CN106762503A - Digital distribution and speed governing type low speed axial plunger pump - Google Patents

Digital distribution and speed governing type low speed axial plunger pump Download PDF

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Publication number
CN106762503A
CN106762503A CN201611164800.2A CN201611164800A CN106762503A CN 106762503 A CN106762503 A CN 106762503A CN 201611164800 A CN201611164800 A CN 201611164800A CN 106762503 A CN106762503 A CN 106762503A
Authority
CN
China
Prior art keywords
speed
solenoid valve
digital distribution
plunger
pressure
Prior art date
Application number
CN201611164800.2A
Other languages
Chinese (zh)
Inventor
郁立成
施光林
Original Assignee
上海交通大学
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 上海交通大学 filed Critical 上海交通大学
Priority to CN201611164800.2A priority Critical patent/CN106762503A/en
Publication of CN106762503A publication Critical patent/CN106762503A/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/16Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26Control
    • F04B1/28Control of machines or pumps with stationary cylinders
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18Lubricating
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00Pump parameters
    • F04B2201/12Parameters of driving or driven means
    • F04B2201/1206Rotational speed of a rotating inclined plate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00Pump parameters
    • F04B2201/12Parameters of driving or driven means
    • F04B2201/1208Angular position of the shaft

Abstract

A kind of digital distribution and speed governing type low speed axial plunger pump, including:Housing, the input axis mechanism being arranged in housing, return mechanism and five groups are respectively provided with the plunger and corresponding flow passage structure of high-speed solenoid valve, wherein:Input axis mechanism tail end is provided with the angular encoder being connected with electronic control unit, controls five high-speed solenoid valves respectively by electronic control unit;Each high-speed solenoid valve input is connected with corresponding plunger cavity, and two output ends are connected with low pressure chamber respectively and high pressure chest is connected.The present invention flow passage structure overall by transforming axial plunger pump, makes each friction pair be in cold oil lubricating status, and pump body structure is simply compact, and energy conversion efficiency is high, long service life;The present invention is using the traditional valve plate of high-speed solenoid valve substitution or flow check valve for being distributed in each plunger cavity simultaneously, formed it is easily controllable be input into for the random slow-speed of revolution under digital distribution and speed governing.

