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 PDFInfo
- 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 pump
- plunger
- Prior art date
- Legal status (The legal status 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 status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-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
- F04B1/16—Multi-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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/18—Lubricating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1206—Rotational speed of a rotating inclined plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1208—Angular position of the shaft
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
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
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.
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 |
Applications Claiming Priority (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 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106762503A true CN106762503A (en) | 2017-05-31 |
Family
ID=58891717
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611164800.2A Pending CN106762503A (en) | 2016-12-16 | 2016-12-16 | Digital distribution and speed governing type low speed axial plunger pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106762503A (en) |
Cited By (7)
| 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 |
| CN109139409A (en) * | 2018-09-30 | 2019-01-04 | 杭州力龙液压有限公司 | Digital constant flow inclined shaft plunger pump |
| CN109441750A (en) * | 2018-09-30 | 2019-03-08 | 江苏金陵智造研究院有限公司 | A kind of axial plunger pump |
| CN111350706A (en) * | 2019-12-27 | 2020-06-30 | 燕山大学 | Pulse width modulation type hydraulic transformer |
| CN113339222A (en) * | 2021-07-20 | 2021-09-03 | 安徽理工大学 | Double-row axial plunger pump based on digital variable |
| CN114483674A (en) * | 2022-02-28 | 2022-05-13 | 浙江工业大学 | Radial digital pump capable of adjusting pressure impact and control method thereof |
| CN115013275A (en) * | 2022-05-31 | 2022-09-06 | 江苏大学流体机械温岭研究院 | Load-sensitive digital axial plunger pump for active valve flow distribution and working method thereof |
Citations (8)
| 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 |
-
2016
- 2016-12-16 CN CN201611164800.2A patent/CN106762503A/en active Pending
Patent Citations (8)
| 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 (10)
| 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 |
| CN109139409A (en) * | 2018-09-30 | 2019-01-04 | 杭州力龙液压有限公司 | Digital constant flow inclined shaft plunger pump |
| CN109441750A (en) * | 2018-09-30 | 2019-03-08 | 江苏金陵智造研究院有限公司 | A kind of axial plunger pump |
| CN111350706A (en) * | 2019-12-27 | 2020-06-30 | 燕山大学 | Pulse width modulation type hydraulic transformer |
| CN113339222A (en) * | 2021-07-20 | 2021-09-03 | 安徽理工大学 | Double-row axial plunger pump based on digital variable |
| CN114483674A (en) * | 2022-02-28 | 2022-05-13 | 浙江工业大学 | Radial digital pump capable of adjusting pressure impact and control method thereof |
| CN114483674B (en) * | 2022-02-28 | 2024-03-19 | 浙江工业大学 | Radial digital pump capable of adjusting pressure impact and control method thereof |
| CN115013275A (en) * | 2022-05-31 | 2022-09-06 | 江苏大学流体机械温岭研究院 | Load-sensitive digital axial plunger pump for active valve flow distribution and working method thereof |
| CN115013275B (en) * | 2022-05-31 | 2024-03-08 | 江苏大学流体机械温岭研究院 | Load-sensitive digital axial plunger pump with active valve flow distribution and working method thereof |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106762503A (en) | Digital distribution and speed governing type low speed axial plunger pump | |
| CN106894962A (en) | A kind of high-pressure high-flow hydraulic planger pump | |
| CN106837725A (en) | Two-dimensional axial plunger displacement pump | |
| CN107630798A (en) | A kind of variable displacement AC synchronous mechanical electronic hydraulic coupler | |
| CN207377751U (en) | A kind of variable displacement mouse-cage type mechanical electronic hydraulic integrated power device | |
| CN207377753U (en) | A kind of DC Variable stator permanent-magnet integrated power device | |
| CN112377382B (en) | Variable axial plunger pump based on proportional pressure reducing valve control | |
| CN101634316A (en) | Hydraulic transformer with safety device | |
| CN206562977U (en) | Two-dimensional axial plunger pump | |
| CN202867198U (en) | Low-pressure oil-injection screw compressor | |
| CN207454192U (en) | A kind of controlled variable plunger pump | |
| CN203809289U (en) | Piston-controlled variable-displacement vane pump | |
| CN202900655U (en) | Low pressure oil injection type screw compressor | |
| CN102878079A (en) | Low pressure oil injected screw compressor | |
| CN212898825U (en) | Novel roller guide rail driving mechanism | |
| CN207377752U (en) | A kind of squirrel-cage mechanical electronic hydraulic integrated power device | |
| CN107559170A (en) | A kind of squirrel-cage mechanical electronic hydraulic integrated power device | |
| CN106321393A (en) | Displacement automatic-compensation variable-rotational-speed adjustment swash plate axial plunger pump | |
| CN202645905U (en) | Double-kinetic-energy flow control pump | |
| CN207485481U (en) | A kind of high-speed permanent magnetic body magnetic-suspension main-shaft air power drive device | |
| CN206309592U (en) | A kind of variable inner curve hydraulic pump of adjustable type or motor | |
| CN201705412U (en) | Three-lobe rotor engine and lubrication device thereof | |
| CN207377738U (en) | A kind of variable displacement AC synchronous mechanical electronic hydraulic coupler | |
| CN206571831U (en) | It is a kind of to rotate the composite bearing integrated with up-and-down motion | |
| CN106121947B (en) | A kind of power end component of reciprocating pump and the multi-cylinder reciprocating pump using the component |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20170531 |