CN104612963A - Rotating device suitable for high pressure scene and mechanical device using rotating device - Google Patents
Rotating device suitable for high pressure scene and mechanical device using rotating device Download PDFInfo
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- CN104612963A CN104612963A CN201410776253.8A CN201410776253A CN104612963A CN 104612963 A CN104612963 A CN 104612963A CN 201410776253 A CN201410776253 A CN 201410776253A CN 104612963 A CN104612963 A CN 104612963A
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- chamber
- bearing
- eccentric shaft
- piston
- cylinder body
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Classifications
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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
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
- F02B55/08—Outer members for co-operation with rotary pistons; Casings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C2/00—Rotary-piston engines
- F03C2/22—Rotary-piston engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
-
- 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
- F04C18/10—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 internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The invention provides a rotating device applied to high pressure scene and a fluid flow machine using the rotating device, in the rotating device, an eccentric axis moving cavity and a piston moving cavity are separated, a bearing can be arranged in the axial direction of the eccentric axis moving cavity, due to the axial length of the eccentric axis moving cavity is greater than the axial length of the piston moving cavity, bearing arrangement number and flexibility are can be n expanded in great space, multi-bearing withstanding pressure is naturally increased, pressure bearing capacity of the fluid flow machine using the rotating device is greatly improved, the rotating device can be applied to the high pressure scene, and the rotating device has practical work life.
Description
Technical field
The invention relates to mechanical field, particularly relate to and be a kind ofly applicable to the slewing gear of high pressure scene and apply its mechanical device, as pump, compressor, fluid motor and motor.
Background technique
In order to improve the recovery rate in oil field, early flooding is proved to be very effective way.Can strata pressure be improved by early flooding, make oil reservoir have strong Flooding Conditions, higher formation pressure can be kept, thus reach the object of oil field stable high yield.
In the last few years, the exploitation of shale oil and shale gas was rapidly flourishing.Exploitation shale oil and the most frequently used method of shale gas are hydrofracturing method, inject oil well, discharge by the oil and gas of trap by high pressure water (being often mixed with chemical substance).At present, shale oil more than half and shale gas mining hydrofracturing method is about had.
Be no matter above-mentioned mention oil field early flooding, shale oil/shale gas exploitation, or the other field such as desalination of sea water, engineering machinery, high-pressure service pump technology all plays an important role, and it has become the key factor that restriction manufacturing efficiency improves further.Various high-pressure service pump has been there is, such as: plunger pump, reciprocating pump, screw pump, eccentric rotarypump etc. in prior art.
The claimant of the application have submitted a patent application (application number: 201310030773.X) on January 15th, 2013.In this part of patent application, applicant provide a kind of star rotating type rotating device and apply its rotor-type compressor and fluid motor.Figure 1A is the longitudinal section schematic diagram of prior art rotor-type compressor.Figure 1B is for rotor-type compressor shown in Figure 1A is along the sectional view in A-A face.As shown in FIG. 1A and 1B, this rotor-type compressor comprises: cylinder body 110, front/rear end cap (120,130), main shaft 200, eccentric rotor assembly 300 and interrupter 400.Wherein, cylinder body 110 limits a cylindrical cavity with the front/rear end cap (120,130) being positioned at its both sides.Main shaft 200 is supported rotationally by front/rear end cap (120,130), is positioned partially in cylindrical cavity, the central axes of its central axis and cylinder body 110.Eccentric rotor assembly 300 is sheathed on the part that main shaft 200 is positioned at cylindrical cavity, comprising: eccentric shaft 310, rolling piston wheel 330 and two rolling bearings 320.Wherein, eccentric shaft 310 is sheathed on the part that main shaft 200 is positioned at cylindric inner chamber, the centerline axis parallel of its central axis and main shaft 200 and the predeterminable range that staggers.Rolling piston wheel 330 is sheathed on eccentric shaft 310, the central axes of its central axis and eccentric shaft 310.Two rolling bearings 320, be sheathed on eccentric shaft 310 symmetrically, its inside race is fixed on eccentric shaft 310, its outer collar is fixed on rolling piston wheel 330, to completely cut off both rotations, rolling piston is taken turns the inner cylinder face that 330 are pressed in cylindrical cavity by the pretension elastic force that two rolling bearings 320 and rolling piston are taken turns between 330, makes the external cylindrical surface of the inner cylinder face of cylindrical cavity and rolling piston wheel 330 form axially extended sealed chamber.Sealed chamber is divided into the first separate chamber and the second chamber by interrupter 400, and this first chamber and the second chamber are connected with second group of through hole with the first group of through hole being arranged on cylinder body 110 respectively.
For the star-rotary-type compressor shown in Figure 1A, Figure 1B, it adopts rolling bearing between eccentric shaft and rolling piston wheel.After using rolling bearing, rotor compressor is just expected to realize non-oil ultra high vacuum system and lacks oiling in other words, overcomes with regard to being expected to the shortcomings brought because using lubricant oil in a large number, thus this structure can be applied in large-scale compressor, air compressor, pump field.