Description

Digital distribution and speed governing type low speed axial plunger pump
Technical field
The present invention relates to a kind of technology in hydraulic planger pump field, specifically a kind of digital distribution and speed governing type low speed Axial plunger pump.
Background technology
Axial plunger pump compact conformation, volumetric efficiency is high, is one of conventional hydraulic pump.When the rotation of its entering spindle is turned around, Each piston reciprocation is moved once, in order to be correctly completed oil suction and oil extraction work, it will usually use valve plate flow or Flat valve Technology.In valve plate flow, plunger group rotation, valve plate is fixed with swash plate.There is a pair of Port Plate Pair between plunger and valve plate, Complex process is inevitable to produce leakage and be lost;And plunger rotary inertia is larger, it is unfavorable for becoming at random in extraneous input speed Worked during change.In Flat valve, plunger is fixed, swash plate rotation, and plunger distinguishes oil suction and force feed work by check valve, eliminates a pair Port Plate Pair.But check valve generally has suctional oil valve hysteresis, its volumetric efficiency is reduced, and flow there are certain requirements. Also, either valve plate flow or Flat valve, each friction pair is only lubricated by Leakage Energy in pump.When needing that pump is carried out During speed governing, it is required for an extra control valve to carry out vari- able flow control.
In recent years, hydraulic electricity generation technology is employed in the generations of electricity by new energy such as wind energy, ocean energy.Conventional hydraulic electrification structure is adopted Wind energy or ocean energy are collected with the loop of " quantitative hydraulic pump-variable hydraulic motor ", mainly by variable hydraulic motor Speed stabilizing control and generating are realized in discharge capacity regulation, and hydraulic pump is still employed according to quantifying that constant rotating speed driving principle high is designed Hydraulic pump, it is difficult to ensure that it meets random generation and the indefinite operating mode of size specific to wind-power electricity generation and power generation with marine energy for a long time Demand.Only when pump adapts to random slow-speed of revolution input status in itself, and only when its flow or speed adjusting technique are all stablized When reliable, application demand could be met.
The content of the invention
The present invention is lubricated by Leakage Energy mostly for prior art causes pump each friction pair presence when continuously running Substantially heat up, and the defects such as the regulation of continuous-stable cannot be carried out to flow under extraneous random slow-speed of revolution input, propose one Digital distribution and speed governing type low speed axial plunger pump are planted, the flow passage structure overall by transforming pump is in each kinematic pair cold Oil lubrication state, and flow and speed-regulating function are realized in one, pump body structure is simply compact, and energy conversion efficiency is high, uses the longevity Life length;Simultaneously the present invention using be distributed in the traditional valve plate of high-speed solenoid valve substitution of each plunger cavity, flow check valve or Regular tap valve, forms easily controllable digital distribution and speed governing.
The present invention is achieved by the following technical solutions.
The present invention includes:Housing, the input axis mechanism being arranged in housing, return mechanism and five groups are respectively provided with electricity at a high speed The plunger of magnetic switch valve and corresponding flow passage structure, wherein:Input axis mechanism tail end is provided with the angle being connected with electronic control unit Degree encoder, five high-speed solenoid valves are controlled by electronic control unit respectively;Each high-speed solenoid valve input It is connected with corresponding plunger cavity, two output ends are connected with low pressure chamber respectively and high pressure chest is connected.
The described angular encoder that Shaft angle is input into for detecting is absolute value type angular encoder, electronic control unit Angle and angular speed are calculated according to the analog signal that angular encoder is exported, each high-speed solenoid valve is entered further according to needs Row adjusts dutycycle with oil and speed regulating controlWherein:D θ/dt is the differential of the current angular signal of encoder, ω0 It is rated speed.
Described high-speed solenoid valve is preferably two-position three way high-speed solenoid valve, and A ends are connected with plunger cavity, high pressure End is that P ends are connected with high-voltage load, and low-pressure end is that T-port is connected with low pressure oil pocket, when high-speed solenoid valve must not be electric, post Plug is interval to be connected with low pressure interval;When high-speed solenoid valve is obtained it is electric when, plunger cavity and high pressure interval connect.
