CN106246493A - A kind of no pulse hydraulic pressure 4 cylinder direct driving type slush pump system - Google Patents
A kind of no pulse hydraulic pressure 4 cylinder direct driving type slush pump system Download PDFInfo
- Publication number
- CN106246493A CN106246493A CN201610830831.0A CN201610830831A CN106246493A CN 106246493 A CN106246493 A CN 106246493A CN 201610830831 A CN201610830831 A CN 201610830831A CN 106246493 A CN106246493 A CN 106246493A
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- Prior art keywords
- oil
- oil pump
- hydraulic pumping
- pump
- cylinder
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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
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
- F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
- F04B9/113—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor
Abstract
The invention discloses a kind of no pulse hydraulic pressure 4 cylinder direct driving type slush pump system, including the hydraulic pumping oil pump output unit of two groups of independences, slush pump, the proportioning valve controlling described oil circuit and the reversal valve that described often group hydraulic pumping oil pump output unit includes a hydraulic pumping oil pump, two oil cylinders connected being connected with described oil pump by oil circuit are connected with described oil cylinder；For 180 degree of angles of each cycle between two oil cylinders in described hydraulic pumping oil pump output unit, forming 90 degree of angles of each cycle between the oil cylinder of described two groups of hydraulic pumping oil pump output units, the flow making described hydraulic pumping oil pump inject oil cylinder by described proportioning valve realizes alternation according to trapezoidal wave change and exports.The present invention is by controlling the output variable speed of four output cylinders, effectively the great advantage set of existing hydraulic slurry pump and bent axle slush pump, has the plurality of advantages such as volume is little, lightweight, pulse steady, mechanical abrasion.
Description
Technical field
The invention belongs to slush pump, be specifically related to a kind of no pulse hydraulic pressure 4 cylinder direct driving type slush pump system.
Background technology
Fluid pressure drive device uses, the most widely as slip casting water pump in terms of providing reciprocating machine motion at present
Fluid pressure drive device.The advantage of this fluid pressure drive device is that volume is little, lightweight, structure is substantially the single, double cylinder of hydraulic pressure
Working method two kinds, wherein the fluid pressure drive device of twin-tub is connected the oil cylinder of 2 series connection by a hydraulic pumping oil pump, passes through liquid
Press pump fuel circulating pump and reversal valve work so that the oil circuit of two oil cylinders forms the counteragent of 180 degree and drives slush pump.No matter
Being single oil cylinder or double oil cylinder, they common shortcomings are, output pulse is big, unstable.In order to obtain pulse more smoothly,
Prior art widely applies 3 cylinders or 5 cylinder machinery crank type devices in terms of the driving means of pump, but this puts and body
Long-pending huge, the shortcoming such as quality is heavy and mechanical wear is fast.
Summary of the invention
It is an object of the invention to the shortcoming for above prior art, it is provided that a kind of output pulse is steady, and power consumption is few, weight
Gently, the no pulse hydraulic pressure 4 cylinder direct driving type slush pump system that volume is little, output energy is big.
The technical scheme is that and be achieved in that:
The no pulse hydraulic pressure 4 cylinder direct driving type slush pump system that the present invention provides, the hydraulic pumping oil pump including two groups of independences exports
Unit, described often group hydraulic pumping oil pump output unit is included a hydraulic pumping oil pump, is connected with described oil pump by oil circuit
The mud that is connected with described oil cylinder of oil cylinders of two series connection export assembly, the proportioning valve controlling described oil circuit and reversal valve；Institute
State between two oil cylinders in hydraulic pumping oil pump output unit as 180 degree of angles of each cycle, described two groups of hydraulic pumping oil pumps
Form 90 degree of angles of each cycle between the oil cylinder of output unit, make described hydraulic pumping oil pump inject oil cylinder by described proportioning valve
Flow according to trapezoidal wave change realize alternation output.
The analog signals that described proportioning valve is controlled part input 0-10v by PLC is controlled.
Beneficial effect
Present system, owing to often organizing the output of the hydraulic pumping oil pump in hydraulic pumping oil pump output unit according to trapezoidal wave
Change realizes 180 degree of checkers of two oil cylinders, and is formed every between the oil cylinder of two groups of hydraulic pumping oil pump output units
90 degree of angles of cycle, when system is run, arbitrary moment output stream value summation is equal to the maximum flow value of single cylinder output.Cause
This, the draining output pulse of present system is close to zero.
