CN115596652A - Pumping hydraulic system and concrete pumping machine - Google Patents
Pumping hydraulic system and concrete pumping machine Download PDFInfo
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- CN115596652A CN115596652A CN202211296101.9A CN202211296101A CN115596652A CN 115596652 A CN115596652 A CN 115596652A CN 202211296101 A CN202211296101 A CN 202211296101A CN 115596652 A CN115596652 A CN 115596652A
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- 238000005086 pumping Methods 0.000 title claims abstract description 152
- 239000003921 oil Substances 0.000 claims abstract description 277
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 12
- 230000009471 action Effects 0.000 claims abstract description 8
- 238000000034 method Methods 0.000 description 10
- 230000008569 process Effects 0.000 description 9
- 238000006243 chemical reaction Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
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Abstract
The invention provides a pumping hydraulic system and a concrete pumping machine, wherein the pumping hydraulic system comprises two pumping oil cylinders which are connected in series, a main oil pump, a main reversing valve and a high-low pressure switching valve; the main oil pump pumps hydraulic oil to the pumping hydraulic system through a pumping oil path; the main reversing valve is arranged on the pumping oil path and controls the telescopic action of the pumping oil cylinder; the high-low pressure switching valve is arranged on an oil supply oil path of the main reversing valve, and a valve core of the high-low pressure switching valve can be switched between a first working position and a second working position, so that hydraulic oil pumped by the main oil pump enters a rod cavity or a rodless cavity of one of the pumping oil cylinders through the high-low pressure switching valve. The pumping hydraulic system can realize the high-pressure and low-pressure pumping states of the pumping oil cylinder by matching the high-pressure and low-pressure switching valve with the main reversing valve, simplifies the structure and improves the pumping efficiency.
Description
Technical Field
The invention belongs to the technical field of concrete pumping, and particularly relates to a hydraulic pumping system and a concrete pumping machine.
Background
Concrete pumping equipment is used for conveying concrete and is widely applied to modern engineering construction. Generally, concrete pumping equipment realizes suction and discharge of concrete through reciprocating motion of two concrete pistons in concrete cylinders, and a hydraulic system for controlling and driving the concrete pistons is called as a pumping hydraulic system. In pumping equipment, in order to improve the capability of the equipment for adapting to working conditions, two connection modes are provided for a pumping oil cylinder, and the corresponding working state industry is called high-pressure pumping and low-pressure pumping. High-pressure pumping pressure oil enters a rodless cavity of the pumping oil cylinder, and the concrete conveying pressure is high but the speed is low due to the large action area. The low-pressure pumping pressure oil enters a rod cavity of the pumping oil cylinder, the acting area is small, but the speed is high. In the pumping hydraulic system with high-low pressure conversion function in the prior art, high-low pressure conversion is realized by adopting two reversing valves, and the two main reversing valves are in a parallel state. Because the middle position is needed in each reversing process, the system pressure needs to be unloaded through the electromagnetic overflow valve before the reversing valve reaches the middle position, and the pressure of the electromagnetic overflow valve needs to be built after the reversing valve is reversed in place, so that the reversing process is complex. Under different working conditions, the time for the reversing valve to return to the neutral position and the time for reversing to the other side are different, so that complete matching is difficult to achieve, when the matching is not good, the situation that the system is unstable due to impact can be caused, or the reversing process needs to be prolonged, but the system efficiency is reduced.
Disclosure of Invention
The invention mainly aims to provide a pumping hydraulic system and a concrete pumping machine, and aims to solve the technical problems that the reversing process of the pumping hydraulic system with a high-low pressure conversion function in the prior art is complex and unstable.
In order to achieve the above object, the present invention provides a pumping hydraulic system including two pumping cylinders connected in series, the pumping hydraulic system including:
the main oil pump pumps hydraulic oil to the pumping hydraulic system through a pumping oil path;
the main reversing valve is arranged on the pumping oil path and controls the telescopic action of the first pumping oil cylinder and the second pumping oil cylinder; and
and the high-low pressure switching valve is arranged on an oil supply oil path of the main reversing valve, and a valve core of the high-low pressure switching valve can be switched between a first working position and a second working position so that hydraulic oil pumped by the main oil pump enters a rod cavity or a rodless cavity of one of the pumping oil cylinders through the high-low pressure switching valve.