But for the high pressure water-injection pump that such as oil field uses, due to the existence of high pressure factor, said structure there will be problem and can not use.For a kind of on market dual-faced roller bearing of model.As shown in Figure 2, the height of this dual-faced roller bearing is 50mm, and external diameter is 180mm, and internal diameter is 130mm.Suppose that the length L of piston is 6.6cm, radius R is 28cm, and operating air pressure P is 20MPa (200kgf/cm
2), the throw of eccentric l of eccentric rotor is 5mm (i.e. 0.005m), and the rotating speed n of pump is 740rev/min, due to the restriction of cavity space axial distance, can only arrange 1 rolling bearing, then:
Piston area S=28 × 6.6=184.8cm
2
Piston thrust F=P × S=100kgf/cm
2× 184.8cm
2=18480kgf
Rotor torque M=l × F=0.005m × 18480kgf=906.444N-m
The load f=18480kgf that this 1 rolling bearing bears
The basic dynamic load C=27900kgf of bearing
Velocity coefficient fn=(33.3/n) 3/10=0.394
Life factor fh=(33.3/n) 3/10 × C/f=0.394 × 27900/18480=0.5948
Life time h=500 × fh10/3=500 × (0.5948) 10/3=500 × 0=88.5h
Visible, because the piston space of inner chamber of cylinder block is very narrow and small, 1 NNU4926 bearing can only be held.For eccentric rotor slewing gear, the pressure carried due to rolling bearing is excessive, causes its life time to be only 88.5h, does not reach practical requirement far away.
At present, urgently occur in the industry that one has larger space and to bear elevated pressures, thus has the high-pressure service pump of adequate service life to hold more multiple bearing.
Summary of the invention
(1) technical problem that will solve
In view of above-mentioned technical problem, the invention provides a kind of slewing gear and apply its mechanical device, under it can be applied to high pressure scene, and have can be practical operating life.
(2) technological scheme
According to an aspect of the present invention, a kind of slewing gear is provided.This slewing gear comprises: cylinder body 110, front and rear cover (120,130), main shaft 200, eccentric rotary assembly 300, interrupter 400.Wherein, cylinder body 110 and front and rear cover (120,130), three limits an inner chamber jointly, and this inner chamber is divided into two-part of central axes, and first portion is cylindrical chamber, as eccentric shaft motion chamber; Second portion is to cave in toward the outer side the annular chamber formed at the inwall of first portion, as piston movement chamber.Main shaft 200, is supported rotationally by cylinder body 110 and/or front and rear cover (120,130), and part is positioned at inner chamber, and its central axis and eccentric shaft move the central axes in chamber.Eccentric rotary assembly 300 comprises: eccentric shaft 310, is sheathed on the part that main shaft 200 is positioned at inner chamber, the centerline axis parallel of its central axis and main shaft 200 and the predeterminable range that staggers; Rolling piston wheel 330, comprising: sleeve part 331 and piston portion 332, sleeve part 331 cylindrically constructs, and is sheathed on the outside of eccentric shaft 310; Piston portion 332 is in circular structure, be sheathed on the outside of sleeve part 331, its axial length equals the axial length in piston movement chamber, its side contacts with the bi-side in piston movement chamber and seals, wherein, eccentric shaft 310 and sleeve part 331 move in eccentric shaft motion chamber, and moving at least part of position of piston portion 332 in piston movement chamber, forms axially extended crescent shape sealed chamber between the inner cylinder face in piston movement chamber and the external cylindrical surface of piston portion 332; And at least one bearing 320, be arranged at eccentric shaft 310 and rolling piston wheel sleeve part 331 between, eccentric shaft motion chamber axial range in.Interrupter 400, is divided into the first separate chamber and the second chamber by crescent shape sealed chamber, and this first chamber and the second chamber are connected with second group of through hole with the first group of through hole be arranged on cylinder body respectively.
According to another aspect of the present invention, a kind of pump is additionally provided.This pump comprises above-mentioned slewing gear, and wherein: the first chamber is entrance cavity 411, it is connected with fluid inlet by the suction through hole 412 be opened on cylinder body; Second chamber is outlet plenum 413, and it is connected with fluid output by the discharge through hole 414 be opened on cylinder body.
According to a further aspect of the invention, a kind of compressor is additionally provided.This compressor comprises above-mentioned slewing gear, and wherein: the second chamber is suction chamber, it is connected with low pressure compressed media inlet opening by the second group of through hole be opened on cylinder body; First chamber is compression chamber, and it is connected with high pressure compressed medium exhaust port by the first group of through hole be opened on cylinder body.
According to a further aspect of the invention, a kind of fluid motor is additionally provided.This fluid motor comprises above-mentioned slewing gear, wherein: the second chamber is acting chamber, and it is connected with high-pressure liquid import by the second group of through hole be opened on cylinder body; First chamber is discharge side, and it is connected with low pressure fluid output by the first group of through hole be opened on cylinder body.
According to a further aspect of the invention, a kind of motor is additionally provided.This motor comprises above-mentioned slewing gear, wherein: the second chamber is by being opened in second group of through hole on cylinder body and combustion chamber; First chamber is connected with outlet port by the first group of through hole be opened on cylinder body.
(3) beneficial effect
As can be seen from technique scheme, the slewing gear of applying high voltage scene of the present invention and the fluid machinery applying it have following beneficial effect:
(1) chamber of being moved by eccentric shaft separates with piston movement chamber, bearing can eccentric shaft move chamber axis arrange, axial length due to eccentric shaft motion chamber is greater than the axial length in piston movement chamber, thus bearing magnitude setting and flexibility ratio have all had very large spatial expansion, the pressure that multiple bearing can bear increases naturally, and then the bearing capacity of the fluid machinery applying this slewing gear significantly improves, high pressure scene can be applied to, and have can be practical operating life;
(2) owing to having larger eccentric shaft motion chamber, thus counterweight is convenient to arrange more, can alleviate the problem of the momentum imbalance caused due to slewing gear eccentric rotary better, more meet accurate engineering principle, operation gets up to vibrate little, and noise is low;
(3) under general scene, adopted multiple rolling bearing enough, and in superpressure pump, the ultrahigh pressure load that planetary piston wheel is born can bear with hydrostatic bearing, works more reliable.