Described housing includes:For oil suction and allow plunger in it low-pressure shell of motion, for setting electricity at a high speed The High Pressure Shell being connected with oilcan body and with load of magnetic switch valve.
Described input axis mechanism includes:Input shaft and swash plate and asessory shaft, the taper roll bearing of co-axial connection And deep groove ball bearing, wherein:Taper roll bearing is arranged at low-pressure shell side, and swash plate is arranged on taper roll bearing, tiltedly Disk is coordinated with input shaft by key, and deep groove ball bearing is arranged at on oilcan body, and the asessory shaft shaft shoulder is arranged on deep groove ball bearing, One end is coordinated with swash plate by key, and the other end is connected through with oily housing central bore to High Pressure Shell with encoder.
Hollow flow passage is provided with inside described asessory shaft, asessory shaft is circumferentially with aperture, for by low pressure oil from low pressure shell It is sucked into in oilcan body in vivo.
Described return mechanism includes:Spring on asessory shaft, platen, needle roller thrust bearing and return plate are nested in, its In:Spring one end is arranged on the asessory shaft shaft shoulder, and the other end is arranged on platen vertical plane, and the inclined plane of platen is arranged at thrust The side of needle bearing, the opposite side of needle roller thrust bearing is arranged on return plate, and return plate is arranged on piston shoes.
Technique effect
Compared with prior art, the present invention is by digital valve Technology application to axial plunger pump, and optimizes its original machinery Structure, integrated electronic control technology, sensing detection technology and high-speed solenoid valve technology design a kind of novel digital type Flow and speed governing axial plunger pump, fundamentally solve low intrinsic of volumetric efficiency that original mechanical flow mode brings and lack Point, and strengthen the lubrication function of each friction pair, extend the service life of pump.In addition, pump carries speed-regulating function in itself, The control characteristic of pump is improve, can effectively apply to random slow-speed of revolution input occasion.
Brief description of the drawings
Fig. 1 is mechanical construction drawing of the present invention;
In figure:A is outside schematic diagram;B is A-A faces sectional view;
Fig. 2 is circuit control schematic diagram of the present invention;
In figure:1 input shaft, 2 low-pressure shells, 3 taper roll bearings, 4 swash plates, 5 needle roller thrust bearings, 6 piston shoes, 7 backhauls Oilcan body, 16 rings are matched somebody with somebody in disk, 8 platens, 9 springs, 10 plungers, 11 oil inlets, 12 plunger cavities, 13 deep groove ball bearings, 14 asessory shafts, 15 Type groove, 17 High Pressure Shells, 18 oil-outs, 19 angular encoders, 20 high-speed solenoid valves, 21 fuel tanks, 22 loads, 23 electronics controls Unit processed, the plunger cavities of I~V first to the 5th, 1.~5. first to the 5th high-speed solenoid valve.
Specific embodiment
As shown in figure 1, the present embodiment includes:The input axis mechanism being arranged in low-pressure shell 2 is connected with input axis mechanism Swash plate 4 and be in contact with swash plate 4 five groups plungers 10 and its plunger cavity 12 with high-speed solenoid valve 20, wherein: Input axis mechanism is provided with the angular encoder 19 being connected with electronic control unit 23, is controlled respectively by electronic control unit 23 Five high-speed solenoid valves 20;The input of each high-speed solenoid valve 20 (I~V in figure) and corresponding plunger cavity 1.~5. It is connected, output end low-pressure port is connected by asessory shaft 14, low-pressure shell 2, oil inlet 11 with fuel tank 21, high pressure port is by height The interior annular groove 16 of pressure shell body 17, oil-out 18 are connected with load 22.The described angular encoder for detecting the corner of input shaft 1 19 is absolute value type angular encoder, and electronic control unit 23 calculates angle according to the analog signal that angular encoder 19 is exported And angular speed, further according to needing to carry out each high-speed solenoid valve with oil and speed regulating control, that is, adjust dutycycle Wherein:D θ/dt is the differential of the current angular signal of encoder 19, ω0It is rated speed.
Described high-speed solenoid valve is preferably two-position three way high-speed solenoid valve, and A ends are connected with plunger cavity 12, high Pressure side is that P ends are connected with high-voltage load 22, and low-pressure end is that T-port is connected with low-pressure reservoir 20, when high-speed solenoid valve 20 not When obtaining electric, plunger cavity 12 is connected with low pressure interval;When high-speed solenoid valve 16 must be electric, plunger cavity 12 is interval with high pressure even It is logical.
Described housing includes:For to the oil suction of fuel tank 21 and set plunger cavity 1.~low-pressure shell 2 5. etc., for setting Put high-speed solenoid valve 20 with oilcan body 15 and with for setting encoder 19 and connecting the pressure shell high of high-voltage load 22 Body 17.
