CN102705227A - Multi-tooth difference internal gear pump - Google Patents
Multi-tooth difference internal gear pump Download PDFInfo
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- CN102705227A CN102705227A CN2012101951560A CN201210195156A CN102705227A CN 102705227 A CN102705227 A CN 102705227A CN 2012101951560 A CN2012101951560 A CN 2012101951560A CN 201210195156 A CN201210195156 A CN 201210195156A CN 102705227 A CN102705227 A CN 102705227A
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Abstract
The invention belongs to the technical field of gear pumps, and relates to a multi-tooth difference internal gear pump, in particular to a multi-tooth difference internal gear pump which is applied to hydraulic equipment such as machine tools, automobiles, injection molding machines and oil field machines. The multi-tooth difference internal gear pump is characterized in that the tooth profile of an inner rotor and the tooth profile of an outer rotor are a cycloid curve and an arc curve respectively, a working fluid inlet and a working fluid outlet are formed on the housing of a rotor chamber and communicate with a part of the fluid of the rotor chamber respectively, a backing plate and an eccentric sleeve are arranged in the housing of the rotor chamber, the inner rotor and the outer rotor are rotatable and arranged in the eccentric sleeve, the difference in tooth number between the inner rotor and the outer rotor is more than 1, the tooth number of the inner rotor and the tooth number of the outer rotor are a mutually prime number, a non-complete crescent member is adopted, and the profile of the non-complete crescent member is a part of arc of intersection of the root circle (radius of r2f) of the outer rotor and the crown circle (radius of r1a) of the inner rotor. The working pressure pulsation and working noise of the internal gear pump are reduced, the problem of oil accumulation in the rotor chamber is solved, and the production efficiency of the hydraulic equipment is effectively increased.
Description
Technical field
The invention belongs to the gear pump field, particularly a kind of multiple tooth poor crescent gear pump is applicable to hydraulic equipments such as lathe, automobile, injection machine and oilfield machinery.
Background technique
In the Fluid Transmission and Control technology; Mostly the gear pump that uses is full depth tooth wheel pump, vane pump and plunger pump etc.; Have simple in structure, advantages such as volume is little, anti-pollution, manufacturing easily, convenient for maintaining, be widely used in hydraulic equipment technical fields such as lathe, automobile, injection machine and oilfield machinery.
Can know according to present design; The internal rotor of crescent gear pump and external rotor are installed in the pump case with rotatable mode; Pump case is provided with entrance and exit, and the spin axis of two rotors is spaced from each other engagement in the zone of their tooth between the entrance and exit of pump case.Between two rotors, be provided with the crescent shape member with the corresponding position, engagement place of tooth; When the rotor rotation allows pump to pressurize to working fluid with the inlet outlet that separates housing; The tooth top of internal rotor is with the internal surface of sealing means joint crescent shape member, and the tooth top of external rotor engages the outer surface of crescent shape member with sealing means.The rotor of crescent gear pump comprises internal rotor and external rotor, and the profile geometry of design, the especially inner and outer rotors of other auxiliary device, and is extremely important for the proper functioning of guaranteeing pump.
Chinese patent file CN101120172A proposes a kind of crescent gear pump and the rotor set that is used for intermeshing gear pump.Outer rotor teeth in this rotor set has compound flank profil, and compound flank profil forms circular arc on the part near tooth root, on the part near tooth top, forms the hypocycloid arc.Patent document: disclosed crescent gear pump comprises internal rotor and external rotor among the open 11-811935A of JP patent, and this internal rotor comprises epicycloid tooth top and hypocycloid teeth groove, and this external rotor comprises hypocycloid tooth top and epicycloid teeth groove.Though existing crescent gear pump provides rational performance; But still can produce pressure pulsation and the operational noise more much higher than aspiration level; Adopt present structural type in addition, have entrap phenomenon in the pump, can't improve the manufacturing efficiency of hydraulic equipment effectively.
