CN112032138A

CN112032138A - Hydraulic injection pump reversing method and system

Info

Publication number: CN112032138A
Application number: CN202010900180.4A
Authority: CN
Inventors: 王宗雷; 李曼曼; 程贵华; 王继平; 张浩谦; 杨成永; 张桂昌; 王佳琦; 宫兆玲; 薛帅; 石宛铭
Original assignee: Dezhou United Petroleum Technology Corp
Current assignee: Dezhou United Petroleum Technology Corp
Priority date: 2020-07-30
Filing date: 2020-08-31
Publication date: 2020-12-04
Anticipated expiration: 2040-08-31
Also published as: CN213016526U; CN213331733U; CN112032138B; CN213116645U; CN213116284U; CN213478820U; CN112032011A; CN213298473U; CN112032147A; CN112032139B; CN213331049U; CN213017023U; CN213298193U; CN112032139A; CN112032147B; CN213331052U; CN112032011B; CN213017024U

Abstract

A reversing method and a system for a hydraulic injection pump relate to the technical field of petroleum equipment, and the reversing method mainly comprises the following steps: detecting and comparing the reversing time lengths of the hydraulic cylinders, and taking one of the hydraulic cylinders as a reference hydraulic cylinder to enable the difference value between the reversing time lengths of the other hydraulic cylinders and the reversing time length of the reference hydraulic cylinder to be smaller than a first threshold value; detecting and comparing the reversing time points of all the hydraulic cylinders, wherein the difference value of the time intervals of the reversing time points of the other hydraulic cylinders on the same side as the reference hydraulic cylinder is smaller than a second threshold value; the controller is used for receiving and comparing the reversing time length and the reversing time point of each hydraulic cylinder, and adjusting the flow rate of the hydraulic oil conveyed to the corresponding working unit by the oil supply unit through the frequency converter, so that the difference value between the reversing time length of the rest of the hydraulic cylinders and the reference hydraulic cylinder is smaller than a first threshold value, and the difference value between the time intervals of the reversing time points on the same side of the rest of the hydraulic cylinders and the reference hydraulic cylinder is smaller than a second threshold value.

Description

Hydraulic injection pump reversing method and system

Technical Field

The invention relates to the technical field of petroleum equipment, in particular to a reversing method and a reversing system for a hydraulic injection pump.

Background

In the crankshaft type plunger pump in the prior art, the stroke is short, the reversing times are many, the plunger is frequently moved, and the service life of a wearing part is short, for example, the service life of a valve seat, a valve rubber sheet and the like at a hydraulic end is only dozens of hours; in addition, the coverage range of the output pressure and the flow of the crankshaft type plunger pump is narrow, and if the coverage range is required to be improved, the hydraulic ends with different cylinder diameters are required to be replaced; in addition, when the plunger is frequently and quickly reversed, fracturing fluid is discharged without being fully sucked, so that the suction efficiency is not high, and the working efficiency is low; in addition, a crankshaft, a power input gear, a connecting rod, a box body of a hydraulic end, a seat body and the like are integrally installed in the fracturing pump, so that the fracturing pump is complex in structure, high in manufacturing cost and inconvenient to assemble, disassemble and maintain; in addition, the power input gear rotates at high speed and heavy load, the requirements on lubrication and cooling are high, and a lubrication system with a complex arrangement structure and a corresponding cooling system are required.

The hydraulic injection pump has the advantages of long stroke, less reversing times, long service life of easily damaged parts and the like. However, the conventional hydraulic injection equipment has small discharge capacity and is difficult to meet the use requirements of injection operations such as profile control, pressure flooding, fracturing and the like of an oil field. If a plurality of working units are arranged in the hydraulic injection pump, the integral displacement of the equipment can be improved, but the technical problem which besets the technical difficulty of the technical personnel is how to enable the working units to work in coordination.

Disclosure of Invention

In the embodiment, the reversing duration and the reversing time point of each hydraulic cylinder are detected by the detection unit, the reversing duration of each hydraulic cylinder is controlled to be approximately the same by dynamically controlling the output frequency of the frequency converter, the regularity of the reversing time points is improved, and a plurality of working units can work in a coordinated manner.

In order to achieve the above technical object, an aspect of the embodiments of the present invention provides a hydraulic injection pump reversing method, for a hydraulic injection pump, where the hydraulic injection pump includes a plurality of working units, each of the working units includes a hydraulic cylinder, and a hydraulic piston rod is disposed in the hydraulic cylinder, the reversing method mainly includes the following steps: detecting and comparing the reversing time lengths of the hydraulic cylinders, and taking one of the hydraulic cylinders as a reference hydraulic cylinder to enable the difference value between the reversing time lengths of the other hydraulic cylinders and the reversing time length of the reference hydraulic cylinder to be smaller than a first threshold value; and detecting and comparing the reversing time points of the hydraulic cylinders, so that the difference value of the time intervals of the reversing time points of the other hydraulic cylinders on the same side with the reference hydraulic cylinder is smaller than a second threshold value.

Another aspect of an embodiment of the present invention provides a hydraulic injection pump reversing system, where the hydraulic injection pump includes a plurality of oil supply units and a plurality of working units, and the oil supply units are connected to the working units in a one-to-one correspondence; each working unit comprises a hydraulic cylinder, and a hydraulic piston rod is arranged in each hydraulic cylinder; the reversing system comprises a controller, a plurality of frequency converters and a plurality of detection units, wherein the controller is respectively connected with the frequency converters, the controller is respectively connected with the plurality of detection units, the frequency converters are correspondingly connected with the oil supply units one by one, the detection units are connected with the working units in a one-to-one correspondence manner and are used for detecting the reversing duration and the reversing time point of the hydraulic cylinder, the controller is used for receiving and comparing the reversing duration and the reversing time point of each hydraulic cylinder, and the flow rate of the hydraulic oil conveyed to the corresponding working unit by the oil supply unit is adjusted by a frequency converter, taking one of the hydraulic cylinders as a reference hydraulic cylinder, enabling the difference value between the reversing duration of the other hydraulic cylinders and the reference hydraulic cylinder to be smaller than a first threshold value, and making the difference value of the time intervals of the reversing time points of the other hydraulic cylinders on the same side with the reference hydraulic cylinder smaller than a second threshold value.

One or more technical solutions provided in the embodiments of the present invention have at least the following technical effects or advantages: in the embodiment of the invention, the reversing time and the reversing time point of each hydraulic cylinder are detected by the detection unit, the output frequency of the frequency converter is dynamically controlled, the reversing time of each hydraulic cylinder is controlled to be approximately the same, and the regularity of the reversing time points is improved, namely the reversing time points are staggered and have similar time intervals in sequence.

Drawings

FIG. 1 is a top view of an embodiment of a hydraulic infusion pump.

FIG. 2 is a hydraulic schematic of a hydraulic injection pump of an embodiment.

FIG. 3 is a front view of a hydraulic pump station pry according to one embodiment.

FIG. 4 is a top view of an embodiment of a hydraulic pump station pry.

Fig. 5 is a schematic structural diagram of a hydraulic oil tank according to an embodiment.

Fig. 6 is a top view of fig. 5.

Fig. 7 is a view taken along direction a in fig. 6.

Fig. 8 is a schematic structural diagram of the box body according to an embodiment of the invention.

Fig. 9 is a view taken along direction B in fig. 8.

Fig. 10 is a front view of an embodiment of a hydraulic charge pump hydraulic sled.

Fig. 11 is a top view of an embodiment hydraulic charge pump hydraulic sled.

Fig. 12 is a left side view of fig. 10.

Fig. 13 is a schematic structural view of the rack.

Fig. 14 is a schematic structural diagram of a first pipeline in a slurry suction pipeline system according to an embodiment.

Fig. 15 is a sectional view a-a in fig. 14.

Fig. 16 is a schematic structural diagram of a first pipeline in a slurry suction pipeline system according to another embodiment.

Fig. 17 is a partial enlarged view B in fig. 16.

FIG. 18 is a schematic diagram of an exemplary embodiment of a hydraulic injection pump discharge line system.

Fig. 19 is a left side view of fig. 18.

FIG. 20 is a schematic diagram of a structure of a buffer in a slurry discharge piping system of a hydraulic injection pump according to an embodiment.

Fig. 21 is a schematic structural diagram of a hydraulic injection pump spray system according to an embodiment.

Fig. 22 is a top view of an embodiment of a hydraulic injection pump spray system.

Fig. 23 is a partial enlarged view C of fig. 10.

Fig. 24 is a partial enlarged view D in fig. 10.

Fig. 25 is a schematic structural view of a split connection pipeline according to an embodiment.

Fig. 26 is a top view of fig. 25.

Fig. 27 is a left side view of fig. 25.

FIG. 28 is a schematic diagram of a hydraulic charge pump reversal system according to one embodiment.

FIG. 29 is a schematic diagram of a detection unit of the hydraulic charge pump reversal system of an embodiment.

FIG. 30 is a schematic diagram of another detection unit of the hydraulic charge pump reversal system of an embodiment.