There is inlet port on the described body of low pressure shell 2, include input axis mechanism, return mechanism, plunger 10 and its supporting piston shoes 6。
Described includes with oilcan body 15:Allow plunger in interior reciprocating plunger cavity 12, high speed electromagnetic switch is set The mounting hole of valve 20, allows the centre bore that asessory shaft 14 is passed through from center, and high-speed solenoid valve 20 respectively with plunger cavity 12nd, centre bore, the runner of the connection of High Pressure Shell annular groove 16.
The connecting hole and annular groove 16 for setting angular encoder 19 are provided with described High Pressure Shell 17.
Described input axis mechanism includes:Input shaft 1 and the swash plate of co-axial connection 4 and asessory shaft 14, taper roller Bearing 3 and deep groove ball bearing 13, wherein:Taper roll bearing 3 is arranged at the input side of low-pressure shell 2, and swash plate 4 is arranged at circular cone rolling On sub- bearing 3, swash plate 4 and input shaft 1 are coordinated by key, and deep groove ball bearing 13 is arranged at on oilcan body 15, the axle of asessory shaft 14 Shoulder is arranged on deep groove ball bearing 13, and the one end of asessory shaft 14 coordinates with the key of swash plate 4, and one end is paramount through the centre bore of oilcan body 15 is matched somebody with somebody Pressure shell body 17 is connected with angular encoder 19.
The inside of described asessory shaft 14 is provided with hollow flow passage, and asessory shaft 14 is circumferentially with aperture, so as to by low pressure oil 2 are sucked into in oilcan body 15 from low-pressure shell.
Described return mechanism includes:It is nested in spring 9 on asessory shaft 14, platen 8, needle roller thrust bearing 5 and backhaul Disk 7, wherein:One end of spring 9 is arranged on the shaft shoulder of asessory shaft 14, the other end is arranged on the vertical plane of platen 8, and platen 8 inclines Inclined-plane is arranged at the side of needle roller thrust bearing 5, and the opposite side of needle roller thrust bearing is arranged on return plate 7, and return plate is set In on piston shoes 6.
Said apparatus are operated in the following manner:Random external slow-speed of revolution power drives swash plate 4 to revolve by input shaft 1 Turn.Asessory shaft 14 is also rotated together with due to being connect to be bonded with swash plate 4.Platen 8 is also to be bonded to connect with asessory shaft 14, and by In spring 9, it is pressed on needle roller thrust bearing 5, needle roller thrust bearing 5 is pressed on return plate 7, and then presses return plate 7 Piston shoes 6 are on swash plate 4.When input shaft 1 rotates, swash plate 4, asessory shaft 14, platen 8, spring 9 are also followed and rotated together, while auxiliary Help axle 14 that rotational positional relationship is transferred into encoder 19.Piston shoes 6 are relative on swash plate to be slided, and affects plunger 10, completes plunger The oil suction and force feed work in chamber.
In oil suction, low pressure oil enters in low-pressure shell 2 from oil inlet 11, and directly taper roll bearing 3, thrust can be rolled Needle bearing 5 and deep groove ball bearing 13 are lubricated, and the hollow flow passage in rear asessory shaft 14 enters matches somebody with somebody oilcan body 15, and by a high speed The inner flow passage of electromagnetic switch valve 20 is connected with plunger cavity 12.In oil extraction, hydraulic oil discharge from plunger cavity 12, by high speed electromagnetic The inner flow passage of switch valve 20 enters in the intermediate annular groove 16 of High Pressure Shell 17, and load is fed to eventually through oil-out 18.
As shown in Fig. 2 rotating shaft angle signal is delivered to electronic control unit 23 by angular encoder 19, calculate current angular and match somebody with somebody Flow relation and duty cycle relationship, then PWM ripples are delivered into each high-speed solenoid valve.When 1. high-speed solenoid valve 10 is powered off When, I plunger cavities 5 and low pressure oil UNICOM, when high-speed solenoid valve 10 is powered, plunger cavity 5 and the UNICOM of high-voltage load 16.With this Analogize.Each valve is as shown in table 1 with flow relation in respective bins.When input shaft input speed overrate, then control High-speed solenoid valve in the interval plunger cavity of oil extraction will be powered in dutycycle mode, and Duty ratio control algorithmic formula is:α is the dutycycle of two-position three way high-speed solenoid valve, and d θ/dt is the differential of the current angular signal of encoder, ω0It is rated speed.
Table 1 respectively rotates interval flow relation
Above-mentioned specific implementation can by those skilled in the art on the premise of without departing substantially from the principle of the invention and objective with difference Mode local directed complete set is carried out to it, protection scope of the present invention is defined and not by above-mentioned specific implementation institute by claims Limit, each implementation in the range of it is by the constraint of the present invention.

