Hydraulic system of filling industrial pump

Abstract

The embodiment of the invention discloses a hydraulic system of a filling industrial pump, relates to the technical field of industrial pumps, and can effectively reduce the influence of reversing of the filling industrial pump on slurry conveying. The filling industrial pump hydraulic system comprises a first main pump, a second main pump, a third main pump, a first hydraulic cylinder, a second hydraulic cylinder, a first main valve, a second main valve and a third main valve. The first main valve is connected with the first main pump and the first hydraulic cylinder so that hydraulic oil of the first main pump can flow into the first hydraulic cylinder through the first main valve. The second main valve is connected with the second main pump and the second hydraulic cylinder so that hydraulic oil of the second main pump can flow into the second hydraulic cylinder through the second main valve. The third main valve is connected with the third main pump, the first main valve and the second main valve so that hydraulic oil of the third main pump can flow into the first hydraulic cylinder through the third main valve and the first main valve, or the hydraulic oil of the third main pump can flow into the second hydraulic cylinder through the third main valve and the second main valve. The method is suitable for filling industrial pump design and application scenes.

Description

Technical Field

[0001] The present application relates to the technical field of industrial pumps, and in particular to a filling industrial pump hydraulic system. Background Art

[0002] As the country strengthens its environmental protection efforts, the production requirements for existing mining companies are becoming increasingly stringent. In order to avoid excessive pollution of the mining area and the risk of collapse in the goaf, most companies currently use solid waste such as mine tailings, gravel, fly ash, industrial slag, etc. to make a paste-like slurry that does not require dehydration, and transport it to the underground goaf for filling through filling industrial pumps. This can not only improve the resource extraction rate, but also reduce land occupation and pollution to the environment.

[0003] Filling industrial pumps are crucial for the stable delivery of slurries. However, current filling industrial pumps experience flow interruption when reversing. The instantaneous flow interruption of the slurry causes a sudden change in the flow velocity in the pipeline, resulting in large starting resistance and causing pipeline vibration. Moreover, when transporting the slurry upward, the time difference in reversing the filling industrial pump will cause the slurry to produce a water hammer effect in the pipeline, resulting in excessive impact and reduced component service life. Summary of the Invention

[0004] In view of this, the present application provides a filling industrial pump hydraulic system, which can effectively reduce the impact of the filling industrial pump reversal on slurry transportation.

[0005] An embodiment of the present application provides a filling industrial pump hydraulic system, including: a first main pump, a second main pump, a third main pump, a first hydraulic cylinder, and a second hydraulic cylinder; a first main valve and a second main valve; the first main valve is respectively connected to the first main pump and the first hydraulic cylinder, so that the hydraulic oil of the first main pump can flow into the first hydraulic cylinder through the first main valve; the second main valve is respectively connected to the second main pump and the second hydraulic cylinder, so that the hydraulic oil of the second main pump can flow into the second hydraulic cylinder through the second main valve; a third main valve, the third main valve is respectively connected to the third main pump, the first main valve, and the second main valve, so that the hydraulic oil of the third main pump can flow into the first hydraulic cylinder through the third main valve and the first main valve, or the hydraulic oil of the third main pump can flow into the second hydraulic cylinder through the third main valve and the second main valve.