In the embodiment of the invention, the main reversing valve comprises a first hydraulic reversing valve and a first pilot electromagnetic valve for controlling the first hydraulic reversing valve to switch between a first switching position and a second switching position, and the first hydraulic reversing valve comprises a main oil inlet and a main oil return opening which are positioned on one side, and a first oil supply opening and a second oil supply opening which are positioned on the other side;
when the first switching position is carried out, the first working oil port is communicated with the main oil inlet, and the second working oil port is communicated with the main oil return port;
when the second switching position is carried out, the first working oil port is communicated with the main oil return port, and the second working oil port is communicated with the main oil inlet.
In an embodiment of the present invention, the first hydraulically operated directional control valve further includes a middle stopping position for communicating the main oil inlet with the main oil return port and stopping both the first oil supply port and the second oil supply port.
In the embodiment of the invention, the high-low pressure switching valve is a two-position six-way valve electro-hydraulic reversing valve.
In the embodiment of the invention, the high-low pressure switching valve comprises a second hydraulic directional control valve, a first side first working oil port and a first side second working oil port of the second hydraulic directional control valve are respectively communicated with rod cavities of the two pumping cylinders, a first side third working oil port and a first side fourth working oil port are respectively communicated with rodless cavities of the two pumping cylinders, and a second side first working oil port and a second side second working oil port of the second hydraulic directional control valve are respectively communicated with a first oil supply port and a second oil supply port of the main directional control valve.
In an embodiment of the present invention, the high-low pressure directional control valve further comprises a second pilot solenoid valve controlling the second hydraulic directional control valve to switch between the first operating position and the second operating position, wherein:
in the first working position, the first side third working oil port is communicated with the first side fourth working oil port, the first side first working oil port is communicated with the second side first working oil port, and the first side second working oil port is communicated with the second side second working oil port;
in the second working position, the first side first working oil port is communicated with the first side second working oil port, the first side third working oil port is communicated with the second side first working oil port, and the first side fourth working oil port is communicated with the second side second working oil port.
In an embodiment of the invention, the second pilot electromagnetic valve is a two-position four-way electromagnetic valve, the second pilot electromagnetic valve comprises an electromagnet for controlling switching between a first position and a second position, the second pilot electromagnetic valve comprises a third oil supply port, a fourth oil supply port, a first oil inlet and a first oil return port, and the third oil supply port is communicated with a cavity where a second working position of the second hydraulic directional control valve is located;
when the second hydraulic reversing valve is at the first position, the second hydraulic reversing valve is unloaded through a third oil supply port of the electromagnetic reversing valve;
when the hydraulic control system is at the second position, hydraulic oil of the external control oil way enters the second hydraulic directional control valve through the first oil inlet.
In the embodiment of the invention, the main reversing valve and the high-low pressure switching valve are of an integrated valve group structure, and the first pilot electromagnetic valve and the second pilot electromagnetic valve are integrated on the valve body or the end cover.
In the embodiment of the invention, a pressure control device is also arranged on an oil inlet path of the pumping hydraulic system.
In an embodiment of the present invention, a concrete pumping machine is also provided, which includes the above pumping hydraulic system.
Through the technical scheme, the pumping hydraulic system provided by the embodiment of the invention has the following beneficial effects:
compared with the situation that high pressure and low pressure are respectively controlled by one reversing valve in the prior art, the high-low pressure switching valve is arranged on the oil supply oil path of the main reversing valve, the telescopic reversing action of the two pumping oil pumps is controlled through the main reversing valve, and the high-low pressure switching valve selects pressure oil pumped by the main oil pump to be pumped to a rod cavity or a rodless cavity of the two pumping oil cylinders connected in series; when the pump is sent to the rod cavity of one of the pumping oil cylinders, the effective area of the rod cavity is smaller than that of the rodless cavity, so that the thrust of the other pumping oil cylinder is smaller, but the speed is high, and a low-pressure pumping state can be realized; when the pump is pumped to the rodless cavity of one of the pumping oil cylinders, the effective area is large, the thrust is large, and the high-pressure pumping state of the pumping oil cylinders is realized. The high-low pressure switching process is simple in structure, the trouble of middle position unloading is omitted, the reversing process is more stable, and the efficiency of the whole hydraulic pumping system is improved.
Additional features and advantages of the invention will be set forth in the detailed description which follows.