FIG. 31 is a flow chart illustrating a method for reversing a hydraulic charge pump according to an embodiment.

Description of the reference numerals

1. Prying a hydraulic pump station; 101. a power element; 102. a transmission element; 103. a transfer case; 104a, 104b, a hydraulic oil pump; 105. an oil suction pipeline; 106. an oil outlet pipeline; 107. an accumulator; 108. a valve block; 109. an oil return integrated block; 110. an overflow line; 111. an oil return line; 112a, 112b, a return oil filter; 113. an oil supply integrated block; 114. a one-way valve;

2. a hydraulic oil tank; 201. a box body; 2011. an oil outlet of the oil tank; 2012. a first separator; 2013. a second separator; 2014. a third partition plate; 202. a heat sink; 203. a heat-dissipating oil pump; 204. a heat dissipation oil suction pipe; 2041. an oil suction hole; 205. a heat dissipation oil return pipe; 2051. a first branch pipe; 2052. a second branch pipe; 206. a vent pipe;

3. hydraulic prying; 301. a frame; 301a, a first receiving cavity; 301b, a second receiving cavity; 301c, water through holes; 301d, a water return hole; 3011. a first wall panel; 3012. a second wall panel; 3013. a first end plate; 3014. a second end plate; 3015. a first separator; 3016. a second separator; 3017. a first fixing plate; 3018. a second fixing plate; 3019a, a first support plate; 3019b, a second support plate; 302. a hydraulic cylinder; 303. a hydraulic piston rod; 304. a diverter valve; 305. a first valve housing; 306. a second valve housing; 307. a first cylinder liner; 308. a second cylinder liner;

6. the pipeline system is connected in a split manner; 601. an oil inlet pipeline; 602. a first connection block; 603. a second connecting block; 604. a first valve; 605. a first hose; 606. a second hose; 607. a support frame; 607a, a support panel; 608. an oil receiving pan; 609. a second valve; 610. an oil transfer pump; 611. a small oil tank; 612. an oil filter; 613. an oil suction pipe; 614. an oil return line; 615. a third rubber tube; 616. a fourth rubber tube; 617. a support frame; 618. an oil discharge pipe;

7. a slurry suction pipeline system; 701. a first pipeline; 701a, a first connecting section; 701b and a second connecting section; 701c, a third connecting section; 7012. externally connecting a layer pipe; 7014. a seal ring; 7015. an outer nut; 7016. a concave hole portion; 7017. a radial projection; 703. a support; 705. an oil union; 706. a second pipeline; 707. a branch pipeline; 709. sucking an air bag; 710. a third pipeline;

8. a slurry discharge pipeline system; 801. a first tee joint; 802. a first high pressure pipe; 803. a second tee joint; 804. a second high-pressure tube; 805. a third tee joint; 806. discharging the air bag; 807. an exhaust valve; 808. a buffer; 808a, a deposition cavity; 808b, an inner tube; 809. a pressure gauge; 810. a first header; 811. a second header; 812. a pillar;

9. a spray system; 901. a spray water tank; 901a and a water return port; 902. a spray water pump; 903. a water supply pipe; 904. a horizontal water diversion pipe; 905. a water spray pipe;

10. a base.

Detailed Description

Other objects and advantages of the present invention will become apparent from the following explanation of the preferred embodiments of the present application.

The hydraulic injection pump comprises a hydraulic pump station pry 1 and a hydraulic pry 3, wherein the hydraulic pump station pry 1 comprises a power element 101,

hydraulic oil pumps

104a and 104b and a hydraulic oil tank 2; the hydraulic pry 3 comprises a rack, a main working hydraulic cylinder and a valve box, and the hydraulic pump station pry 1 is connected with the hydraulic pry 3 through a split connecting pipeline 6. Hydraulic pump station sled 1 is used for providing hydraulic oil to hydraulic sled 3, and hydraulic sled 3 then is used for turning into the pressure of working medium with the pressure of hydraulic oil, carries out injection operations such as profile control, fracturing, pressure drive, water shutoff.

Example 1

As shown in fig. 1 to 4, a hydraulic pump station pry 1 comprises a plurality of oil supply units, each oil supply unit comprises a power element 101, a transfer case 103 and two

hydraulic oil pumps

104a and 104b, the power element 101 is in transmission connection with an input end of the transfer case 103, the transfer case 103 is provided with two output ends, and the output ends of the transfer case 103 are in transmission connection with the

hydraulic oil pumps

104a and 104b respectively.

In the prior art, the displacement of the

hydraulic oil pumps

104a and 104b cannot be selected at will, and particularly, the model selection of the hydraulic oil pumps with large displacement is often limited by factors such as technical maturity and price, in the hydraulic pump station pry 1 of the embodiment, one power element 101 is adopted to drive the two

hydraulic oil pumps

104a and 104b, and the transfer case 103 is used for transmission, and under the condition that a small amount of power elements 101 are used, the maximum displacement of the hydraulic injection pump can be greatly improved by selecting the conventional

hydraulic oil pumps

104a and 104 b.

In the embodiment, the power element is an electric motor, the electric motor is connected with the transfer case 103 through a transmission element 102, the transmission element 102 can comprise a bell jar and a coupler, a shell of the electric motor is connected with a shell of the transfer case 103 through the bell jar, an output shaft of the electric motor is connected with an input end of the transfer case 103 through the coupler, and transmission connection is carried out through the bell jar and the coupler, so that the coaxiality is good, and the cost performance is high.

The power element 101 may be, for example, an electric motor or a diesel engine, and those skilled in the art have many options, which are not particularly limited. In this embodiment, the transfer case 103 has an input end and two output ends, and the two output ends are in transmission connection with a hydraulic oil pump 104a and a hydraulic oil pump 104b respectively. Of course, a greater number of outputs of the transfer case 103 may be used as desired and will not be described further herein.

In some embodiments, the motive element 101 is plural. For example, two, three, four, five … … power elements 101 are mounted in one hydraulic pump station sled 1. A plurality of power elements 101 are installed in one hydraulic pump station skid 1, and meanwhile, each power element 101 drives two

hydraulic oil pumps

104a and 104b, or certainly, a plurality of hydraulic oil pumps, so that the technical effect of greatly improving the maximum displacement of a hydraulic injection pump is achieved, and the requirement of hydraulic pressure drive operation on large-displacement injection equipment is met.

In this embodiment, hydraulic power unit sled 1 includes three power component 101, and every power component 101 then can drive two hydraulic oil pumps simultaneously, then has six hydraulic oil pumps in a hydraulic injection pump like this, for traditional hydraulic pressure profile control pump, under the hydraulic oil pump condition that adopts the same specification, the discharge capacity of complete machine can improve to six times.

In this embodiment, the outlet of each hydraulic oil pump is provided with a check valve 114, so that the hydraulic oil pump is prevented from being damaged by return oil of the hydraulic system, and the hydraulic oil pump is protected.

In some embodiments, the hydraulic pump station skid 1 further comprises a hydraulic oil tank 2; the suction ports of the

hydraulic oil pumps

104a and 104b are connected to the hydraulic oil tank 2 through an oil suction line 105.

The oil suction pipeline 105 can be provided with an oil inlet filter and a hose clamp, for example, the oil inlet filter is used for filtering out impurities in hydraulic oil and preventing the impurities from entering circulation; the hose clamp is convenient for connect the pipeline, also can play the effect of vibration isolation.

The hydraulic oil tank 2 mainly functions to store oil, and also functions to dissipate heat of the oil, precipitate impurities, and allow air in the oil to escape. The oil tank can be divided into an open type and a closed type according to whether the liquid level of the oil tank is communicated with the atmosphere or not. The open oil tank is used in a general hydraulic system; the closed oil tank is used underwater and in hydraulic systems with strict requirements on working stability and noise. The hydraulic oil tank 2 in this embodiment is an open tank. The suction ports of the

hydraulic oil pumps

104a and 104b are connected to the hydraulic oil tank 2, and suck hydraulic oil from the hydraulic oil tank 2, and send the

hydraulic oil pumps

104a and 104b to the main working hydraulic cylinder, and the oil flowing back from the main working hydraulic cylinder flows back to the hydraulic oil tank 2 through the oil return line 111.

In some embodiments, the hydraulic oil tank 2 includes a tank 201, a radiator 202, and a radiator oil pump 203, a suction end of the radiator oil pump 203 is connected to the tank 201, a discharge end of the radiator oil pump 203 is connected to the radiator 202, and a discharge end of the radiator 202 is connected to the tank 201. Connect radiator 202 to oil return line 111 in traditional hydraulic pressure profile control pump on, hydraulic tank 2 in this embodiment then adopts the bypass heat dissipation, and radiator 202 avoids the hydraulic oil impact of backward flow on the one hand, and on the other hand is convenient for match reasonable heat dissipation oil pump 203 according to radiating needs, carries out high-efficient heat dissipation to hydraulic oil.