Accompanying drawing explanation
Figure 1A is the longitudinal section schematic diagram of prior art rotor-type compressor;
Figure 1B is for rotor-type compressor shown in Figure 1A is along the sectional view in A-A face;
Fig. 2 is the schematic diagram of bearing life time model;
Fig. 3 is the longitudinal section sectional view according to embodiment of the present invention eccentric rotator type pump
Fig. 4 A and Fig. 4 B is respectively the pump of eccentric rotator type shown in Fig. 3 under two states along the sectional view in A-A face;
Fig. 5 is the schematic diagram of the pump adopting hydrostatic bearing according to another embodiment of the present invention;
The schematic diagram of stopcock sheet in the interrupter that Fig. 6 is the pump of eccentric rotator type shown in Fig. 3;
Fig. 7 be according in another embodiment of the present invention by the schematic diagram of eccentric shaft and bearing integrated.
Embodiment
For making the object, technical solutions and advantages of the present invention clearly understand, below in conjunction with specific embodiment, and with reference to accompanying drawing, the present invention is described in more detail.It should be noted that, in accompanying drawing or specification describe, similar or identical part all uses identical figure number.The implementation not illustrating in accompanying drawing or describe is form known to a person of ordinary skill in the art in art.In addition, although herein can providing package containing the demonstration of the parameter of particular value, should be appreciated that, parameter without the need to definitely equaling corresponding value, but can be similar to corresponding value in acceptable error margin or design constraints.The direction term mentioned in embodiment, such as " on ", D score, "front", "rear", "left", "right" etc., be only the direction with reference to accompanying drawing.Therefore, the direction term of use is used to illustrate and is not used for limiting the scope of the invention.
In the present invention, chamber of being moved by eccentric shaft separates with piston movement chamber, thus has widened the installation space of the bearing between eccentric shaft and planetary piston wheel greatly, can meet the demand of various high-pressure machinery device.For ease of illustrating, the existing reference character corresponding to each element that the present invention relates to is listed as follows:
110-cylinder body;
111-cylinder body body; 112-front end housing;
113-back cylinder cover;
120-front cover; 130-rear end cover;
140-cylinder head;
200-main shaft;
210-first main shaft bearing; 220-second main shaft bearing;
300-eccentric rotor assembly;
310-eccentric shaft;
320-rolling bearing;
330-rolling piston is taken turns;
331-sleeve part; 332-piston portion;
333-Packing spring; 334-side seal;
335-elastic ring;
340-equilibrate counterweight;
350-hydrostatic bearing;
351-fuel oil supply nozzle;
400-interrupter;
410-stopcock body;
420-entrance cavity; 421-sucks through hole;
430-outlet plenum; 431-discharges through hole.
Below will be described in detail respectively to each embodiment of the present invention.
One, slewing gear
First, the invention provides a kind of slewing gear, this slewing gear comprises: cylinder body, front/rear end cap, main shaft, eccentric rotor assembly, rolling piston wheel and interrupter.
Cylinder body and front and rear cover limit an inner chamber jointly, and this inner chamber is divided into two-part of central axes, and first portion is cylindrical chamber, as eccentric shaft motion chamber; Second portion is to cave in toward the outer side the annular chamber formed at the inwall of first portion, as piston movement chamber.
Main shaft is supported rotationally by cylinder body and/or front and rear cover, and part is positioned at inner chamber, and its central axis and eccentric shaft move the central axes in chamber.
Eccentric rotary assembly comprises: eccentric shaft, is sheathed on the part that main shaft is positioned at inner chamber, the centerline axis parallel of its central axis and main shaft and the predeterminable range that staggers.
Rolling piston is taken turns, and comprising: sleeve part and piston portion, sleeve part cylindrically constructs, and is sheathed on the outside of eccentric shaft; Piston portion is circular structure, be sheathed on the outside of sleeve part, its axial length equals the axial length in piston movement chamber, its side contacts with the bi-side in piston movement chamber and seals, wherein, eccentric shaft and sleeve part move in eccentric shaft motion chamber, and moving at least part of position of piston portion in piston movement chamber, forms axially extended crescent shape sealed chamber between the inner cylinder face in piston movement chamber and the external cylindrical surface of piston portion.And at least one bearing, be arranged at eccentric shaft and rolling piston wheel sleeve part between, eccentric shaft motion chamber axial range in.
Crescent shape sealed chamber is divided into the first separate chamber and the second chamber by interrupter, and this first chamber and the second chamber are connected with second group of through hole with the first group of through hole be arranged on cylinder body respectively.For different fluid machineries, this first chamber, the second chamber, first group of through hole, second group of through hole all have different designs, and these contents are described in concrete mechanism.
In the present embodiment, chamber of being moved by eccentric shaft separates with piston movement chamber, the axial length in eccentric shaft motion chamber is greater than the axial length in piston movement chamber, and bearing can be arranged in the move axis in chamber of eccentric shaft, thus magnitude setting and flexibility ratio have all had very large spatial expansion.