Drawings
The accompanying drawings, which are included to provide an understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:
FIG. 1 is a schematic diagram of a hydraulic configuration of a pumped hydraulic system according to an embodiment of the present invention;
fig. 2 is a schematic diagram of an integrated valve group structure of a main reversing valve and a high-low pressure switching method in a pumping hydraulic system according to an embodiment of the invention.
Description of the reference numerals
Detailed Description
The following detailed description of specific embodiments of the invention refers to the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative and explanatory of the invention and are not restrictive thereof.
A pumped hydraulic system according to the invention is described below with reference to the accompanying drawings.
As shown in fig. 1, in an embodiment of the present invention, there is provided a pumping hydraulic system including a first pumping cylinder 40 and a second pumping cylinder 50 connected in series, the pumping hydraulic system including:
the main oil pump 10 pumps hydraulic oil to a pumping hydraulic system through a pumping oil path L1;
a main directional control valve 21 disposed on the pumping oil path L1 and controlling the expansion and contraction of the first and second pumping cylinders 40 and 50; and
and the high-low pressure switching valve 22 is arranged on the oil supply oil path L2 of the main directional control valve 21, and a valve core of the high-low pressure switching valve 22 can be switched between a first working position and a second working position, so that hydraulic oil pumped by the main oil pump 10 enters the rod cavity or the rodless cavity of the first pumping cylinder 40 and the second pumping cylinder 50 through the high-low pressure switching valve 22.
For example, as shown in fig. 1, when the main oil pump 10 pumps pressure oil to the rod cavity of the first pumping cylinder 40, the rod-less cavity of the first pumping cylinder 40 returns oil, and since two pumping cylinders are connected in series, the rod-less cavity of the second pumping cylinder 50 takes oil, and then the telescopic rod of the second pumping cylinder 50 is driven to extend; at this time, since the pressure oil enters from the rod chamber of the first pumping cylinder 40 and the effective area of the rod chamber is smaller than that of the rodless chamber, the thrust of the pressure oil is smaller at this time, that is, the thrust generated by the second pumping cylinder 50 to the outside is smaller under the action of the pressure oil, but the speed is high, and the low-pressure pumping state can be realized. On the contrary, when the main oil pump 10 pumps the pressure oil to the rodless cavity of the second pumping cylinder 50, the telescopic rod of the second pumping cylinder 50 extends out, and at this time, the effective area of the rodless cavity is large, and the thrust generated by the pressure oil is large, so that the high-pressure pumping state of the pumping cylinder is realized. The high-low pressure switching process is simple in structure, the trouble of middle position unloading is omitted, the reversing process is more stable, and the efficiency of the whole hydraulic pumping system is improved.
In the embodiment of the present invention, the main directional control valve 21 includes a first hydraulic directional control valve 211, and a first pilot electromagnetic valve 212 that controls the first hydraulic directional control valve 211 to switch between a first switching position and a second switching position, where the first hydraulic directional control valve 211 includes a main oil inlet P1 and a main oil return port T1 located on one side, and a first oil supply port A5 and a second oil supply port B5 located on the other side; when the first switching position is carried out, the first working oil port is communicated with the main oil inlet P1, and the second working oil port is communicated with the main oil return port T1; when the second switching position is carried out, the first working oil port is communicated with the main oil return port T1, and the second working oil port is communicated with the main oil inlet P1.
In addition, the first hydraulic directional control valve 211 further includes a middle stop position at which the main oil inlet P1 is communicated with the main oil return port T1 and the first oil supply port A5 and the second oil supply port B5 are both stopped, that is, when the first hydraulic directional control valve 211 is shifted, the valve core automatically passes through an unloading position of the middle stop position, and the shifting impact is small.
Specifically, under the condition that the first hydraulic directional control valve 211 is used for reversing, when the first hydraulic directional control valve 211 is at the first switching position on the left side, the pressure oil pumped from the main oil pump 10 is introduced into the first oil supply port A5, and enters the rod chamber of the first pumping cylinder 40 or the rodless chamber of the second pumping cylinder 50 through the second hydraulic directional control valve 221 (depending on the spool position of the second hydraulic directional control valve 221), the piston rod of the first pumping cylinder 40 retracts (or the piston rod of the second pumping cylinder 50 extends), and the piston rod of the second pumping cylinder 50 extends (or the piston rod of the first pumping cylinder 40 retracts). When the first hydraulic directional control valve 211 is located at the second switching position on the right side, the pressure oil pumped from the main oil pump 10 is introduced into the second oil supply port B5, and enters the rodless cavity of the second pumping cylinder 50 or the rod cavity of the first pumping cylinder 40 through the second hydraulic directional control valve 221 (depending on the spool position of the second hydraulic directional control valve 221), the piston rod of the second pumping cylinder 50 retracts (or the piston rod of the first pumping cylinder 40 extends), and the piston rod of the first pumping cylinder 40 extends (or the piston rod of the second pumping cylinder 50 retracts). The reciprocating action of the pumping oil cylinder is realized by the circulation.
