CN104712555B - Inner engaging cycloidal pump cycloidal gear design method - Google Patents
Inner engaging cycloidal pump cycloidal gear design method Download PDFInfo
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- CN104712555B CN104712555B CN201310682591.0A CN201310682591A CN104712555B CN 104712555 B CN104712555 B CN 104712555B CN 201310682591 A CN201310682591 A CN 201310682591A CN 104712555 B CN104712555 B CN 104712555B
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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
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—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
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
The present invention belongs to a mechanical gear technology, and particularly relates to an inner engaging cycloidal pump cycloidal gear design method. According to the method, the maximum outer circle diameter and the thinnest wall thickness of the inner engaging external gear are determined to obtain the inner engaging external gear root circle diameter, the design flow and the assumed gear width value are combined to obtain the functional relation of the eccentricity to the assumed gear width value, the rotation position of the inner engaging external gear is combined with the eccentricity and the inner engaging external gear root circle value to obtain the remaining structure parameters of the inner engaging internal external gear, the number of the teeth, the generated circle radius and the tooth-shaped circle radius are determined, the mathematical formula of the cycloidal gear is combined so as to obtain the exact curve equation of the internal tooth profile, and finally the gear thickness is determined through the flow formula. The test results of the cycloidal gear component designed by the inner engaging cycloidal pump cycloidal gear design method of the present invention verify that: the set of the gears can be well engaged in the case of high speed, and has good wear resistance.
Description
Technical field
The invention belongs to mechanical gear technology, and in particular to a kind of internal messing Gerotor pump cycloid gear method for designing.
Background technology
Internal messing cycloid gear pump, with compact conformation compared with other gear pumps, part is few, and noise is low, flow pulsation
Little, self-priming performance is good, the advantages of life-span length, is particularly suitable for high rotation speed operation.
But the design of cycloid gear is complicated, influence factor is more, and foreign countries are due to blockade on new techniques, it is difficult to obtain related detailed
Design data, and domestic relevant cycloid gear usually surveys imitative and manufacture, has no special, complete design cycle.
The content of the invention
The object of the invention：
One kind is provided under existence conditionses, the internal messing Gerotor pump cycloid gear of efficiency high, scientific structure can be designed
Method for designing.
Technical scheme：
Described internal messing Gerotor pump cycloid gear method for designing, internal messing Gerotor pump cycloid gear are divided into external gear and interior
Gear, which first determines that the maximum exradius of external gear and most thin-walled are thick, obtains external gear teeth root radius, then by design stream
Amount formula combines the gear width value for assuming, obtains eccentric throw to the functional relationship between hypothesis gear width value, then by inside and outside
The specific position of gear rotation obtains remaining structure of internal-external gear with reference to the numerical value of eccentric throw and external gear teeth root radius joins
Number, it is then determined that the number of teeth and create into radius of circle and profile of tooth radius of circle, in conjunction with cycloid gear mathematical formulae be obtained in
The accurate curvilinear equation of gear-profile.Gear thickness is determined finally by flow formula.
Described internal messing Gerotor pump cycloid gear method for designing, its detailed process are as follows：
Step 1：Determine external gear maximum exradius " ROutward”。
According to performance requirement, limited by structure or weight, use volume maximum principle, release maximum cylindrical the half of external gear
Footpath.
Step 2：Determine external gear teeth root radius " Ri2”。
According to external gear maximum exradius, in conjunction with the strength of materials under design conditions, the most thin-walled of external gear is released
Thickness, so as to obtain external gear teeth root radius.
Step 3：Determine the eccentric distance e of internal-external gear.