Summary of the invention
The technical barrier that the present invention will solve is the technological deficiency to existing crescent gear pump; Invent a kind of multiple tooth poor crescent gear pump; The internal rotor in the gear pump and the flank profil of external rotor are respectively cycloid and circular curve; The difference of the number of teeth of internal rotor and external rotor has reduced the working pressure pulsation and the operational noise of pump greater than 1; Shape through changing the crescent shape member has been avoided the pocketed oil problem in the rotor chamber, has improved the manufacturing efficiency of hydraulic equipment effectively.
The technological scheme that the present invention adopts is that internal rotor 1 and the flank profil of external rotor 2 in a kind of multiple tooth poor crescent gear pump is respectively cycloid and circular curve, and cycloid and circular curve flank profil are to generate in the following manner:
If the radius of basic circle I is r
1, round as a ball II radius be r
2, with the center of circle O of basic circle I
1Be true origin, set up fixed coordinate system S
f(O
1, x
f, y
f), and make its x
fAxle is through two circle point of contact p; Center of circle O with basic circle I
1Be true origin, set up moving coordinate system S
1(O
1, x
1, y
1), and itself and basic circle I are connected; With the radius is the center of circle O of L, round as a ball II
2Be true origin, set up moving coordinate system S
2(O
2, x
2, y
2), and itself and round as a ball II are connected, and on its axis of abscissas, select 1 C; Moving coordinate system S
1, S
2The x of initial position
1, x
2Axle and fixed coordinate system S
fX
fAxle overlaps; Make basic circle I turn over around its center of circle
During angle, round as a ball II turns over around its center of circle
Angle.C point and moving coordinate system S
2(O
2, x
2, y
2) be connected mutually, the coordinate that C is ordered is (L, 0).
1) external rotor 2 tooth curves
With the C point is that the center of circle, R are that radius is justified, and the M point is at moving coordinate system S on the circle
2(O
2, x
2y
2) in coordinate be (L-Rcos θ ,-Rsin θ); At moving coordinate system S
2(O
2, x
2, y
2) in, the track that M is ordered is circle III, and circle III promptly is to be that the center of circle, radius are external rotor 2 tooth curves of R with the C point, and its equation is:
In the formula (1), x
2, y
2Be the coordinate of external rotor (2) tooth curve, unit: mm, R are radius, and unit: mm, θ are angles, unit: rad; Utilization is r with the radius
2a External rotor 2 tip circle IV be r with the radius
2fExternal rotor root circle V and the intercepting mutually of this tooth curve, obtain two sections circular arc profiles on the external rotor flank profil curve, these two sections circular arc profiles are with center of circle O
2Change angle 2 π/z
2To next position, by that analogy, until forming complete external rotor 2 flank profils.
2) tooth curve of internal rotor 1
The M point is at fixed coordinate system S
f(O
1, x
f, y
f) in track be actual line of action, and the M point is at moving coordinate system S
1(O
1, x
1, y
1) in track be the tooth curve of internal rotor 1, its equation is:
In the formula (2), x
1, y
1Be the coordinate of internal rotor 1 tooth curve, unit: mm; E is the centre distance of internal rotor 1 and external rotor 2, unit: mm; θ with
Relation be:
Be the angle that internal rotor 1 and external rotor 2 turn over, unit: rad.When internal rotor 1 turns over
During angle, external rotor 2 turns over
Angle, the tooth curve of internal rotor 1 is a hypocycloid; Utilize radius to be r
1aThe tip circle VI and the radius of internal rotor 1 be r
1fInternal rotor root circle VII and the intercepting mutually of this cycloid, obtain two sections cycloids on the internal rotor tooth; These two sections cycloids are with center of circle O
1Change angle 2 π/z
1To next position, by that analogy, until forming complete internal rotor 1 flank profil.
