CN109488257B - Pressure complementary hydraulic pumping unit - Google Patents
Pressure complementary hydraulic pumping unit Download PDFInfo
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- CN109488257B CN109488257B CN201811598504.2A CN201811598504A CN109488257B CN 109488257 B CN109488257 B CN 109488257B CN 201811598504 A CN201811598504 A CN 201811598504A CN 109488257 B CN109488257 B CN 109488257B
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- 238000005086 pumping Methods 0.000 title claims abstract description 49
- 230000000295 complement effect Effects 0.000 title abstract description 10
- 239000003921 oil Substances 0.000 claims abstract description 78
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 47
- 239000007788 liquid Substances 0.000 claims description 17
- 230000009471 action Effects 0.000 claims description 13
- 230000033001 locomotion Effects 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 4
- 230000002457 bidirectional effect Effects 0.000 abstract description 38
- 230000000694 effects Effects 0.000 abstract description 7
- 230000001174 ascending effect Effects 0.000 abstract description 5
- 238000005381 potential energy Methods 0.000 abstract description 3
- 238000010586 diagram Methods 0.000 description 6
- 230000005484 gravity Effects 0.000 description 6
- 238000012423 maintenance Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 238000000605 extraction Methods 0.000 description 2
- 239000000047 product Substances 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000001502 supplementing effect Effects 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000003245 working effect Effects 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Classifications
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
- E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20561—Type of pump reversible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
- F15B2211/20592—Combinations of pumps for supplying high and low pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/765—Control of position or angle of the output member
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Geology (AREA)
- Life Sciences & Earth Sciences (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Environmental & Geological Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A hydraulic pumping unit with complementary pressure is a hydraulic cylinder arranged in pairs, and the two hydraulic cylinders alternately move up and down to drive a downhole pump to work so as to achieve the purpose of pumping oil. When one hydraulic cylinder rod ascends to pump oil, the bidirectional hydraulic pump is required to be filled with oil to provide ascending energy. At this time, the other hydraulic cylinder is in a descending stage, the gravitational potential energy of parts below the lifting rope is released, and part of the energy is supplied to the ascending hydraulic cylinder through hydraulic oil to the double hydraulic pump, so that the power of the driving motor is reduced, and the energy-saving effect is achieved. Continuous forward and reverse operation of the bi-directional hydraulic pump will cause one cylinder rod to rise and the other cylinder rod to fall. The invention can continuously complete the oil pumping work. Under the condition of adding the flow divider, a plurality of pairs of hydraulic cylinders can be configured, so that the requirement of locally using a plurality of pumping units is met.
Description
Technical Field
The invention belongs to the technical field of oil pumping units for oil fields, and particularly relates to a hydraulic oil pumping unit with complementary pressure.
Technical Field
Beam-pumping units for oil fields are most typically used. The device has reliable performance, simple structure, simple operation and maintenance and mature technology. It is mainly characterized in that: the whole machine has reasonable structure, stable work, low noise and convenient operation and maintenance; the strength is high, the rigidity is good, the bearing capacity is high, and the service life is long; the brake adopts an external holding type structure and is provided with a safety device, so that the operation is flexible, the braking is rapid, and the safety and the reliability are high. His drawbacks are: the unbalance caused by the structure causes large fluctuation of output torque and large motor loss.
As shown in fig. 6, the conventional beam pumping unit operates on the principle that a link mechanism mainly composed of a crank, a gearbox, a link and a beam is driven by a motor through the gearbox to move a horsehead up and down. The actuating component of the underground pump is driven to move up and down by the driving of the lifting rope, the rope hanger and the polish rod, so that underground liquid is pumped out of the ground. Wherein the balance weight plays a role in boosting when the horsehead rises, and is used for storing energy when the horsehead descends.
In fig. 6, 201 is a base, 202 is a gearbox, 203 is a motor, 204 is a brake, 205 is a belt pulley, 206 is a crank, 207 is a counterweight, 208 is a connecting rod, 209 is a walking beam, 210 is a horsehead, 211 is a lifting rope, 212 is a rope hanger, 213 is a bracket, 214 is an oil pipe, 215 is a polished rod, and 216 is a downhole pump.