In this slewing gear, the quantity often organizing through hole in through hole can be 1, also can be multiple.Further, bearing can be rolling bearing, also can be hydrostatic bearing.And rolling bearing can be roller bearing, ball bearing, needle bearing, aerodynamics rolling bearing or composite bearing.Wherein, preferably, bearing is symmetrical set.Herein symmetrical, refers to relative to following plane symmetry: this plane crosses the axis centre of piston portion, and perpendicular to the axis of piston portion.
The present embodiment slewing gear can be applied in the fluid machinery such as compressor, fluid motor.Below by the correspondence pump of above-mentioned slewing gear, compressor, fluid motor and motor, especially pump, be described in detail.By the following description, those skilled in the art should have understanding clearly to slewing gear of the present invention.
Two, pump
In one exemplary embodiment of the present invention, provide a kind of pump.Fig. 3 is the longitudinal sectional view according to embodiment of the present invention pump.Fig. 4 A and Fig. 4 B is respectively the sectional view along A-A face under two states of pump shown in Fig. 3.Please refer to Fig. 3, Fig. 4 A and Fig. 4 B, this pump comprises: cylinder body 110, front and rear cover (120 and 130), main shaft 200, eccentric rotor assembly 300 and interrupter 400.
Below respectively each constituent element of the present embodiment eccentric rotator type pump is described in detail.
Please refer to Fig. 3, cylinder body 110 comprises cylinder body body 111, is separately positioned on front end housing 112 and the back cylinder cover 113 of the front/rear end face of this cylinder body body 111.Predeterminated position outside cylinder body body 111, is generally top, arranges cylinder head 140.The stopcock body of follow-up interrupter and resetting-mechanism thereof, suction through hole 421, discharge through hole 431 all to should the position of cylinder head 140 arrange, these contents will hereafter be described in detail.
Cylinder body 110 and front and rear cover (120,130), three limits an inner chamber jointly, this inner chamber is divided into two-part of central axes, and first portion is cylindrical chamber, and second portion is to cave in toward the outer side the annular chamber formed at the inwall of first portion.Wherein, this cylindrical chamber is called eccentric shaft motion chamber, the activity space of its sleeve part of taking turns as eccentric shaft and rolling piston.Annular chamber is called piston movement chamber, and it is as the activity space of the piston portion of rolling piston wheel.These contents will be described in detail hereinafter.
In the present embodiment, piston movement chamber is positioned at the axially middle part in piston movement chamber, but the present invention is not as limit, the position in this piston movement chamber can move left and right, even be positioned at left side or the right side of cylindrical chamber, all can realize the present invention, but this will bring the problem of shaft strength inequality, do not recommend to adopt.
In order to the convenience of follow-up statement, according to its function, inner chamber is radially divided into eccentric shaft motion chamber and piston movement chamber.But also can distinguish the various piece of this inner chamber vertically, namely it is divided into chamber, left side, intermediate cavity and right-side cavity from left to right.Wherein, chamber, left side is identical with the radius of right-side cavity, and the radius of intermediate cavity is then large than the radius in these two chambeies.It should be noted that, the axial length of chamber, left side and right-side cavity can be identical or different, and the radius of chamber, left side and right-side cavity also can difference to some extent, all can by user's sets itself as required.
Main shaft 200 is supported rotationally by front and rear cover (120,130), and part is positioned at described inner chamber, and its central axis and eccentric shaft move the central axes in chamber.The first portion of main shaft 200 is positioned at outside inner chamber, connects with external power source, and torque transfer external power source inputted is to inner chamber; Second portion is positioned at inner chamber, and the moment of torsion utilizing external power source to input drives eccentric rotor assembly 300 to rotate.
For reducing friction, the first main shaft bearing 210, second main shaft bearing 220 is set between main shaft 200 and front and back cylinder cap (112 and 113) respectively.This first main shaft bearing 210 and the second main shaft bearing 220 are by front cover 120 (or rear end cover 130) location.Wherein, the first main shaft bearing 210 preferably adopts high bearing capacity, long lifetime, high-precision tapered roller bearing, controlled to ensure the gap precision in rotor side surface and cylinder cap face.
It should be noted that, although main shaft 200 is supported rotationally by front end housing 112 and back cylinder cover 113 in the present embodiment, it also can by front/rear end cap (120,130) rotating support.In addition, although main shaft only has one end to stretch out outside cylindrical cavity in the present embodiment, the present invention comprises main shaft two ends equally and stretches out outside cylindrical cavity, by the situation of input torque while of the left and right sides.Those skilled in the art should very clearly understand how technique scheme realizes, and repeats no more herein.
As shown in Figure 1A, eccentric rotor assembly 300 comprises: eccentric shaft 310, rolling piston wheel 330 and the bearing 320 be positioned between the two.By adopting bearing between eccentric shaft and rolling piston wheel, avoiding the dependence to lubricant oil, overcoming the shortcomings brought because using lubricant oil in a large number.Under the drive of main shaft, eccentric shaft 310, rolling piston wheel 330 rolls in inner chamber.
Eccentric shaft 310 is sheathed on the part that main shaft 200 is positioned at cylindrical chamber, the centerline axis parallel of its central axis and main shaft 200 and the predeterminable range that staggers.The axial length of this eccentric shaft 310 is greater than the axial length in piston movement chamber, and is less than or equal to the axial length of cylindrical chamber.The size of the degree of eccentricity e of eccentric shaft 310 is determined according to compressor displacement, and such as get 4.5mm when discharge capacity is 53c.c, discharge capacity is larger, and degree of eccentricity e is larger.
