WO2014044000A1

WO2014044000A1 - Jumping-proof stopping method of dual-cylinder pumping system, dual-cylinder pumping system, and pumping equipment

Info

Publication number: WO2014044000A1
Application number: PCT/CN2012/086135
Authority: WO
Inventors: 李沛林; 曹奎; 王佳茜; 高荣芝; 李华
Original assignee: 中联重科股份有限公司
Priority date: 2012-09-19
Filing date: 2012-12-07
Publication date: 2014-03-27
Also published as: CN102840123A; CN102840123B

Abstract

A jumping-proof stopping method of a dual-cylinder pumping system. The dual-cylinder pumping system comprises a dual-cylinder pumping device having two master cylinders (4, 5) and a hydraulic control system of the dual-cylinder pumping device. The stopping method comprises: first, controlling the dual-cylinder pumping device to stop pumping; second, making at least one chamber among rod chambers (A, C) and rodless chambers (B, D) of the two master cylinders (4, 5) be in communication with an oil tank or a return oil path. A dual-cylinder pumping system and pumping equipment. On the basis of the dual-cylinder pumping system, a pressure releasing step is added, so that the chambers of the master cylinders of the dual-cylinder pumping system are in low pressure or zero-pressure state, unexpected jumping of the piston rod of the master cylinder caused by the high pressure oil is effectively prevented, and during maintenance of the dual-cylinder pumping system, the safety of maintenance personnel is effectively ensured.

Description

Double cylinder pumping system anti-rolling shutdown method, double cylinder pumping system and pumping equipment

The invention relates to a control method of a two-cylinder pumping system, in particular to a method for preventing a turbulence of a two-cylinder pumping system. Further, the present invention relates to a two-cylinder pumping system capable of implementing the anti-rolling shutdown method. Furthermore, the invention relates to a pumping device comprising the two-cylinder pumping system. Background technique

Viscous materials such as concrete and mud are commonly used construction materials in the field of engineering construction. These viscous materials are typically pumped through a two-cylinder pumping system, which generally includes a two-cylinder pumping device and its hydraulic control. system. For the two-cylinder pumping device, the main structure can refer to the concrete double-cylinder pumping device widely used in engineering construction. This two-cylinder pumping device is controlled by its hydraulic control system, so that it will be thickened by pressure. The material is continuously transported along the pipeline. Specifically, the two-cylinder pumping system generally can drive a hydraulic pump to form a hydraulic oil having a certain pressure by an electric motor (or an internal combustion engine), and drive the main cylinder to drive the pistons in the two conveying cylinders to alternately reciprocate, so that the viscous material continuously The transfer cylinder is sucked from the hopper and transported to the construction site through the transfer pipe.

In order to facilitate understanding, the main structure and disadvantages of the twin-cylinder pumping system will be briefly described below with reference to Figs. 1 and 2, taking a concrete two-cylinder pumping device and its hydraulic control system as an example.

Specifically, referring to Figure 1, a concrete two-cylinder pumping apparatus generally includes two main cylinders 4, 5 (also referred to as "master cylinders"), two delivery cylinders (also known to those skilled in the art as "cylinders"). Two pumping pistons 12, 13, two oscillating cylinders, a hopper and a distribution valve, wherein the oscillating cylinder, the hopper, the distribution valve, etc. are not shown in Fig. 1, which are known components, which are not described later, and these components are assembled together. , constitute a concrete two-cylinder pumping device. In the case of the hydraulic control system of the concrete twin-cylinder pumping unit, it mainly refers to the corresponding hydraulic control circuit connected to the main cylinder and the oscillating cylinder.

As shown in Fig. 1, the rod chambers C and C of the two main cylinders 4, 5 are connected to each other, and the rodless chambers B and D are respectively connected to the main reversing valve 3, and the main reversing valve 3 is connected to the oil inlet passage. And the oil tank, through the reversing direction of the main reversing valve 3, selectively connecting the rodless chamber D of the first main cylinder 4 of the two main cylinders with the oil inlet passage, and the rodless chamber B of the second main cylinder 5 The tank is connected to the tank, or the rodless chamber D of the first master cylinder 4 is communicated with the tank, and the rodless chamber B of the second master cylinder 5 is in communication with the oil inlet passage. Since the rod chambers A, C of the two main cylinders 4, 5 are connected to each other and closed with hydraulic oil, the hydraulic oil in the rod chambers A, C of the two main cylinders 4, 5 acts as a transmission medium, through Alternately, the rodless chambers B, D of the two main cylinders 4, 5 are fed with oil so that the two main cylinders 4, 5 can be alternately expanded and contracted. Two pumping pistons 12, 13 are respectively located in the two conveying cylinders and are respectively connected with the piston rods of the main cylinders 4, 5 to drive the respective pumping pistons 12, 13 to alternately move to alternately pump or pump. Viscous material, such as concrete.

Further, FIG. 1 shows some more specific details of the conventional concrete double-cylinder pumping device. Specifically, the outer peripheral faces of the pumping pistons 12, 13 are respectively provided with inner circumferential surface sealability for the respective transfer cylinders. Sliding mating seals 14, 15. A water tank 16 is installed between the two main cylinders 4, 5 and the two transfer cylinders, and the piston rods of the two main cylinders 4, 5 are connected to the corresponding pumping piston 12 through the water tank 16, 13, during the pumping operation The two pumping pistons 12, 13 are alternately telescoped in the corresponding conveying cylinders, wherein the water tank 16 is mainly used for cooling, because the pumping pistons 12, 13 are constantly rubbed with the corresponding conveying cylinders, so that they can pass through the water tank 16 The cooling water or coolant cools the pumping pistons 12, 13. The main reversing valve 3 in the hydraulic control system of the above-described concrete two-cylinder pumping device is connected to the intake oil passage. As is well known to those skilled in the art, the intake oil passage generally includes driving by a power unit (engine or motor, etc.). The hydraulic pump 1 , wherein the input port of the hydraulic pump 1 is in communication with the oil tank, the output port is connected to the oil inlet P of the main reversing valve 3, and the output port of the hydraulic pump 1 and the oil inlet P of the main reversing valve 3 An overflow oil passage including a relief valve 2 is generally connected to the oil passage for overpressure protection.