The front beam pumping unit is one kind of modified beam pumping unit. The rotation angle of the crank is designed to be about 195 ° when the horsehead is rushed up, and about 165 ° when the horsehead is lowered. The time of the horsehead in the ascending process is prolonged, so that the power of the motor can be reduced. Playing the role of energy saving.
The tower-type pumping unit is a beam-less pumping unit, and is characterized by that the beam and horsehead of conventional beam-type pumping unit are changed into an assembled concentric composite wheel, and its support frame has a long high stroke. The working principle of the device is as follows: the motor supplies power, and the rope hanger drives the underground pump to reciprocate up and down through the speed reducer, the crank, the connecting rod, the lifting rope and the compound transmission, so that underground liquid is pumped out of the ground. Its advantages are long stroke, high liquid-extracting power, stable running and reliability. The device has the defects of complex structure, large weight and height of the whole machine, more laborious installation, parameter adjustment and maintenance, easy damage of the lifting rope caused by heavy-load extrusion and more difficult replacement.
One of the non-beam pumping units is a proprietary product introduced from the united states. The load belt has the vibration absorption characteristic, impact is relieved, the reversing time is prolonged by the large chain wheel, reversing impact is reduced, and the transmission reliability is improved by the chain. The advantages of long stroke, energy saving, low stroke frequency, simple operation, high reliability and the like are realized. The method has the defects that the requirements on the wellhead height and wellhead type are high, and the stroke cannot be adjusted.
Disclosure of Invention
The invention aims to design a hydraulic system to control two hydraulic cylinders to alternately make the action of an oil pumping unit which reciprocates up and down. When the cylinder rod of one hydraulic cylinder moves downwards, namely, during the downstroke of the pumping unit, the cylinder rod of the other hydraulic cylinder moves upwards, namely, during the upstroke of the pumping unit. When the rod of one hydraulic cylinder moves downwards, the potential energy of the part below the lifting rope is released under the action of gravity, and at the moment, the rod of the other hydraulic cylinder moves upwards, so that the energy is required to rise. Part of energy released by the hydraulic cylinder with the descending cylinder rod is transmitted to the hydraulic cylinder with the ascending cylinder rod through the hydraulic oil through the two-way hydraulic pump, so that the energy required by the ascending cylinder rod is reduced, and the energy-saving effect is achieved. When the direction of movement of the two hydraulic cylinders is changed, the hydraulic energy between them is to some extent complementary. Because the pumping units are usually operated simultaneously by a plurality of adjacent pumping units in the oil extraction area, the scheme of the pumping units used as pairs is not problematic. When the oil extraction area needs a plurality of pairs of oil pumping units to work, the invention can realize the up-and-down movement of the hydraulic cylinders of the plurality of pairs in a pairwise alternating way by arranging the flow divider, thereby realizing the simultaneous work of a plurality of oil pumping units in a smaller area.
The use of hydraulic oil as energy transfer is not limited by structure and distance, and is far superior to pure mechanical energy transfer.
For a hydraulic pump, the calculation formula of the relation between the input power and the torque is as follows:
M=V•ΔP/6.28ηm
wherein M- -input torque N.M, V- -displacement L/min, ΔP- -inlet-outlet pressure difference bar, etam- -total efficiency of the hydraulic pump.
From the formula it can be seen that: under the condition that other values are constant, the smaller the pressure difference between the inlet and the outlet of the hydraulic pump is, the smaller the torque required to be input is, and the pressure for discharging the oil is definitely larger than the pressure of the oil provided in the oil tank when the cylinder rod of the hydraulic cylinder descends. Therefore, when the hydraulic pump sucks the oil discharged when the cylinder rod of one cylinder is lowered to charge the hydraulic oil when the cylinder rod of the other cylinder is raised, the required torque is smaller. And the hydraulic oil is injected when the cylinder rod of the other hydraulic cylinder is lifted by sucking oil from the oil tank, so that the required torque is larger. If the hydraulic pump is a bidirectional hydraulic pump, the flow direction of the hydraulic oil is changed according to the requirement, the cylinder rods of the two hydraulic cylinders alternately move up and down to complete the same pumping action, the torque required by the bidirectional hydraulic pump is reduced, and the power required by the motor is smaller.