When the first hydraulic directional control valve 211 is at the middle cut-off position, the pressure oil of the main oil pump 10 flows back to the oil tank 60 through the main oil inlet P1 and the main oil return port T1, so as to realize system unloading.
Further, the first pilot electromagnetic valve 212 of the present application is a three-position four-way electromagnetic valve, the fifth oil supply port A6 and the sixth oil supply port B6 of the first pilot electromagnetic valve 212 are respectively communicated with the main oil inlet P1 and the main oil return port T1 of the first hydraulic-operated directional valve 211, and the second oil inlet P3 and the second oil return port T3 of the first pilot electromagnetic valve 212 are respectively communicated with the external control oil path and the oil tank 60; two ends of the first hydraulic directional valve 211 are respectively provided with a first control cavity, the two first control cavities on the left side and the right side are respectively communicated with a fifth oil supply port A6 and a sixth oil supply port B6 of the first pilot electromagnetic valve 212, and two electromagnets for controlling switching at a left position, a middle position and a right position are arranged at the left end and the right end of the first pilot electromagnetic valve 212.
For a clearer understanding of the switching principle of the first hydraulically switchable valve 211, the switching process of the position of the first hydraulically switchable valve 211 controlled by the first pilot solenoid valve 212 is explained in detail as follows:
when the first pilot electromagnetic valve 212 is in the left position, the sixth oil supply port B6 is communicated with the second oil inlet P3, pressure oil in the first control cavity on the left side of the first hydraulic reversing valve 211 is unloaded through the first pilot electromagnetic valve 212, at this time, no pressure oil exists in the first control cavity on the left side, and pressure oil is introduced into the first control cavity on the right side, so that the first hydraulic reversing valve 211 is controlled to be switched to the first switching position on the left side;
when the first pilot electromagnetic valve 212 is in the middle position, the fifth oil supply port A6 and the sixth oil supply port B6 are both communicated with the second oil return port T3, and at this time, the pressure oil in the first control cavities on the left and right sides is unloaded through the first pilot electromagnetic valve 212, so that the first hydraulic directional control valve 211 is in the middle stop position.
When the first pilot electromagnetic valve 212 is in the right position, the fifth oil supply port A6 is communicated with the second oil inlet P3, pressure oil is introduced into the first control cavity on the left side of the first hydraulic directional valve 211, the pressure oil in the first control cavity on the right side is unloaded through the first pilot electromagnetic valve 212, and at this time, no pressure oil exists in the first control cavity on the right side, so that the first hydraulic directional valve 211 is controlled to be switched to the second switching position on the right side.
As shown in fig. 1, the high-low pressure switching valve 22 of the present application is a two-position six-way electro-hydraulic directional valve.
In the embodiment of the present invention, the high-low pressure switching valve 22 includes a second hydraulic directional control valve 221, a first side first working oil port A1 and a first side second working oil port B1 of the second hydraulic directional control valve 221 are respectively communicated with rod cavities of the first pumping cylinder 40 and the second pumping cylinder 50, a first side third working oil port A2 and a first side fourth working oil port B2 are respectively communicated with rodless cavities of the first pumping cylinder 40 and the second pumping cylinder 50, and a second side first working oil port A3 and a second side second working oil port B3 of the second hydraulic directional control valve 221 are respectively communicated with a first oil supply port A5 and a second oil supply port B5 of the main directional control valve 21.