Rolling piston wheel 330 can be divided into two-part, i.e. sleeve part 331 and piston portion 332.Sleeve part 331 cylindrically constructs, and is sheathed on the outside of eccentric shaft 310, and piston portion 332, in circular structure, is sheathed on the outside of sleeve part 331.Wherein, the axial length of sleeve part 331 is less than or equal to the axial length of eccentric shaft 310.The axial length of piston portion 332 equals the axial length in piston movement chamber, and its side contacts with the bi-side in piston movement chamber and seals.
In the course of the work, eccentric shaft and sleeve part move all the time in eccentric shaft motion chamber, then moving at least part of position of piston portion in piston movement chamber, thus forms axially extended crescent shape sealed chamber between the inner cylinder face in piston movement chamber and the external cylindrical surface of piston portion.
In the present embodiment, the outer ledge of the sleeve part 331 of planetary piston wheel and eccentric shaft move chamber inside edge between distance be more than or equal to 1mm, thus in the course of the work, both do not contact, and, the radius of this sleeve part (and eccentric shaft) can reduce further, and the present invention does not limit its radius.
In order to avoid the piston portion of planetary piston wheel comes off from piston movement chamber, and ensure the sealing in piston portion and piston movement chamber, both sides, therefore in the course of the work, piston portion both sides contact distance and must ensure to be more than or equal to 3mm with the radial direction in piston movement chamber, be preferably more than and equal 5mm.
It should be noted that, in the present embodiment, sleeve part 331 and piston portion 332 are two parts be separated.But in other embodiments of the invention, the one-piece element that both also can make, namely both integration systems are standby.Consider many-sided factor such as difficulty of processing and cost, be preferably both separate machined and be socketed, the both sides of both contact position arrange elastic ring 335 to alleviate friction, and compensation vibration, as shown in Figure 3 and Figure 5.
In order to ensure the sealing between the bi-side of piston portion 332 and the bi-side in piston movement chamber, slotting in the position contacted with piston movement chamber in the bi-side of piston portion 332, and offers through hole vertically at the predeterminated position of groove bottom.Packing spring 333 is installed in through hole, side seal 334 is installed in groove.Thus in the process of rotating in piston movement chamber at piston portion 332, under the effect of Packing spring 333, side seal 334 side touching piston movement chamber tightly all the time, realizes the reliable sealing of piston portion and bi-side, piston movement chamber.
It should be noted that, this side seal 334 in the form of sheets, can adopt the preparation of the wear-resisting and material that friction factor is low, such as bronze-graphite material, teflon (PTFE), polyether-ether-ketone (PEEK) or antifriction alloy etc.In addition, Packing spring also can adopt elastic component to replace, such as pneumatic spring, elastic caoutchouc rod.Further, also can adopt and offer disconnected blind hole respectively in the bottom of piston portion 332 bi-side groove, in blind hole, elastic component is set respectively.Or even, when requirement on machining accuracy meet between the bi-side of piston portion 332 and piston movement chamber, realize reliable sealing, the parts such as side seal, elastic component also can omit.
In the present embodiment, between eccentric shaft 310 and rolling piston wheel sleeve portion 331, in the axial range in eccentric shaft motion chamber, be provided with 5 rolling bearings 320.The pressure that this 5 rolling bearing shareds are conducted by piston portion 332.These rolling bearings can be roller bearing, ball bearing, needle bearing, aerodynamics rolling bearing or composite bearing.
Same with the scene mentioned in background technique, namely the length L of piston is 6.6cm, and radius R is 28cm, and operating air pressure P is 20MPa (200kgf/cm
2), the throw of eccentric l of eccentric rotor is 5mm (i.e. 0.005m), and the rotating speed n of eccentric rotator type pump is 740rev/min is example, when applying the technological scheme of the present embodiment, then
Piston area S=28 × 6.6=184.8cm
2
Piston thrust F=P × S=100kgf/cm
2× 184.8cm
2=18480kgf
Rotor torque M=l × F=0.005m × 18480kgf=906.444N-m
The load F=18480kgf that rolling bearing bears
The basic dynamic load C=27900 × 5=139500kgf of bearing
Velocity coefficient fn=(33.3/n) 3/10=0.394
Life factor fh=(33.3/n) 3/10 × C/P=0.394 × 139500/18980=2.8958
Life time h=500 × fh10/3=500 × (2.8958) 10/3=500 × 34.612=17306h
Via above-mentioned calculating, the life time of the present embodiment rolling bearing is 17306 hours (continuous operation 2 years), substantially meets the needs of oil field practice application.
It should be noted that, in the present invention, the quantity of rolling bearing 5 of being also not limited to that the present embodiment limits, and can be symmetrical set multiple, such as: 3 ~ 10.
When more high pressure, rolling bearing can not meet the demands, and in this case, then needs to introduce hydrostatic bearing.Fig. 5 is the schematic diagram of the eccentric rotator type pump adopting hydrostatic bearing according to another embodiment of the present invention.As shown in Figure 5, between the sleeve part 331 that eccentric shaft 310 and rolling piston are taken turns, hydrostatic bearing 350 is set.This hydrostatic bearing adopts high-pressure oil passage system to the static-pressure oil chamber fuel feeding of hydrostatic bearing by the hydrostatic bearing fuel oil supply nozzle 351 be arranged at outside cylinder body, reliable operation.
In the design of traditional eccentric rotator type pump, the inner cavity size of eccentric rotor structure is compact especially, causes the setting of bearing to be subject to great limitation, or adopts oil lubrication, or adopts little bearing, limited efficiency.And in the present embodiment, chamber of being moved by eccentric shaft separates with piston movement chamber, the axial length in eccentric shaft motion chamber is far longer than the axial length in piston movement chamber, and bearing can set gradually in the move axis in chamber of eccentric shaft, thus magnitude setting and flexibility ratio have all had very large improvement.