Adopts the technical proposal that
An electrical control system is designed for providing power and control for the main hydraulic drive system and the auxiliary hydraulic drive system, receiving feedback signals, and adjusting the power provided for the main hydraulic drive system and the auxiliary hydraulic drive system according to the feedback signals, wherein the electrical control system comprises the starting, stopping, forward running, reverse running, overload protection, corresponding monitoring and control of the main hydraulic drive system and the auxiliary hydraulic drive system, and the like, so that the movement speed and the reciprocating stroke adjustment of the hydraulic cylinder are realized. In the main hydraulic driving system and the auxiliary hydraulic driving system, the motor drives the bidirectional hydraulic pump to pump out the liquid in one hydraulic cylinder and inject the liquid into the other hydraulic cylinder to repeatedly work so as to realize the alternate pumping action of lifting the cylinder rod of the one hydraulic cylinder and lowering the cylinder rod of the other hydraulic cylinder.
The main hydraulic driving system is designed and mainly consists of an electric motor and a bidirectional hydraulic pump, and is mainly used for injecting or extracting oil from two hydraulic cylinders. Due to leakage of the piping, etc., there is a case where the oil amount on the high pressure side of the main hydraulic drive system is insufficient.
In order to allow the movement of the two cylinder rods to reach the set position at the same time, the auxiliary hydraulic drive system is arranged to suck a part of hydraulic oil from the oil tank to supplement the high-pressure side.
In order to obtain effective control of the movements of the two hydraulic cylinders, sensors are respectively arranged on the two hydraulic cylinders to monitor the movements of the hydraulic cylinders. The sensor feeds back the needed information to the electric control system, the electric control system judges and sends out corresponding instructions through a preset program, the running states of motors in the main hydraulic drive system and the auxiliary hydraulic drive system are adjusted, and hydraulic oil is injected or extracted into the hydraulic cylinder through the bidirectional hydraulic pump.
The two-way hydraulic pump in the main hydraulic driving system can be used as a hydraulic motor, the rotating shaft of the motor extends out of two ends of the motor, each side of the motor shaft is connected with the two-way hydraulic pump, each two-way hydraulic pump independently injects and discharges hydraulic oil to the corresponding hydraulic cylinder, and the oil tank is used as an oil source. When one bidirectional hydraulic pump injects hydraulic oil into one hydraulic cylinder, the other hydraulic cylinder flows back to the oil tank through the other bidirectional hydraulic pump under the action of the carried gravity load, and the other bidirectional hydraulic pump rotates with the identity of the hydraulic motor under the action of the oil flowing back to the oil tank to help the motor rotate, so that the motor drives the bidirectional hydraulic pump, and when the hydraulic cylinder is filled with oil, the rising torque of the cylinder rod of the hydraulic cylinder is reduced, and the energy-saving effect is achieved. The same is true of the other.
In oil field pumping operations, there may be more than two pumping units in a small area. According to this situation, a flow divider is connected to both ports of the main hydraulic drive system. The number of the shunt outlets connected with the shunt is set according to the number of the pumping units required, the oil way driving interfaces of the paired hydraulic cylinders are respectively correspondingly connected with the shunt outlets of the shunt, and meanwhile auxiliary hydraulic driving systems are configured in pairs, so that the working effect of the pumping units is achieved. The diverter is a pipeline component which is provided with a plurality of branch outlets, and each branch outlet is provided with a valve which can proportionally divert the liquid in the main pipeline to each branch outlet.
The diverter, hydraulic cylinder, motor, bi-directional hydraulic pump and sensor are commercially available products.
Drawings
FIG. 1 is a block diagram of a pressure-compensated hydraulic pumping unit system;
FIG. 2 is a system block diagram of a pressure-compensated hydraulic pumping unit derivative scheme;
FIG. 3 is a schematic diagram of the operation of a hydraulic pumping unit with complementary pressure;
FIG. 4 is a second working schematic diagram of a hydraulic pumping unit with complementary pressure;
FIG. 5 is a third schematic diagram of the operation of a hydraulic pumping unit with complementary pressure;
fig. 6 is an assembled schematic view of a conventional beam pumping unit.