The second hydraulic directional control valve 221 is used to switch the working state of the pumping hydraulic system, when the second hydraulic directional control valve 221 is at the position shown in fig. 1, the pressure oil pumped by the main oil pump 10 enters the rod cavity of the first pumping cylinder 40 or the second pumping cylinder 50, and the rod-free cavities of the first pumping cylinder 40 and the second pumping cylinder 50 are communicated through the second hydraulic directional control valve 221. At this time, no matter the rod cavity of the first pumping cylinder 40 is filled with oil or the rod cavity of the second pumping cylinder 50 is filled with oil, the thrust of the pumping cylinder is small but the action speed is high because the effective area of the rod cavity is small, and the working state is called a low-pressure pumping state in the industry. When the second pilot electromagnetic valve 222 is powered on, the second hydraulic directional control valve 221 is switched to a second working position on the right side, at this time, the pressure oil pumped by the main oil pump 10 enters the second pumping cylinder 50 or the rodless cavity of the first pumping cylinder 40 through the second hydraulic directional control valve 221, and the rod cavities of the first pumping cylinder 40 and the second pumping cylinder 50 are communicated through the second hydraulic directional control valve 221. The effective area of the rodless cavity is large, so that the thrust of the pumping oil cylinder is large, but the speed is low, and the working state is called a high-pressure pumping state in the industry. According to the hydraulic system, the purpose of high-pressure and low-pressure switching can be achieved through the second hydraulic reversing valve 221, and the pumping efficiency of the whole pumping hydraulic system is improved.
In order to better realize the valve core position switching of the second hydraulic directional control valve 221, the high-low pressure directional control valve further comprises a second pilot electromagnetic valve 222 for controlling the second hydraulic directional control valve 221 to switch between a first working position and a second working position, wherein when the first working position is adopted, a first side third working oil port A2 is communicated with a first side fourth working oil port B2, a first side first working oil port A1 is communicated with a second side first working oil port A3, a first side second working oil port B1 is communicated with a second side second working oil port B3, at the moment, a rodless cavity of the first pumping oil cylinder 40 is communicated with a rodless cavity of the second pumping oil cylinder 50, and a rod cavity of the first pumping oil cylinder 40 or the second pumping oil cylinder 50 feeds oil; when the first pumping oil cylinder 40 is in the first working position, the first side first working oil port A1 is communicated with the first side second working oil port B1, the first side third working oil port A2 is communicated with the second side first working oil port A3, and the first side fourth working oil port B2 is communicated with the second side second working oil port B3, at this time, the rod cavity of the first pumping oil cylinder 40 or the rod cavity of the second pumping oil cylinder 50 is fed with oil, and the rodless cavity of the second pumping oil cylinder 50 or the first pumping oil cylinder 40 is fed with oil. Specifically, whether the oil is fed from the first pumping cylinder 40 or the second pumping cylinder 50 is determined according to the switching position of the first hydraulically operated directional control valve 211.
In an embodiment of the present application, as shown in fig. 1 and fig. 2, the second pilot solenoid valve 222 is a two-position four-way solenoid valve, the second pilot solenoid valve 222 includes an electromagnet for controlling switching between a first position and a second position, the second pilot solenoid valve 222 includes a third oil supply port A4, a fourth oil supply port B4, a first oil inlet P2 and a first oil return port T2, the third oil supply port A4 is communicated with a cavity where the second working position of the second hydraulic directional control valve 221 is located, and the effective working ports of the second pilot solenoid valve 222 are only three: a third oil supply port A4, a first oil inlet P2 and a first oil return port T2. When the spool of the second pilot electromagnetic valve 222 is at the first position, the second hydraulically-operated directional valve 221 is unloaded through the third oil supply port A4 of the electromagnetic directional valve; when the spool of the second pilot electromagnetic valve 222 is at the second position, the hydraulic oil of the external control oil path enters the second hydraulic directional control valve 221 through the first oil inlet P2.
Specifically, the second elastic buffer 72 is disposed at the left end of the second hydraulic directional control valve 221, a cavity where the second working position of the second hydraulic directional control valve 221 is located is a control cavity, the control cavity is communicated with the third oil supply port A4 of the second pilot electromagnetic valve 222, when the electromagnet on the second pilot electromagnetic valve 222 is de-energized, the spring of the second pilot electromagnetic valve 222 pushes the spool of the second pilot electromagnetic valve 222 to move, so that when the second pilot electromagnetic valve 222 is located at the first position on the left side, pressure oil in the control cavity of the second hydraulic directional control valve 221 is unloaded through the second pilot electromagnetic valve 222, no pressure oil exists in the control cavity, and at this time, the second elastic buffer 72 pushes the spool of the second hydraulic directional control valve 221 to move, so that the second hydraulic directional control valve 221 is switched to the first working position on the left side. When the electromagnet on the second pilot electromagnetic valve 222 is energized, the electromagnet overcomes the elastic force of the second pilot electromagnetic valve 222 and pushes the valve spool of the second pilot electromagnetic valve 222 to operate, so that the second pilot electromagnetic valve 222 is located at the second position on the right side, the control oil of the external control oil path enters the control cavity of the second hydraulic directional control valve 221 through the second pilot electromagnetic valve 222, and the control oil pushes the valve spool of the second hydraulic directional control valve 221 to operate against the elastic force of the second elastic buffer 72, so that the second hydraulic directional control valve 221 is controlled to be switched to the second operating position on the right side.