[0006] In a specific embodiment, the filling industrial pump hydraulic system is configured as follows: the hydraulic oil of the first main pump flows into the rodless chamber of the first hydraulic cylinder through the first main valve at a first front-end outward flow rate, the hydraulic oil of the second main pump flows into the rodless chamber of the second hydraulic cylinder through the second main valve at a second rear-end outward flow rate, and the hydraulic oil of the third main pump flows into the rodless chamber of the first hydraulic cylinder through the third main valve and the first main valve, so that the first piston of the first hydraulic cylinder moves from the first proximal position to the first transition position, and the second piston of the second hydraulic cylinder moves from the second transition position to the second distal position; and, if the second piston of the second hydraulic cylinder moves from the second transition position to the second distal position, the hydraulic oil of the second main pump flows into the rod chamber of the second hydraulic cylinder through the second main valve, so that the second piston of the second hydraulic cylinder moves from the second distal position to the second proximal position; The hydraulic oil of the first master pump flows into the rodless chamber of the first hydraulic cylinder through the first master valve at a first rear-end outward flow rate, the hydraulic oil of the second master pump flows into the rodless chamber of the second hydraulic cylinder through the second master valve at a second front-end outward flow rate, and the hydraulic oil of the third master pump flows into the rodless chamber of the second hydraulic cylinder through the third master valve and the second master valve, so that the first piston of the first hydraulic cylinder moves from the first transition position to the first distal position, and the second piston of the second hydraulic cylinder moves from the second proximal position to the second transition position; and, if the first piston of the first hydraulic cylinder moves from the first transition position to the first distal position, the hydraulic oil of the first master pump flows into the rod chamber of the first hydraulic cylinder through the first master valve, so that the first piston of the first hydraulic cylinder moves from the first distal position to the first proximal position; Among them, the first transition position is located between the first proximal position and the first distal position; the second transition position is located between the second proximal position and the second distal position; the first front-end outbound flow rate is greater than the first rear-end outbound flow rate; the second front-end outbound flow rate is greater than the second rear-end outbound flow rate.

[0007] In a specific embodiment, the first hydraulic cylinder is provided with at least a first transition position detection member and a first remote position detection member; the first transition position detection member is used to detect whether the first piston of the first hydraulic cylinder moves to the first transition position; the first remote position detection member is used to detect whether the first piston of the first hydraulic cylinder moves to the first remote position; the second hydraulic cylinder is provided with at least a second transition position detection member and a second remote position detection member; the second transition position detection member is used to detect whether the second piston of the second hydraulic cylinder moves to the second transition position; the second remote position detection member is used to detect whether the second piston of the second hydraulic cylinder moves to the second remote position.

[0008] In a specific embodiment, the first hydraulic cylinder is provided with a first rod chamber oil port and a first rodless chamber oil port; the second hydraulic cylinder is provided with a second rod chamber oil port and a second rodless chamber oil port; the first main valve is provided with a first oil inlet, a first oil outlet, a first reversing oil port, and a first mutual oil port; the first oil inlet is connected to the oil supply port of the first main pump, the first oil outlet is connected to the oil tank, the first reversing oil port is connected to the first rodless chamber oil port, and the first mutual oil port is connected to the first rod chamber oil port; the second main valve is provided with a second oil inlet, a second oil outlet, a second reversing oil port, and a second mutual oil port; the second oil inlet is connected to the oil supply port of the second main pump, the second oil outlet is connected to the oil tank, the second reversing oil port is connected to the second rodless chamber oil port, and the second mutual oil port is connected to the second rod chamber oil port.

[0009] In a specific embodiment, the third main valve is provided with a third oil inlet, a third oil outlet, a third reversing oil port, and a third mutual oil port; the third oil inlet is connected to the oil supply port of the third main pump, the third oil outlet is connected to the oil tank, the third reversing oil port is connected to the first oil inlet of the first main valve, and the third mutual oil port is connected to the second oil inlet of the second main valve.

[0010] In a specific embodiment, it also includes a first supply pump, a first reversing valve, a first pressure valve cylinder, and a first suction valve cylinder; the first reversing valve is respectively connected to the first supply pump, the first pressure valve cylinder, and the first suction valve cylinder, so that the hydraulic oil of the first supply pump can flow into the first pressure valve cylinder and the first suction valve cylinder through the first reversing valve; it also includes a second supply pump, a second reversing valve, a second pressure valve cylinder, and a second suction valve cylinder; the second reversing valve is respectively connected to the second supply pump, the second pressure valve cylinder, and the second suction valve cylinder, so that the hydraulic oil of the second supply pump can flow into the second pressure valve cylinder and the first suction valve cylinder through the second reversing valve.