Detailed Description
Example 1
A pressure-compensated hydraulic pumping unit comprising: a main hydraulic drive system 1, an auxiliary hydraulic drive system 2, an oil tank 3, a first hydraulic cylinder 4, a first sensor 5, a second hydraulic cylinder 6, a second sensor 7 and an electrical control system 8. The method is characterized in that:
as shown in fig. 1, the pipeline port A1 of the main hydraulic drive system 1 is connected with the pipeline port A2 of the first hydraulic cylinder 4 in a pipeline manner, and when the pipeline port A1 of the main hydraulic drive system 1 injects high-pressure liquid into the oil path port A2 of the first hydraulic cylinder 4, the cylinder rod of the first hydraulic cylinder 4 rises.
The pipeline connector A1 of the first hydraulic oil cylinder 4 is connected with the pipeline connector A1 of the oil tank 3 through a pipeline. This connection has essentially no functional effect as an up-and-down movement of the upper part of the cylinder piston to suck or discharge oil from the tank 3. Because the lower part of the cylinder rod is connected with the weight of the part when the cylinder rod descends, the weight is enough to cause the cylinder rod to descend.
The trigger switching side A1 of the first sensor 5 is connected to the set position A3 on the first hydraulic cylinder 4, and the signal output terminal A2 of the first sensor 5 is connected to the signal receiving terminal a12 of the electrical control system 8.
The pipeline interface A2 of the main hydraulic drive system 1 is connected with the pipeline interface A2 of the second hydraulic cylinder 6 in a pipeline manner, and when the pipeline interface A2 of the main hydraulic drive system 1 injects high-pressure liquid into the oil way interface A2 of the second hydraulic cylinder 6, the cylinder rod of the second hydraulic cylinder 6 rises.
The pipeline interface A1 of the second hydraulic oil cylinder 6 is connected with the pipeline interface A2 of the oil tank 3 through a pipeline.
The trigger switching side A1 of the second sensor 7 is connected to the set position A3 on the second hydraulic cylinder 6, and the signal output terminal A2 of the second sensor 7 is connected to the signal receiving terminal a13 of the electrical control system 8.
The power, control and signal connection A4 of the main hydraulic drive system 1 is connected with the power, control and signal connection A1 of the electric control system 8.
The oil way interface A1 of the auxiliary hydraulic driving system 2 is connected with the pipeline interface A2 of the first hydraulic oil cylinder 4 in a pipeline way, and the oil way interface A2 of the auxiliary hydraulic driving system 2 is connected with the oil way interface A8 of the oil tank 3 in a pipeline way. The oil way interface A3 of the auxiliary hydraulic driving system 2 is connected with the pipeline interface A2 of the second hydraulic oil cylinder 6 in a pipeline way, and the power and control terminal A4 of the auxiliary hydraulic driving system 2 is connected with the power and control terminal A11 of the electric control system 8 in a pipeline way.
The pipeline interface A1 and the pipeline interface A2 of the main hydraulic driving system 1 are pipeline interfaces for liquid to enter and exit. When the main hydraulic drive system 1 works, the auxiliary hydraulic drive system 2 is supplemented when one side of the pipeline interface A1 and the pipeline interface A2 lacks liquid.