Working-fluid intaking a and working fluid outlet b is arranged on the housing 10 of rotor chamber, and they are communicated with the rotor chamber segment fluid flow respectively; Backing plate 4 and eccentric bushing 16 are arranged in rotor chamber housing 10, rotatable internal rotor 1 and external rotor 2 are arranged in the eccentric bushing 16; Provide the crescent shape member 3 of the non-complete shape of the sealing surfaces between rotor tooth to be inserted between internal rotor 1 and the external rotor 2, to separate Working-fluid intaking a and the working fluid outlet b in the rotor chamber; Non-complete crescent shape member 3 profiles are to be r with the radius
2f External rotor 2 root circle V be r with the radius
1aThe partial arc that the tip circle VI of internal rotor 1 intersects.
Coupling 8 in the crescent gear pump links to each other with line shaft 6 through flat key 11; The motive force that motor provides is imported line shaft 6; Internal rotor 1 is installed on the line shaft 6 through flat key 15; Lower bearing 13 and upper bearing (metal) 20 are installed on the line shaft 6, and lower bearing end cap 12 is connected with the housing 10 of gear pump with tack hex head bolt 17 through hexagon socket head cap screw 7 respectively with top bearing cover 18; Fluid input adpting flange 14 is connected with the housing 10 of gear pump through bolt with fluid output adpting flange 5, and sealing plate 19 is installed on the top bearing cover 18 through screw 21.
The present invention also provides so a kind of multiple tooth poor crescent gear pump, it is characterized in that gear pump external rotor 2 number of teeth z
2With internal rotor 1 number of teeth z
1Difference Δ z=z
2-z
1, and Δ z is greater than 1; External rotor 2 number of teeth z
2With internal rotor 1 number of teeth z
1Prime number each other.
The invention has the beneficial effects as follows: external rotor adopts circular arc profile curve, internal rotor to adopt the cycloidal profile curve of conjugation with it; And through employing increase crescent gear pump internal rotor 1 and the number of teeth of external rotor 2 and the unit time discharge capacity that number of teeth difference improves crescent gear pump, and the work fluctuation pressure and the noise of reduction pump; Shape through changing the crescent shape member has been avoided the pocketed oil problem in the rotor chamber, improves the manufacturing efficiency of hydraulic equipment effectively.
Description of drawings
Fig. 1 is that multiple tooth poor crescent gear pump internal rotor, outer rotor teeth profile become schematic diagram; Fig. 2 is non-complete crescent shape element structure schematic representation; Fig. 3 is the structure sectional view of multiple tooth poor crescent gear pump; Fig. 4 be K among Fig. 3 to view, Fig. 5 is the flank profil view of embodiment's one crescent gear pump, Fig. 6 is the flank profil view of embodiment's two crescent gear pumps.Wherein: S
f(O
1, x
f, y
f)-fixed coordinate system, S
1(O
1, x
1, y
1)-moving coordinate system is with the center of circle O of basic circle I
1Be true origin, and make itself and basic circle I be connected S
2(O
2, x
2, y
2)-moving coordinate system is the center of circle O of L, round as a ball II with the radius
2Be true origin; The I-basic circle, II-is round as a ball, III-external rotor 2 tooth curves, the tip circle of IV-external rotor 2, the root circle of V-external rotor 2, the tip circle of VI-internal rotor 1, the root circle of VII-internal rotor 1; The 1-internal rotor, 2-external rotor, the non-complete crescent shape member of 3-, 4-backing plate, 5-fluid output adpting flange, 6-line shaft; The 7-Allen bolt, the 8-coupling, 9-flexibly connects pin, the housing of 10-gear pump, 11-flat key; 12-lower bearing end cap, 13-lower bearing, 14-fluid input adpting flange, 15-flat key, 16-eccentric bushing; 17-tack hex head bolt, 18-top bearing cover, 19-sealing plate, 20-upper bearing (metal), 21-screw.
Embodiment
Specify embodiment of the present invention below in conjunction with accompanying drawing and technological scheme.