Further, the two main cylinders 4, 5 are also respectively connected with the buffering communication oil passages, that is, the buffering oil passages are respectively connected to the regions near the two ends of the cylinder barrels of the respective main cylinders 4, 5, that is, the first main cylinder 4 in FIG. The left end region is provided with a first shut-off valve 6 (typically a ball valve) and a rodless cavity buffer oil passage of the check valve 8, and a rod cavity buffer oil passage provided with a check valve 10 in the right end region; The left end region of the cylinder 5 is provided with a second shutoff valve 7 (typically a ball valve) and a rodless cavity buffer oil passage of the check valve 9, and a rod cavity buffer oil passage provided with a check valve 11 in the right end region. This kind of buffer oil circuit is often used in the prior art concrete double-cylinder pumping device, which is mainly used for buffering the piston rod of the main oil cylinder during the telescopic movement, preventing the piston of the main oil cylinder from striking the main end at the end of the telescopic stroke. Cylinder of the cylinder. For example, in the operation process of the buffer oil passage on the first main cylinder 4, when the rod chamber C of the first main cylinder 4 is oiled and the rod chamber D is returned to the oil, the piston rod of the first main cylinder 4 is directed to the left. Side movement, when running to the left end area close to the bottom of the cylinder, at this time, the two ends of the rodless chamber buffer oil passage are respectively connected with the rodless chamber D and the rod chamber C of the first main cylinder 4, if there is oil of the rod chamber C If the pressure is too high and the speed of movement of the piston rod is too fast, the first shutoff valve 6 can be opened, so that part of the hydraulic oil in the rod chamber C of the first main cylinder 4 flows through the check valve 8 and the first shutoff valve 6 to none. The rod cavity D, so that the oil pressure in the rodless chamber D is increased to some extent, increasing the movement resistance of the piston rod of the first main cylinder 4, so that the piston rod of the first main cylinder 4 can move relatively gently to the contraction Return to the end of the stroke to avoid too much impact on the bottom of the tank. Similarly, in the case of the rod cavity buffer oil passage in the right end region of the first master cylinder 4, since the piston rod of the first master cylinder 4 is used to push the concrete outwardly during the extension process, the oil pressure is large, Therefore, only the check valve 10 is provided on the rod buffer buffer on the right end, once the piston on the piston rod of the first main cylinder 4 moves to the rod cavity buffer When the rod chamber C and the rodless chamber D are connected to both ends of the oil passage, the rod chamber buffer oil passage performs the same function as the above operation, and will not be described herein. In addition, each of the above buffer oil passages is generally provided with a throttle valve, which mainly limits the buffer flow rate, and prevents the flow of hydraulic oil between the rodless chamber D and the rod chamber C from being excessive.

The main structure of the two-cylinder pumping system is described above with reference to Fig. 1 taking a concrete double-cylinder pumping system as an example. It should be noted that the two master cylinders 4, 5 are not limited to the two masters shown in Fig. 1. The rod chambers A, C of the cylinders 4, 5 are connected to each other to form a communication chamber. Alternatively, the rodless chambers B and D of the two main cylinders 4, 5 may be connected to each other to form a communication chamber. In this case, the rod chambers A, C of the two main cylinders 4, 5 respectively form a drive chamber and are connected to the reversing valve. In the actual two-cylinder pumping device, the rodless chambers B, D or the rod chambers A, C of the two main cylinders 4, 5 can be selectively used as communication chambers by switching, which is generally carried out by a two-cylinder pumping system ( For example, a concrete double-cylinder pumping system is commonly used for high and low pressure switching valves, such as the high and low pressure switching valves formed by six two-way cartridge valves as shown in FIG. It should be noted here that the high and low pressure switching valves employed in the two-cylinder pumping system can take many forms and are not limited to the specific form shown in FIG.

However, the above-mentioned prior art two-cylinder pumping system has certain safety hazards during maintenance and repair, and is prone to safety accidents.

Specifically, referring to Fig. 1, in order to prevent backflow of the pumped viscous material (e.g., concrete), when the main reversing valve 3 is in the neutral position, the working ports A, B of the main reversing valve 3 are cut off ( That is, the main reversing valve 3 used in FIG. 2 is an M-type three-position four-way reversing valve), therefore, when the pumping is stopped, the first main cylinder 4 has the rod chamber C and the rodless chamber D and the second main The hydraulic oil in the rod chamber A and the rodless chamber B of the cylinder 5 is closed, and high pressure oil is often enclosed in the rod chamber and the rodless chamber. Sometimes even if the machine is shut down, the high-pressure oil will not be quickly discharged, which will bring certain safety hazards. Especially during maintenance and repair, the high-pressure hydraulic oil enclosed in the rod cavity and the rodless cavity may be in the During the maintenance and repair operation, the piston rod of the main cylinder is moved forward, and the operation of the emergency maintenance personnel is safe.

In a two-cylinder pumping system with high and low pressure switching valves, this safety problem due to high pressure oil sealing is more serious. For example, see Figure 2, where the hydraulic control system of the two-cylinder pumping unit uses a high and low pressure switching valve consisting of six two-way cartridge valves 17-22, three of which are two-way cartridge valves 17, 18, 19 The hydraulic control port communicates with the first working port A1 of the two-position four-way electromagnetic reversing valve 23, the hydraulic control port of the three two-way cartridge valves 20, 21, 22 and the two-position four-way electromagnetic reversing valve 23 The second working port B1 is connected, the oil return port of the electromagnetic reversing valve 23 is connected to the oil cylinder, and the oil inlet port is connected to the pumping oil path and the distribution oil path through the oil passages via the check valves 24, 25 respectively, so that the oil pump can be driven from the pump Hydraulic oil with relatively high oil pressure is introduced into the oil supply road or the distribution oil passage as the hydraulic oil of the above-mentioned two-way cartridge valve to realize high-low pressure conversion of the two-cylinder pumping device (for example, a concrete two-cylinder pumping device). When the electromagnet DT1 of the electromagnetic reversing valve 23 is de-energized and the electromagnetic reversing valve 23 is in the left position, the hydraulic control chambers of the two-way cartridge valves 20, 21, 22 pass through the hydraulic control oil lock The liquid control chamber of the two-way cartridge valves 17, 18, 19 is in communication with the fuel tank, and the three two-way cartridge valves 17, 18, 19 function as hydraulic oil on the working oil lines of the two main cylinders 4, 5. Opened downward, wherein the rodless cavity of the main cylinders 4, 5 is communicated through the two-way insertion valve 18, and when the main reversing valve 3 is in the left position, the hydraulic oil of the first working port A of the main reversing valve 3 passes through the two-way The cartridge valve 19 is input to the rod chamber A of the main cylinder 5, and the return hydraulic oil of the main cylinder 4 having the rod chamber C flows back to the second working port B of the main diverter valve 3 via the two-way cartridge valve 17; When the main reversing valve 3 is in the right position, the hydraulic oil of the second working port B of the main reversing valve 3 is input to the rod chamber C of the main cylinder 4 via the two-way cartridge valve 17, and the rod chamber of the main cylinder 5 is provided. The return hydraulic oil in A flows back to the second working port A of the main reversing valve 3 via the two-way cartridge valve 19, thereby realizing the low-pressure pumping state of the two-cylinder pumping system (at this time, due to the main cylinder 4, The rod cavity of 5 is alternately used as the driving cavity during the telescopic process, and the effective working area of the hydraulic oil of the main cylinder piston in the rod cavity is relatively small, and the pumping force generated by the same oil pressure Smaller, so-called low-pressure pumping state). When the electromagnet DT1 is energized and the electromagnetic reversing valve 23 is in the right position, the hydraulic control chambers of the two-way cartridge valves 17, 18, 19 are locked by the hydraulic oil control, and the liquid control of the two-way cartridge valves 20, 21, 22 The cavity communicates with the oil tank, and the rodless chambers D and B of the main cylinders 4, 5 are respectively connected with the working oil ports A and B of the main reversing valve through the two-way cartridge valves 20 and 22, and the rod chambers A and C are inserted through the two-way plug. The valve 21 is communicated with each other, and the twin-cylinder pumping system is in a high-pressure pumping state.