As shown in fig. 3, an electrical control system provides power supply, start-stop, measurement, forward rotation, reverse rotation, rotation speed control and power adjustment functions for a motor a, and the motor a drives a bidirectional hydraulic pump to forward rotate or reverse rotate. When the bidirectional hydraulic pump conveys hydraulic oil from the hydraulic oil cylinder A to the hydraulic oil cylinder B, the pressure of the oil pushes the piston of the hydraulic oil cylinder B to move upwards, and the cylinder rod of the hydraulic oil cylinder B is driven to move upwards. At this time, the hydraulic cylinder B acts to perform pumping of the downhole pump, and the hydraulic oil in the hydraulic cylinder a is decreasing, and the cylinder rod in the hydraulic cylinder a is descending. Referring to fig. 6, the descending power of the cylinder rod in the hydraulic cylinder a has the effect of the gravity of the rope hanger, the polish rod, and the like. That is, the oil in the hydraulic cylinder a is reduced, and the action of gravity of the rope hanger, the polish rod, and the like is also taken into account in addition to the action of the bidirectional hydraulic pump. When the cylinder rod of the hydraulic cylinder A moves downwards, oil at the lower part of the piston of the hydraulic cylinder A is pressurized under the action of gravity of the rope hanger, the polish rod and the like, and the pressure is definitely larger than the pressure of the oil in the oil tank. According to the aforementioned formula m=v·Δp/6.28 etam, if the difference between the pressure of the oil in the lower part of the piston of the hydraulic cylinder a and the pressure of the oil in the lower part of the piston of the hydraulic cylinder B is reduced, and the torque M required for the bidirectional hydraulic pump is reduced with V and etam unchanged, the output force of the motor is reduced. In this way, the potential energy of the part of the hydraulic cylinder A, which is lowered by the lower part of the cylinder rod, is converted into the upward driving of the cylinder rod of the hydraulic cylinder B, and the energy-saving effect is achieved. When the oil delivery direction of the bidirectional hydraulic pump is changed, the working effect is the same.
And the motor B receives power electricity and control of the electric control system and drives the bidirectional hydraulic regulating pump to operate. Because of the reasons such as pipeline leakage, the phenomenon of insufficient oil quantity at the high-pressure oil side exists, the bidirectional hydraulic regulating pump plays a role in supplementing oil quantity, and the supplemented hydraulic oil is drawn from the oil tank. In this way, the movement of the cylinder rod in the hydraulic cylinder a and the cylinder rod in the hydraulic cylinder B is facilitated to reach the desired set positions.
In order to enable the electric control system to effectively control the operation of the bidirectional hydraulic pump in real time, a sensor A and a sensor B are respectively arranged on a hydraulic cylinder A and a hydraulic cylinder B, and operation state signals of the hydraulic cylinder A and the hydraulic cylinder B are collected to provide an electric control system. The electrical control system provides the most suitable power output and control output according to a preset operation program.
In fig. 3, 001 is an electrical control system, 002 is an electric motor a,003 is a bidirectional hydraulic pump, 004 is an oil tank, 005 is a bidirectional hydraulic adjusting pump, 006 is a hydraulic cylinder a,007 is a sensor a,008 is a sensor B,009 is a hydraulic cylinder B, and 010 is an electric motor B.
Fig. 4 is a second working schematic diagram of a hydraulic pumping unit with complementary pressure, which is different from the scheme of fig. 3 in that the main shaft of the motor a extends out of two sides of the motor a, the shaft at one end is connected with the bidirectional hydraulic pump a, the shaft at the other end is connected with the bidirectional hydraulic pump B, the shaft of the motor, the bidirectional hydraulic pump a and the bidirectional hydraulic pump B rotate together, and the bidirectional hydraulic pump a and the bidirectional hydraulic pump B are also used as hydraulic motors.
When the bidirectional hydraulic pump B pumps oil from the oil tank to the hydraulic oil cylinder B, the cylinder rod of the hydraulic oil cylinder B is lifted, and meanwhile, the bidirectional hydraulic oil cylinder A sends hydraulic oil to the oil return tank through the bidirectional hydraulic pump A under the action of gravity. The bidirectional hydraulic pump a acts as a hydraulic motor, and transmits the output torque to the motor a, thereby assisting the rotation of the main shaft of the motor a. The motor a can be made to exert little force to maintain the normal driving of the bidirectional hydraulic pump B. The same is true of the other.
In fig. 4, 101 denotes an electric control system, 102 denotes a bidirectional hydraulic pump a,103 denotes a motor a,104 denotes a bidirectional hydraulic pump B,105 denotes an oil tank, 106 denotes a bidirectional hydraulic adjustment pump, 107 denotes a motor B,108 denotes a hydraulic cylinder a,109 denotes a sensor a,110 denotes a sensor B, and 111 denotes a hydraulic cylinder B.