In some embodiments, there are a plurality of radiators 202 and radiator oil pumps 203, and the radiators 202 correspond to the radiator oil pumps 203 one to one. The heat dissipation capacity of the hydraulic pump station prying 1 can be increased by increasing the number of the radiators 202 and the heat dissipation oil pumps 203, when the heat production quantity of the system is low, the heat dissipation requirement can be met by working the starting part heat dissipation oil pumps 203, the energy waste is avoided, and the oil temperature of hydraulic oil is convenient to maintain in a reasonable interval.

In some embodiments, the hydraulic pump station skid 1 further includes an oil supply manifold 113, an oil inlet of the oil supply manifold 113 is connected to an outlet of the

hydraulic oil pump

104a or 104b through an oil outlet pipeline 106, an accumulator 107 may be disposed in the oil outlet pipeline 106, and the accumulator 107 is used for buffering hydraulic impact in the hydraulic circuit. One end of the oil outlet pipeline 106 is connected with the hydraulic oil pump, the other end of the oil outlet pipeline is connected with the valve block 108, an overflow valve can be arranged on the valve block 108, an overflow port of the overflow valve is connected to the oil return integrated block 109 through an overflow pipeline 110, hydraulic oil can directly flow back to the hydraulic oil tank through the overflow valve, and the hydraulic pry is controlled to start and stop. In addition, a safety valve can be arranged on the valve block 108 to limit the pressure of the hydraulic system, so that the hydraulic system is protected.

The oil supply manifold 113 has a plurality of oil outlets. The hydraulic injection pump is designed to be split type, that is, includes a hydraulic pump station sled 1 and a hydraulic sled 3 for supplying hydraulic oil, so that each part has small volume and weight and is convenient to transport. The oil supply integrated block 113 is arranged on the hydraulic pump station pry 1, so that the hydraulic pump station pry 1 is connected with the hydraulic pry 3 through a hydraulic oil pipe.

In some embodiments, the hydraulic pump station skid 1 further includes a return manifold 109 connected to one end of a return line 111, the other end of the return line 111 being connected to return

oil filters

112a, 112b, the

return oil filters

112a, 112b being connected to the oil tank, the return manifold 109 being configured to facilitate connection of hydraulic oil flowing back from the hydraulic skid 3 to the hydraulic oil tank 2 via the hydraulic lines.

In some embodiments, return

oil filters

112a, 112b are multiple; the return line 111 has a plurality of outlet ports, and the outlet ports of the return line 111 are connected to one

return oil strainer

112a, 112b, respectively. The

return oil filters

112a and 112b commonly used in the prior art have several specifications, and a plurality of

return oil filters

112a and 112b are arranged to meet the requirement of large-displacement return oil filtration, and the conventional

return oil filters

112a and 112b are convenient to maintain, and the conventional filter elements are replaced during equipment maintenance.

Example 2

As shown in fig. 1 to 9, a hydraulic oil tank 2 includes a tank 201, a radiator 202, and a radiator oil pump 203, a suction end of the radiator oil pump 203 is connected to the tank 201, a discharge end of the radiator oil pump 203 is connected to the radiator 202, and a discharge end of the radiator 202 is connected to the tank 201. Connect radiator 202 to oil return line 111 in traditional hydraulic pressure profile control pump on, hydraulic tank 2 in this embodiment then adopts the bypass heat dissipation, and radiator 202 avoids the hydraulic oil impact of backward flow on the one hand, and on the other hand is convenient for match reasonable heat dissipation oil pump 203 according to radiating needs, carries out high-efficient heat dissipation to hydraulic oil.

The number of the radiators 202 and the heat-dissipating oil pumps 203 is plural, and the radiators 202 and the heat-dissipating oil pumps 203 correspond to each other one by one. The heat dissipation capacity of the hydraulic pump station prying 1 can be increased by increasing the number of the radiators 202 and the heat dissipation oil pumps 203, when the heat production quantity of the system is low, the heat dissipation requirement can be met by working the starting part heat dissipation oil pumps 203, the energy waste is avoided, and the oil temperature of hydraulic oil is convenient to maintain in a reasonable interval.

The hydraulic oil tank 2 of the present embodiment has three heat-radiating oil pumps 203 and three radiators 202, and the heat-radiating oil pumps 203 and the radiators 202 correspond one to one. That is, each radiator 202 is supplied with oil by one radiator oil pump 203. Of course, three heat-dissipating oil pumps 203 may be used to supply oil to two radiators 202, or two heat-dissipating oil pumps 203 may be used to supply oil to three radiators 202, that is, the number of the two oil pumps may be different.

In this embodiment, the heat sink 202 is located above the case 201. The radiator 202 draws air from the lower side and discharges hot air upward. A gap for air circulation is provided between the heat sink 202 and the case 201. The radiator 202 is arranged above the tank body 201, so that the space above the tank body 201 is reasonably utilized, and the space occupation of the hydraulic oil tank 2 in the length direction and the width direction is reduced.

A plurality of oil tank outlets 2011 are arranged on one side wall of the tank body 201. Each hydraulic oil pump corresponds to an oil tank outlet 2011, and the hydraulic oil is sucked from the hydraulic oil tank 2 through the oil tank outlet 2011.

Be equipped with a plurality of baffles in the box 201, the baffle separates the inner chamber of box 201 for a plurality of holding chambeies, and every holding chamber all corresponds there is at least one oil tank oil-out 2011. In this embodiment, each receiving cavity corresponds to two tank outlets 2011.

In this embodiment, a first partition 2012 and a second partition 2013 are arranged in the box 201, and the first partition 2012 and the second partition 2013 are arranged in parallel to divide the inner cavity of the box 201 into three accommodating cavities. The first partition 2012 and the second partition 2013 extend upwards from the bottom of the tank 201, but a certain interval is reserved between the first partition and the top of the tank 201, and when the oil level of one accommodating cavity exceeds the height of the partition, the hydraulic oil in the accommodating cavity can overflow to the adjacent accommodating cavity.

As shown in fig. 6, a tank outlet 2011 is provided on the right side wall of the tank 201, and a return oil filter is provided on the left side of the top of the tank 201. And the first bulkhead 2012 and the second bulkhead 2013 extend in the left-right direction.

A heat dissipation oil suction pipe 204 is arranged in the box body 201, one end of the heat dissipation oil suction pipe 204 is connected with the heat dissipation oil pump 203, the other end of the heat dissipation oil suction pipe 204 penetrates through at least one partition plate, a plurality of oil suction holes 2041 are formed in the heat dissipation oil suction pipe 204, and the heat dissipation oil suction pipe 204 is communicated with the plurality of accommodating cavities through the oil suction holes 2041. The heat dissipation oil pump 203 can absorb hydraulic oil from different accommodating cavities, and the hydraulic oil temperature in each accommodating cavity in the hydraulic oil tank 2 is guaranteed to be balanced.

The discharge end of the radiator 202 is connected to the heat dissipation oil return pipe 205, the heat dissipation oil return pipe 205 includes a first branch pipe 2051 and a second branch pipe 2052, and the first branch pipe 2051 and the second branch pipe 2052 are respectively communicated with different accommodating cavities. The hydraulic oil cooled by the radiator 202 is distributed to the two accommodating cavities, so that the oil temperature of the hydraulic oil in each accommodating cavity is further ensured to be balanced.

As shown in fig. 8, a third partition 2014 is disposed at the middle of the box 201, and the third partition 2014 is perpendicular to the extending direction of the first partition 2012 and divides the inner cavity of the box 201 in the left-right direction. The return oil filter is on one side of the third partition 2014 and the tank outlet 2011 is on the other side of the third partition 2014. After the system circulation, the hydraulic oil flows back to the oil tank from the return oil filter, and flows to the right side of the third partition 2014 after being settled on the left side of the third partition 2014, and the third partition 2014 can play a role in settling impurities in the hydraulic oil.

The box body 201 is also provided with a plurality of ventilation pipes 206, the ventilation pipes 206 penetrate through the box body 201 in the vertical direction, and ventilation holes communicating the upper side and the lower side of the box body 201 are formed in the ventilation pipes 206. The air duct 206 is located below the heat sink 202. On one hand, the vent holes can provide air inlet channels for the radiator 202 and have the function of cooling hydraulic oil in the box body 201; on the other hand, the structural strength of the case 201 can be enhanced.

Example 3

As shown in fig. 10 to 13, a hydraulic injection pump hydraulic pry 3 includes three working units in which a frame 301 is connected to the frame 301. The working unit comprises a hydraulic cylinder 302 and a first hydraulic end and a second hydraulic end which are symmetrically arranged at two sides of the hydraulic cylinder 302. The hydraulic cylinder 302 includes a hydraulic piston rod 303, and the hydraulic piston rod 303 has a first output end and a second output end which are oppositely arranged, the first output end is connected with the first hydraulic end, and the second output end is connected with the second hydraulic end.

The rack 301 is installed on the upper side of the base 10, and the base 10 is used for providing support for the rack 301, the slurry suction pipeline system 7, the slurry discharge pipeline system 8 and the spraying system 9.

In this embodiment, there are three working units, but it should be noted that there are 2 to 10 working units as required. Further preferably, the number of the working units is 3-5. The present invention increases the maximum displacement of the hydraulic injection pump by increasing the number of working units.