According to flow rate calculation formula, the eccentric throw of internal messing cycloid internal-external gear and the functional relationship of gear width are derived
" f1 ", and because gear width is typically between 5～25mm, it is possible to a span of eccentric throw is obtained, in the model
Enclose interior, no more than the value of 1/2 profile of tooth radius of circle " a " is virtual value.Because 2e is the fully teeth height of external gear and internal gear.Examine
Consider intensity at tooth root, general recommendations K × 2e≤internal gear teeth root radius Ri1, wherein K typically take for safety coefficient (1.2～
1.8) the bigger value of toughness of material is less, and the bigger value of material stiffness is bigger.Further according to the mutual pass of internal-external gear structural parameters
System, can obtain K × 2e≤Ri2-3e。
Step 4：Determine internal-external gear remaining structural parameters internal gear radius of addendum " Re1", internal gear teeth root radius
“Ri1", external gear radius of addendum " Re2”
Rotated according to internal-external gear to the specific position of minimum confined space, with reference to eccentric throw and external gear root circle half
Footpath, can derive structural parameters and eccentric throw and the pass of external gear teeth root radius of internal messing cycloid gear internal-external gear
System, such that it is able to determine remaining structural parameters internal gear radius of addendum by known external gear teeth root radius and eccentric throw
“Re1", internal gear teeth root radius " Ri1", external gear radius of addendum " Re2”。
Step 5：Determine the number of teeth of internal messing cycloid gear internal-external gear
Requirement by limiting with reference to the geometry in flow pulsation, structure and to smoothness of operation determines internal messing cycloid
The number of teeth of gear internal-external gear, and require the external gear gear ratio internal gear number of teeth many a tooth, i.e. Z2=Z1+1。Z2:External gear teeth
Number；Z1:The internal gear number of teeth.
Step 6：Determine that internal messing cycloid gear creates into radius of circle R and profile of tooth radius of circle a
First according to external gear radius of addendum Re2With the relation for creating into radius of circle R and profile of tooth radius of circle a differences, using optimum
Y-factor method Y, obtains creating into COEFFICIENT K and arc footpath coefficient h, further according to create into coefficient and arc footpath coefficient with create into radius of circle and profile of tooth circle
The relation of radius, i.e.,：
It is determined that radius of circle R and profile of tooth radius of circle a is created into, wherein, R2 sectionsFor eccentric distance e and the product of the external gear number of teeth.
Step 7：Obtain the accurate curvilinear equation of internal gear tooth.
By known internal gear tooth number Z1, external gear tooth number Z2, eccentric distance e, Chuan Cheng gardens radius R, profile of tooth radius of circle a, with reference to
The mathematical formulae of cycloid is obtained the accurate curvilinear equation of internal gear tooth.
Step 8：Determine gear thickness
According to flow rate calculation formula, with reference to volumetric efficiency, inside engaged gear width is redefined, finally by flow formula
Determine gear thickness.
Wherein the internal gear number of teeth is 3～12.
The structural parameters relation of the internal-external gear in step 3 is as follows：
Ri2=Ri1+3e；
The structural parameters relation of the internal-external gear in step 4 is as follows：
Ri1=R-a-e；
Re1=Ri1+ 2e=R-a+e；
Ri2=Re1+ e=R-a+2e；
Re2=R-a；
R1 section=e*Z1 and R2 sections=e*Z2,
Wherein, Re1：Internal gear radius of addendum, Ri1：Internal gear teeth root radius, Re2：External gear radius of addendum, Ri2：
External gear teeth root radius, R1 section：Internal gear pitch radius, R2 sections：External gear pitch radius.
Structure limiting factor in step 5 is referred to：R2 sections≤ROutward；Smoothness of operation requires to refer to：Z2≥5；Flow pulsation will
Seeking Truth refers to：Z2Odd number is taken as far as possible.
Wherein：R2 sections：External gear pitch radius=eccentric distance e and external gear tooth number Z2Product.
Profile of tooth radius of circle a in step 6 have to be larger than 2 times of eccentric distance e, and meet：a+Ri2＞ R ＞ Ri2, wherein, Ri2
For external gear teeth root radius；If being unsatisfactory for above-mentioned requirements, the wound in step 6 is entered into radius of circle R and profile of tooth radius of circle a
Row amendment, wherein, r is obtained using curtate ratio TgSpan, further determine R scope, wherein,Its
Middle T spans are 0.5～0.75, andrg:Rolling circle radius；Z1：The internal gear number of teeth；Z2:The external gear number of teeth.
Flow formula in step 3 and step 8 is：
Wherein, Qsj：Design discharge (L/min), Q：Actual requirement flow (L/min),
ηv：Volumetric efficiency, n：Internal tooth wheel speed (r/min), B：Gear thickness (mm), cq：Compare discharge capacity.
In step 7, the mathematical formulae of cycloid is as follows：
WhereinFor the angle parameter variable of this mathematical formulae.Z1：The internal gear number of teeth, Z2:The external gear number of teeth.