Example 2
Example 2 of a hydraulic pumping unit of complementary pressure is substantially the same as example 1 except that:
as shown in fig. 2, a first flow divider 9 is added between the main hydraulic drive system (1) and the pipeline connection of the auxiliary hydraulic drive system (2) and the first hydraulic cylinder (4). The line connection a of the first flow divider 9 is connected to the line connection A1 of the main hydraulic drive system 1. The pipelines of the pipeline interfaces A2 of the first hydraulic cylinders 4 are correspondingly connected with the corresponding set split pipeline interfaces of the first splitter 9.
The trigger switching sides A1 of the first sensors 5 are respectively and correspondingly connected to the set positions A3 on the first hydraulic cylinders 4, and the signal output terminals A2 of the first sensors 5 are respectively and correspondingly connected to the corresponding signal receiving terminals of the electric control system 8.
The pipeline interfaces A1 of the first hydraulic cylinders 4 are respectively connected with corresponding pipeline interfaces of the oil tank 3 in a pipeline mode.
A second flow divider 10 is additionally arranged between the pipeline connection of the main hydraulic drive system (1) and the second hydraulic oil cylinder (6). The pipeline interface A of the second flow divider 10 is connected with the pipeline interface A2 of the main hydraulic drive system 1 in a pipeline way. The pipelines of the pipeline interfaces A2 of the plurality of second hydraulic cylinders 6 are correspondingly connected with the corresponding set split pipeline interfaces on the second splitter 10.
The trigger switching sides A1 of the plurality of second sensors 7 are respectively and correspondingly connected to the set positions A3 on the plurality of second hydraulic cylinders 6, and the signal output terminals A2 of the plurality of second sensors 7 are respectively and correspondingly connected to the corresponding signal receiving terminals of the electrical control system 8.
The pipeline interfaces A1 of the second hydraulic cylinders 6 are respectively corresponding to the pipeline interfaces corresponding to the pipeline connection oil tank 3.
The pipeline interfaces A1 of the auxiliary hydraulic drive systems 2 are correspondingly connected with the pipeline interfaces A2 of the first hydraulic cylinders 4 in pairs. The pipeline interfaces A3 of the auxiliary hydraulic drive systems 2 are correspondingly connected with the pipeline interfaces A2 of the second hydraulic cylinders 6 in pairs.
The pipeline interfaces A2 of the auxiliary hydraulic drive systems 2 are respectively connected with corresponding pipeline interfaces of the oil tank 3 in a pipeline mode. The power, control and signal connection terminals A4 of the plurality of auxiliary hydraulic drive systems 2 are respectively connected with corresponding power, control and signal connection terminals of the electric control system 8.
The liquid flow direction of the plurality of shunt line interfaces of the first shunt 9 is opposite to the liquid flow direction of the plurality of shunt line interfaces of the second shunt 10.
As shown in fig. 5, which is modified on the basis of fig. 3. The oil pumping device realizes the simultaneous alternate up-down reciprocating motion of a plurality of pairs of hydraulic cylinders, thereby realizing the oil pumping work of a plurality of pairs of oil pumping units in a local area.
The oil way interfaces at two ends of the bidirectional hydraulic pump are respectively connected with the flow divider A and the flow divider B, and the number of the flow dividing outlets of each flow divider is set according to the needs. The split outlet of the splitter A is correspondingly connected with the oil receiving ports at the lower parts of the pistons of the hydraulic cylinders A, and the split outlet of the splitter B is correspondingly connected with the oil receiving ports at the lower parts of the pistons of the hydraulic cylinders B. Thus, when the cylinder rods of the plurality of hydraulic cylinders a are raised, the cylinder rods of the plurality of hydraulic cylinders B are lowered. The plurality of motors B and the bidirectional hydraulic regulating pump are arranged between each pair of hydraulic cylinders A and B to play a role in supplementing oil. The set pairs of sensors A and B are correspondingly arranged at set positions on the hydraulic cylinders A and B, and the signal output ends of the sensors A and B are connected to corresponding interfaces of the electric control system to perform feedback control on the operation of the hydraulic cylinders A and B.