The present invention is by controlling, effectively existing hydraulic slurry pump and bent axle the output variable speed of four output cylinders
The great advantage set of slush pump, by automated procedures control so that it is become and have that volume is little, lightweight, pulse
Steadily, the all-hydraulic mud pump system of the plurality of advantages such as mechanical abrasion.
Further illustrate technical scheme below in conjunction with the accompanying drawings.
Accompanying drawing explanation
Fig. 1 is the structural principle schematic diagram of the present invention.
Fig. 2 to Fig. 5 is the working state schematic representation of the present invention respectively.
Fig. 6, Fig. 7 are two hydraulic pumping oil pump output units output stream spirograms at a cycle of operation respectively.
Fig. 8 is two hydraulic pumping oil pump output units output flow stacking charts at a cycle of operation.
Detailed description of the invention
As it is shown in figure 1, the no pulse hydraulic pressure 4 cylinder direct driving type slush pump system that the present invention provides, including hydraulic pumping oil pump
Part 1, oil cylinder part 2, mud output part 3 and oil circuit and PLC control part 4, and described hydraulic pumping oil pump part 1 includes two
Individual hydraulic pumping oil pump 1a, 1b, oil cylinder part 2 includes that four oil cylinder 2a 2d, mud output part 3 include four mud outputs
Assembly 3a 3d, oil circuit and PLC control part 4 include oil circuit and PLC (not shown), be located on oil circuit two groups
The reversal valve etc. of proportioning valve 4a, 4b composition corresponding with proportioning valve 4a, 4b and oil cylinder 2a 2d；Wherein hydraulic pumping oil pump 1a, oil
The compositions one such as cylinder 2a, 2b, mud output assembly 3a, 3b, one group of proportioning valve 4a and corresponding reversal valve (not shown) are solely
Vertical hydraulic pumping oil pump output unit, oil-out A1, B1 of hydraulic pumping oil pump 1a is by oil circuit and the oil cylinder of two series connection
2a, 2b connect, and oil cylinder 2a, 2b are connected with mud output assembly 3a, 3b respectively by piston rod, arrange ratio by PLC
Example valve 4a exports analog signals, controls output flow and the size variation of described hydraulic pumping oil pump 1a oil circuit；Hydraulic pumping
Oil pump 1b, oil cylinder 2c, 2d, mud output assembly 3c, 3d, another group proportioning valve 4b and corresponding reversal valve (not shown) etc.
Forming another independent hydraulic pumping oil pump output unit, oil-out A2, B2 of hydraulic pumping oil pump 1b passes through oil circuit and two
Only oil cylinder 2c, 2d of series connection connects, and oil cylinder 2c, 2d are connected with mud output assembly 3c, 3d respectively by piston rod, pass through PLC
Controller Set scale valve 4b exports analog signals, controls output flow and the size variation of hydraulic pumping oil pump 1b oil circuit；
By being positioned proximate to switch j1, j2, j3 on the stroke L of oil cylinder 2a so that two in each hydraulic pumping oil pump output unit
For 180 degree of angles of each cycle between oil cylinder, between the oil cylinder of two hydraulic pumping oil pump output units, form each cycle 90 degree
Angle, is controlled hydraulic pumping oil pump 1a, 1b by PLC and runs, and arrange the 0-10v analog quantity of described proportioning valve 4a, 4b
Signal exports, and control signal and the oil cylinder speed of service are linear relationship, makes described hydraulic pumping oil pump 1a, 1b inject oil cylinder 2a
The flow of 2d realizes alternation output according to trapezoidal wave change, is more directly pushed away mud output assembly 3a 3d shape by described oil cylinder 2a 2d
Speed change is become to move back and forth.
Operation principle
See that Fig. 1: hydraulic pumping oil pump 1a place hydraulic pumping oil pump output unit is in original state, two oil cylinders 2a, 2b it
Between the angle of cycle of operation be 180 degree, at this moment their piston rod is in the rearmost end and foremost of oil cylinder 2a, 2b respectively,
The cycle of operation between two oil cylinders 2c, 2d in another hydraulic pumping oil pump output unit at hydraulic pumping oil pump 1b place
Angle be 180 degree.