The technique effect of the present invention：The gerotor type designed using internal messing Gerotor pump cycloid gear method for designing of the present invention
Gear assembly, through verification experimental verification, this group of gear can be very good engagement at high speeds, and wear resistance is good.
Description of the drawings
Fig. 1 is the flow chart of internal messing Gerotor pump cycloid gear method for designing of the present invention；
Fig. 2 is the structural representation of inside engaged gear internal-external gear；
Fig. 3 is the structural representation of cycloid gear Chuan Cheng gardens radius R and profile of tooth radius of circle a；
Fig. 4 is the structural representation of internal messing cycloid gear eccentric throw,
Wherein, 1- internal gears, 2- external gears.
Specific embodiment
The present invention will be further described with reference to the accompanying drawings and examples：
Internal messing cycloid gear is divided into external gear and internal gear.The present invention first determines the maximum exradius and most of external gear
Thin-walled is thick, obtains external gear teeth root radius, and the gear width value for assuming then is combined by design discharge formula, eccentric throw is obtained
To assuming the functional relationship between gear width value, then its eccentric throw and external gear are combined by the specific position that internal-external gear rotates
The numerical value of root radius obtains remaining structural parameters of internal-external gear, it is then determined that the number of teeth and create into radius of circle and profile of tooth circle
Radius, is obtained the accurate curvilinear equation of internal gear tooth in conjunction with the mathematical formulae of cycloid gear.It is public finally by flow
Formula determines gear thickness.Fig. 1 is referred to, the detailed process of internal messing Gerotor pump cycloid gear method for designing of the present invention is as follows：
2nd, the requirement of the project is as follows：Rated speed is 6000 turns/min, and inlet pressure is 0.034MPa, and outlet pressure is
1.03MPa, it is desirable to which flow is 48L/min.Housing maximum internal bore radius are 24.5mm.Specific design process is as follows：
Step 1：Determine external gear maximum exradius " ROutward”。
According to performance requirement, limited by structure or weight, with volume maximum principle, release maximum cylindrical the half of external gear
Footpath " ROutward”.In the Gerotor pump product item cooperated with Honeywell, the maximum internal bore radius of housing are 24.5mm；And according to
Structural requirement, needs by the stator that a wall thickness is 3mm in outer rotor with housing transitional region.So by maximum volume principle
The outer rotor maximum exradius R of releaseOutward=21.5m.The external gear exradius for obtaining in such a way is in the condition
Lower maximum outside diameter.In the case of identical material, external gear teeth root radius can be caused as big as possible, so as to increase
The discharge capacity of the gear.
Step 2：Determine external gear teeth root radius " Ri2”。
According to external gear maximum exradius ROutward=21.5mm, in conjunction with the strength of materials under design conditions, releases external tooth
It is 2.9mm that the most thin-walled of wheel is thick, so as to obtain external gear teeth root radius Ri2For 18.6mm.
Step 3：Determine the eccentric distance e of internal-external gear.
According to flow rate calculation formula
Wherein, volumetric efficiency ηv0.6 is taken typically；Actual requirement flow Q=48L/min；Specification requirement rotating speed n is 6000
Turn/min；Bring these parameters into above-mentioned flow rate calculation formula, it is possible to obtain the eccentric throw of internal messing cycloid internal-external gear with
The functional relationship " f1 " of gear width is e=18.6/ (16.007- (286.77/B)., and because gear width typically 5～
Between 25mm, it is possible to which a span for obtaining eccentric distance e is e ∈ [0,4.1] (as long as on the occasion of), within the range,
No more than the value of 1/2 profile of tooth radius of circle " a " is virtual value.Due to value also no standardization in the world of eccentric distance e, Er Qieyou
Also do not determine in profile of tooth radius of circle " a " in this step, so typically choosing the intermediate value in the range of this.Because 2e is outer
The fully teeth height of gear and internal gear.Consider intensity at tooth root, general recommendations K × 2e≤internal gear teeth root radius Ri1, so there is K
×2e≤Ri1=Ri2- 3e, when safety coefficient K takes 1.33, i.e. e≤2.794.According to flow rate calculation formula, in other factors phase
With in the case of, e is proportional with flow, so e is taken large values as far as possible.So in this instance choose eccentric distance e=
2.794mm。
Step 4：Determine internal-external gear remaining structural parameters internal gear radius of addendum " Re1", internal gear teeth root radius
Ri1“Ri1", external gear radius of addendum " Re2”
Rotated according to internal-external gear to the specific position of minimum confined space, with reference to eccentric throw and external gear root circle half
Footpath, can derive structural parameters and eccentric throw and the pass of external gear teeth root radius of internal messing cycloid gear internal-external gear
System, such that it is able to determine remaining structural parameters by known external gear teeth root radius and eccentric throw.That is Ri2=Re1+ e, institute
With Re1=15.806mm；
Re1=Ri1+ 2e, so Ri1=10.218mm, Ri2=Re2+ 2e, so Re2=13.012mm.I.e.：
Again because Re2=R-a, so R-a=13.012mm.