The working principle of multiple tooth poor crescent gear pump and characteristics: 1. external rotor 2 profiles of tooth of crescent gear pump are circular arc, and the profile of tooth of internal rotor 1 is a cycloid; The number of teeth of internal rotor 1 and external rotor 2 is prime number each other, and the difference of the rotor number of teeth improved the unit time mean flowrate of pump greater than 1, has reduced the flow pulsation level of gear pump.2. the differentiation of the height pressure of crescent gear pump is non-complete crescent shape member at a distance from member, has avoided the pocketed oil problem of gear pump.3. Working-fluid intaking a and working fluid outlet b is arranged on the housing 10 of rotor chamber, and they are communicated with the rotor chamber segment fluid flow respectively; Backing plate 11 and eccentric bushing 12 are arranged in the rotor chamber housing, and the lower end of eccentric bushing 12 has locating stud to be fixed on the backing plate 4, and the upper end locating stud is fixed on the top bearing cover 18; Rotatable internal rotor 1 and external rotor 2 are arranged in the eccentric bushing 12; And the crescent shape member 3 of non-complete shape; It is inserted between internal rotor 1 and the external rotor 2, and the sealing surfaces between rotor tooth is provided, to separate Working-fluid intaking a and the working fluid outlet b in the rotor chamber.4. the coupling in the crescent gear pump 8 is imported line shaft 6 with the motive force that motor provides; Line shaft 6 drives internal rotor 1; Internal rotor 1 drives external rotor 2 and rotates, and forms negative pressure in the rotor chamber, and a sucks working fluid from inlet; Compress after working fluid exports the b discharge through the active chamber of internal rotor 1, thereby reach the function of transportation work fluid with external rotor 2.5. the work drive motor of crescent gear pump is connected with gear pump through flexibly connecting pin 9; The installation position of motor is positioned at the inside of housing 10, and housing 10 kept the inlet of working fluid and the outlet adpting flange 5 of working fluid, and leaves the bolt hole of installation; Make gear pump to be connected with machine tool closely; Volume is less, and compact structure is saved space and cost.
Fig. 2, Fig. 3 have provided crescent gear pump schematic representation of apparatus of the present invention.As shown in Figure 2, in the crescent gear pump, Working-fluid intaking a and working fluid outlet b is arranged on the housing 10 of rotor chamber, they are communicated with the rotor chamber segment fluid flow respectively; Backing plate 4 and eccentric bushing 12 are arranged in the rotor chamber housing, rotatable internal rotor 1 and external rotor 2 are arranged in the eccentric bushing 12; Provide the crescent shape member 3 of the non-complete shape of the sealing surfaces between rotor tooth to be inserted between internal rotor 1 and the external rotor 2, to separate Working-fluid intaking a and the working fluid outlet b in the rotor chamber; Coupling 8 in the crescent gear pump links to each other with line shaft 6 through flat key 11; The motive force that motor provides is imported line shaft 6; Line shaft 6 drives internal rotor 1, and internal rotor 1 drives external rotor 2 and rotates, and forms negative pressure in the rotor chamber; A sucks working fluid from inlet, compresses after working fluid outlet b discharges through the active chamber of internal rotor 1 with external rotor 2; Internal rotor 1 is installed on the line shaft 6 through flat key, and lower bearing 13 and upper bearing (metal) 20 are installed on the line shaft 6, and lower bearing end cap 12 is connected with the housing 10 of gear pump with tack hex head bolt 17 through Allen bolt 7 respectively with top bearing cover 18; Fluid input adpting flange 14 is connected with the housing 10 of gear pump through bolt with fluid output adpting flange 5, and sealing plate 19 is installed on the top bearing cover 18 through screw 21.
