump 10.Because it is high to discharge plot ratio, therefore can realize the miniaturization of screw pump 10.
Because second rotor 30 is formed by cycloidal curve and trochoid curves, therefore can reduce the acute angle portion of second rotor 30.If acute angle portion reduces, then processing becomes easy.And, can improve the quality of second rotor 30.
For the first rotor 20 and since week upwards uniformly-spaced and from facing in each week 3 tooth 20A being set radially radially, so the balance during the first rotor 20 rotations is good.For second rotor 30, owing to making progress in week uniformly-spaced and from facing in each week 4 tooth 30A to be set radially radially, the balance when therefore second rotor 30 rotates is good.And then as screw pump 10, balance is good when the first rotor 20 and the 30 engagement rotations of second rotor.
Be set to more than the minimum value of setting up boundary and with respect to the ratio of the external diameter circle 20B3 of the first rotor 20 for the interval L of the axis of rotation A1 of the first rotor 20 and the axis of rotation A2 of second rotor 30 than in the scope below the value of minimum value big 0.02.The theory that thus, can improve screw pump 10 is discharged efficient.And, can realize the miniaturization of screw pump 10.
The present invention is not limited to above-mentioned mode of execution.Though in the above-described embodiment, the profile of the first rotor 20 and third trochanter 30 is only formed by cycloidal curve and trochoid curves, is not limited thereto.For example shown in Figure 8, can utilize involute curve to form the part of profile of the 60A1 of tooth root portion of the first rotor 60.Fig. 8 is the sectional view of screw pump, in this screw pump, width angle be θ the first rotor that possesses 4 tooth 60A 60, with second rotor 70 engagement that possesses 6 tooth 70A.Tooth 60A has: the 60A1 of tooth root portion, and the 60A1 of this tooth root portion is between internal diameter circle 60B1 and middle footpath circle 60B2; The 60A2 of crown portion, the 60A2 of this crown portion is between middle footpath circle 60B2 and external diameter circle 60B3; And crown end 60A3, this crown end 60A3 is the tip of the 60A2 of crown portion.Tooth 70A has: the 70A1 of tooth root portion, and the 70A1 of this tooth root portion is between internal diameter circle 70B1 and middle footpath circle 70B2; The 70A2 of crown portion, the 70A2 of this crown portion is between middle footpath circle 70B2 and external diameter circle 70B3; And crown end 70A3, this crown end 70A3 is the tip of the 70A2 of crown portion.
The profile of the 60A1 of tooth root portion of the first rotor 60 is formed by involute curve and trochoid curves.The profile of the 60A1 of tooth root portion therefrom footpath circle 60B2 forms involute curve towards internal diameter circle 60B1, near internal diameter circle 60B1, changes trochoid curves into.The profile of the 70A2 of crown portion of second rotor 70 is formed by cycloidal curve and involute curve.The involute curve of the 60A1 of tooth root portion of the first rotor 60 is corresponding with the involute curve of the 70A2 of crown portion of second rotor 70.If the first rotor 60 and second rotor 70 rotate synchronously, then involute curve contacts with each other.Even in the profile of the first rotor 20 and second rotor 30, all adopt under the situation of involute curve, the discharge plot ratio is also big, thereby can realize the miniaturization of screw pump.The basic angle same of discharge plot ratio when the width angle θ of the first rotor 60 is set at the discharge plot ratio that makes screw pump and above-mentioned minimum angles.
Though in screw pump shown in Figure 8, omitted diagram, identical with screw pump 10 shown in Figure 1, screw pump has: housing, this housing is made up of rotor housing 11, front end shell 12 and rear end housing 13.The first rotor 60 and second rotor 70 are contained in the space portion in the housing.The profile of the profile of the 60A2 of crown portion of the first rotor 60 and the 20A2 of crown portion of the first rotor 20 is formed by cycloidal curve equally.The profile of the profile of the 70A1 of tooth root portion of second rotor 70 and the 30A1 of tooth root portion of second rotor 30 is formed by trochoid curves equally.Set the pitch circle of second rotor 70 for pitch circle greater than the first rotor 60.On the intermeshing pitch circle of tooth 70A of the tooth 60A of the first rotor 60 and second rotor 70; The cycloidal curve of the 60A2 of crown portion changes to the involute curve of the 60A1 of tooth root portion, and the involute curve of the 70A2 of crown portion changes to the trochoid curves of the 70A1 of tooth root portion.The interval L of the axis of rotation of the first rotor 60 and the axis of rotation of second rotor 70 is with respect to the ratio of the external diameter circle 60B3 of the first rotor 60, and it is above and than in the scope below the value of minimum value big 0.02 to be set to the minimum value of setting up boundary.Angle when the width angle θ of the first rotor 60 and discharge plot ratio are maximum differs in 4 degree.And the width angle θ of the first rotor 60 is more than the minimum angles and below the angle than big 9 degree of minimum angles.