In fig. 5, 001 is an electrical control system, 002 is an electric motor a,003 is a bidirectional hydraulic pump, 004 is an oil tank, 005 is a bidirectional hydraulic adjusting pump, 006 is a hydraulic cylinder a,007 is a sensor a,008 is a sensor B,009 is a hydraulic cylinder B,010 is an electric motor B,011 is a shunt a, and 012 is a shunt B.
The main technical feature of the invention is that the two hydraulic cylinders are driven to alternately move up and down through the hydraulic functional loop, so as to generate the pumping action of the two pumping units. When the cylinder rod of one hydraulic cylinder descends, the pressure of the discharged hydraulic oil assists the hydraulic pump to enable the cylinder rod of the other hydraulic cylinder to move upwards. The torque required by the hydraulic pump to independently drive the cylinder rod of the hydraulic cylinder to move upwards is reduced, and the energy-saving effect is achieved. The shunt is additionally arranged, so that the oil pumping work of multiple pairs of oil pumping in the local area can be realized.
Claims (2)
1. A pressure-compensated hydraulic pumping unit comprising: the hydraulic control system comprises a main hydraulic drive system (1), an auxiliary hydraulic drive system (2), an oil tank (3), a first hydraulic oil cylinder (4), a first sensor (5), a second hydraulic oil cylinder (6), a second sensor (7) and an electrical control system (8); the method is characterized in that:
the pipeline interface A1 of the main hydraulic drive system (1) is connected with the pipeline interface A2 of the first hydraulic oil cylinder (4), and when the pipeline interface A1 of the main hydraulic drive system (1) injects high-pressure liquid into the pipeline interface A2 of the first hydraulic oil cylinder (4), a cylinder rod of the first hydraulic oil cylinder (4) rises;
the pipeline connector A1 of the first hydraulic oil cylinder (4) is connected with the pipeline connector A1 of the oil tank (3) through a pipeline;
the triggering switching side A1 of the first sensor (5) is connected to a set position A3 on the first hydraulic cylinder (4), and the signal output terminal A2 of the first sensor (5) is connected to the signal receiving terminal A12 of the electrical control system (8);
the pipeline interface A2 of the main hydraulic drive system (1) is connected with the pipeline interface A2 of the second hydraulic oil cylinder (6), and when the pipeline interface A2 of the main hydraulic drive system (1) injects high-pressure liquid into the pipeline interface A2 of the second hydraulic oil cylinder (6), the cylinder rod of the second hydraulic oil cylinder (6) rises;
the pipeline interface A1 of the second hydraulic oil cylinder (6) is connected with the pipeline interface A2 of the oil tank (3) through a pipeline;
the triggering switching side A1 of the second sensor (7) is connected to a set position A3 on the second hydraulic cylinder (6), and the signal output terminal A2 of the second sensor (7) is connected to the signal receiving terminal A13 of the electrical control system (8);
the power, control and signal connection end A4 of the main hydraulic driving system (1) is connected with the power, control and signal connection end A1 of the electric control system (8);
the pipeline interface A1 of the auxiliary hydraulic driving system (2) is connected with the pipeline interface A2 of the first hydraulic oil cylinder (4) through a pipeline, and the pipeline interface A2 of the auxiliary hydraulic driving system (2) is connected with the pipeline interface A8 of the oil tank (3) through a pipeline; the pipeline interface A3 of the auxiliary hydraulic driving system (2) is connected with the pipeline interface A2 of the second hydraulic oil cylinder (6) in a pipeline way, and the power, control and signal terminal A4 of the auxiliary hydraulic driving system (2) is connected with the power, control and signal terminal A11 of the electric control system (8) in a pipeline way;
the pipeline interface A1 and the pipeline interface A2 of the main hydraulic driving system (1) are pipeline interfaces for liquid to enter and exit each other; when the main hydraulic driving system (1) works and one side of the pipeline interface A1 and the pipeline interface A2 lacks liquid, the auxiliary hydraulic driving system (2) is supplemented;