Mode of execution one:
Fig. 5 is the flank profil view of embodiment's one crescent gear pump, wherein: number of inner teeth z
1=7, external rotor number of teeth z
2=9, the radius of basic circle I is r
1The radius of=26.25mm, round as a ball II is r
2=33.75mm.Radius L=54.31mm, external rotor 2 flank profil radius of a circle R=32.06mm, the radius r of the root circle V of external rotor 2
2f=35.34mm, the radius r of the tip circle IV of external rotor 2
2a=25.51mm, the radius r of the root circle VII of internal rotor 1
1f=17.81mm, the radius r of the tip circle VI of internal rotor 1
1a=27.64mm, the centre distance e=7.5mm between internal rotor 1 and the external rotor 2.
1) external rotor 2 tooth curves
At moving coordinate system S
2(O
2, x
2, y
2), the C point coordinates is (54.31,0).With the C point is that the center of circle, R=32.06mm are that radius is justified, at moving coordinate system S
2(O
2, x
2, y
2) in, the equation of the tooth curve place circle III of external rotor 2 is:
In the formula (3), θ is an angle, unit: rad; Utilization is r with the radius
2aThe tip circle IV of the external rotor 2 of=25.51mm be r with the radius
2fThe external rotor root circle V of=35.34mm and this circle intercepting mutually obtain two sections circular arc profiles on the external rotor flank profil curve, and these two sections circular arc profiles are with center of circle O
2Change angle 2 π/9 to next position, by that analogy, until forming complete external rotor 2 flank profils.
2) internal rotor 1 tooth curve
M point on the tooth curve place circle III of external rotor 2 is at fixed coordinate system S
f(O
1, x
f, y
f) in track be actual line of action, and the M point is at moving coordinate system S
1(O
1, x
1, y
1) in track be the tooth curve of internal rotor 1, its equation is:
Utilize radius to be r
1aThe tip circle VI of the internal rotor 1 of=27.64mm and radius are r
1fInternal rotor root circle VII and the intercepting mutually of this hypocycloid of=17.81mm obtain two sections cycloids on the internal rotor tooth; These two sections cycloids are with center of circle O
1Change angle 2 π/7 to next position, by that analogy, until forming complete internal rotor 1 flank profil; Non-complete crescent shape member 3 profiles are to be R with the radius
2fThe root of the external rotor 2 of=35.34mm is justified V and is r with the radius
1aThe partial arc that the tip circle VI of the internal rotor 1 of=27.64mm intersects.
Mode of execution two:
Fig. 6 is the flank profil view of embodiment's two crescent gear pumps, wherein: number of inner teeth z
1=8, external rotor number of teeth z
2=11, the radius of basic circle I is r
1The radius of=25.33mm, round as a ball II is r
2=34.83mm.Radius L=62.70mm, external rotor 2 flank profil radius of a circle R=45.47mm, the radius r of the root circle V of external rotor 2
2f=35.26mm, the radius r of the tip circle IV of external rotor 2
2a=23.04mm, the radius r of the root circle VII of internal rotor 1
1f=13.34mm, the radius r of the tip circle VI of internal rotor 1
1a=25.56mm, the centre distance e=9.5mm between internal rotor 1 and the external rotor 2.
1) external rotor 2 tooth curves
At moving coordinate system S
2(O
2, x
2, y
2), the coordinate that C is ordered is (62.70,0), is that the center of circle, R=45.47mm are that radius is justified with the C point, at moving coordinate system S
2(O
2, x
2, y
2) in, the equation of the tooth curve place circle III of external rotor 2 is:
In the formula (5), θ is an angle, unit: radian; Utilization is r with the radius
2aThe tip circle IV of the external rotor 2 of=23.04mm be r with the radius
2fThe external rotor root circle V of=35.26mm and this circle intercepting mutually obtain two sections circular arc profiles on the external rotor flank profil curve, and these two sections circular arc profiles are with center of circle O
2Change angle 2 π/11 to next position, by that analogy, until forming complete external rotor 2 flank profils.