Each working unit comprises a hydraulic cylinder 302 and a first hydraulic end and a second hydraulic end which are symmetrically arranged at two sides of the hydraulic cylinder 302. The hydraulic cylinder 302, the first hydraulic end and the second hydraulic end are all fixedly connected with the frame 301. In this embodiment, the hydraulic cylinder 302 is configured to convert hydraulic energy into a reciprocating linear motion of the hydraulic piston rod 303, and the hydraulic piston rod 303 drives the first hydraulic end and the second hydraulic end to alternately suck in and discharge a pressure driving medium.

The hydraulic cylinder 302 is connected to a reversing valve 304, and the reversing valve 304 is used for driving the hydraulic cylinder 302 to reverse in a reciprocating manner.

The first hydraulic end includes a first valve housing 305 and a first cylinder jacket 307. The first valve box 305 is fixedly connected with the frame 301, and the first cylinder sleeve 307 is hermetically connected with the first valve box 305. The first output end is provided with a mud piston, which is in sealed and slidable connection with the inner bore of the first cylinder 307.

The second hydraulic end includes a second valve housing 306 and a second cylinder jacket 308. The second valve box 306 is fixedly connected with the frame 301, and the second cylinder sleeve 308 is hermetically connected with the second valve box 306. The second output end is provided with a slurry piston which is in sealed and slidable connection with the inner hole of the second cylinder sleeve 308.

A water supply valve and a water drain valve are arranged in the first valve box 305 and the second valve box 306. When the hydraulic piston rod 303 moves from left to right, the slurry piston in the first cylinder sleeve 307 moves from left to right, the water outlet valve of the first valve box 305 positioned on the left side of the rack 301 is opened, the water inlet valve is closed, and the pressure driving medium is sucked into the first cylinder sleeve 307; meanwhile, the mud piston in the second cylinder sleeve 308 moves from left to right, the water feeding valve of the second valve box 306 on the right side of the frame 301 is opened, the water discharging valve is closed, and the pressure driving medium in the second cylinder sleeve 308 is discharged outwards. When the hydraulic piston rod 303 moves from right to left, the above process is reversed, and the description is omitted. Thereby, the pressure energy of the hydraulic oil can be converted into the pressure energy of the pressure driving medium by the reciprocating motion of the hydraulic piston rod 303.

In this embodiment, three working units are arranged in parallel.

In this embodiment, the first valve housing 305 and the second valve housing 306 are preferably L-shaped valve housings having a large diameter and a large pressure-bearing capacity.

The hydraulic injection pump hydraulic pry 3 further comprises a slurry suction pipeline system 7, the slurry suction pipeline system 7 is respectively connected with suction ports of the first hydraulic end and the second hydraulic end, and the first hydraulic end and the second hydraulic end suck a pressure driving medium into the first cylinder sleeve 307 or the second cylinder sleeve 308 through the slurry suction pipeline system 7.

The hydraulic injection pump further comprises a slurry discharge pipeline system 8, and the slurry discharge pipeline system 8 is connected with the discharge ports of the first hydraulic end and the second hydraulic end respectively. The first hydraulic end and the second hydraulic end discharge the pressure driving medium in the first cylinder jacket 307 and the second cylinder jacket 308 through the slurry discharge pipe system 8.

Example 4

In order to provide support for the structures such as the hydraulic cylinder 302, the valve box, the cylinder sleeve and the like, the embodiment of the invention also provides a hydraulic end frame 301, which meets the installation requirements of a plurality of working hydraulic cylinders.

The embodiment of the invention provides a hydraulic end rack 301, which comprises a first wall board 3011, a first end board 3013, a second wall board 3012 and a second end board 3014, wherein the first wall board 3011, the first end board 3013, the second wall board 3012 and the second end board 3014 are vertically arranged and sequentially connected end to end, an accommodating space is formed by enclosing the first wall board 3011, the first end board 3013, the second wall board 3012 and the second end board 3014, and the accommodating space is divided into a grid shape by vertically arranged boards. The accommodating space inside the rack 301 is divided into a grid shape by the vertically arranged plates, so that the bearing capacity of the rack 301 as a whole is greatly enhanced.

Specifically, frame 301 includes vertical setting and fixed first wallboard 3011, second wallboard 3012, first end plate 3013 and the second end plate 3014 as an organic whole, and first wallboard 3011 sets up with second wallboard 3012 is relative, and first end plate 3013 and second end plate 3014 set up relatively. First wallboard 3011, first end plate 3013, second wallboard 3012 and second end plate 3014 end to end connection in order, and weld as an organic whole, enclose to close and form the skin of frame 301 to at the inside accommodation space that forms of frame 301. The first end plate 3013 and the second end plate 3014 provide support for installing the valve box, and the first wall plate 3011 and the second wall plate 3012 can connect the first end plate 3014 and the second end plate 3014 together and can bear loads in the length direction of the frame 301 when the hydraulic cylinder 302 works.

The plate comprises at least one partition board extending along the length direction of the frame 301, one end of the partition board is fixedly connected with the first end plate 3013, and the other end of the partition board is fixed with the second end plate 3014. In the rack 301 of this embodiment, a first partition 3015 and a second partition 3016 are provided, and the first wall 3011, the second wall 3012, the first partition 3015, and the second partition 3016 jointly bear the load in the length direction of the rack 301.

The panel further comprises at least one fixing plate extending along the width direction of the rack 301, and one end of the fixing plate is fixedly connected with the first wall plate 3011, and the other end of the fixing plate is fixedly connected with the second wall plate 3012. In this embodiment, two fixing plates, that is, a first fixing plate 3017 and a second fixing plate 3018, are disposed in the frame 301, through holes are disposed on the first fixing plate 3017 and the second fixing plate 3018, and the first fixing plate 3017, the second fixing plate 3018 and the through holes thereon can provide support for the hydraulic cylinder 302.

The panel includes at least one backup pad that extends along frame 301 width direction, and the one end and first wallboard 3011 fixed connection, the other end and second wallboard 3012 fixed connection of backup pad. The cylinder sleeve comprises a first supporting plate 3019a and a second supporting plate 3019b, through holes are formed in the first supporting plate 3019a and the second supporting plate 3019b, and the through holes in the first supporting plate 3019a and the second supporting plate 3019b can provide support for the cylinder sleeve.

It is emphasized that the diameters of the through holes of the first end plate 3013, the second end plate 3014, the first fixing plate 3017, the second fixing plate 3018, the first support plate 3019a and the second support plate 3019b may be the same or different, but all are coaxial, corresponding to the same working unit.

Further, the both ends downside of frame 301 is equipped with one respectively and holds the chamber, should hold the chamber and can be used for placing spray system 9's water tank, has rationally utilized the space on the hydraulic sled 3.

Example 5

As shown in fig. 1 and fig. 10 to 17, a hydraulic injection pump slurry suction pipeline system 7 is used for a hydraulic injection pump, and the hydraulic injection pump includes a frame 301, three first valve boxes 305 are arranged at one end of the frame 301 in the length direction, and three second valve boxes 306 are arranged at the other end of the frame 301 in the length direction. The number of the first valve boxes 305 and the second valve boxes 306 is not particularly limited, and may be a larger number, for example, five first valve boxes 305 and five second valve boxes 306, which will not be described again. The hydraulic injection pump sucks in the pressure driving medium through the slurry suction pipe system 7.

In this embodiment, the slurry suction pipeline system 7 includes a first pipeline 701, a second pipeline 706 and a third pipeline 710, one end of the first pipeline 701 is connected to the second pipeline 706, and the other end of the first pipeline 701 is connected to the third pipeline 710, so that the first pipeline 701, the second pipeline 706 and the third pipeline 710 are communicated with each other, and a suction port is disposed on the slurry suction pipeline system 7, which is convenient to install. Preferably, second conduit 706 and/or third conduit 710 are connected to first conduit 701 by a flange. In this embodiment, the slurry suction piping system 7 is mounted on the base 10 by a plurality of brackets 703.

The upper side of the second pipeline 706 is provided with a plurality of first branch pipelines 707, the first branch pipelines 707 correspond to the first valve box 305 one by one, and the first branch pipelines 707 are connected with the suction inlet of the first valve box 305; the third pipe 710 has a plurality of second branch pipes 707 on the upper side, the second branch pipes 707 correspond to the second valve boxes 306 one by one, and the second branch pipes 707 are connected to the suction ports of the second valve boxes 306. The number of first branch lines 707 is matched to the number of first valve boxes 305, and the upper ends of the first branch lines 707 may be connected to the first valve boxes 305 by flanges. Likewise, the number of the second branch pipes 707 may match the number of the second valve boxes 306, and the upper ends of the second branch pipes 707 may be connected to the second valve boxes 306 by flanges.

In some embodiments, a suction port of the slurry suction piping system 7 is formed on the first piping 701. The suction port may be formed in the middle of the first pipe 701, so that the first valve box 305 and the second valve box 306 at both ends of the frame 301 in the length direction have the same distance from the suction port, which is convenient for the first valve box 305 and the second valve box 306 to obtain the same amount of pressure driving medium.