a first shunt (9) is additionally arranged between the main hydraulic driving system (1) and the pipeline connection of the auxiliary hydraulic driving system (2) and the first hydraulic oil cylinder (4); the pipeline main connector A of the first flow divider (9) is connected with the pipeline connector A1 of the main hydraulic driving system (1) in a pipeline way, and the flow dividing connector A1 of the first flow divider (9) is connected with the pipeline connector A1 of the auxiliary hydraulic driving system (2) and the pipeline connector A2 of the first hydraulic oil cylinder (4) in a pipeline way;
a second shunt (10) is additionally arranged between the pipeline connection of the main hydraulic driving system (1) and the second hydraulic oil cylinder (6); the pipeline main port A pipeline connection pipeline of the second current divider (10) is connected with the pipeline port A2 of the main hydraulic drive system (1), and the current dividing port A1 pipeline connection pipeline of the second current divider (10) is connected with the pipeline port A2 of the second hydraulic cylinder (6);
the pipeline of the pipeline interface A2 of the plurality of first hydraulic cylinders (4) is correspondingly connected with a plurality of corresponding set split pipeline interfaces of the first splitter (9);
the triggering switching sides A1 of the first sensors (5) are respectively and correspondingly connected to the set positions A3 on the first hydraulic cylinders (4), and the signal output terminals A2 of the first sensors (5) are respectively and correspondingly connected to the corresponding signal receiving terminals of the electric control system (8);
pipeline interfaces A1 of the plurality of first hydraulic cylinders (4) are respectively connected with corresponding pipeline interfaces of the oil tank (3) in a pipeline way;
the pipeline of the pipeline interface A2 of the plurality of second hydraulic cylinders (6) is correspondingly connected with a plurality of corresponding set shunt pipeline interfaces on the second shunt (10);
the triggering switching sides A1 of the second sensors (7) are respectively and correspondingly connected to the set positions A3 on the second hydraulic cylinders (6), and the signal output terminals A2 of the second sensors (7) are respectively and correspondingly connected to the corresponding signal receiving terminals of the electric control system (8);
pipeline interfaces A1 of the plurality of second hydraulic cylinders (6) are respectively connected with corresponding pipeline interfaces on the oil tank (3) correspondingly;
the pipeline interfaces A1 of the auxiliary hydraulic driving systems (2) are correspondingly connected with the pipeline interfaces A2 of the first hydraulic cylinders (4) in pairs; the pipeline interfaces A3 of the auxiliary hydraulic driving systems (2) are correspondingly connected with the pipeline interfaces A2 of the second hydraulic cylinders (6) in pairs;
pipeline interfaces A2 of the auxiliary hydraulic driving systems (2) are respectively connected with corresponding pipeline interfaces of the oil tank (3) in a pipeline way; the power, control and signal connection ends A4 of the auxiliary hydraulic driving systems (2) are respectively connected with corresponding power, control and signal connection ends of the electric control system (8);
the liquid flow directions of the plurality of diversion pipeline interfaces of the first diverter (9) are opposite to and correspondingly equal to the liquid flow directions of the plurality of diversion pipeline interfaces of the second diverter (10).
2. The pressure compensating hydraulic pumping unit of claim 1 wherein: the first sensor (5) and the second sensor (7) respectively collect action signals of the first hydraulic oil cylinder (4) and the second hydraulic oil cylinder (6) and feed the action signals back to the electric control system (8), so that the electric control system (8) controls the main hydraulic driving system (1) and the auxiliary hydraulic driving system (2) to adjust the reciprocating motion state of the dry rods of the first hydraulic oil cylinder (4) and the second hydraulic oil cylinder (6).
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| CN201811598504.2A CN109488257B (en) | 2018-12-26 | 2018-12-26 | Pressure complementary hydraulic pumping unit |
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| CN201811598504.2A CN109488257B (en) | 2018-12-26 | 2018-12-26 | Pressure complementary hydraulic pumping unit |
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| CN109488257B true CN109488257B (en) | 2024-01-05 |
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