Seeing that Fig. 2, system bring into operation, oil pump 1a place hydraulic pumping oil pump output unit runs 1/4 cycle (i.e. 1/2L row
Journey), the piston rod of oil cylinder 2a, 2b respectively forwardly stretches out and retracts backward half stroke L, and oil cylinder 2a, 2b speed of service is by ratio
(the flow output of hydraulic pumping oil pump 1a is exported by the 0-10v analog signals of proportioning valve 4a and controls to press trapezoidal wave in valve 4a control
Change), at this moment oil cylinder 2a triggers proximity switch j3, oil pump 1b place hydraulic pumping oil pump output unit and brings into operation (oil cylinder 2c
Commutation is completed) with oil cylinder 2d.
See when Fig. 3, oil pump 1a place hydraulic pumping oil pump output unit runs 1/2 cycle (i.e. stroke L), oil pump 1b place
Hydraulic pumping oil pump output unit runs 1/4 cycle (i.e. 1/2L stroke), the piston rod of oil cylinder 2c, 2d retract respectively backward and to
Before stretch out half stroke L, oil cylinder 2c, 2d speed of service by proportioning valve 4b control (output of the flow of hydraulic pumping oil pump 1b by than
The 0-10v analog signals output of example valve 4a controls to press trapezoidal wave change), at this moment oil cylinder 2a triggers proximity switch j2, oil cylinder 2a
Commutate with oil cylinder 2b.
See when Fig. 4, oil pump 1a place hydraulic pumping oil pump output unit runs 3/4 cycle (i.e. 1/2L stroke), oil cylinder 2a
Trigger oil cylinder 2c and the oil cylinder 2d commutation of proximity switch j3, oil pump 1b place hydraulic pumping oil pump output unit.
Seeing that Fig. 5, oil pump 1a place hydraulic pumping oil pump output unit completes a cycle and returns to original state, oil cylinder 2a touches
Sending out proximity switch j1, oil cylinder 2a and oil cylinder 2b commutation, oil pump 1b place hydraulic pumping oil pump output unit then completed for 3/4 cycle.
After walking to half stroke again, so far four oil cylinder 2a 2d are fully completed a cycle variable speed reciprocating motion.
Fig. 6 is the oil pump 1a output periodic stream spirogram to oil cylinder 2a, 2b, and figure is trapezoidal wave, and vertical coordinate is output flow
Q, abscissa is t cycle time, if being 2 seconds 1 cycle time, upper horizontal line is oil pump maximum output stream value.Process is；Start is logical
During electricity, oil cylinder 2a stop through 0.15 second (half buffer time), and beginning is risen to maximum stream flow by 0 speed change, kept 0.3 second
By maximum stream flow speed change to 0 after big flow, stopping through 0.3 second (buffer time), oil cylinder 2b starts to be risen to by 0 speed change
Maximum stream flow, after keeping 0.3 second maximum stream flow, speed change is to 0, completes for 1 cycle output (cycle time is 2 seconds) after 0.15 second.
The uneven degree (pulse) that now flow of oil cylinder 2a, 2b is exported by oil pump is the biggest.
Fig. 7 is the oil pump 1b output periodic stream spirogram to oil cylinder 2c, 2d, and figure is trapezoidal wave.Owing to oil cylinder 2c, 2d are relative
In half stroke of oil cylinder 2a, 2b time difference, namely 1/4 cycle, output procedure is all the output of identical speed change.Now oil pump 1b is to oil
The uneven degree (pulse) of the flow output of cylinder 2a, 2b is ibid.
Fig. 8 is the trapezoidal wave flow summation figure in oil cylinder 2a 2d 1 cycle of output；As seen from the figure at two hydraulic pumping oil
After four oil cylinder 2a 2d flow summation of pump output unit output, in any time of system output, each group output unit is defeated
The additive value of outflow, is equal to the maximum output stream value of single oil cylinder.Owing to uneven degree (pulse) size of output is equal to
Maximum instantaneous flow deducts minimum instantaneous delivery divided by instantaneous average discharge, maximum instantaneous flow shown in overlaying flow figure
Equal to instantaneous minimum discharge, therefore the output form of present system is equal or approximate no pulse output.