A flange or oil union 705 is provided at the suction inlet of the slurry suction piping system 7. In practice, the piping may be quickly connected to the suction port by a flange or oil union 705.

In some embodiments, a suction air pocket 709 is provided on the second conduit 706 and/or the third conduit 710. The suction air pocket 709 can buffer medium pressure fluctuations in the slurry suction pipe system 7.

The first pipeline 701 includes a first connection section 701a, a second connection section 701b and a third connection section 701c, the first connection section 701a is detachably and hermetically connected with one end of the second connection section 701b, and the other end of the second connection section 701b is detachably and hermetically connected with the third connection section 701 c.

For example, the connection structure between the first connection segment 701a and the second connection segment 701b is used, an external connection layer pipe 7012 is sleeved on the first connection segment 701a, and an outer circle of an end portion of the second connection segment 701b can be matched with an inner hole of the external connection layer pipe 7012. A sealing ring 7014 groove is formed in the outer circle of the second connecting section 701b, and a sealing ring 7014 is installed in the sealing ring 7014 groove. Further, a radial protrusion 7017 is formed on the outer contour of the second connecting section 701b, an external nut 7015 is mounted on the outer contour of the second connecting section 701b, and the external nut 7015 is screwed with the outer extension pipe 7012. Preferably, the outer profile of the outer nut 7015 is provided with a plurality of radially extending recessed hole portions 7016, and the recessed hole portions 7016 can facilitate mounting and dismounting of the outer nut 7015.

In this embodiment, the first pipeline 701 is split into three sections, and a detachable and sealed connection structure is provided between two adjacent sections. The first connecting section 701a and the second connecting section 701b are provided with a detachable and sealed connecting structure. In one aspect, the weight of each segment is reduced relative to the total weight of the first conduit 701. On the other hand, adjustment according to the distance between the first valve housing 305 and the second valve housing 306 is facilitated, and installation and maintenance are facilitated.

Example 6

As shown in fig. 18 to 20, the present embodiment provides a hydraulic injection pump slurry discharge pipeline system 8 for a hydraulic injection pump, the hydraulic injection pump includes a frame 301, one end of the frame 301 in the length direction is provided with a plurality of first valve boxes 305, and the other end of the frame 301 in the length direction is provided with a plurality of second valve boxes 306; the slurry discharge piping system 8 includes a first header 810 connected to the discharge ports of the plurality of first valve boxes 305, and a second header 811 connected to the discharge ports of the plurality of second valve boxes 306, the first header 810 and the second header 811 communicating through a slurry discharge manifold.

In this embodiment, three first valve boxes 305 are disposed at one end of the frame 301, and three second valve boxes 306 are disposed at the other end. A discharge port is provided on the side of each first valve housing 305 facing the frame 301, and the discharge ports of the first valve housings 305 communicate with the first collecting pipes 810, respectively. A discharge port is provided on the side of each second valve casing 306 facing the frame 301, and the discharge ports of the second valve casings 306 communicate with second headers 811, respectively. The first collecting pipe 810 and the second collecting pipe 811 are communicated by a slurry outlet manifold, so that the slurry outlet piping system 8 of the present embodiment can be communicated with the plurality of first valve boxes 305 and the plurality of second valve boxes 306, respectively, and can form a uniform outlet on the slurry outlet manifold, thereby facilitating installation of the apparatus.

The slurry outlet manifold comprises a first tee 801, a second tee 803 and a third tee 805, wherein the first header 810, the first tee 801, the second tee 803, the third tee 805 and the second header 811 are communicated in sequence, and a pump discharge port is formed in the second tee 803. The first tee 801 communicates with the second tee 803 via a first high pressure tube 802. The second tee 803 is in communication with the third tee 805 through a second high pressure tube 804.

The first tee 801 and/or the third tee 805 are provided with a bleed air bag 806. The discharge air bag 806 can function to absorb shocks generated during operation of the pump, and the first and

second tees

801 and 803 can provide mounting locations and support for the installation of the discharge air bag 806.

At least one of the first tee 801, the second tee 803, and the third tee 805 is connected to the base 10 of the hydraulic charge pump by a strut 812. The support 812 can support each tee and the bleed air bag 806.

The second three-way pipe 803 is provided with an air exhaust valve 807, and the air exhaust valve 807 can exhaust air in the slurry discharge pipe system 8 when the pump starts to start.

A pressure gauge 809 is arranged on the second tee 803, and the pressure gauge 809 is connected with the second tee 803 through a buffer 808. The pressure gauge 809 is used to measure and realize the pressure of the pressure driving medium in the slurry discharge pipe system 8.

A deposition cavity 808a is arranged in the buffer 808, a first port is arranged at the lower part of the buffer 808, a second port is arranged at the upper part of the buffer 808, the lower end of the first port is connected with the second tee 803, an inner pipe 808b extending upwards in the deposition cavity 808a is arranged at the upper end of the first port, the lower end of the second port is communicated with the deposition cavity 808a, and the upper end of the second port is communicated with the pressure gauge 809.

Hydraulic oil is filled in the deposition chamber 808a, but a small amount of impurities in the pressure driving medium enter the deposition chamber 808a through the first port and are deposited in the deposition chamber 808a, so that the impurities are prevented from blocking a detection hole of the pressure gauge 809. The hydraulic oil in the settling chamber 808a can be prevented from flowing out entirely by providing the inner tube 808 b.

The upper end of the inner tube 808b is bent into an open downward shape. The impurities entering the inner tube 808b are ejected downward to avoid clogging the pressure gauge 809.

Example 7

The present embodiment provides a hydraulic injection pump spray system 9 that can continue to cool down the cylinder liners and pistons, extending the life of the pistons and cylinder liners.

Specifically, as shown in fig. 10, 21 to 24, a hydraulic injection pump shower system 9 is used for a hydraulic injection pump having a frame 301 and a plurality of working units fixed to the frame 301, each of the working units including a hydraulic cylinder 302 and a first cylinder casing 307 and a second cylinder casing 308 provided on both sides in a length direction of the hydraulic cylinder 302. The hydraulic injection pump of the present embodiment has three working units each having one first cylinder liner 307 and one second cylinder liner 308, and therefore, has three first cylinder liners 307 and three second cylinder liners 308 in the present embodiment.

In this embodiment, the hydraulic injection pump shower system 9 includes a horizontal diversion pipe 904, and the horizontal diversion pipe 904 extends along the width direction of the rack 301. Three water spray pipes 905 are arranged on the horizontal water diversion pipe 904. The sprinkler pipe 905 may be, for example, a length of metal pipe secured to the horizontal diverter pipe 904. The sprinkler pipe 905 has one end communicating with the horizontal diversion pipe 904 and the other end facing the end of the first cylinder jacket 307 or the second cylinder jacket 308 close to the hydraulic cylinder 302. The water sprayed out of the water spray pipe 905 can continuously cool the cylinder sleeve and the piston, and the service life of the water spray pipe is prolonged.

In this embodiment, there are two horizontal diversion pipes 904, one of the horizontal diversion pipes 904 is located at the left side of the hydraulic cylinder 302, and the water spray nozzle of the water spray pipe 905 faces the inner hole of the first cylinder jacket 307; the other horizontal diversion pipe 904 is positioned on the right side of the hydraulic cylinder 302, and the water spray of the horizontal diversion pipe 904 faces the inner hole of the second cylinder sleeve 308.

In this embodiment, the hydraulic injection pump spray system 9 includes a spray water tank 901 and a spray water pump 902, a suction port of the spray water pump 902 is connected to the spray water tank 901, and a discharge port of the spray water pump 902 is connected to the horizontal water diversion pipe 904. The spray tank 901 is used to store spray water, and impurities in the spray water may also precipitate in the spray tank 901.

In this embodiment, two spray water tanks 901 and two spray water pumps 902 are provided, and the spray water tanks 901, the spray water pumps 902 and the horizontal water diversion pipes 904 are connected in a one-to-one correspondence manner.

The lower sides of the two ends of the rack 301 in the length direction are provided with accommodating cavities for accommodating the spray water tanks 901.

A water return port 901a is provided on the upper side of the spray water tank 901, the water return port 901a extends in the width direction of the frame 301, and water returned from the cylinder liner flows back into the spray water tank 901 through the water return port 901 a.

The frame 301 is provided with a first receiving cavity 301a and a second receiving cavity 301b, a supporting plate is arranged between the first receiving cavity 301a and the second receiving cavity 301b, and the first receiving cavity 301a and the second receiving cavity 301b are connected through a water through hole 301 c. The supporting plate is used for positioning and supporting the cylinder sleeve. The first receiving cavity 301a is formed on the right side of the support plate, and the second receiving cavity 301b is formed on the left side of the support plate. The support plate is provided with a water through hole 301c, and the spray water flows out from the cylinder sleeve to the first receiving cavity 301a and then flows to the second receiving cavity 301b through the water through hole 301 c.