Step 5：Determine the number of teeth of internal messing cycloid gear internal-external gear
R is limited by the geometry in structure2 sections≤ROutwardZ is obtained2≤7.6；It is obtained by the requirement to stability of rotation
Z2≥5；By the requirement of flow pulsation so Z2Take odd number.So Z2Value be 5,7 teeth.Under equal conditions the number of teeth is fewer,
Discharge capacity is bigger, and the number of teeth is more, and flow pulsation is less.Because less demanding to flow pulsation in this example, in order to obtain height
Discharge capacity, takes Z2Equal to 5.Again because Z2=Z1+1.So Z1=4.
Step 6：Determine that internal messing cycloid gear creates into radius of circle R and profile of tooth radius of circle a
First according to external gear radius of addendum Re2With the relation for creating into radius of circle R and profile of tooth radius of circle a differences, using optimum
Y-factor method Y, obtains creating into COEFFICIENT K=1.3574, arc footpath coefficient h=0.6185.Further according to creating into coefficient and arc footpath coefficient and create into
The relation of radius of circle and profile of tooth radius of circle, i.e.,：
Wherein, R2 sectionsFor eccentric distance e and the product of the external gear number of teeth.So bring known quantity into can obtain creating into radius of circle R
=18.96, profile of tooth radius of circle a=8.64.Thus result can see that the value of R and a meets 1. a >=2e；②a+Ri2＞ R ＞ Ri2。
But but and R-a=Re2=13.012 contradictions.So needing to adjust the value of R and a.Because curtate ratio T=e/rg, and rg=R
×(Z1/Z2), so T=(2.794 × 5)/R, because the span that the span of T is 0.5～0.75, R is
18.62～27.94.In general the little T of pressure takes large values, and the big T of pressure gets the small value.In this example, T takes 0.6, so R=
23.25mm, so a=10.238mm.Empirical tests this results meets 1. a >=2e；②a+Ri2＞ R ＞ Ri2。
Step 7：Obtain the accurate curvilinear equation of internal gear tooth.
By known internal gear tooth number Z1, external gear tooth number Z2, eccentric distance e, Chuan Cheng gardens radius R, profile of tooth radius of circle a, with reference to
The mathematical formulae of cycloid is obtained the accurate curvilinear equation of internal gear tooth.
Step 8：Determine gear thickness
According to flow rate calculation formula：
Bring known quantity into formula, B=30.6mm in this instance can be calculated, as this width is more than 25mm, so
The internal-external gear of this one-level is divided into into two groups of the internal-external gear that thickness is 15.3mm.
Terminate to this all design.The gerotor type internal-external gear according to said method designed, operates steadily, and noise is low, intensity
Height, wearability are good.