2) external rotor 2 tooth curves
M point on the tooth curve place circle III of external rotor 2 is at fixed coordinate system S
f(O
1, x
f, y
f) in track be actual line of action, and the M point is at moving coordinate system S
1(O
1, x
1, y
1) in track be the tooth curve of internal rotor 1, its equation is:
Utilize radius to be r
1aThe tip circle VI of the internal rotor 1 of=25.56mm and radius are r
1fInternal rotor root circle VII and the intercepting mutually of this hypocycloid of=13.34mm obtain two sections cycloids on the internal rotor tooth; These two sections cycloids are with center of circle O
1Change angle π/4 to next position, by that analogy, until forming complete internal rotor 1 flank profil; Non-complete crescent shape member 10 profiles are to be r with the radius
2fThe root of the external rotor 2 of=35.26mm is justified V and is r with the radius
1aThe partial arc that the tip circle VI of the internal rotor 1 of=25.56mm intersects.
Fluid drives fluid outlet through the rotation of internal rotor 1 and external rotor 2; In outlet end working rotor chamber from large to small; It is big that hydrodynamic pressure becomes, and then discharge working fluid, the suction-discharge process of fluid in one-period of finishing the work through working fluid outlet b; When line shaft 6 rotated continuously, working fluid sucked, discharges from outlet end b from fluid input end a continual.
In a kind of multiple tooth poor crescent gear pump of the present invention, its external rotor adopts circular arc profile, and internal rotor adopts the cycloidal profile of its conjugation.Compare with the monodentate difference crescent gear pump of same size, the output ripple of pump reduces, and operational noise reduces, and the mean flowrate in the unit time increases.
Claims (2)
1. a multiple tooth poor crescent gear pump is characterized in that, the internal rotor (1) in the multiple tooth poor crescent gear pump and the flank profil of external rotor (2) are respectively cycloid and circular curve, and hypocycloid and circular curve flank profil are to generate in the following manner:
If the radius of basic circle (I) is r
1, unit: mm; The radius of round as a ball (II) is r
2, unit: mm; Center of circle O with basic circle (I)
1Be true origin, set up fixed coordinate system S
f(O
1, x
f, y
f), and make its x
fAxle is through two circle point of contact p; Center of circle O with basic circle (I)
1Be true origin, set up moving coordinate system S
1(O
1, x
1, y
1), and itself and basic circle (I) are connected; With the radius is the center of circle O of L, round as a ball (II)
2Be true origin, set up moving coordinate system S
2(O
2, x
2, y
2), and itself and round as a ball (II) are connected, and on its axis of abscissas, select 1 C; Moving coordinate system S
1, S
2The x of initial position
1, x
2Axle and fixed coordinate system S
fX
fAxle overlaps; Make basic circle (I) turn over around its center of circle
During angle, round as a ball (II) turns over around its center of circle
Angle, C point and moving coordinate system S
2(O
2, x
2, y
2) be connected mutually, the coordinate that C is ordered is (L, 0);
1) external rotor (2) tooth curve
With the C point is that the center of circle, R are that radius is made circle (III), and the M point is at moving coordinate system S on the circle
2(O
2, x
2, y
2) in coordinate be (L-Rcos θ ,-Rsin θ); At moving coordinate system S
2(O
2, x
2, y
2) in, the track that M is ordered promptly is to be that the center of circle, radius are external rotor (2) tooth curve of R with the C point for circle (III) circle (III), its equation is:
In the formula (1), x
2, y
2Be the coordinate of external rotor (2) tooth curve, unit: mm, R is circle (III) radius, unit: mm, θ are angles, unit: rad; Utilization is r with the radius
2aExternal rotor (2) tip circle (IV) be r with the radius
2fExternal rotor root circle (V) and the intercepting mutually of this tooth curve, obtain two sections circular arc profiles on the external rotor flank profil curve, these two sections circular arc profiles are with center of circle O
2Change angle 2 π/z
2To next position, by that analogy, until forming complete external rotor (2) flank profil;
2) tooth curve of internal rotor (1)
The M point is at fixed coordinate system S
f(O
1, x
f, y
f) in track be actual line of action, and the M point is at moving coordinate system S
1(O
1, x
1, y
1) in track be the tooth curve of internal rotor (1), its equation is:
In the formula (2), x
1, y
1Be the coordinate of internal rotor (1) tooth curve, unit: mm, e are the centre distance of internal rotor (1) and external rotor (2), unit: mm; θ with
Relation be:
Be the angle that internal rotor (1) and external rotor (2) turn over, unit: radian, when internal rotor (1) turns over
During angle, external rotor (2) turns over
Angle, the tooth curve of internal rotor (1) is a hypocycloid; Utilize radius to be r
1aTip circle (VI) and the radius of internal rotor (1) be r
1fInternal rotor root circle (VII) and the intercepting mutually of this cycloid, obtain two sections cycloids on the internal rotor tooth; These two sections cycloids are with center of circle O
1Change angle 2 π/z
1To next position, by that analogy, until forming complete internal rotor (1) flank profil;
Working-fluid intaking (a) and working fluid outlet (b) is arranged on the housing of rotor chamber (10), and they are communicated with the rotor chamber segment fluid flow respectively; Backing plate (4) and eccentric bushing (16) are arranged in rotor chamber housing (10), rotatable internal rotor (1) and external rotor (2) are arranged in the eccentric bushing (16); Provide the crescent shape member (3) of the non-complete shape of the sealing surfaces between rotor tooth to be inserted between internal rotor (1) and the external rotor (2), to separate Working-fluid intaking (a) and the working fluid outlet (b) in the rotor chamber; Non-complete crescent shape member (3) profile is to be r with the radius
2fExternal rotor (2) root circle (V) be r with the radius
1aThe crossing partial arc of tip circle (VI) of internal rotor (1); Coupling in the crescent gear pump (8) links to each other through the line shaft (6) of flat key (11) and motor, and the motive force that motor provides is passed to line shaft (6) through coupling (8); Internal rotor (1) is installed on the line shaft (6) through flat key (15); Lower bearing (13) and upper bearing (metal) (20) also are installed on the line shaft (6), and lower bearing end cap (12) is connected with the housing (10) of gear pump with tack hex head bolt (17) through Allen bolt (7) respectively with top bearing cover (18); Fluid input adpting flange (14) is connected with the housing (10) of gear pump through bolt with fluid output adpting flange (5), and sealing plate (19) is installed on the top bearing cover (18) through screw (21).
2. a kind of multiple tooth poor crescent gear pump as claimed in claim 1 is characterized in that, gear pump external rotor (2) number of teeth z
2With internal rotor (1) number of teeth z
1Difference Δ z=z
2-z
1, and Δ z is greater than 1; External rotor (2) number of teeth z
2With internal rotor (1) number of teeth z
1Prime number each other.