The bottom walls of the first receiving cavity 301a and the second receiving cavity 301b are obliquely arranged and are lower near one side of the support plate. In the first receiving chamber 301a, the left side of the bottom wall thereof is lower, facilitating the shower water to flow leftward to the water passing hole 301 c. And in the second receiving chamber 301b, the bottom wall thereof is lower on the right side, facilitating the shower water to be collected to the right side.

A water return hole 301d penetrating through the bottom wall is formed in the bottom wall of the second receiving cavity 301b, and the water return hole 301d is located on the upper side of the water return port 901 a. The shower water in the second receiving chamber 301b flows back to the shower water tank 901 through the return hole 301 d.

Example 8

As shown in fig. 25 to 27, a hydraulic injection pump is separately connected to a piping system 6 for a hydraulic injection pump, and the hydraulic injection pump includes a hydraulic pump station sled 1 and a hydraulic sled 3. The split connection pipeline system 6 comprises a plurality of oil inlet pipelines 601, one end of each oil inlet pipeline 601 is connected with the hydraulic pump station pry 1, and the other end of each oil inlet pipeline 601 is connected with the hydraulic pry 3; one end of the oil return pipeline 614 is connected with the hydraulic pump station pry 1, and the other end of the oil return pipeline 614 is connected with the hydraulic pump station pry 3; the support frame 607, the oil inlet pipeline 601 and the oil return pipeline 614 are fixedly connected with the support frame 607.

In this embodiment, the oil inlet pipeline 601 and the oil return pipeline 614 are metal pipes, which are convenient to fix and have good safety. Preferably, one end of the oil inlet pipeline 601 is provided with a first connecting block 602, and the other end is provided with a second connecting block 603; the first connecting block 602 is connected with the hydraulic power pry through a first rubber hose 605, and the second connecting block 603 is connected with the hydraulic power pump station pry through a second rubber hose 606. Preferably, one end of the oil return pipeline 614 is connected with the hydraulic pry through a plurality of third rubber hoses 615, and the other end of the oil return pipeline is connected with the hydraulic pump station pry through a fourth rubber hose 616.

In this embodiment, the supporting frame 607 is arranged to fix the oil inlet pipelines 601 and the at least one oil return pipeline 614 together, so that the hydraulic pipelines between the hydraulic pump station pry 1 and the hydraulic pry 3 are arranged in order, and the pipelines are convenient to connect and transport.

In this embodiment, the upper surface of the supporting frame 607 is provided with a porous supporting panel 607 a; an oil receiving pan 608 is provided in the support frame 607, and the oil receiving pan 608 is located below the support panel 607 a. Further, a second valve 609 is provided at the bottom of the drip pan 608. When the hydraulic line is installed or removed, the leaked hydraulic oil flows into the oil receiving pan 608 through the porous support panel 607a, thereby reducing environmental pollution. The hydraulic oil in the oil pan 608 can be drained through the second valve 609.

In this embodiment, a small oil tank 611 is provided in the supporting frame 607; the oil inlet pipeline 601 and the oil return pipeline 614 are provided with a first valve 604, and a small oil tank 611 can be connected with the first valve 604. When the pipeline is disassembled, the connection between the oil inlet pipeline 601 and the oil return pipeline 614 and the hydraulic pump station pry and the hydraulic pry can be disassembled (an exhaust valve can also be arranged), the first valve 604 is opened, hydraulic oil flows into the small oil tank 611 through the first valve 604, and the hydraulic oil in the hydraulic pipeline is collected.

The split connection pipeline system 6 of the embodiment further includes an oil transfer pump 610 and an oil discharge pipe 618, one end of the oil transfer pump 610 is connected with the small oil tank 611, the other end of the oil transfer pump 610 is connected with the oil discharge pipe 618, and the oil discharge pipe 618 can be connected with an oil tank prized by the hydraulic pump station. The oil transfer pump 610 is started to transfer the hydraulic oil in the small oil tank 611 to the oil tank prized by the hydraulic pump station, and the hydraulic oil in the hydraulic pipeline is recycled. Preferably, an oil filter 612 may be disposed between the oil delivery pump 610 and the hydraulic oil tank to filter the hydraulic oil in the small oil tank 611, so as to avoid polluting the hydraulic oil in the oil tank pried by the hydraulic pump station.

The top of the supporting frame 607 is provided with a supporting frame 617, the first rubber pipe 605 can be supported on the supporting frame 617, and the supporting frame 617 can fix and support the first rubber pipe 605, the second rubber pipe 606 and the third rubber pipe 615.

Example 9

As shown in fig. 28 to 30, a reversing system of a hydraulic injection pump is used for coordinating reversing time periods and reversing time points of a plurality of working units of the hydraulic injection pump, so that the difference value of the reversing time periods of the hydraulic cylinders of the working units is smaller than a first threshold value, and the reversing time points are staggered and have similar time intervals in sequence.

The reversing system of the hydraulic injection pump of the embodiment comprises a first frequency converter, a second frequency converter and a third frequency converter; a first detection unit, a second detection unit and a third detection unit; and a controller. The hydraulic injection pump comprises a first oil supply unit, a second oil supply unit and a third oil supply unit; the first working unit, the second working unit and the third working unit.

The controller is respectively electrically connected with the first frequency converter, the second frequency converter and the third frequency converter. The controller of this embodiment may be, for example, a PLC, or a PLC acquisition and upper computer cooperative control. The controller is used for controlling the start/stop of the first frequency converter, the second frequency converter and the third frequency converter, collecting frequency signals of the frequency converters and adjusting the operating frequency of the frequency converters so as to enable the working units to work in a coordinated mode.

The first frequency converter is connected with the first oil supply unit, the second frequency converter is connected with the second oil supply unit, the third frequency converter is connected with the third oil supply unit, and the flow rate of hydraulic oil conveyed by the first, second and third oil supply units can be adjusted by adjusting the output frequency of the first, second and third frequency converters. That is, increasing the output frequency of the inverter can increase the flow rate of the hydraulic oil delivered by the oil supply unit, and decreasing the output frequency of the inverter can decrease the flow rate of the hydraulic oil delivered by the oil supply unit.

Specifically, each oil supply unit comprises a motor and a hydraulic oil pump, the motor is in transmission connection with the hydraulic oil pump, and a frequency converter is in transmission connection with the motor. The rotating speed of the motor can be adjusted by adjusting the output frequency of the frequency converter, and then the rotating speed and the real-time discharge capacity of the hydraulic oil pump are adjusted.

The suction inlet of the hydraulic oil pump is connected with the hydraulic oil tank, the discharge outlet of the hydraulic oil pump is connected with the reversing valve through a pipeline, and the reversing valve is connected with the hydraulic cylinder. The reversing time of the hydraulic cylinder can be adjusted by adjusting the real-time discharge capacity of the hydraulic oil pump, and the larger the real-time discharge capacity of the hydraulic oil pump is, the shorter the reversing time of the hydraulic cylinder is.

As shown in fig. 29, a first hydraulic cylinder (1#) is provided in the first working unit, a second hydraulic cylinder (2#) is provided in the second working unit, and a third hydraulic cylinder (3#) is provided in the third working unit. The specifications of the first hydraulic cylinder, the second hydraulic cylinder, and the third hydraulic cylinder are preferably the same. If the hydraulic oil is supplied to the individual cylinders at the same flow rate, the reversal times of the individual cylinders are theoretically identical. However, in actual operation, there are many other factors, such as different volumetric efficiencies of the hydraulic oil pumps, different internal leakage amounts of hydraulic oil in the hydraulic system, etc., and even if the output frequencies of the frequency converters are the same, the commutation periods of the hydraulic cylinders will be different after a certain period of time is accumulated, and the commutation timing will also become irregular.

In this embodiment, the detection unit detects the commutation time length and the commutation time point of each hydraulic cylinder, and the output frequency of the dynamic control frequency converter is used to control the commutation time lengths of the hydraulic cylinders to be approximately the same, and to improve the regularity of the commutation time points, that is, the commutation time points are staggered and have similar time intervals in sequence.

In the following description, the first hydraulic cylinder is taken as an example, and in the present embodiment, the reversing period is defined as the length of time from the a1 position to the C1 position. Of course, the commutation period can also be defined as the length of time from the a position to the C1 position and back to the a1 position from the C1 position (which may be referred to as the commutation period).

And regarding the reversing time point of each hydraulic cylinder, the time for the first hydraulic cylinder to reverse at the A1 position is the first time, the time for the second hydraulic cylinder to reverse at the A2 position is the second time, and the time for the third hydraulic cylinder to reverse at the A3 position is the third time. The reversing time points of the hydraulic cylinders are staggered and have similar time intervals in sequence, namely that in the same direction changing process, the first time is earlier, the second time is later than the first time, and the third time is later than the second time; and the first time of the next rotation process is later than the third time of the last rotation process. In the cycle of the first time, the second time, the third time, the first time and the second time … …, the fluctuation of the time interval between two adjacent times is smaller than the second threshold value.