As described above, when the pumping is stopped, the first main cylinder 4 has the rod chamber C and the rodless chamber D and the second main cylinder

There may be high pressure oil enclosed in the rod chamber A and the rodless chamber B, especially when replacing the seals 14 and 15 of the pumping pistons 12, 13, the shutoff valve 6 is required to be closed, and then driven. The main cylinders 4, 5 cause the pumping pistons 12, 13 to alternately return to the water tank 16, respectively. Since the pistons of the main cylinders 4, 5 are retracted to the limit position, the system pressure will rise sharply, and then the drive will be stopped. The high oil pressure hydraulic oil is enclosed in some of the chambers of the main cylinders 4, 5. At this time, if the machine is shut down, since the pumping oil line and the distribution oil line are unloaded, the liquid control chambers on the six cartridge valves have no control pressure. Under the action of the pressure oil in the main cylinder, the cartridge valve will open, resulting in The rod chambers and the rodless chambers of the main cylinders 4, 5 are connected. Due to the flow of oil, the piston rods of the main cylinders 4, 5 are often moved forward, and the pumping pistons 12, 13 are specifically represented after the shutdown. It will move forward a certain distance, and the flow of such hydraulic oil often does not reliably eliminate the oil pressure, and there may still be safety hazards when the maintenance personnel repair. In addition, if the turbulence distance is too large, the pumping piston may re-enter the delivery cylinder and the piston seal cannot be replaced.

In order to solve this problem, the following solutions are commonly used in the prior art: As shown in FIG. 2, when the machine is stopped, the hydraulic control system is not de-energized, and the accumulator that distributes the oil path is not automatically unloaded, therefore, the three in the cartridge valve The liquid control chamber of the cartridge valve always has pressure, and the high and low pressure state of the system remains unchanged. Therefore, the rod chamber of the main cylinders 4, 5 is not connected to the rodless chamber. At this time, the main cylinder is driven again to unload the cylinder chambers, and then the accumulator of the distribution oil passage is manually discharged. However, the prior art has high requirements on the operator, and when the operation steps are wrong, it is easy to cause a safety accident. The distribution oil accumulator is not automatically unloaded, and there are certain safety hazards and does not meet the requirements of relevant national standards. In addition, if the hydraulic system does not lose power during maintenance and maintenance, it may cause safety hazards such as malfunction of the actuator.

In view of the above-discussed deficiencies of the prior art, it is desirable to provide a shutdown operation method for a two-cylinder pumping system that can effectively solve or alleviate the above problems. Summary of the invention

The technical problem to be solved by the present invention is to provide a two-cylinder pumping system anti-rolling shutdown method, which can effectively prevent the piston rod of the main cylinder from swaying after stopping, thereby ensuring Maintenance and maintenance work safety.

Further, the technical problem to be solved by the present invention is to provide a two-cylinder pumping system capable of relatively effectively implementing the anti-rolling function of the piston rod of the main cylinder after stopping, thereby ensuring maintenance work. Security.

In addition, the technical problem to be solved by the present invention is to provide a pumping device, which can relatively effectively realize the anti-rolling function of the piston rod of the main cylinder after stopping, thereby ensuring maintenance and repair. The safety of work.

In order to solve the above technical problem, the present invention provides a two-cylinder pumping system anti-rolling shutdown method, the two-cylinder pumping system comprising a two-cylinder pumping device having two main cylinders and a hydraulic pressure of the two-cylinder pumping device a control system, the shutdown method comprising the steps of: first, controlling the two-cylinder pumping device to stop pumping operation, thereby causing the rod chamber and the rodless chamber of the two main cylinders to have an oil passage and returning The oil and oil passages are all in an off state; secondly, at least one of the rod chamber and the rodless chamber of the two main cylinders is communicated with the oil tank or the return oil passage.

Preferably, in the second step, at least one of the rod chamber and the rodless chamber of the two main cylinders is brought into communication with the fuel tank or the return oil passage for a predetermined time.

Specifically, the predetermined time is 1-5 seconds.

Preferably, in the first step, the two-cylinder pumping device is controlled to switch to stop the pumping operation in the low-pressure pumping state.

Preferably, in the first step, in a case where one pumping piston of the two-cylinder pumping device is stopped in the water tank of the two-cylinder pumping device, the two-cylinder pumping device is controlled to stop pumping. operation.

More preferably, in the first step, in a case where it is detected that one of the pumping pistons of the two-cylinder pumping device is stopped in the water tank, the two-cylinder pumping device is controlled to stop the pumping operation. Typically, the two-cylinder pumping system is a concrete two-cylinder pumping system that is a concrete two-cylinder pumping device.

Preferably, in the second step, all of the main cylinders of the two-cylinder pumping device have a rod chamber and a rodless chamber in communication with the fuel tank or the return oil passage.

Based on the technical solution of the above shutdown method, the present invention provides a two-cylinder pumping system including a two-cylinder pumping device and a hydraulic control system thereof, the two-cylinder pumping device comprising two main cylinders, wherein The hydraulic control system further includes a pressure relief oil passage, one end of the pressure relief oil passage is connected to the oil tank or the return oil passage, and the other end is connected to the rod chamber and the rodless chamber of the two main oil cylinders via corresponding oil passages. At least one of the chambers, the pressure relief oil passage is provided with an on-off valve to enable control of at least one of the rod chamber and the rodless chamber of the master cylinder when the two-cylinder pumping system is shut down The fuel tank or return oil passage is connected.

Typically, the hydraulic control system includes a main reversing valve and a high and low pressure switching valve, and respective interfaces of the high and low pressure switching valves are respectively connected to the rod chamber and the rodless chamber of the two main cylinders, and the main exchange The first working port and the second working port of the valve.

Specifically, the main reversing valve is an M-type three-position four-way reversing valve or a zero-position three-position four-way reversing valve, and the oil inlet of the main reversing valve is connected to the pumping oil passage and the oil return port. Connected to the oil tank, the first working oil port and the second working oil port are respectively connected to the two main oil cylinders via the high and low pressure switching valves.

Typically, the high and low pressure switching valve includes first to sixth two-way cartridge valves, and the hydraulic control ports of the first to sixth two-way cartridge valves are respectively connected to the hydraulic control oil passage, and the hydraulic control oil passage includes two a four-way reversing valve, the oil inlet of the two-position four-way reversing valve is respectively connected to the pumping oil passage and the distribution oil passage of the hydraulic control system via a one-way valve, and the oil return port is connected to the oil tank, a working oil port is connected to the hydraulic control ports of the fourth to sixth two-way cartridge valves, and a second working oil port is connected to the hydraulic control ports of the first to third two-way cartridge valves, wherein two The respective reverse ports of the one-way valves are in communication with the oil inlet of the two-position four-way selector valve.

Preferably, the other end of the pressure relief oil passage is connected to any one of the oil passages between the high and low pressure switching valves and the two master cylinders.

In another preferred form, the other end of the pressure relief oil passage is respectively connected to a reverse port of the first check valve and the second check valve, and a forward port of the first check valve is connected to the a second working port of the main reversing valve, and a forward port of the second one-way valve is coupled to the first working port of the main reversing valve.

Preferably, the on-off valve on the pressure relief oil line is an electrically controlled on-off valve.

Specifically, the electronically controlled on-off valve is a normally open two-position two-way electromagnetic reversing valve or a normally closed two-position two-way electromagnetic reversing valve. More preferably, the water tank of the two-cylinder pumping device is provided with position detecting means for detecting whether the pumping piston of the two-cylinder pumping device is located in the water tank.