As shown in fig. 2, the main directional control valve 21 and the high-low pressure switching valve 22 are in an integrated valve set 20 structure, and the first pilot solenoid valve 212 and the second pilot solenoid valve 222 are integrated on the valve body or the end cap, wherein the valve body and the end cap may be in a casting structure to reduce pressure loss. Of course, second pilot solenoid valve 222 may be a two-position three-way solenoid valve as long as the above-described function can be achieved. It should be noted that both the first pilot solenoid valve 212 and the second pilot solenoid valve 222 may be plug-in solenoid valves, and are inserted into the valve body or the end cover. Other hydraulic components such as relief valves can also be inserted into the valve body. In addition, because main change valve 21 and high-low pressure diverter valve 22 all integrate in same valve body, compare in conventional plate valve group system, the system of this application is simple, and is small, light in weight, and the oil duct is simple, and pressure loss is little.
As shown in fig. 2, the fifth oil supply port A6 and the sixth oil supply port B6 of the first pilot electromagnetic valve 212 are respectively communicated with the left and right control cavities of the first hydraulically-operated directional valve 211 through two first control oil passages 81; the two ends of the first hydraulic reversing valve 211 are both provided with a first elastic buffer member 71, the first elastic buffer member 71 is located in the end covers at the two ends, and when the first control oil passage 81 returns oil, the first elastic buffer member 71 drives the valve core of the first hydraulic reversing valve 211 to return to the middle position. A third oil supply port A4 of the second pilot solenoid valve 222 is communicated with a control cavity on the right side of the second hydraulic directional control valve 221 through a second oil passage; the second elastic buffer 72 is also located in the end cover of the second hydraulic directional control valve 221, and when the second control oil passage 82 returns oil, the second elastic buffer 72 drives the spool of the second hydraulic directional control valve 221 to return to the first working position on the left side.
In the scheme of this application, the main oil inlet P1 of first switching-over valve 211 that surges can be a plurality of, through first connection oil duct 91 intercommunication between a plurality of main oil inlets P1, main oil return port T1's quantity can be two, communicates through second connection oil duct 92 between two main oil return port T1.
In the embodiment of the present invention, the oil inlet path of the pumping hydraulic system is further provided with a pressure control device 30, wherein the pressure control device 30 may be an overflow valve, and the overflow valve is arranged on the oil inlet path where the main oil inlet P1 is located, so as to control the highest working pressure of the system.
In an embodiment of the present invention, a concrete pumping machine is also provided, which includes the above pumping hydraulic system. The concrete pumping machine adopts all the embodiments of the pumping hydraulic system, so that all the beneficial effects of the pumping hydraulic system are achieved, and the detailed description is omitted.
In the description of the present invention, it is to be understood that the terms "first", "second" and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implying any number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless explicitly specified otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be interconnected within two elements or in a relationship where two elements interact with each other unless otherwise specifically limited. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.
Claims (10)
1. A pumping hydraulic system comprising two pumping cylinders in series, characterized in that it comprises:
a main oil pump (10) for pumping hydraulic oil to the pumping hydraulic system through a pumping oil path (L1);
the main reversing valve (21) is arranged on the pumping oil way (L1) and controls the telescopic action of the two pumping oil cylinders; and
and the high-low pressure switching valve (22) is arranged on an oil supply oil path (L2) of the main reversing valve (21), and a valve core of the high-low pressure switching valve (22) can be switched between a first working position and a second working position, so that hydraulic oil pumped by the main oil pump (10) enters a rod cavity or a rodless cavity of one of the pumping oil cylinders through the high-low pressure switching valve (22).