Claims (9)

1. a kind of digital distribution and speed governing type low speed axial plunger pump, it is characterised in that including:Housing, it is arranged in housing Input axis mechanism, return mechanism and five groups are respectively provided with the plunger and corresponding flow passage structure of high-speed solenoid valve, wherein:Input Axis mechanism tail end is provided with the angular encoder being connected with electronic control unit, controlled respectively by electronic control unit five it is high Fast electromagnetic switch valve;Each high-speed solenoid valve input and corresponding plunger cavity are connected, two output ends respectively with low pressure chamber It is connected and is connected with high pressure chest.
2. digital distribution according to claim 1 and speed governing type low speed axial plunger pump, it is characterized in that, it is input into for detecting The angular encoder of Shaft angle is absolute value type angular encoder, the simulation letter that electronic control unit is exported according to angular encoder Number angle and angular speed are calculated, further according to needing that each high-speed solenoid valve is carried out to be accounted for oil and speed regulating control, i.e. adjustment Sky ratioWherein:D θ/dt is the differential of the current angular signal of encoder, ω0It is rated speed.
3. digital distribution according to claim 1 and speed governing type low speed axial plunger pump, it is characterized in that, described high speed electricity Magnetic switch valve is two-position three way high-speed solenoid valve, and A ends are connected with plunger cavity, and high-pressure side is that P ends are connected with high-voltage load, low Pressure side is that T-port is connected with low pressure oil pocket, and when high-speed solenoid valve must not be electric, plunger is interval to be connected with low pressure interval;When When magnetic valve obtains electric, plunger cavity is connected with high pressure interval.
4. digital distribution according to claim 1 and speed governing type low speed axial plunger pump, it is characterized in that, described housing bag Include:For setting the low-pressure shell of plunger cavity, for setting being connected with oilcan body and with load for high-speed solenoid valve High Pressure Shell.
5. digital distribution according to claim 4 and speed governing type low speed axial plunger pump, it is characterized in that, it is described with oilcan Body includes:Allow plunger in interior reciprocating plunger cavity, the mounting hole of high-speed solenoid valve, high-speed solenoid valve are set The runner for being connected with plunger cavity, centre bore, High Pressure Shell annular groove respectively, and allow the center that asessory shaft is passed through from center Hole.
6. digital distribution according to claim 4 and speed governing type low speed axial plunger pump, it is characterized in that, described pressure shell high There are oil-out and the mounting hole for setting encoder on body, inside is provided with annular groove.
7. digital distribution according to claim 1 and speed governing type low speed axial plunger pump, it is characterized in that, described input shaft Mechanism includes:Input shaft and swash plate and asessory shaft, the taper roll bearing and deep groove ball bearing of co-axial connection, wherein:Circle Taper roller bearing is arranged at low-pressure shell side, and swash plate is arranged on taper roll bearing, and swash plate is coordinated with input shaft by key, Deep groove ball bearing is arranged at on oilcan body, and the asessory shaft shaft shoulder is arranged on deep groove ball bearing, and one end is coordinated with swash plate by key, The other end is connected through with oily housing central bore to High Pressure Shell with encoder.
8. digital distribution according to claim 7 and speed governing type low speed axial plunger pump, it is characterized in that, described asessory shaft Inside be provided with hollow flow passage, asessory shaft and be circumferentially with aperture, for by low pressure oil from being sucked into low-pressure shell with oilcan body.
9. digital distribution according to claim 1 and speed governing type low speed axial plunger pump, it is characterized in that, described backhaul machine Structure includes:Spring on asessory shaft, platen, needle roller thrust bearing and return plate are nested in, wherein:Spring one end is arranged at auxiliary On the axle shaft shoulder, the other end is arranged on platen vertical plane, and the inclined plane of platen is arranged at the side of needle roller thrust bearing, thrust rolling The opposite side of needle bearing is arranged on return plate, and return plate is arranged on piston shoes.
CN201611164800.2A 2016-12-16 2016-12-16 Digital distribution and speed governing type low speed axial plunger pump CN106762503A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201611164800.2A CN106762503A (en) 2016-12-16 2016-12-16 Digital distribution and speed governing type low speed axial plunger pump