Further, the present invention provides a pumping apparatus, wherein the pumping apparatus comprises the twin-cylinder pumping system described in any one of the above aspects.

Through the above technical solution, the anti-cracking shutdown method of the double-cylinder pumping system of the present invention and the double-cylinder pumping system capable of realizing the shutdown method are uniquely added to the existing two-cylinder pumping system shutdown method. The pressure relief step can make the chambers of the main cylinder of the two-cylinder pumping system be in a low pressure or no pressure state, effectively preventing the piston rod of the main cylinder from accidentally tumbling due to the closed high pressure oil, and relatively effectively ensuring The safety of the maintenance personnel during the maintenance and repair work of the two-cylinder pumping system. The anti-turbine shutdown method of the twin-cylinder pumping system of the invention has universal applicability, in particular, can be effectively applied to a two-cylinder pumping system with high and low pressure switching valves, which relatively reliably prevents the shutdown of the two-cylinder pumping system When the piston rod of the main cylinder is tilted, the two-cylinder pumping system effectively removes the pressure of each chamber of the main cylinder during the shutdown, making the two-cylinder pumping system safer. The pumping apparatus of the present invention includes the two-cylinder pumping system, and thus it also has the above advantages.

Other features and advantages of the invention will be described in detail in the detailed description which follows. DRAWINGS

The following drawings are provided to provide a further understanding of the present invention, and are a part of the specification, which is used to explain the invention together with the specific embodiments described below, but the scope of the invention is not limited to the following drawings and embodiments. the way. In the drawing:

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a schematic diagram of a prior art two-cylinder pumping system showing a two-cylinder pumping unit and its hydraulic control system for the two-cylinder pumping system.

2 is a schematic diagram of a prior art double cylinder pumping system in which a high and low pressure switching valve is added to the hydraulic control system.

Figure 3 is a schematic view showing the structure of a two-cylinder pumping system according to a first embodiment of the present invention.

4 is a schematic structural view of a two-cylinder pumping system according to a second embodiment of the present invention.

Fig. 5 is a structural schematic view of a two-cylinder pumping system according to a third embodiment of the present invention.

Figure 6 is a structural schematic view of a two-cylinder pumping system in accordance with a fourth embodiment of the present invention.

Figure 7 is a block diagram showing the steps of the anti-cracking shutdown method of the two-cylinder pumping system of the present invention.

Description of the reference signs:

1 hydraulic pump; 2 overflow valve; 3 main reversing valve; 4 main cylinder;

5 main cylinder; 6 first stop valve;

7 second stop valve; 8, 9, 10, 11 check valve;

12 pumping piston; 13 pumping piston;

14 seals; 15 seals;

16 water tank; 17 first two-way cartridge valve;

18 second two-way cartridge valve; 19 third two-way cartridge valve;

20 fourth two-way cartridge valve; 21 fifth two-way cartridge valve;

22 sixth two-way cartridge valve; 23 two-position four-way electromagnetic reversing valve;

24, 25 check valve; 26 normally open two-position two-way electromagnetic reversing valve;

27 first check valve; 28 second check valve;

29 normally closed two-position two-way electromagnetic reversing valve; 30 first position detecting device;

31 second position detecting device; 32 high and low pressure switching valve;

33 pressure relief oil circuit. detailed description

The specific embodiments of the present invention are described in detail below with reference to the accompanying drawings. .

In order to make the description of the specific embodiments more specific and specific to facilitate the understanding of those skilled in the art, the specific embodiments of the present invention are mainly described below by taking a concrete double cylinder pumping system as an example. Accordingly, in the following description, the anti-twisting shutdown method of the twin-cylinder pumping system of the present invention may be referred to as "the concrete double-cylinder pumping system anti-turbation shutdown method", and the twin-cylinder pumping system may be referred to as "concrete twin-cylinder" Pumping system" and the like, but it is apparent to those skilled in the art that the main structure of the two-cylinder pumping device and its hydraulic control system according to the present invention is similar to that of the concrete two-cylinder pumping device and its hydraulic control system. The specific embodiments described below can be universally applied to the shutdown control of a fluid material two-cylinder pumping system, such as the control of a two-cylinder pumping system such as mud or mortar.

The structural form of the concrete double-cylinder pumping device and its hydraulic control system itself is well known to those skilled in the art, and has been briefly described above, and therefore, in the description of the technical solution of the following text, the well-known structure will be omitted. The description focuses on the key technical concepts of the present invention. In addition, some other well-known components of the concrete two-cylinder pumping device, such as a distribution valve, a swing cylinder, a hopper, etc., are omitted in FIGS. 4 to 6, but do not affect Those skilled in the art will understand the technical solutions of the present invention. The distinction between "first" and "second" and the like is for convenience of description and does not constitute a limitation of the scope of the present invention.

Hereinafter, a specific embodiment of the anti-cracking shutdown method of the twin-cylinder pumping system of the present invention will be described first, and then a specific embodiment of the twin-cylinder pumping system of the present invention will be described. In the description process, the related operation process will be described. Typical hydraulics used and some possible variants.

Referring to Figure 7, the anti-trick shutdown method of the dual-cylinder pumping system of the present invention is applicable to a two-cylinder pumping system comprising a two-cylinder pumping device having two main cylinders 4, 5 and The hydraulic control system of the two-cylinder pumping device, the anti-cracking shutdown method of the two-cylinder pumping system includes: a first step of controlling a two-cylinder pumping device of the two-cylinder pumping system to stop pumping operation, thereby When the pumping operation is stopped, the rod chamber and the rodless chamber of the two main cylinders 4, 5 and the oil inlet and return oil passages are both in an off state; the second step is to make the two main cylinders 4, At least one of the rod chamber and the rodless chamber of 5 is in communication with the fuel tank or the return oil passage.

Preferably, in the second step, at least one of the rod chamber and the rodless chamber of the two main cylinders 4, 5 may be connected to the fuel tank or the return oil passage for a predetermined time (for example, 1-5) Seconds, this effectively prevents material in the material transfer line, such as concrete backflow (see description of the twin-cylinder pumping system below). In addition, although FIGS. 3 to 6 each show that the pressure relief oil passage 33 is directly connected to the fuel tank, it is obvious to those skilled in the art that the pressure relief oil passage 33 is connected to the oil return passage of the fuel tank or the hydraulic control system. To the purpose of pressure relief.

It should be understood here that whether in the high-pressure pumping state or the low-pressure pumping state of the two-cylinder pumping device, in the rod chamber and the rodless chamber of the two main cylinders 4, 5 when the pumping operation is stopped The low pressure oil or high pressure oil will be closed for the following reasons: For example, as shown in Fig. 3, if the double cylinder pumping device is in the low pressure pumping state at this time, it is assumed that the rod chamber C of the first main cylinder 4 is oiled at this time. The rod chamber A of the second main cylinder 5 is returned to the oil, and the rodless chambers B and D of the first main cylinder 4 and the second main cylinder 5 are connected to each other. In FIG. 3, the piston rod of the first main cylinder 5 has moved. When the pumping operation is stopped at the predetermined position on the left end, the main reversing valve 3 is quickly switched to the neutral position, the rod chamber C of the first main cylinder 4 is stopped, and the oil returning from the rod chamber A of the second main cylinder 5 is also cut off. However, the piston rods of the first and second master cylinders 4, 5 have a moving inertia which maintains the inertia of the forward movement, so that the hydraulic oil of the rod chamber A of the second master cylinder 5 is pressed to prevent the first and second master cylinders. 4, 5 movement of the piston rod, the piston rods of the first and second main cylinders 4, 5 are instantaneously stopped, 4 through the first master cylinder rod chamber. a communication chamber formed by the rodless chambers B, D of the first main cylinder 4 and the second main cylinder 5, and a hydraulic oil corresponding to the corresponding oil pressure enclosed in the rod chamber C of the first main cylinder 4 for the first and second The action of the piston rods of the main cylinders 4, 5 forms a force balance, and the two main cylinders 4, 5 actually form a hydraulic linkage structure. In this case, although the hydraulic oils enclosed in the rod chambers and the rodless chambers of the two main cylinders 4, 5 have oil pressure, as long as any one chamber is depressurized, the other chambers are also balanced due to the force. Will relieve pressure. Therefore, just stop pumping The object of the present invention can be achieved by depressurizing any of the rod chambers and the rodless chambers of the two main cylinders 4, 5 during operation.