The profile of all 20A1 of tooth root portion, 30A1 and the 20A2 of crown portion, 30A2 can not be involute curve or trochoid curves.For example, can be near crown end 20A3,30A3, make circular-arc curve localized variation and form tooth 20A, 30A.In footpath circle 20B2,30B2 may not one fix on the pitch circle.Even middle footpath circle 20B2,30B2 are greater than or less than each pitch circle, the theoretical plot ratio of discharging is also big, thereby also can realize the miniaturization of screw pump.
Though the external diameter of the first rotor 20 circle 20B3 is identical with the external diameter circle 30B3 size of second rotor 30 in this mode of execution, is not limited thereto.Though in the structure shown in Figure 2 of this mode of execution, each external diameter circle 20B3,30B3 are made as identically, can be used in combination the purposes and the place of screw pump 10, change the size that each external diameter is justified 20B3,30B3.
According to the invention of description like this, obviously can change this invention in many ways.Should these changes not regarded as and break away from purport of the present invention and scope, and all these changes will be apparent to those skilled in the art, thereby all these changes should be included in the scope of claims.
Claims (12)
1. screw pump is characterized in that possessing:
Housing, this housing is formed with suction port and exhaust port;
The first rotor, this first rotor has spiral helicine tooth, and the rotation be contained in freely in the said housing, wherein this tooth comprises the first tooth root portion, the first crown portion and the first crown end that contacts with said housing;
Second rotor; This second rotor has spiral helicine tooth; And to be contained in the said housing with the synchronous rotation of said the first rotor mode freely; Wherein this tooth comprises the second tooth root portion, the second crown portion and the second crown end that contacts with said housing, and the said tooth engagement of this tooth and said the first rotor
The profile of said first crown portion and the said second crown portion is formed by cycloidal curve, and the profile of said first tooth root portion and the said second tooth root portion forms by trochoid curves,
The pitch circle of said second rotor is greater than the pitch circle of said the first rotor,
The number of said second rotor is more than the number of said the first rotor,
The width angle of the said the first rotor minimum angles that to be the said first crown end contact with the external diameter of said the first rotor circle line is above and below the basic angle same of discharge plot ratio when making discharge plot ratio and said minimum angles.
2. screw pump according to claim 1 is characterized in that,
On the intermeshing pitch circle of said tooth of the said tooth of said the first rotor and said second rotor; The cycloidal curve of the said first crown portion changes to the trochoid curves of the said first tooth root portion, and the cycloidal curve of the said second crown portion changes to the trochoid curves of the said second tooth root portion.
3. screw pump according to claim 1 and 2 is characterized in that,
Angle when the width angle of said the first rotor and said discharge plot ratio are maximum differs in 4 degree.
4. screw pump according to claim 1 and 2 is characterized in that,
The width angle of said the first rotor is more than the said minimum angles and for below the angle than big 9 degree of said minimum angles.
5. according to each described screw pump in the claim 1～4, it is characterized in that,
The interval of the axis of rotation of said the first rotor and the axis of rotation of said second rotor is with respect to the ratio of the external diameter diameter of a circle of said the first rotor, for more than the minimum value of setting up boundary and than in the scope below the value of said minimum value big 0.02.
6. according to each described screw pump in the claim 1～5, it is characterized in that,
Said the first rotor has 3 said teeth,
Said second rotor has 4 said teeth.
7. screw pump is characterized in that possessing:
Housing, this housing is formed with suction port and exhaust port;
The first rotor, this first rotor has spiral helicine tooth, and the rotation be contained in freely in the said housing, wherein this tooth comprises the first tooth root portion, the first crown portion and the first crown end that contacts with said housing; And
Second rotor; This second rotor has spiral helicine tooth; And to be contained in the said housing with the synchronous rotation of said the first rotor mode freely; Wherein this tooth comprises the second tooth root portion, the second crown portion and the second crown end that contacts with said housing, and the said tooth engagement of this tooth and said the first rotor
The profile of the said first crown portion is formed by cycloidal curve, and the profile of the said first tooth root portion forms by involute curve,
The profile of the said second crown portion is formed by involute curve, and the profile of the said second tooth root portion forms by trochoid curves,
The pitch circle of said second rotor is greater than the pitch circle of said the first rotor,
The number of said second rotor is more than the number of said the first rotor,
The width angle of the said the first rotor minimum angles that to be the said first crown end contact with the external diameter of said the first rotor circle line is above and below the basic angle same of discharge plot ratio when making discharge plot ratio and said minimum angles.