Claims (8)
1. a kind of internal messing Gerotor pump cycloid gear method for designing, it is characterised in that internal messing Gerotor pump cycloid gear is divided into outer
Gear and internal gear, first determine that the maximum outside diameter and most thin-walled of external gear is thick, obtain external gear teeth root diameter, Ran Houyou
Design discharge combines the gear width value for assuming, obtains eccentric throw to the functional relationship between hypothesis gear width value, then by interior
The specific position of the internal-external gear rotation of engagement cycloid gear obtains interior external tooth with reference to the numerical value of eccentric throw and external gear root circle
Remaining structural parameters of wheel, it is then determined that the number of teeth and radius of circle and profile of tooth radius of circle are created into, in conjunction with the mathematics of cycloid gear
Formula is obtained the accurate curvilinear equation of internal gear tooth, determines gear thickness finally by flow formula, and detailed process is such as
Under：
Step 1：Determine external gear maximum exradius " ROutward”
According to performance requirement, limited by structure or weight, use volume maximum principle, release the maximum exradius of external gear；
Step 2：Determine external gear teeth root radius " Ri2”
According to external gear maximum exradius, in conjunction with the strength of materials under design conditions, the most thin-walled for releasing external gear is thick, from
And obtain external gear teeth root radius；
Step 3：Determine the eccentric distance e of internal-external gear
According to flow rate calculation formula, the eccentric throw of internal messing cycloid internal-external gear and the functional relationship of gear width are derived
" f1 ", and because gear width is between 5～25mm, so as to obtain a span of eccentric throw, within the range, less
In the value of 1/2 profile of tooth radius of circle " a " be virtual value because 2e is the fully teeth height of external gear and internal gear, it is considered to strong at tooth root
Degree, makes K × 2e≤internal gear teeth root radius Ri1, wherein K is safety coefficient, takes 1.2～1.8, further according to internal-external gear structure
The mutual relation of parameter, obtains K × 2e≤Ri2-3e；
Step 4：Determine internal-external gear remaining structural parameters internal gear radius of addendum " Re1", internal gear teeth root radius " Ri1",
External gear radius of addendum " Re2”
Rotated according to internal-external gear to the specific position of minimum confined space, with reference to eccentric throw and external gear teeth root radius, pushed away
The structural parameters and eccentric throw and the relation of external gear teeth root radius of internal messing cycloid gear internal-external gear are derived, so as to pass through
Known external gear teeth root radius and eccentric throw determine remaining structural parameters internal gear radius of addendum " Re1", internal gear tooth root
Radius of circle " Ri1", external gear radius of addendum " Re2”；
Step 5：Determine the number of teeth of internal messing cycloid gear internal-external gear
Requirement by limiting with reference to the geometry in flow pulsation, structure and to smoothness of operation determines internal messing cycloid gear
The number of teeth of internal-external gear, and require the external gear gear ratio internal gear number of teeth many a tooth, i.e. Z2=Z1+ 1, Z2:The external gear number of teeth；Z1:
The internal gear number of teeth；
Step 6：Determine that internal messing cycloid gear creates into radius of circle R and profile of tooth radius of circle a
First according to external gear radius of addendum Re2With the relation for creating into radius of circle R and profile of tooth radius of circle a differences, using optimal coefficient
Method, obtains creating into COEFFICIENT K and arc footpath coefficient h, further according to creating into coefficient and arc footpath coefficient and create into radius of circle and profile of tooth radius of circle
Relation, i.e.,：
It is determined that radius of circle R and profile of tooth radius of circle a is created into, wherein, R2 sectionsFor eccentric distance e and the product of the external gear number of teeth；
Step 7：Obtain the accurate curvilinear equation of internal gear tooth
By known internal gear tooth number Z1, external gear tooth number Z2, eccentric distance e creates into radius of circle R, profile of tooth radius of circle a, with reference to pendulum
The mathematical formulae of line is obtained the accurate curvilinear equation of internal gear tooth；
Step 8：Determine gear thickness
According to flow rate calculation formula, with reference to volumetric efficiency, inside engaged gear width is redefined, determined finally by flow formula
Gear thickness.
2. internal messing Gerotor pump cycloid gear method for designing according to claim 1, it is characterised in that the internal gear number of teeth is
3～12.
3. internal messing Gerotor pump cycloid gear method for designing according to claim 1, it is characterised in that interior in step 3
The structural parameters relation of external gear is as follows：
Ri2=Ri1+3e。
4. internal messing Gerotor pump cycloid gear method for designing according to claim 2, it is characterised in that interior in step 4
The structural parameters relation of external gear is as follows：
Ri1=R-a-e；
Re1=Ri1+ 2e=R-a+e；
Ri2=Re1+ e=R-a+2e；
Re2=R-a；
R1 section=e*Z1And R2 sections=e*Z2,
Wherein, Re1：Internal gear radius of addendum, Ri1：Internal gear teeth root radius, Re2：External gear radius of addendum, Ri2：External tooth
Wheel root radius, R1 section：Internal gear pitch radius, R2 sections：External gear pitch radius.