Claims (2)
1. a no pulse hydraulic pressure 4 cylinder direct driving type slush pump system, is characterized in that the hydraulic pumping oil pump including two groups of independences is defeated
Going out unit, described often group hydraulic pumping oil pump output unit is included a hydraulic pumping oil pump, is connected with described oil pump by oil circuit
The mud output assembly that the oil cylinder of two series connection connect is connected with described oil cylinder, the proportioning valve controlling described oil circuit and reversal valve；
For 180 degree of angles of each cycle between two oil cylinders in described hydraulic pumping oil pump output unit, described two groups of hydraulic pumpings oil
Form 90 degree of angles of each cycle between the oil cylinder of pump output unit, make described hydraulic pumping oil pump inject oil by described proportioning valve
The flow of cylinder realizes alternation output according to trapezoidal wave change.
No pulse hydraulic pressure 4 cylinder direct driving type slush pump system the most according to claim 1, it is characterized in that described proportioning valve by
PLC controls the analog signals of part input 0-10v and is controlled.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610830831.0A CN106246493A (en) | 2016-09-19 | 2016-09-19 | A kind of no pulse hydraulic pressure 4 cylinder direct driving type slush pump system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610830831.0A CN106246493A (en) | 2016-09-19 | 2016-09-19 | A kind of no pulse hydraulic pressure 4 cylinder direct driving type slush pump system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106246493A true CN106246493A (en) | 2016-12-21 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610830831.0A Pending CN106246493A (en) | 2016-09-19 | 2016-09-19 | A kind of no pulse hydraulic pressure 4 cylinder direct driving type slush pump system |
Country Status (1)
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| CN (1) | CN106246493A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106870316A (en) * | 2017-04-18 | 2017-06-20 | 黄山市汇润机械有限公司 | A kind of hydraulic double-acting compression pump sledge |
| CN108799100A (en) * | 2018-06-19 | 2018-11-13 | 姚长水 | The design method and device of elimination hydraulic pulsation can be achieved |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030170127A1 (en) * | 2000-07-24 | 2003-09-11 | Werner Muenzenmaier | Thick matter pump |
| CN101328874A (en) * | 2008-07-28 | 2008-12-24 | 李星宇 | Hydraulic slurry pump |
| CN201730780U (en) * | 2010-06-18 | 2011-02-02 | 宝鸡石油机械有限责任公司 | Hydraulically driven difunctional multi-cylinder slurry pump |
| CN205370884U (en) * | 2016-01-14 | 2016-07-06 | 四川劳玛斯特高胜石油钻采设备有限公司 | Many hydraulic cylinders of plunger type combination slush pump |
| CN206054208U (en) * | 2016-09-19 | 2017-03-29 | 李星宇 | A kind of 4 cylinder direct driving type slush pump system of no pulse hydraulic pressure |
-
2016
- 2016-09-19 CN CN201610830831.0A patent/CN106246493A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030170127A1 (en) * | 2000-07-24 | 2003-09-11 | Werner Muenzenmaier | Thick matter pump |
| CN101328874A (en) * | 2008-07-28 | 2008-12-24 | 李星宇 | Hydraulic slurry pump |
| CN201730780U (en) * | 2010-06-18 | 2011-02-02 | 宝鸡石油机械有限责任公司 | Hydraulically driven difunctional multi-cylinder slurry pump |
| CN205370884U (en) * | 2016-01-14 | 2016-07-06 | 四川劳玛斯特高胜石油钻采设备有限公司 | Many hydraulic cylinders of plunger type combination slush pump |
| CN206054208U (en) * | 2016-09-19 | 2017-03-29 | 李星宇 | A kind of 4 cylinder direct driving type slush pump system of no pulse hydraulic pressure |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106870316A (en) * | 2017-04-18 | 2017-06-20 | 黄山市汇润机械有限公司 | A kind of hydraulic double-acting compression pump sledge |
| CN106870316B (en) * | 2017-04-18 | 2019-06-11 | 黄山市汇润机械有限公司 | A kind of hydraulic double-acting fracturing pump sledge |
| CN108799100A (en) * | 2018-06-19 | 2018-11-13 | 姚长水 | The design method and device of elimination hydraulic pulsation can be achieved |
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Application publication date: 20161221 |
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