Specifically, for example, as shown in FIG. 3, if the double cylinder pumping device is in the low pressure pumping state at this time, it is assumed that the rod chamber C of the first master cylinder 4 is oiled at this time, and the rod chamber A of the second master cylinder 5 is Returning oil, the rodless chambers B, D of the first main cylinder 4 and the second main cylinder 5 serve as communication chambers, and when the pumping operation is stopped, the hopper is no longer supplied, since the oil pressure depends on the load, the first main cylinder 4 The hydraulic oil in the rod chamber C needs to drive the two piston rods of the first main cylinder 4 and the second main cylinder 5, so that the oil pressure is the highest; the communication chamber (ie, the first main cylinder 4 and the second main cylinder 5 are absent) The hydraulic oil in the rod chambers B, D) only needs to drive the piston rod of the second main cylinder 5, and the hydraulic oil in the rodless chamber has a large effective working area on the piston rod, so the oil pressure in the communication chamber is lower. State, but there is still a certain oil pressure (may be called medium oil pressure); the rod chamber A of the second master cylinder 5 is connected to the tank via the main reversing valve 3, the oil pressure is the lowest (approximately zero), if in the The piston rod of a main cylinder 4 moves to the left end of the predetermined position shown in FIG. The double cylinder pumping device is stopped, as described above, the rod chamber A of the second main cylinder 5 stops returning to the oil, and the piston rod of the second main cylinder 5 is caused to have the rod chamber A of the second main cylinder 5 due to the inertia of motion. The hydraulic oil is pressurized to form an oil pressure, that is, the oil pressure in the rod chamber A of the second main cylinder 5 is instantaneously increased, and the first main cylinder 4 has a rod chamber. The communication chamber and the oil pressure of the rod chamber A of the second main cylinder 5 exert a force on the piston portions of the piston rods of the first main cylinder 4 and the second main cylinder 5, so that the first main cylinder 4 and the second The piston rod of the master cylinder 5 is stopped in a force balanced state. In this case, in order to prevent the hydraulic pressure of the hydraulic oil enclosed in the main cylinders 4, 5 from being unbalanced due to an accident during the maintenance and repair process, the piston rod is swayed, and the oil pressure in the main cylinders 4, 5 needs to be unloaded. go with. In the high pressure pumping state, the corresponding oil pressure change state is similar, and will not be described here.

In order to ensure that the piston rod is prevented from being swayed, the oil pressure in any of the rod chambers and the rodless chambers of the two main cylinders 4, 5 can generally be removed during pressure relief, due to the two main cylinders 4 The hydraulic linkage structure of the piston rod of 5 and the force balance, the oil pressure in other chambers will be naturally removed. Therefore, within the scope of the above-described technical idea of the present invention, any one or all of the cavity and the rodless cavity of the master cylinders 4, 5 are provided as long as the operation of the pumping operation is stopped according to the dual pump pumping device. The hydraulic pressure of the indoor closed hydraulic oil is removed, which are all within the scope of the present invention. Most preferably, all of the main cylinders 4, 5 of the two-cylinder pumping unit can be connected to the tank or the return oil passage, which can most reliably prevent turbulence and prevent accidental reasons. The oil pressure in some of the rod chambers or the rodless chambers of the two main cylinders 4, 5 is not removed.

Within the scope of the technical idea of the above-described anti-tip stop method of the present invention, when controlling the two-cylinder pumping device to stop pumping, the two-cylinder pumping device can be controlled in the low-pressure pump by controlling (for example, through the high-low pressure switching valve 32). Stop in the delivery state. As described above, the main problem existing in the prior art is the first main cylinder 4 or the second main cylinder at the time of shutdown. The piston rod of 5 may be turbulent due to high oil pressure, resulting in a safety hazard when replacing the first and second pumping pistons 12, 13 of the seals 14, 15. When the hybrid seals 14, 15 are replaced, it is necessary to drive the first and second master cylinders 4, 5 (generally in a jog mode of operation) such that the respective pumping pistons are retracted back to the water tank 16. When the first and second master cylinders 4, 5 are jogged in the high pressure pumping state, when the master cylinders 4, 5 are in position, the three chambers of the master cylinders 4, 5 have a relatively high oil pressure (for example, it may be a figure The second main cylinder 5 of the third main cylinder 5 has a rod chamber, a rodless chamber B, and a rod chamber C) of the first main cylinder. When the main cylinder is jogged in a low pressure state, only one of the rod chamber and the rodless chamber of the main cylinders 4, 5 has a high pressure (refer to the above analysis, for example, the first main cylinder shown in FIG. 3 Rod cavity C). Therefore, when the engine is stopped under high pressure, the piston rod of the pumping cylinder is more likely to be turbulent. When the engine is stopped under low pressure, the piston rod is less likely to move. Therefore, it is particularly necessary to control the technical solution of the two-cylinder pumping device to stop the pumping operation in the low-pressure pumping state within the scope of the technical idea of the present invention, which can be used as a preferred control. The way can also constitute an independent control method. In the case where it is an independent control mode, as described above, it is possible to effectively reduce the possibility of the piston rod of the first master cylinder 4 or the second master cylinder 5 being swayed, even if it does not have any subsequent pressure relief. Steps can also solve security problems relatively effectively. In the case where it is a preferred control mode, when the hydraulic pressure is subsequently unloaded to prevent the piston rod of the first main cylinder 4 or the second main cylinder 5 from being pulsated, due to the two main cylinders 4 in the low pressure pumping state, The overall oil pressure of 5 is relatively low, so the pressure relief operation is easier and the safety after pressure relief is more reliable.

In order to facilitate the replacement of the seals 14, 15 of the pumping pistons 12, 13, preferably, in the first step described above, a pumping piston 12, 13 of the twin-cylinder pumping device is stopped at the twin-cylinder pump In the case of the water tank 16 of the delivery device, the two-cylinder pumping device that controls the two-cylinder pumping system stops the pumping operation. It will be apparent to those skilled in the art that since the first pumping piston 12 and the second pumping piston 13 move alternately, only one pumping piston 12 or 13 can be stopped in the water tank 16 at a time. Further preferably, based on the above technical solution, a corresponding detecting step may be added, that is, when a pumping piston 12, 13 of the two-cylinder pumping device is detected, stopping in the water tank 16 of the two-cylinder pumping device In the case of the two-cylinder pumping device controlling the two-cylinder pumping system, the pumping operation is stopped.