5. internal messing Gerotor pump cycloid gear method for designing according to claim 1, it is characterised in that the knot in step 5
Structure limiting factor is referred to：R2 sections≤ROutward；Smoothness of operation requires to refer to：Z2≥5；The requirement of flow pulsation is：Z2Take odd number,
Wherein：R2 sections：External gear pitch radius=eccentric distance e and external gear tooth number Z2Product.
6. internal messing Gerotor pump cycloid gear method for designing according to claim 1, it is characterised in that the tooth in step 6
Shape radius of circle a have to be larger than 2 times of eccentric distance e, and meet：a+Ri2＞ R ＞ Ri2, wherein, Ri2For external gear teeth root radius；
If being unsatisfactory for above-mentioned requirements, the wound in step 6 is modified into radius of circle R and profile of tooth radius of circle a, wherein, using short
Width coefficient T obtains rgSpan, further determine R scope, wherein,T spans are 0.5～0.75,
Andrg:Rolling circle radius；Z1：The internal gear number of teeth；Z2:The external gear number of teeth.
7. internal messing Gerotor pump cycloid gear method for designing according to claim 3, it is characterised in that step 3 and step 8
In flow formula be：
Wherein, Qsj：Design discharge, unit L/min, Q：Actual requirement flow, unit L/min,
ηv：Volumetric efficiency, n：Internal tooth wheel speed, unit r/min, B：Gear thickness, unit mm, cq：Compare discharge capacity.
8. internal messing Gerotor pump cycloid gear method for designing according to claim 1, it is characterised in that cycloid in step 7
Mathematical formulae it is as follows：
WhereinFor the angle parameter variable of this mathematical formulae, Z1：The internal gear number of teeth, Z2:The external gear number of teeth, e is eccentric throw, and R is
Radius of circle is created into, a is profile of tooth radius of circle.
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| CN105508521A (en) * | 2016-01-08 | 2016-04-20 | 贾萌 | High-contact-ratio internal-gearing cycloidal gear mechanism |
| CN110069799B (en) * | 2018-09-18 | 2023-02-24 | 中车戚墅堰机车车辆工艺研究所有限公司 | Method for calculating strength of cycloid gear |
| CN111756203B (en) * | 2020-06-24 | 2021-11-19 | 潍柴动力股份有限公司 | Rotor assembly and design method thereof, rotor pump and engine assembly |
| US11898560B1 (en) * | 2022-07-22 | 2024-02-13 | Perfobore Inc. | Working members of a rotary hydraulic or pneumatic machine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2144200Y (en) * | 1992-10-07 | 1993-10-20 | 戴定中 | Cycloidal teeth-shaped internal and external rotors for rotary pump |
| JP2003322089A (en) * | 2002-03-01 | 2003-11-14 | Mitsubishi Materials Corp | Oil pump rotor |
| CN2591275Y (en) * | 2002-09-11 | 2003-12-10 | 宜兴市恒发特种粉末冶金厂 | Cycloidal oil pump rotator |
| CN202900633U (en) * | 2012-10-17 | 2013-04-24 | 新乡航空工业(集团)有限公司 | Eight-tooth cycloid pump and cycloid pump rotor structure thereof |
-
2013
- 2013-12-12 CN CN201310682591.0A patent/CN104712555B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2144200Y (en) * | 1992-10-07 | 1993-10-20 | 戴定中 | Cycloidal teeth-shaped internal and external rotors for rotary pump |
| JP2003322089A (en) * | 2002-03-01 | 2003-11-14 | Mitsubishi Materials Corp | Oil pump rotor |
| CN2591275Y (en) * | 2002-09-11 | 2003-12-10 | 宜兴市恒发特种粉末冶金厂 | Cycloidal oil pump rotator |
| CN202900633U (en) * | 2012-10-17 | 2013-04-24 | 新乡航空工业(集团)有限公司 | Eight-tooth cycloid pump and cycloid pump rotor structure thereof |
Non-Patent Citations (2)
| Title |
|---|
| 圆弧-泛摆线齿轮油泵及其在罗茨泵上的应用;任跃军等;《真空》;20040325(第02期);第41页-第43页，图1、2 * |
| 摆线转子式齿轮泵的设计;毛华永等;《粉末冶金技术》;20031030(第05期);第282页-第284页，图1 * |
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