As shown in fig. 30, in order to obtain the above-mentioned reversing duration and reversing time point, the reversing system of the hydraulic injection pump of the present embodiment may be implemented at D1, D2, D3; proximity sensors are arranged at J1, J2 and J3. For convenience of description, the proximity sensor at the position D1 is simply referred to as the proximity sensor D1, the proximity sensor at the position D2 is simply referred to as the proximity sensor D2, and the numbers of the remaining proximity sensors are analogized.

Taking the first hydraulic cylinder as an example, the hydraulic piston rod of the first hydraulic cylinder has a first output end and a second output end which are oppositely arranged, wherein the first output end of the hydraulic piston rod is located at the left side, the second output end is located at the right side, when the left end of the first output end moves to the position D1, the first output end is detected by the proximity sensor D1, the proximity sensor D1 sends a signal to the controller, and the controller receives the signal and records the reversing time T_D1The controller controls the pilot electromagnetic valve to change direction, the pilot electromagnetic valve controls the reversing valve to change direction, and the reversing valve further drives the first hydraulic cylinder to change direction. The hydraulic piston rod of the first hydraulic cylinder is shifted to move to the right side, and when the right end of the hydraulic piston rod of the first hydraulic cylinder moves to the position J1, the right end is detected by the proximity sensor J1. The proximity sensor sends a signal to the controller, and the controller receives the signal and records the commutation time point T_J1The controller further switches the movement direction of the hydraulic piston rod through a pilot electromagnetic valve and a reversing valve.

In this embodiment, a proximity sensor may be further disposed at E2 and/or H2, the controller is in signal connection with the proximity sensors E2 and H2, respectively, the proximity sensor E2 or H2 is configured to send a signal to the controller when detecting that the hydraulic piston rod of the second hydraulic cylinder moves to the intermediate position, and the controller may control the second oil supply unit to stop supplying oil to the second hydraulic cylinder through the frequency converter, so that the hydraulic piston rod of the second hydraulic cylinder stops at the intermediate position.

As shown in fig. 30 and 31, the present embodiment further provides a hydraulic injection pump reversing method, which includes the following steps:

s100, adjusting the initial positions of the hydraulic piston rods in the hydraulic cylinders in the length direction of the hydraulic cylinders, and enabling the hydraulic piston rods to be arranged at equal intervals in sequence.

The right end of the hydraulic piston rod of the first hydraulic cylinder (1#) is located at the position of the proximity sensor J1, the right end of the hydraulic piston rod of the second hydraulic cylinder (2#) is located at the position of the proximity sensor H2, and the left end of the hydraulic piston rod of the third hydraulic cylinder (3#) is located at the position of the proximity sensor D3. Thus, the hydraulic piston rods are arranged in the order of 1# to 3# at equal intervals in the longitudinal direction of the hydraulic cylinder. To achieve the above arrangement, the motor may be operated at a low frequency, and when the right end of the hydraulic piston rod of the first hydraulic cylinder is detected by the proximity sensor J1, the proximity sensor J1 sends a signal to the controller, and the controller controls the motor of the first oil supply unit to stop rotating through the first frequency converter, so as to stop supplying oil to the first hydraulic cylinder, and the hydraulic piston rod of the first hydraulic cylinder stops at the position shown in fig. 30. Similarly, the positions of the hydraulic piston rods of the second hydraulic cylinder and the third hydraulic cylinder can be controlled in the same manner, so that the initial state of the hydraulic injection pump is completed.

And S200, delivering hydraulic oil with the same flow rate to the hydraulic cylinders of the working units.

In this embodiment, the first frequency converter, the second frequency converter and the third frequency converter are started synchronously, and each frequency converter has the same output frequency, that is, the hydraulic oil can be delivered to the hydraulic cylinder of each working unit at the same flow rate. Under the condition that the output frequency of each frequency converter is the same, the oil supply units corresponding to each frequency converter have the same real-time displacement, so that each hydraulic cylinder has the same reversing time length and reversing frequency in the initial state.

S300, detecting and comparing the reversing time lengths of the hydraulic cylinders, and enabling the difference value of the reversing time lengths of the hydraulic cylinders to be smaller than a first threshold value.

Specifically, the method mainly comprises the following steps:

measuring and recording the reversing time length of each hydraulic cylinder, wherein the reversing time length is the time interval between two adjacent reversing;

the controller passes the reversing time point T_J1And a commutation time point T_D1The reversing time T of the first hydraulic cylinder can be obtained through calculation₁I.e. T₁＝T_J1-T_D1(ii) a The same method can be adopted to obtain the reversing time length T of the second hydraulic cylinder₂And a commutation period T of the third cylinder₃。

Taking one hydraulic cylinder as a reference hydraulic cylinder, taking the reversing time length of the reference hydraulic cylinder as a reference value, and calculating the difference value between the reversing time lengths of other hydraulic cylinders and the reference value one by one;

the controller compares the reversing time lengths T1, T2 and T3, and takes the first hydraulic cylinder as a reference hydraulic cylinder, and the reversing time length T1 of the reference hydraulic cylinder is defined as a reference value T1₀Calculating the reversing duration of other hydraulic cylinders and the reference value T one by one₀The difference of (a).

If the commutation time length T2 of the second hydraulic cylinder is greater than the reference value T₀And if the difference is greater than the first preset time (e.g., 1 second), which indicates that the flow rate of the hydraulic oil delivered to the second hydraulic cylinder is lower than that of the reference hydraulic cylinder, the flow rate of the hydraulic oil delivered to the second hydraulic cylinder should be increased. The output frequency of the second frequency converter is increased by 1HZ each time, and the commutation duration T2 and the reference value T are measured and compared after each increase₀When the difference is smaller than the first preset time, the output frequency of the second frequency converter is kept.

If the commutation period T2 of the second hydraulic cylinder is less than the reference value T₀And if the difference is greater than the first preset time, the flow path for conveying the hydraulic oil to the second hydraulic cylinder is faster than that of the reference hydraulic cylinder, and the flow path is decreasedThe second hydraulic cylinder delivers a flow rate of hydraulic oil. In this embodiment, the frequency conversion can be realized by gradually reducing the output frequency of the second frequency converter. The output frequency of the second frequency converter is reduced by 1HZ each time, and the commutation period T2 and the reference value T are measured and compared after each reduction₀When the difference is smaller than the first preset time, the output frequency of the second-pass frequency is kept.

And if the frequency of the frequency converter needing to be increased reaches 50HZ (the domestic power frequency is 50HZ), reducing the frequency of the frequency converter corresponding to the hydraulic cylinder with shorter steering duration.

Therefore, the reversing time lengths of the hydraulic cylinders are detected and compared, so that the reversing time length difference of the hydraulic cylinders is smaller than the first threshold value.

S400, detecting and comparing the reversing time points of the hydraulic cylinders, and enabling the time interval fluctuation of the reversing time points of the hydraulic cylinders to be smaller than a second threshold value.

Measuring and recording the reversing time point of each hydraulic cylinder, wherein in the same direction changing process, the reversing time point of the first hydraulic cylinder on the left side is T_D1The reversing time point of the second hydraulic cylinder on the left side is T_D2The reversing time point of the third hydraulic cylinder on the left side is T_D3。

The controller passes the reversing time point T_D1、T_D2、T_D3The time interval for reversing each hydraulic cylinder can be calculated, if the first hydraulic cylinder is taken as a reference hydraulic cylinder, the time interval is calculated

T₁₂＝T_D2-T_D1；

T₁₃＝T_D3-T_D1；

Wherein, T₁₂In the same direction changing process, the direction changing time interval between the first hydraulic cylinder and the second hydraulic cylinder is at the same side; t is₁₃In the same direction changing process, the first hydraulic cylinder and the third hydraulic cylinder are at the same side for the reversing time interval.

Taking the first hydraulic cylinder as a reference hydraulic cylinder, and measuring and recording the reversing time length T1 of the reference hydraulic cylinder, wherein the reversing time length is the time interval between two adjacent reversals; the reversing time point of the reference hydraulic cylinder is taken as a reference valueT₀。

The first hydraulic cylinder and the second hydraulic cylinder will be described as an example.

If T₁₂＞kT₀Where k is the first calibration coefficient, where k is 0.7. Increasing the flow rate of hydraulic oil supplied to the second hydraulic cylinder can be achieved by increasing the output frequency of the second frequency converter by 1HZ each time, and until T is reached₁₂≤kT₀When the flow rate of the hydraulic oil conveyed to the second hydraulic cylinder is recovered to be the same as the flow rate of the hydraulic oil conveyed to the first hydraulic cylinder, the output frequency of the second frequency converter can be increased to be the same as the output frequency of the first frequency converter.

If T₁₂＜fT₀And f is a second calibration coefficient, where f is taken to be 0.3. The flow rate of the hydraulic oil to the other hydraulic cylinder is reduced by reducing the output frequency of the second frequency converter by 1HZ each time and to T₁₂≥f T₀And when the hydraulic oil is not delivered to the other hydraulic cylinders, the flow rate of the hydraulic oil delivered to the other hydraulic cylinders is recovered to be the same as the flow rate of the hydraulic oil delivered to the reference hydraulic cylinder.