Further, in the above technical idea of the shutdown method of the twin-cylinder pumping system of the present invention, preferably, at least one of the rod chamber and the rodless chamber of the two main cylinders 4, 5 is made with a fuel tank or The return oil passage is connected for 1-5 seconds.

The above describes a specific embodiment of the anti-throttle shutdown method of the twin-cylinder pumping system of the present invention. The following describes a specific embodiment of the twin-cylinder pumping system for implementing the above-described shutdown method. It should be emphasized here that since the structure of the two-cylinder pumping device of the two-cylinder pumping system and the hydraulic control system thereof are well known, the following is known for known structures or The elements are not described again, but only the structures embodying the technical idea of the present invention are described.

Referring to Figures 3 to 6, the twin-cylinder pumping system of the present invention comprises a two-cylinder pumping device and a hydraulic control system thereof, the two-cylinder pumping device comprising two main cylinders 4, 5, wherein the hydraulic control system Also included is a pressure relief oil passage 33, one end of which is connected to the oil tank or the return oil passage, and the other end is connected to the two main cylinders 4, 5 with a rod chamber and a rodless via a corresponding oil passage. At least one chamber in the chamber, the pressure relief oil passage 33 is provided with an on-off valve to enable control of the rod chamber and the rodless chamber of the main cylinders 4, 5 when the two-cylinder pumping system is shut down At least one chamber is in communication with the fuel tank or return oil passage.

It should be understood that, within the scope of the technical idea of the present invention, the two-cylinder pumping system of the present invention is not limited to the specific form shown in FIGS. 3 to 6, and may have various embodiments, for example, see FIG. It can be shown that the pressure relief oil passage 33 provided with the on-off valve can be respectively connected to the rod chamber and the rodless chamber of each of the two main cylinders 4, 5, so that when the pressure relief is performed, the corresponding pressure relief oil passage can be made as needed. 33 is turned on to relieve pressure. These modifications are intended to be within the scope of the present invention as long as the above technical concept of the present invention is employed.

Various preferred embodiments of the two-cylinder pumping system of the present invention are described below with particular reference to Figures 3 and 6.

Referring to Figures 3 through 6, similar to a conventional two-cylinder pumping system, the two-cylinder pumping system includes a two-cylinder pumping device and a hydraulic control system for the two-cylinder pumping device. The main structure of the two-cylinder pumping apparatus has been described above and will not be described again. The hydraulic control system generally includes a main reversing valve 3, which is generally known as a three-position four-way reversing valve, and an oil inlet P of the main reversing valve 3 is connected to a pumping oil passage ( That is, the oil inlet passage), the oil return port T is connected to the oil tank, and the first working oil port A and the second working oil port B are respectively connected to the two main oil cylinders 4, 5 via the corresponding oil passages. As is well known to those skilled in the art, the oil inlet passage generally includes a hydraulic pump 1 driven by a power unit (engine or motor, etc.), wherein the input port of the hydraulic pump 1 is in communication with the fuel tank, and the output port is connected to the main reversing valve 3 The oil inlet P, the oil passage between the output port of the hydraulic pump 1 and the oil inlet P of the main directional control valve 3 is also generally connected with an overflow oil passage including the relief valve 2 for overpressure protection. As described above, in order to prevent the material flowing back during the pumping operation of the two-cylinder pumping device, the main reversing valve 3 needs to have a neutral cut-off function, so the main reversing valve 3 generally adopts an M-type three-position four-way reversing valve. Or type 0 three-position four-way reversing valve.

The hydraulic control system of the two-cylinder pumping device shown in FIG. 3 to FIG. 6 includes a high and low pressure switching valve 32, that is, the first working port A and the second working port B of the main reversing valve 3 are connected via a high and low pressure switching valve. 32 is connected to the two main cylinders 4, 5. In general, the high and low pressure switching valves that can be used in a two-cylinder pumping system can take many forms, and are primarily used to achieve high and low pressure switching of a two-cylinder pumping unit. The high and low pressure switching valves may be formed in the form of a composite valve, or a dispersed valve may be connected through the oil passage, and the respective interfaces on the high and low pressure switching valves are respectively connected to the two main cylinders 4 via respective oil passages, 5 each having The interface between the rod chamber and the rodless chamber and the first working port A of the main reversing valve 3 The second working port B. For example, in FIGS. 3 to 6, the high and low pressure switching valve 32 is composed of six two-way cartridge valves, namely, a first two-way cartridge valve 17, a second two-way cartridge valve 18, and a third two-way cartridge. The valve 19, the fourth two-way cartridge valve 20, the fifth two-way cartridge valve 21, and the sixth two-way cartridge valve 22, the two-way cartridge valve are well-known hydraulic components in the hydraulic field, and are not described herein again. The first port of the first two-way cartridge valve 17 is in communication with the second working port B of the main reversing valve 3, and the second port is in communication with the rod chamber C of the first main cylinder 4; the second two-way insertion The first port of the valve 18 is in communication with the rodless chamber B of the second master cylinder 5, the second port is in communication with the rodless chamber D of the first master cylinder 4; the first port of the third two-way cartridge valve 19 is exchanged with the main port Connected to the first working port A of the valve 3, the second port communicates with the rod chamber A of the second main cylinder 5; the first port of the fourth two-way cartridge valve 20 and the first operation of the main reversing valve 3 The port A is connected, the second port is in communication with the rodless chamber B of the second master cylinder 5; the first port of the fifth two-way cartridge valve 21 is in communication with the rod chamber C of the first master cylinder 4, the second port is The second main cylinder 5 has a rod chamber A communicating; the first port of the sixth two-way cartridge valve 22 is in communication with the second working port B of the main reversing valve 3, and the second port is opposite to the first main cylinder 4 The rod cavity D is connected. In addition, the liquid control ports of the above six two-way cartridge valves are respectively connected to the hydraulic control oil passage. Specifically, for example, in FIG. 3, the hydraulic control oil passage includes a two-position four-way reversing valve (for example, the two positions shown in FIG. 3) The four-way electromagnetic reversing valve 23), the hydraulic control ports of the first to third two-way cartridge valves 17, 18, 19 of the above six two-way cartridge valves are connected to the two-position four-way electromagnetic reversing valve 23 The second working port B1, the liquid control port of the fourth to sixth two-way cartridge valves 20, 21, 22 are connected to the first working port A1 of the two-position four-way electromagnetic reversing valve 23, the two-position four-way The oil inlet port P1 of the electromagnetic reversing valve is connected to the pumping oil passage and the distribution oil passage via the check valves 24, 25, respectively, and the oil return port T1 is connected to the oil tank, wherein the respective reverse ports of the check valves 24, 25 are The oil inlet P1 of the two-position four-way electromagnetic reversing valve is connected, so that the hydraulic oil with a large oil pressure on the pumping oil passage or the distribution oil is introduced into the oil inlet P1 of the two-position four-way electromagnetic reversing valve, and passes through two The four-way electromagnetic reversing valve 23 selectively controls the first to third two-way cartridge valves 17, 18, 19 or the fourth to sixth two-way cartridge valves 20, 21, 22. Of course, the above-described two-position four-way electromagnetic reversing valve 23 is only a specific form described for the sake of example, and that various types of reversing valves can be used as long as the first to third two-way cartridge valves 17, 18 can be made. The hydraulic control port of 19 and the hydraulic control ports of the fourth to sixth two-way cartridge valves 20, 21, 22 are selectively connected to the hydraulic oil source.