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|---|---|---|---|
| CN2012101951560A CN102705227A (en) | 2012-06-13 | 2012-06-13 | Multi-tooth difference internal gear pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012101951560A CN102705227A (en) | 2012-06-13 | 2012-06-13 | Multi-tooth difference internal gear pump |
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| CN102705227A true CN102705227A (en) | 2012-10-03 |
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| CN104266063A (en) * | 2014-09-24 | 2015-01-07 | 湖南大学 | Elliptic-circular compound cycloid rotor oil pump, rotor thereof and rotor design method |
| CN104514711A (en) * | 2013-09-20 | 2015-04-15 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Internal-Gear Pump and Hydraulic Circuit for a Motor Vehicle Drivetrain |
| CN106958547A (en) * | 2017-05-10 | 2017-07-18 | 四川大学 | Press stream transformer and pressure retarded osmosis energy electricity generation system |
| CN110285051A (en) * | 2019-07-03 | 2019-09-27 | 张满云 | A kind of synchronous inner gearing dual rotors structure and the impeller pump based on this structure |
| CN113236553A (en) * | 2021-05-24 | 2021-08-10 | 大连冰山帕特技术有限公司 | Two-tooth-difference high-pressure oil pump for high-pressure screw compressor |
| CN114186336A (en) * | 2021-11-26 | 2022-03-15 | 华南理工大学 | Method for calculating inner and outer rotor tooth profile molded lines of multi-arc composite cycloid rotor pump |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201144799Y (en) * | 2007-10-31 | 2008-11-05 | 宁波华液电液控制工程股份有限公司 | Internal gear pump |
| DE102009047643A1 (en) * | 2009-12-08 | 2011-06-09 | Robert Bosch Gmbh | Internal gear pump e.g. hydraulic pump, for conveying brake fluid in hydraulic vehicle brake system, has filling piece including spring whose legs are processed in circumferential direction and act inwardly and outwardly opposite to heads |
| JP2011122548A (en) * | 2009-12-14 | 2011-06-23 | Jtekt Corp | Inscribed gear pump |
| CN202789508U (en) * | 2011-11-28 | 2013-03-13 | 艾可勒工业电子有限公司 | Internal gear pump |
| CN103429896A (en) * | 2010-11-30 | 2013-12-04 | 罗伯特·博世有限公司 | Internal gear pump |
-
2012
- 2012-06-13 CN CN2012101951560A patent/CN102705227A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201144799Y (en) * | 2007-10-31 | 2008-11-05 | 宁波华液电液控制工程股份有限公司 | Internal gear pump |
| DE102009047643A1 (en) * | 2009-12-08 | 2011-06-09 | Robert Bosch Gmbh | Internal gear pump e.g. hydraulic pump, for conveying brake fluid in hydraulic vehicle brake system, has filling piece including spring whose legs are processed in circumferential direction and act inwardly and outwardly opposite to heads |
| JP2011122548A (en) * | 2009-12-14 | 2011-06-23 | Jtekt Corp | Inscribed gear pump |
| CN103429896A (en) * | 2010-11-30 | 2013-12-04 | 罗伯特·博世有限公司 | Internal gear pump |
| CN202789508U (en) * | 2011-11-28 | 2013-03-13 | 艾可勒工业电子有限公司 | Internal gear pump |
Non-Patent Citations (1)
| Title |
|---|
| 徐学忠: "内啮合摆线齿轮泵的理论研究与仿真", 《中国博士学位论文全文数据库 工程科技Ⅱ辑》, 15 July 2007 (2007-07-15) * |
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| CN104514711A (en) * | 2013-09-20 | 2015-04-15 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Internal-Gear Pump and Hydraulic Circuit for a Motor Vehicle Drivetrain |
| CN104514711B (en) * | 2013-09-20 | 2017-04-12 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Internal-Gear Pump and Hydraulic Circuit for a Motor Vehicle Drivetrain |
| US10119539B2 (en) | 2013-09-20 | 2018-11-06 | GETRAG Getriebe—und Zahnradfabrik Hermann Hagen | Internal-gear pump and hydraulic circuit for a motor vehicle drivetrain |
| CN104266063A (en) * | 2014-09-24 | 2015-01-07 | 湖南大学 | Elliptic-circular compound cycloid rotor oil pump, rotor thereof and rotor design method |
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| CN106958547B (en) * | 2017-05-10 | 2018-10-12 | 四川大学 | Press stream transformer and pressure retarded osmosis energy electricity generation system |
| CN110285051A (en) * | 2019-07-03 | 2019-09-27 | 张满云 | A kind of synchronous inner gearing dual rotors structure and the impeller pump based on this structure |
| CN110285051B (en) * | 2019-07-03 | 2024-04-26 | 张满云 | Synchronous inner-meshing double-rotor structure and rotor pump based on same |
| CN113236553A (en) * | 2021-05-24 | 2021-08-10 | 大连冰山帕特技术有限公司 | Two-tooth-difference high-pressure oil pump for high-pressure screw compressor |
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