[0011] In a specific embodiment, the first pressure valve oil cylinder is provided with a first pressure valve rod chamber oil port and a first pressure valve rodless chamber oil port; the first suction valve oil cylinder is provided with a first suction valve rod chamber oil port and a first suction valve rodless chamber oil port; the second pressure valve oil cylinder is provided with a second pressure valve rod chamber oil port and a second pressure valve rodless chamber oil port; the second suction valve oil cylinder is provided with a second suction valve rod chamber oil port and a second suction valve rodless chamber oil port; the first reversing valve is provided with a first reversing valve oil inlet, a first reversing valve oil outlet, a first reversing valve reversing oil port, and a first reversing valve mutual oil port; the first reversing valve oil inlet is connected to the oil supply port of the first supply pump, the first reversing valve oil outlet is connected to the oil tank, and the first reversing valve reversing oil port is divided They are respectively connected to the rodless chamber oil port of the first pressure valve and the rod chamber oil port of the first suction valve, and the mutual oil port of the first reversing valve is respectively connected to the rod chamber oil port of the first pressure valve and the rodless chamber oil port of the first suction valve; the second reversing valve is provided with a second reversing valve oil inlet, a second reversing valve oil outlet, a second reversing valve reversing oil port, and a second reversing valve mutual oil port; the second reversing valve oil inlet is connected to the oil supply port of the second supply pump, the second reversing valve oil outlet is connected to the oil tank, the reversing oil port of the second reversing valve is respectively connected to the rodless chamber oil port of the second pressure valve and the rod chamber oil port of the second suction valve, and the mutual oil port of the second reversing valve is respectively connected to the rod chamber oil port of the second pressure valve and the rodless chamber oil port of the second suction valve.

[0012] In a specific embodiment, it also includes a first accumulator and a second accumulator, the first accumulator is respectively connected to the oil supply port of the first supply pump and the oil inlet of the first reversing valve; the second accumulator is respectively connected to the oil supply port of the second supply pump and the oil inlet of the second reversing valve.

[0013] The filling industrial pump hydraulic system provided by the embodiment of the present application includes: a first main pump, a second main pump, a third main pump, a first hydraulic cylinder, a second hydraulic cylinder, a first main valve, a second main valve, and a third main valve; the first main valve is respectively connected to the first main pump and the first hydraulic cylinder, so that the hydraulic oil of the first main pump can flow into the first hydraulic cylinder through the first main valve; the second main valve is respectively connected to the second main pump and the second hydraulic cylinder, so that the hydraulic oil of the second main pump can flow into the second hydraulic cylinder through the second main valve; the third main valve is respectively connected to the third main pump, the first main valve, and the second main valve, so that the hydraulic oil of the third main pump can flow into the first hydraulic cylinder through the third main valve and the first main valve, or the hydraulic oil of the third main pump can flow into the second hydraulic cylinder through the third main valve and the second main valve. The hydraulic system uses a first main valve to control the first hydraulic cylinder, a second main valve to control the second hydraulic cylinder, and a third main valve to switch to supplying hydraulic oil to the first hydraulic cylinder and the second hydraulic cylinder to increase the propulsion force, so that the action strokes of the first piston rod of the first hydraulic cylinder and the second piston rod of the second hydraulic cylinder can be matched, so as to avoid the interruption of slurry flow due to reversal of the filling industrial pump and reduce the impact of the reversal of the filling industrial pump on slurry transportation. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0015] Figure 1 A schematic diagram of a filling industrial pump hydraulic system provided in an embodiment of the present application.

[0016] Description of main reference numerals: 100 - filling industrial pump hydraulic system; 11 - first main pump; 12 - second main pump; 13 - third main pump; 21 - first hydraulic cylinder; 211 - first transition position detection member; 212 - first distal position detection member; 213 - first rod chamber oil port; 214 - first rodless chamber oil port; 22 - second hydraulic cylinder; 221 - second transition position detection member; 222 - second distal position detection member; 223 - second rod chamber oil port; 224 - second rodless chamber oil port; 31-first main valve; 311-first oil inlet; 312-first oil outlet; 313-first reversing oil port; 314-first interposition oil port; 32-second main valve; 321-second oil inlet; 322-second oil outlet; 323-second reversing oil port; 324-second interposition oil port; 33-third main valve; 331-third oil inlet; 332-third oil outlet; 333-third reversing oil port; 334-third interposition oil port; 40-oil tank; 51-first Supply pump; 52-second supply pump; 61-first reversing valve; 611-first reversing valve oil inlet; 612-first reversing valve oil outlet; 613-first reversing valve reversing oil port; 614-first reversing valve reciprocating oil port; 62-second reversing valve; 621-second reversing valve oil inlet; 622-second reversing valve oil outlet; 623-second reversing valve reversing oil port; 624-second reversing valve reciprocating oil port; 71-first pressure valve cylinder; 711-first pressure valve cylinder Rod chamber oil port; 712- rodless chamber oil port of the first pressure valve; 72- second pressure valve cylinder; 721- rod chamber oil port of the second pressure valve; 722- rodless chamber oil port of the second pressure valve; 81- first suction valve cylinder; 811- rod chamber oil port of the first suction valve; 812- rodless chamber oil port of the first suction valve; 82- second suction valve cylinder; 821- rod chamber oil port of the second suction valve; 822- rodless chamber oil port of the second suction valve; 91- first accumulator; 92- second accumulator. DETAILED DESCRIPTION