The specific form of the two-cylinder pumping system of the present invention will be described below with reference to Figs. 3 through 6, respectively.

As shown in FIG. 3, the on-off valve used on the pressure relief oil passage 33 is a normally open two-position two-way electromagnetic reversing valve 26, one end of the pressure relief oil passage 33 is connected to the oil tank, and the other end can be connected to the high and low pressure switching valve 32. And any oil passage between the rod chamber and the rodless chamber of each of the two main cylinders 4, 5, for example, the other end of the pressure relief oil passage 33 in Fig. 3 is connected to the high and low pressure switching valve 32 and the first main cylinder 4 on the oil line between the rodless chamber D. When the two-cylinder pumping system is working, the normally open two-position two-way electromagnetic reversing valve 26 is energized, and the pressure-removing oil passage 33 is in an off-off state. When the machine is stopped, the normally open two-position two-way electromagnetic reversing valve 26 power loss, the pressure relief oil circuit 33 is turned on. At this time, even because of the shutdown, each two-way cartridge valve is because The hydraulic oil can not be opened and the hydraulic oil is also discharged to the fuel tank via the normally open two-position two-way electromagnetic reversing valve 26, and the piston rod is not shaken.

As shown in FIG. 4, although the technical solution shown in FIG. 3 can prevent the piston rod from swaying, the technical solution is that in some states, the portions of the two main cylinders 4, 5 have a rod cavity and a rodless cavity. The pressure inside the chamber may not be removed in time due to accidents. As another preferred embodiment, as shown in FIG. 4, the on-off valve used on the pressure relief oil passage 33 is a normally open two-position two-way electromagnetic reversing valve 26, and one end of the pressure relief oil passage 33 is connected to the fuel tank, and One end is connected to the opposite port of the first one-way valve 27 and the second one-way valve 28, respectively, and the forward port of the first one-way valve 27 is connected to the second working port B of the main reversing valve 3, and The forward port of the second check valve 28 is connected to the first working port A of the main reversing valve 3, and the distinction between the forward port and the reverse port of the check valve is well known, that is, forward conduction, direction cutoff . Thus, when working, the solenoid valve 26 is energized, the port 3A and port B of the reversing valve are disconnected from the fuel tank, and the system can work normally. When the machine is stopped, the normally open two-position two-way electromagnetic reversing valve 26 is de-energized, and the pressure relief oil is discharged. The road 33 is turned on, and the hydraulic oil having the rod chamber and the rodless chamber of the two main cylinders 4, 5 flows through the first working port A and the second working port B of the main reversing valve 3, A check valve 27 or a second check valve 28 flows back to the oil tank via the pressure relief oil passage 33, and at the same time, due to the connection relationship between the first check valve 27 and the second check valve 28, the pressure relief oil passage 33 is preferentially relieved. For hydraulic oil with high oil pressure, once the oil pressure in some chambers is removed, the other chambers of the main cylinder will also be relieved due to the balance of forces.

As shown in FIG. 5, as an alternative modification, the normally open two-position two-way electromagnetic reversing valve 26 of FIG. 4 can be replaced with the normally closed two-position two-way electromagnetic reversing valve 29 of FIG. This alternative variant allows the normally closed 2/2-way solenoid reversing valve 29 to be de-energized while the dual-cylinder pumping system is operating normally to keep the relief pressure line 33 open. When the pumping is stopped, the normally closed 2/2-way electromagnetic reversing valve 29 is energized to cause the pressure relief oil passage 33 to be turned on for a predetermined time (for example, 1-5 seconds), thereby removing the high oil of the main cylinders 4, 5. Pressure. This alternative modification makes it possible to prevent the hydraulic oil in the main cylinders 4, 5 from flowing back to the tank in a large amount because the pressure relief oil passage 33 is only turned on for a predetermined time, so that the unloading of the pressure relief oil passage can be effectively prevented. Causes material (such as concrete) in the pipeline to flow backwards. Of course, in the embodiment shown in FIG. 3 and FIG. 4, this technical effect can also be obtained by controlling the power failure time of the normally open two-position two-way electromagnetic reversing valve 26, and of course, the normally open type in this case. The two-position two-way electromagnetic reversing valve 26 can adopt an independent control circuit.

Since the purpose of the present invention to prevent the piston rod of the main cylinder of the two-cylinder pumping unit from turbulence is mainly to eliminate the safety hazard during inspection and maintenance, for example, when the seals 14 and 15 of the pumping pistons 12, 13 are replaced, the piston rod is tilted. . Therefore, when the seal is replaced, the pumping piston 12 or 13 must be retracted to the water tank 16, by detecting whether the piston is located in the water tank 16, as shown in Fig. 6, preferably, the water tank 16 may be provided with a pumping piston for detecting 12, 13 is located in the position detecting device in the water tank 16, the position detecting device may include the first position for detecting the pumping piston 12 A detecting device 30 and a second position detecting device 31 for detecting the pumping piston 13 are disposed. The first position detecting device 30 and the second position detecting device 31 may employ various well-known sensors, such as a magnetoresistive linear displacement sensor, a Hall sensor, etc., of course, in this case, the first position detecting device 30 and the second position The detecting device 31 can be electrically connected to a corresponding controller, and the controller is electrically connected to the normally closed 2/2-way electromagnetic reversing valve 29 (as long as it is an electronically controlled switching valve), so that the controller can detect according to the first position The signal detected by the device 30 and the second position detecting device 31 controls the normally closed 2/2-way electromagnetic reversing valve 29 to control the on/off of the pressure relief oil passage 33. By the first position detecting device 30 and the second position detecting device 31, it is detected whether the pumping pistons 12, 13 are returned to the water tank 16, and if the corresponding pumping piston has been returned to the water tank 16, the pumping operation is stopped, so that the normally closed type II is The two-way electromagnetic reversing valve 29 is energized first, and the pressure relief oil passage 33 is turned on, and the first working port A and the second working port B of the main reversing valve 3 and the chambers of the main cylinder are unloaded, and the time delay After a period of time (for example, 2 seconds), the normally closed 2/2-way electromagnetic reversing valve 29 is de-energized, and each chamber is closed, but the oil pressure has been removed, and the closed-loop is low-pressure oil. If the piston is not returned to the water tank, the normally closed two-position two-way electromagnetic reversing valve 29 is not energized regardless of whether the pumping is operating.

In addition to the above-described technical solution of the two-cylinder pumping system, the present invention also provides a pumping apparatus comprising the above-described two-cylinder pumping system. Typically, the pumping device can be a concrete pump truck.

As can be seen from the above description, the present invention provides the following advantages: The present invention provides a two-cylinder pumping system anti-rolling shutdown method and a two-cylinder pumping system capable of implementing the shutdown method, which is uniquely existing in the existing two-cylinder The pumping system shutdown method is based on adding a pressure relief step, so that the chambers of the main cylinder of the two-cylinder pumping system can be in a low pressure or no pressure state, effectively preventing the piston rod of the main cylinder from being closed due to high pressure oil. Accidental agitation occurs, which effectively ensures the safety of the maintenance personnel during the maintenance and repair work of the two-cylinder pumping system. The anti-turbine shutdown method of the twin-cylinder pumping system of the invention has universal applicability, in particular, can be effectively applied to a two-cylinder pumping system with high and low pressure switching valves, which relatively reliably prevents the shutdown of the two-cylinder pumping system When the piston rod of the main cylinder is swayed, the two-cylinder pumping system effectively removes the pressure of each chamber of the main cylinder during the shutdown, making the two-cylinder pumping system safer.