8. screw pump according to claim 7 is characterized in that,
On the intermeshing pitch circle of said tooth of the said tooth of said the first rotor and said second rotor; The cycloidal curve of the said first crown portion changes to the involute curve of the said first tooth root portion, and the involute curve of the said second crown portion changes to the trochoid curves of the said second tooth root portion.
9. according to claim 7 or 8 described screw pumps, it is characterized in that,
Angle when the width angle of said the first rotor and said discharge plot ratio are maximum differs in 4 degree.
10. according to claim 7 or 8 described screw pumps, it is characterized in that,
The width angle of said the first rotor is more than the said minimum angles and for below the angle than big 9 degree of said minimum angles.
11. according to each described screw pump in the claim 7～10, it is characterized in that,
The interval of the axis of rotation of said the first rotor and the axis of rotation of said second rotor is with respect to the ratio of the external diameter diameter of a circle of said the first rotor, for more than the minimum value of setting up boundary and than in the scope below the value of said minimum value big 0.02.
12. according to each described screw pump in the claim 7～11, it is characterized in that,
Said the first rotor has 4 said teeth,
Said second rotor has 6 said teeth.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011054168 | 2011-03-11 | ||
| JP2011-054168 | 2011-03-11 | ||
| JP2012-034454 | 2012-02-20 | ||
| JP2012034454A JP2012207660A (en) | 2011-03-11 | 2012-02-20 | Screw pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102678542A true CN102678542A (en) | 2012-09-19 |
Family
ID=45833204
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012100601911A Pending CN102678542A (en) | 2011-03-11 | 2012-03-08 | Screw pump |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20120230858A1 (en) |
| JP (1) | JP2012207660A (en) |
| KR (1) | KR20120104113A (en) |
| CN (1) | CN102678542A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103850931A (en) * | 2012-12-05 | 2014-06-11 | 上海易昆机械工程有限公司 | Pulseless rotor pump |
| CN107110156A (en) * | 2015-01-05 | 2017-08-29 | 株式会社爱发科 | Screw vacuum pump |
| CN112639414A (en) * | 2018-09-11 | 2021-04-09 | 科门股份公司 | Rotary flowmeter for measuring gas flow |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013021902B4 (en) * | 2013-12-26 | 2017-06-14 | HENKE Property UG (haftungsbeschränkt) | Melting pump for building up pressure for pushing plastic melt through a tool |
| WO2016031413A1 (en) * | 2014-08-28 | 2016-03-03 | 株式会社Ihi | Screw rotor |
| CN109441811A (en) * | 2018-12-26 | 2019-03-08 | 东莞赫升机电有限公司 | Stack rotator type helical-lobe compressor |
| PL3938657T3 (en) * | 2019-03-14 | 2023-10-16 | Ateliers Busch S.A. | Dry pump for gas and set of a plurality of dry pumps for gas |
| US11708832B2 (en) | 2019-08-02 | 2023-07-25 | Fruvac Ltd. | Cooled dry vacuum screw pump |
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| US3692441A (en) * | 1971-05-20 | 1972-09-19 | Pavel Evgenievich Amosov | Screw rotor machine for compressible media |
| CA2298689C (en) * | 1998-06-01 | 2006-03-21 | Mayekawa Mfg., Ltd. | Screw compressor with adjustable full-load capacity |
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- 2012-02-20 JP JP2012034454A patent/JP2012207660A/en active Pending
- 2012-03-08 CN CN2012100601911A patent/CN102678542A/en active Pending
- 2012-03-09 US US13/416,795 patent/US20120230858A1/en not_active Abandoned
- 2012-03-09 KR KR1020120024384A patent/KR20120104113A/en not_active Application Discontinuation
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| JPH05296159A (en) * | 1992-04-20 | 1993-11-09 | Tokico Ltd | Rotor for positive displacement rotating machine |
| CN1172215A (en) * | 1997-01-14 | 1998-02-04 | 中国船舶工业总公司第七研究院第七一一研究所 | Mixed transfer pump with internal compression screw arbor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103850931A (en) * | 2012-12-05 | 2014-06-11 | 上海易昆机械工程有限公司 | Pulseless rotor pump |
| CN107110156A (en) * | 2015-01-05 | 2017-08-29 | 株式会社爱发科 | Screw vacuum pump |
| CN112639414A (en) * | 2018-09-11 | 2021-04-09 | 科门股份公司 | Rotary flowmeter for measuring gas flow |
Also Published As
| Publication number | Publication date |
|---|---|
| US20120230858A1 (en) | 2012-09-13 |
| JP2012207660A (en) | 2012-10-25 |
| KR20120104113A (en) | 2012-09-20 |
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Application publication date: 20120919 |