Through the operation, the time interval fT of the reversing time points of the first hydraulic cylinder and the second hydraulic cylinder on the left side (or the right side) in the same reversing process can be enabled to be in the same reversing process₀≤T₁₂≤k T₀In this embodiment, it is specifically 0.3T₀≤T₁₂≤0.7T₀。

The first hydraulic cylinder and the third hydraulic cylinder will be described as an example.

If T₁₃＞kT₀Where k takes 1.2. Increasing the flow rate of hydraulic oil to the third hydraulic cylinder may be achieved by increasing the output frequency of the third frequency converter by 1HZ each time, and until T is reached₁₃≤kT₀And when the flow rate of the hydraulic oil conveyed to the third hydraulic cylinder is recovered to be the same as the flow rate of the hydraulic oil conveyed to the first hydraulic cylinder, the output frequency of the third frequency converter can be reduced to be the same as the output frequency of the first frequency converter.

If T₁₂＜fT₀Where f takes 0.8. Reducing the supply of hydraulic oil to the third cylinderThe flow rate can be reduced by 1Hz each time and is increased to T₁₃And when the flow rate is larger than or equal to fT, the flow rate of the hydraulic oil conveyed to the third hydraulic cylinder is recovered to be the same as the flow rate of the hydraulic oil conveyed to the first hydraulic cylinder.

The time interval fT of the reversing time points of the first hydraulic cylinder and the third hydraulic cylinder on the left side (or the right side) in the same reversing process can be enabled through the operation₀≤T₁₂≤k T₀In this embodiment, it is specifically 0.8T₀≤T₁₃≤1.2T₀。

In this embodiment, the time interval of the commutation time points of the first hydraulic cylinder and the second hydraulic cylinder on the same side in the same direction-changing process can be controlled to be within the interval [0.3T ]_0，0.7T₀]To (c) to (d); the time interval of the reversing time points of the first hydraulic cylinder and the third hydraulic cylinder on the same side in the same direction-changing process can be controlled to be in the interval [0.8T ]_0，1.2T₀]In the meantime. Therefore, by detecting and comparing the reversing time points of the hydraulic cylinders, the fluctuation of the time intervals of the reversing time points of the hydraulic cylinders is smaller than the second threshold value.

The apparatus of the present application has been described in detail with reference to the preferred embodiments thereof, however, it should be noted that those skilled in the art can make modifications, alterations and adaptations based on the above disclosure without departing from the spirit of the present application. The present application includes the specific embodiments described above and any equivalents thereof.

Claims

1. A hydraulic injection pump reversing method is used for a hydraulic injection pump and is characterized in that the hydraulic injection pump comprises a plurality of working units, each working unit comprises a hydraulic cylinder, a hydraulic piston rod is arranged in each hydraulic cylinder, and the reversing method mainly comprises the following steps:

detecting and comparing the reversing time lengths of the hydraulic cylinders, and taking one of the hydraulic cylinders as a reference hydraulic cylinder to enable the difference value between the reversing time lengths of the other hydraulic cylinders and the reversing time length of the reference hydraulic cylinder to be smaller than a first threshold value;

and detecting and comparing the reversing time points of the hydraulic cylinders, so that the difference value of the time intervals of the reversing time points of the other hydraulic cylinders on the same side with the reference hydraulic cylinder is smaller than a second threshold value.

2. The method of claim 1, wherein the step of detecting and comparing the commutation durations of the hydraulic cylinders, wherein one of the hydraulic cylinders is used as a reference hydraulic cylinder, and the difference between the commutation durations of the remaining hydraulic cylinders and the commutation duration of the reference hydraulic cylinder is smaller than a first threshold value further comprises:

and adjusting the initial position of each hydraulic piston rod in the hydraulic cylinder in the length direction of the hydraulic cylinder to ensure that the hydraulic piston rods are arranged at equal intervals in sequence.

3. The method of claim 2, wherein the step of detecting and comparing the switch-over durations of the hydraulic cylinders, wherein one of the hydraulic cylinders is used as a reference hydraulic cylinder, and the difference between the switch-over durations of the remaining hydraulic cylinders and the switch-over duration of the reference hydraulic cylinder is smaller than a first threshold value further comprises:

and delivering hydraulic oil with the same flow rate to the hydraulic cylinders of the working units.

4. The method of claim 1, wherein detecting and comparing the commutation durations of the respective hydraulic cylinders, and using one of the hydraulic cylinders as a reference hydraulic cylinder, the step of causing the difference between the commutation durations of the remaining hydraulic cylinders and the commutation duration of the reference hydraulic cylinder to be less than a first threshold value, substantially comprises:

if the reversing duration of the other hydraulic cylinders is greater than the reference value and the difference value is greater than a first preset time, increasing the flow rate of the hydraulic oil conveyed to the other hydraulic cylinders; and if the reversing duration of the other hydraulic cylinders is less than the reference value and the difference value is greater than a first preset time, reducing the flow rate of the hydraulic oil conveyed to the other hydraulic cylinders.

5. A method for reversing a hydraulic injection pump according to claim 4, wherein the steps of detecting and comparing the reversal points of the respective cylinders so that the difference in the time intervals of the reversal points of the same side of the remaining cylinders as the reference cylinder is less than a second threshold value mainly comprise:

measuring and recording the reversing time points of the same side of each hydraulic cylinder;

measuring and recording the reversing time length of the reference hydraulic cylinder, wherein the reversing time length is the time interval between two adjacent reversing; taking the reversing time point of the reference hydraulic cylinder as a reference value T₀Calculating the reversing time points of other hydraulic cylinders one by one and the reference value T₀Time difference T of (d);

if T > kT₀Increasing the flow rate of the hydraulic oil conveyed to the other hydraulic cylinders until T is less than or equal to k T₀When the hydraulic oil is conveyed to the other hydraulic cylinders, the flow rate of the hydraulic oil conveyed to the other hydraulic cylinders is recovered to be the same as the flow rate of the hydraulic oil conveyed to the reference hydraulic cylinder;

if T < fT₀The flow rate of the hydraulic oil to the other hydraulic cylinder is reduced, and when T is more than or equal to f T₀When the hydraulic oil is conveyed to the other hydraulic cylinders, the flow rate of the hydraulic oil conveyed to the other hydraulic cylinders is recovered to be the same as the flow rate of the hydraulic oil conveyed to the reference hydraulic cylinder;

wherein k is a first calibration coefficient, f is a second calibration coefficient, and k is greater than f.

6. A reversing system of a hydraulic injection pump is used for the hydraulic injection pump and is characterized in that the hydraulic injection pump comprises a plurality of oil supply units and a plurality of working units, and the oil supply units are connected with the working units in a one-to-one correspondence manner; each working unit comprises a hydraulic cylinder, and a hydraulic piston rod is arranged in each hydraulic cylinder; the reversing system comprises a controller, a plurality of frequency converters and a plurality of detection units, wherein the controller is respectively connected with the frequency converters, the controller is respectively connected with the plurality of detection units, the frequency converters are correspondingly connected with the oil supply units one by one, the detection units are connected with the working units in a one-to-one correspondence manner and are used for detecting the reversing duration and the reversing time point of the hydraulic cylinder, the controller is used for receiving and comparing the reversing duration and the reversing time point of each hydraulic cylinder, and the flow rate of the hydraulic oil conveyed to the corresponding working unit by the oil supply unit is adjusted by a frequency converter, taking one of the hydraulic cylinders as a reference hydraulic cylinder, enabling the difference value between the reversing duration of the other hydraulic cylinders and the reference hydraulic cylinder to be smaller than a first threshold value, and making the difference value of the time intervals of the reversing time points of the other hydraulic cylinders on the same side with the reference hydraulic cylinder smaller than a second threshold value.

7. The hydraulic infusion pump reversing system according to claim 6, wherein the oil supply unit comprises an electric motor and at least one hydraulic oil pump, the frequency converter is electrically connected with the electric motor, an output end of the electric motor is in transmission connection with the hydraulic oil pump, and the hydraulic oil pump is connected with the hydraulic cylinder through a reversing valve.

8. The hydraulic infusion pump reversing system of claim 6, wherein the work unit further comprises a first hydraulic end and a second hydraulic end symmetrically disposed on both sides of the hydraulic cylinder in a length direction; the hydraulic piston rod is provided with a first output end and a second output end which are oppositely arranged, the first output end is connected with the first hydraulic end, and the second output end is connected with the second hydraulic end.

9. The hydraulic charge pump reversal system of claim 6, wherein the detection unit includes proximity sensors disposed at the ends of travel on either side of the hydraulic piston rod, the proximity sensors being electrically connected to the controller.

10. The hydraulic injection pump reversing system of claim 6, comprising a frame, wherein the frame comprises a first wall plate, a first end plate, a second wall plate and a second end plate which are vertically arranged and sequentially connected end to end, the first wall plate, the first end plate, the second wall plate and the second end plate surround to form an accommodating space, and the accommodating space is divided into a grid shape by a vertically arranged plate.