In addition, by the restriction that traditional eccentric rotator type pump intracavity space is little, arranging of equilibrate counterweight is very inconvenient, and even have to outside equilibrate counterweight being arranged at cylinder body, this causes great inconvenience to operation and maintenance.
And in the present embodiment, chamber of being moved by eccentric shaft separates with piston movement chamber, the axial length of eccentric shaft 310 is less than the axial length in eccentric shaft motion chamber, and the space between inside eccentric shaft 310 and cylindrical chamber is then used for arranging equilibrate counterweight 340.
By in eccentric shaft motion chamber, the both sides load balance balancing weight 340 of eccentric shaft 310, alleviates the problem of the momentum imbalance caused due to eccentric rotary due to rotor-type compressor, more meets accurate engineering principle.Through the eccentric rotator type pump of rotor momentum balance design, operation gets up to vibrate little, and noise is low.
As shown in Figure 4 A and 4 B shown in FIG., axially extended crescent shape sealed chamber is formed between the inner cylinder face in piston movement chamber and the external cylindrical surface of piston portion.
This crescent shape sealed chamber is divided into the first chamber and the second chamber by interrupter 400.For eccentric rotator type pump, this first chamber is entrance cavity 420, and it is connected with fluid inlet by sucking through hole 421; This second chamber is outlet plenum 430, and it is connected with fluid output by discharging through hole 431.
In the present embodiment, the position on cylinder body body 111 inside corresponding cylinder head 140 be formed one axially extended, open wide towards cylindrical cavity put groove.Interrupter 400 comprises: stopcock body 410 and stopcock body resetting-mechanism.This stopcock body 410 is fitted in this and puts in groove and by its rotating support, and can swing in predetermined angular range.Stopcock body resetting-mechanism, for the end of stopcock body being installed with all the time the external cylindrical surface in rolling piston wheel, to be divided into separate entrance cavity 420 and outlet plenum 430 by crescent shape sealed chamber.
In the present embodiment, stopcock body 410 is sheet structure, i.e. stopcock sheet.The schematic diagram of stopcock sheet in the interrupter that Fig. 6 is the pump of eccentric rotator type shown in Fig. 3.As shown in Fig. 4 B and Fig. 6, in order to reduce the friction between piston portion 332 that stopcock sheet 410 and rolling piston take turns, the radius of curvature that the radius of curvature R of the side that this stopcock sheet 410 contacts with the external cylindrical surface of piston portion 332 is set to the inner cylindrical surface in the movable chamber with piston is identical.
When eccentric rotor assembly turn to upper position time, stopcock sheet 410 is pressed into this and puts in groove, in press-in state.When eccentric rotor assembly turns to lower position, stopcock sheet is rocked to its maximum position, in the state of stretching out.And the end of stopcock sheet is installed with the external cylindrical surface in rolling piston wheel all the time, thus by the first chamber and the second chamber isolation.Wherein, when stopcock sheet 410 from put show in groove time, its just facing to chamber be the first chamber, i.e. entrance cavity 420, its by suck through hole 421 be connected with fluid inlet; The stopcock body back side towards chamber be the second chamber, i.e. outlet plenum 430, its by discharge through hole 431 be connected with fluid output.
It should be noted that, except the stopcock chip architecture in the present embodiment, 200780027498.9), gate valve (number of patent application: 201110322746.0), bidirectional rotary valve block (201410415170.6) etc. eccentric rotator type pump of the present invention can also the slider of other types, such as, adopt the stopcock body (number of patent application: of semicircular structure.In addition, about stopcock body resetting-mechanism, in these patent applications, also all there is detailed description, be not described in detail herein.
By above-mentioned explanation, the complete description structure of the present embodiment eccentric rotator type pump each several part.The working procedure of the present embodiment eccentric rotator type pump will be introduced below: the moment of torsion outside cylindrical cavity is passed in inner chamber by main shaft; Under the drive of main shaft, take eccentric shaft as medium, the fluid entered by fluid inlet, along cylindrical cavity rolls forward, is pumped into crescent shape seal operation space by rolling piston wheel, and then by fluid output by fluid expulsion.
So far, the present embodiment eccentric rotator type pump is introduced complete.
Three, compressor
In another embodiment of the present invention, a kind of compressor is additionally provided.The structure of this compressor and the structure of said pump similar, difference is only the difference in the direction of entrance design and corresponding fluids.In this compressor, the second chamber of slewing gear, i.e. suction chamber, is connected with low pressure compressed media inlet opening by second group of through hole; First chamber, i.e. compression chamber, be connected with high pressure compressed medium exhaust port after compression by first group of through hole.
Wherein, the moment of torsion outside cylindrical cavity is passed in cylindrical cavity by main shaft, by eccentric rotor assembly to compress compressed media.It should be noted that between discharge through hole and high pressure compressed medium exhaust port, there is open and close valve.Only have when the air pressure of discharging through hole reaches a preset pressure threshold value, this open and close valve just can be opened, thus exports the compressed media after compression to high pressure compressed medium exhaust port.When the air pressure of discharging through hole does not reach this preset pressure threshold value, this open and close valve is close all the time.
So far, the present embodiment compressor is introduced complete.