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Application Number Priority Date Filing Date Title
CN201611164800.2A CN106762503A (en) 2016-12-16 2016-12-16 Digital distribution and speed governing type low speed axial plunger pump

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109139590A (en) * 2018-08-17 2019-01-04 合肥工业大学 Become discharge capacity with streaming system based on switching flow and the open type digital pump for compiling strategy
CN111350706A (en) * 2019-12-27 2020-06-30 燕山大学 Pulse width modulation type hydraulic transformer

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2657125B1 (en) * 1990-01-12 1992-04-10 Leduc Rene Hydro Sa Improvements on axial piston hydraulic pumps and biais plate.
CN1800634A (en) * 2006-01-12 2006-07-12 上海交通大学 Electric control valve flow-distribution mechanism for crankshaft connecting rod type low-speed high-torque hydraulic motor
CN201065815Y (en) * 2007-07-11 2008-05-28 韩树松 Elastic fastener type valve flow distribution plunger pump
CN201786594U (en) * 2010-09-21 2011-04-06 华中科技大学 Plunger water pump
JP2011226413A (en) * 2010-04-21 2011-11-10 Mitsubishi Electric Corp Fuel supply device
CN102734109A (en) * 2012-05-29 2012-10-17 武汉华喜特种液压设备有限公司 Fully water-lubricated valve distribution plunger pump
CN202732256U (en) * 2012-05-03 2013-02-13 邵阳伊顿贝克液压有限责任公司 Valve flow distribution plunger pump
CN105386953A (en) * 2015-12-25 2016-03-09 上海交通大学 Digital flow-distribution constant-flow radial plunger pump

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2657125B1 (en) * 1990-01-12 1992-04-10 Leduc Rene Hydro Sa Improvements on axial piston hydraulic pumps and biais plate.
CN1800634A (en) * 2006-01-12 2006-07-12 上海交通大学 Electric control valve flow-distribution mechanism for crankshaft connecting rod type low-speed high-torque hydraulic motor
CN201065815Y (en) * 2007-07-11 2008-05-28 韩树松 Elastic fastener type valve flow distribution plunger pump
JP2011226413A (en) * 2010-04-21 2011-11-10 Mitsubishi Electric Corp Fuel supply device
CN201786594U (en) * 2010-09-21 2011-04-06 华中科技大学 Plunger water pump
CN202732256U (en) * 2012-05-03 2013-02-13 邵阳伊顿贝克液压有限责任公司 Valve flow distribution plunger pump
CN102734109A (en) * 2012-05-29 2012-10-17 武汉华喜特种液压设备有限公司 Fully water-lubricated valve distribution plunger pump
CN105386953A (en) * 2015-12-25 2016-03-09 上海交通大学 Digital flow-distribution constant-flow radial plunger pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109139590A (en) * 2018-08-17 2019-01-04 合肥工业大学 Become discharge capacity with streaming system based on switching flow and the open type digital pump for compiling strategy
CN109139590B (en) * 2018-08-17 2020-07-28 合肥工业大学 Open type digital pump variable displacement flow distribution system based on switching flow distribution and marshalling strategies
CN111350706A (en) * 2019-12-27 2020-06-30 燕山大学 Pulse width modulation type hydraulic transformer

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Application publication date: 20170531