The preferred embodiments of the present invention have been described in detail above with reference to the drawings, but the present invention is not limited to the specific details of the embodiments described above, and various modifications may be made to the technical solutions of the present invention within the scope of the technical idea of the present invention. Modifications are all within the scope of protection of the present invention. In particular, although the above is mainly described by taking a concrete double cylinder pumping system as an example, the double cylinder pumping system anti-twisting shutdown method of the present invention and the twin-cylinder pumping system for implementing the method are obviously not limited. In the field of concrete twin-cylinder pumping systems, it can be universally applied to the control of two-cylinder pumping systems for conveying other fluid materials, such as the shutdown control of double-cylinder pumping systems such as mud and mortar, correspondingly The concrete two-cylinder pumping system of the present technology concept can also be formed as a two-cylinder pumping system for conveying other viscous materials. It should be further noted that the specific technical features described in the above specific embodiments may be combined in any suitable manner without contradiction. In order to avoid unnecessary repetition, the present invention will not be further described in various possible combinations.

In addition, any combination of various embodiments of the invention may be made, as long as it does not deviate from the idea of the invention, and it should be regarded as the disclosure of the invention.

Claims

Rights request

1. Double-cylinder pumping system anti-channeling shutdown method, the double-cylinder pumping system includes a double-cylinder pumping device with two main oil cylinders (4, 5) and a hydraulic control system of the double-cylinder pumping device, so The shutdown method includes the following steps: First, control the double-cylinder pumping device to stop the pumping operation, so that the rod cavity and the rodless cavity of the two main oil cylinders (4, 5) are in contact with the oil inlet and oil passages. The oil return lines are all cut off;

Second, at least one of the rod chambers and the rodless chambers of the two master cylinders (4, 5) is connected to the oil tank or the oil return line.

2. The shutdown method according to claim 1, wherein in the second step, at least one of the rod chambers and the rodless chambers of the two main cylinders (4, 5) is connected to the oil tank. Or the scheduled time for the return oil line to be connected.

3. The shutdown method according to claim 2, wherein the predetermined time is 1-5 seconds.

4. The shutdown method according to claim 1, wherein in the first step, the double-cylinder pumping device is controlled to switch to stop the pumping operation in a low-pressure pumping state.

5. The shutdown method according to claim 1, wherein, in the first step, one pumping piston (12, 13) of the double-cylinder pumping device stops at the water tank of the double-cylinder pumping device. (16), the double-cylinder pumping device is controlled to stop the pumping operation.

6. The shutdown method according to claim 5, wherein, in the first step, after detecting that one pumping piston (12, 13) of the double-cylinder pumping device stops in the water tank (16) Under the situation, the double-cylinder pumping device is controlled to stop the pumping operation.

7. The shutdown method according to claim 7, wherein the double-cylinder pumping system is a concrete double-cylinder pumping system, and the double-cylinder pumping device is a concrete double-cylinder pumping device.

8. The shutdown method according to any one of claims 1 to 7, wherein in the second step, all the main cylinders (4, 5) of the double-cylinder pumping device have rod cavities and The rodless cavity is connected with the oil tank or oil return line.

9. Double-cylinder pumping system, including a double-cylinder pumping device and its hydraulic control system. The double-cylinder pumping device includes two main oil cylinders (4, 5), wherein the hydraulic control system also includes pressure relief oil. line (33), one end of the pressure relief oil line (33) is connected to the oil tank or the return oil line, and the other end is connected to the rod cavity and the inert cavity of the two main oil cylinders (4, 5) via the corresponding oil line. At least one chamber in the rod chamber, the pressure relief oil line (33) is provided with a switch valve to be able to control the rod chamber of the main cylinder (4, 5) when the dual-cylinder pumping system is shut down. And at least one chamber in the rodless chamber is connected with the oil tank or the oil return line.

10. The double-cylinder pumping system according to claim 9, wherein the hydraulic control system includes a main reversing valve (3) and a high and low pressure switching valve (32), and each interface of the high and low pressure switching valve (32) Connected to the respective rod chambers and rodless chambers of the two main cylinders (4, 5) and the first working oil port (A) and the second working oil port (B) of the main reversing valve (3) ).

11. The double-cylinder pumping system according to claim 10, wherein the main reversing valve (3) is an M-type three-position four-way reversing valve or an O-type three-position four-way reversing valve. The oil inlet (P) of the valve (3) is connected to the pumping oil line, the oil return port (T) is connected to the oil tank, and the first working oil port (A) and the second working oil port (B) are respectively connected through the The high and low pressure switching valve (32) connects the two main oil cylinders (4, 5).

12. The double-cylinder pumping system according to claim 10, wherein the high and low pressure switching valve (32) includes first to sixth two-way cartridge valves (17, 18, 19, 20, 21, 22) , the hydraulic control ports of the first to sixth two-way cartridge valves (17, 18, 19, 20, 21, 22) are respectively connected to the hydraulic control oil circuit, and the hydraulic control oil circuit includes a two-position four-way reversing valve, The oil inlet (P1) of the two-position four-way directional valve is connected to the pumping oil circuit and the distribution oil circuit of the hydraulic control system via a one-way valve (24, 25) respectively, and the oil return port (T1) is connected to In the oil tank, the first working oil port (A1) is connected to the hydraulic control port of the fourth to sixth two-way cartridge valves (20, 21, 22), and the second working oil port (B1) is connected to the third working oil port (B1). The liquid control ports of the first to third two-way cartridge valves (17, 18, 19), where the respective reverse ports of the two one-way valves (24, 25) are connected to the two-position four-way reversing valve. The oil inlet (P1) is connected.

13. The double-cylinder pumping system according to claim 10, wherein the other end of the pressure relief oil circuit (33) is connected to the high and low pressure switching valve (32) and the two main oil cylinders (4, 5) on any of the oil circuits between.

14. The double-cylinder pumping system according to claim 10, wherein the other end of the pressure relief oil line (33) is connected to the first one-way valve (27) and the second one-way valve (28) respectively. Reverse port, the forward port of the first one-way valve (27) is connected to the second working oil port (B) of the main reversing valve (3), and the second one-way valve (28) The forward port is connected to the first working oil port (A) of the main reversing valve (3).

15. The double-cylinder pumping system according to any one of claims 9 to 14, wherein the on-off valve on the pressure relief oil line (33) is an electronically controlled on-off valve.

16. The double-cylinder pumping system according to claim 15, wherein the electronically controlled switch valve is a normally open two-position two-way electromagnetic reversing valve (26) or a normally closed two-position two-way electromagnetic reversing valve. (29).

17. The double-cylinder pumping system according to claim 15, wherein the water tank (16) of the double-cylinder pumping device is provided with a pumping piston (12, 13) for detecting whether the double-cylinder pumping device is A position detection device located in the water tank (16).

18. Pumping equipment, wherein the pumping equipment includes a double-cylinder pumping system according to any one of claims 9 to 17.