Four, fluid motor
In another embodiment of the present invention, a kind of fluid motor is additionally provided.The structure of this fluid motor and the structure of said pump similar, difference is only the difference in the direction of entrance design and corresponding fluids.In this fluid motor, the second chamber of slewing gear, chamber of namely doing work, is connected with high-pressure liquid import by second group of through hole; First chamber, i.e. discharge side, be connected with low pressure fluid output by first group of through hole.
Wherein, high-pressure liquid continues to flow in a steady stream and promotes eccentric rotor into, high-pressure liquid and rotate, and is passed to outside cylindrical cavity by the moment of torsion of main shaft by generation.This high-pressure liquid can be liquid or gas.
So far, the present embodiment fluid motor is introduced complete.
Five, motor
In another embodiment of the present invention, a kind of motor is additionally provided.The structure of this motor and the structure of said pump similar, difference is only the difference in the direction of entrance design and corresponding fluids.In this motor, the second chamber of slewing gear, by second group of through hole and combustion chamber; First chamber, is connected with outlet port by first group of through hole.
Wherein, the pressurized gas entered by firing chamber promote eccentric rotor assembly and roll along cylindrical cavity, and eccentric rotor assembly drives main axis, is passed to outside cylindrical cavity by the moment of torsion of main shaft by generation.
So far, the present embodiment motor is introduced complete.
So far, by reference to the accompanying drawings the present invention five embodiments have been described in detail.Describe according to above, those skilled in the art to the slewing gear of applying high voltage scene of the present invention and the fluid machinery applying it, clearly should be familiar with as pump, compressor, fluid motor and motor have had.
In addition, the above-mentioned definition to each element and method is not limited in various concrete structures, shape or the mode mentioned in embodiment, and those of ordinary skill in the art can change simply it or replace, such as:
(1) Biserial cylindrical roller bearing used in figure, can also make the multiple row roller bearing form that special heavy duty is special;
WTF tetra-as NSK company arranges the bearing of resistance to water dust, can use under the cold rolling harsh and unforgiving environments of iron and steel, than long three times of traditional life-span.
(2) because offset is less, in the present embodiment main shaft and eccentric shaft integration system standby, and the sleeve part integration system that the outer collar of bearing and rolling piston are taken turns is standby, as shown in Figure 7;
In addition, in other embodiments of the invention, eccentric shaft can also be standby with the inside race integration system of bearing.Standby through integration system, bearing space can be strengthened further, increase bearing capacity, extend bearing working life.
(3) in above-described embodiment, for convenience, by main shaft and eccentric shaft described separately, but in fact, main shaft and eccentric shaft can be processed respectively and assemble, and also can integration processs, and, be preferably and main shaft and eccentric shaft integration processed.
In sum, the present invention chamber of being moved by eccentric shaft separates with piston movement chamber, thus widened the bearing between eccentric shaft and planetary piston wheel greatly flexibility ratio is set, thus multiple rolling bearing even hydrostatic bearing can be set, thus alleviate the pressure that bearing bears, and then expanded the working life of whole mechanism, be adapted to very much the demand of the high-voltage field scapes such as oil field.Meanwhile, this structure is equally applicable to multiple fields such as compressor, fluid motor and motor, has high application value.
Above-described specific embodiment; object of the present invention, technological scheme and beneficial effect are further described; be understood that; the foregoing is only specific embodiments of the invention; be not limited to the present invention; within the spirit and principles in the present invention all, any amendment made, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (20)
1. a slewing gear, is characterized in that, comprising:
Cylinder body (110) and front and rear cover (120,130), three limits an inner chamber jointly, and this inner chamber is divided into two-part of central axes, and first portion is cylindrical chamber, as eccentric shaft motion chamber; Second portion is to cave in toward the outer side the annular chamber formed at the inwall of first portion, as piston movement chamber;
Main shaft (200), is supported rotationally by described cylinder body (110) and/or front and rear cover (120,130), and part is positioned at described inner chamber, and its central axis and eccentric shaft move the central axes in chamber;
Eccentric rotary assembly (300) comprising:
Eccentric shaft (310), is sheathed on the part that described main shaft (200) is positioned at inner chamber, the centerline axis parallel of its central axis and described main shaft (200) and the predeterminable range that staggers;
Rolling piston wheel (330), comprising: sleeve part (331) and piston portion (332), described sleeve part (331) cylindrically constructs, and is sheathed on the outside of described eccentric shaft (310), described piston portion (332) is in circular structure, be sheathed on the outside of described sleeve part (331), its axial length equals the axial length in described piston movement chamber, its side contacts with the bi-side in described piston movement chamber and seals, wherein, described eccentric shaft (310) and sleeve part (331) move in described eccentric shaft motion chamber, and move at least part of position of piston portion (332) in described piston movement chamber, axially extended crescent shape sealed chamber is formed between the inner cylinder face in described piston movement chamber and the external cylindrical surface of described piston portion (332), and
At least one bearing (320), between the sleeve part (331) being arranged at described eccentric shaft (310) and rolling piston wheel, in the axial range in described eccentric shaft motion chamber; And
Interrupter (400), is divided into the first separate chamber and the second chamber by described crescent shape sealed chamber, and this first chamber and the second chamber are connected with second group of through hole with the first group of through hole be arranged on cylinder body respectively.
2. slewing gear according to claim 1, is characterized in that, described piston portion (332) both sides contact distance with the radial direction in piston movement chamber and are more than or equal to 3mm.