2. The pumping hydraulic system according to claim 1, wherein the main directional control valve (21) comprises a first hydraulic directional control valve (211), a first pilot electromagnetic valve (212) for controlling the first hydraulic directional control valve (211) to switch between a first switching position and a second switching position, the first hydraulic directional control valve (211) comprises a main oil inlet (P1) and a main oil return (T1) on one side, and a first oil supply port (A5) and a second oil supply port (B5) on the other side;
when the first switching position is carried out, the first working oil port is communicated with the main oil inlet (P1), and the second working oil port is communicated with the main oil return port (T1);
when the second switching position is adopted, the first working oil port is communicated with the main oil return port (T1), and the second working oil port is communicated with the main oil inlet (P1).
3. The pumped hydraulic system of claim 2, wherein the first hydraulically operated directional control valve (211) further comprises an intermediate cut-off position at which the main oil inlet (P1) communicates with the main oil return port (T1) and the first oil supply port (A5) and the second oil supply port (B5) are both cut off.
4. The pumped hydraulic system of claim 2, wherein the high and low pressure switching valve (22) is a two-position, six-way valve electro-hydraulic directional valve.
5. The hydraulic pumping system of claim 4, wherein the high-pressure and low-pressure switching valve (22) comprises a second hydraulic directional valve (221), a first side first working oil port (A1) and a first side second working oil port (B1) of the second hydraulic directional valve (221) are respectively communicated with rod chambers of the two pumping cylinders, a first side third working oil port (A2) and a first side fourth working oil port (B2) are respectively communicated with rodless chambers of the two pumping cylinders, and a second side first working oil port (A3) and a second side second working oil port (B3) of the second hydraulic directional valve (221) are respectively communicated with a first oil supply port (A5) and a second oil supply port (B5) of the main directional valve (21).
6. The pumping hydraulic system of claim 3, wherein the high and low pressure directional control valve further comprises a second pilot solenoid valve (222) that controls the second hydraulically directional control valve (221) to switch between the first and second operating positions, wherein:
in the first working position, the first side third working oil port (A2) is communicated with the first side fourth working oil port (B2), the first side first working oil port (A1) is communicated with the second side first working oil port (A3), and the first side second working oil port (B1) is communicated with the second side second working oil port (B3);
in the second working position, the first side first working oil port (A1) is communicated with the first side second working oil port (B1), the first side third working oil port (A2) is communicated with the second side first working oil port (A3), and the first side fourth working oil port (B2) is communicated with the second side second working oil port (B3).
7. The pumping hydraulic system according to claim 6, wherein the second pilot solenoid valve (222) is a two-position four-way solenoid valve, the second pilot solenoid valve (222) comprises an electromagnet for controlling switching between a first position and a second position, the second pilot solenoid valve (222) comprises a third oil supply port (A4), a fourth oil supply port (B4), a first oil inlet (P2) and a first oil return port (T2), and the third oil supply port (A4) is communicated with a cavity where a second working position of the second hydraulic directional control valve (221) is located;
when the hydraulic control valve is at the first position, the second hydraulic reversing valve (221) is unloaded through a third oil supply port (A4) of the electromagnetic reversing valve;
and when the hydraulic oil enters the second hydraulic reversing valve (221) through the first oil inlet (P2) at the second position, the hydraulic oil of the external control oil way enters the second hydraulic reversing valve (P2).
8. The pumped hydraulic system of claim 6, characterized in that the main directional control valve (21) and the high-low pressure switching valve (22) are of an integrated valve block structure, and the first pilot solenoid valve (212) and the second pilot solenoid valve (222) are integrated on a valve body or an end cover.
9. The pumping hydraulic system according to any one of claims 1 to 8, characterized in that a pressure control device (30) is further arranged on an oil inlet path of the pumping hydraulic system.
10. Concrete pumping machine, characterized in that it comprises a pumping hydraulic system according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211296101.9A CN115596652A (en) | 2022-10-21 | 2022-10-21 | Pumping hydraulic system and concrete pumping machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211296101.9A CN115596652A (en) | 2022-10-21 | 2022-10-21 | Pumping hydraulic system and concrete pumping machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115596652A true CN115596652A (en) | 2023-01-13 |
Family
ID=84849436
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211296101.9A Pending CN115596652A (en) | 2022-10-21 | 2022-10-21 | Pumping hydraulic system and concrete pumping machine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115596652A (en) |
-
2022
- 2022-10-21 CN CN202211296101.9A patent/CN115596652A/en active Pending
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