3. slewing gear according to claim 1, is characterized in that, described piston movement chamber is positioned at the axially middle part in described eccentric shaft motion chamber;
Eccentric shaft motion cavity segment on the right side of described piston movement chamber is identical with the radius of the eccentric shaft motion cavity segment in left side.
4. slewing gear according to claim 1, is characterized in that, the sleeve part (331) of described rolling piston wheel and piston portion (332):
Integration system is standby, or
Be socketed after separate machined, and elastic ring is set in the both sides of both contact position.
5. slewing gear according to claim 1, is characterized in that, described main shaft and eccentric shaft integration system standby.
6. slewing gear according to claim 1, is characterized in that:
The inner sleeve integration system of described eccentric shaft and described at least one bearing (320) is standby; And/or
The sleeve part (331) of described rolling piston wheel is standby with the outer collar integration system of described at least one bearing (320).
7. slewing gear according to claim 1, is characterized in that, slot in the position that the bi-side of described piston portion (332) contact with described piston movement chamber, the predeterminated position perforate vertically of groove bottom;
Be provided with elastic component in hole, be provided with side seal (334) in groove, under the effect of described elastic component, described side seal (334) touch the side in described piston movement chamber.
8. slewing gear according to claim 7, is characterized in that, described elastic component is Packing spring (333), pneumatic spring or elastic caoutchouc rod;
Described side seal (334) in the form of sheets, is prepared by bronze-graphite material, teflon, polyether-ether-ketone or antifriction alloy.
9. slewing gear according to claim 1, is characterized in that, at least one bearing described is symmetrical set;
Wherein, this symmetrical finger is relative to following plane symmetry, and this plane crosses the axis centre of described piston portion (332), and perpendicular to this axis.
10. slewing gear according to claim 9, is characterized in that, at least one bearing described is the multiple rolling bearings be symmetrical set.
11. slewing gears according to claim 10, is characterized in that, the number of described rolling bearing is between 3 ~ 10;
Described rolling bearing is roller bearing, ball bearing, needle bearing, aerodynamics rolling bearing or composite bearing.
12. slewing gears according to claim 9, is characterized in that, at least one bearing described is the hydrostatic bearing be symmetrical set.
13. slewing gears according to claim 1, is characterized in that, described interrupter (400) comprising: slider and slider resetting-mechanism;
Wherein, described slider resetting-mechanism makes the end of described slider be installed with the external cylindrical surface of taking turns in rolling piston all the time, so that described crescent shape sealed chamber is divided into the first chamber and the second chamber.
14. slewing gears according to claim 13, is characterized in that, described slider is gate valve, stopcock body or bidirectional rotary valve body.
15. slewing gears according to claim 14, is characterized in that, the inner side of described cylinder body (110) formed axially extended, put groove towards internal chamber opens;
Described stopcock body in the form of sheets, it is fitted in this and puts in groove and by its rotating support, can swing in predetermined angular range, and the radius of curvature of the inner cylindrical surface in the radius of curvature of side that contacts of the external cylindrical surface of its piston portion of taking turns with described rolling piston and the movable chamber of described piston is identical.
16. slewing gears according to claim 1, is characterized in that, in the movable chamber of described eccentric shaft, the both sides of described eccentric shaft (310) are provided with equilibrate counterweight.
17. 1 kinds of pumps, is characterized in that, comprise the slewing gear according to any one of claim 1 to 16, wherein:
Described first chamber is entrance cavity (411), and it is connected with fluid inlet by the suction through hole (412) be opened on cylinder body;
Described second chamber is outlet plenum (413), and it is connected with fluid output by the discharge through hole (414) be opened on cylinder body.
18. 1 kinds of compressors, is characterized in that, comprise the slewing gear according to any one of claim 1 to 16, wherein:
Described second chamber is suction chamber, and it is connected with low pressure compressed media inlet opening by the second group of through hole be opened on cylinder body;
Described first chamber is compression chamber, and it is connected with high pressure compressed medium exhaust port by the first group of through hole be opened on cylinder body.
19. 1 kinds of fluid motors, is characterized in that, comprise the slewing gear according to any one of claim 1 to 16, wherein:
Described second chamber is acting chamber, and it is connected with high-pressure liquid import by the second group of through hole be opened on cylinder body;
Described first chamber is discharge side, and it is connected with low pressure fluid output by the first group of through hole be opened on cylinder body.
20. 1 kinds of motors, is characterized in that, comprise the slewing gear according to any one of claim 1 to 16, wherein:
Described second chamber is by being opened in second group of through hole on cylinder body and combustion chamber;
Described first chamber is connected with outlet port by the first group of through hole be opened on cylinder body.
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| CN107414655A (en) * | 2017-09-26 | 2017-12-01 | 广州市锐恒科技有限公司 | A kind of double bistrique electro spindle polishing grinding machines |
| WO2018027801A1 (en) * | 2016-08-11 | 2018-02-15 | 姚镇 | Rotating system, and fluid motor, compressor, pump and engine using same |
| CN111878389A (en) * | 2020-09-08 | 2020-11-03 | 青岛大学 | Internal combustion type swinging scraper pump |
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| CN104612963B (en) | 2017-01-18 |
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Effective date of registration: 20170622 Address after: 100176, Beijing economic and Technological Development Zone, No. three, No. 1, Metro Industrial Park, No. two, B3 workshop Patentee after: Beijing Xingxuan Century Technology Co., Ltd. Address before: 100176, Beijing B3 economic and Technological Development Zone, three industrial park, No. 1, two industrial building, Beijing, Daxing District Patentee before: Yao Zhen |