[0017] The embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0018] It should be clear that the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of this application.

[0019] Because the current filling industrial pumps will produce a flow interruption phenomenon when reversing the slurry, the instantaneous flow interruption of the slurry causes a sudden change in the flow velocity in the pipeline, resulting in large starting resistance and causing pipeline vibration. Moreover, when transporting the slurry upward, the time difference of the reversal of the filling industrial pump will cause the slurry to produce a water hammer effect in the pipeline, resulting in excessive impact and reducing the service life of components. In order to solve the above problems, Figure 1As shown, an embodiment of the present application provides a filling industrial pump hydraulic system 100, which may include: a first main pump 11, a second main pump 12, a third main pump 13, a first hydraulic cylinder 21, a second hydraulic cylinder 22, a first main valve 31, a second main valve 32, and a third main valve 33.

[0020] The first master valve 31 is respectively connected to the first main pump 11 and the first hydraulic cylinder 21, so that the hydraulic oil of the first main pump 11 can flow into the first hydraulic cylinder 21 through the first master valve 31; the second master valve 32 is respectively connected to the second main pump 12 and the second hydraulic cylinder 22, so that the hydraulic oil of the second main pump 12 can flow into the second hydraulic cylinder 22 through the second main valve 32; the third main valve 33 is respectively connected to the third main pump 13, the first main valve 31, and the second main valve 32, so that the hydraulic oil of the third main pump 13 can flow into the first hydraulic cylinder 21 through the third main valve 33 and the first main valve 31, or the hydraulic oil of the third main pump 13 can flow into the second hydraulic cylinder 22 through the third main valve 33 and the second main valve 32.

[0021] The first main pump 11 can be composed of one oil pump or two or more oil pumps, the second main pump 12 can also be composed of one oil pump or two or more oil pumps, and the third main pump 13 can also be composed of one oil pump or two or more oil pumps. Figure 1 As shown, the first main pump 11 can be composed of two first main pumps 11A and 11B with a displacement of ‌260 mL / h respectively, the second main pump 12 can also be composed of two second main pumps 12A and 12B with a displacement of ‌260 mL / h respectively, and the third main pump 13 can also be composed of two third main pumps 13A and 13B with a displacement of ‌260 mL / h respectively, so that the first hydraulic cylinder 21 and the second hydraulic cylinder 22 can provide sufficient propulsion force.

[0022] The first hydraulic cylinder 21 is equipped with a first piston and a first piston rod. One end of the first piston rod is connected to the first piston, and the other end of the first piston rod can be connected to the first cylinder piston provided in the first cylinder. The reciprocating movement of the first piston rod can drive the first cylinder piston in the first cylinder to reciprocate, so that the first cylinder can suck slurry from the hopper and push out the sucked slurry for delivery to the filling pipe. The second hydraulic cylinder 22 is equipped with a second piston and a second piston rod. One end of the second piston rod is connected to the second piston, and the other end of the second piston rod can be connected to the second cylinder piston provided in the second cylinder. The reciprocating movement of the second piston rod can drive the second cylinder piston in the second cylinder to reciprocate, so that the second cylinder can suck slurry from the hopper and push out the sucked slurry for delivery to the filling pipe.

[0023] The first master valve 31 is connected to the first main pump 11 and the first hydraulic cylinder 21 via pipelines. The first master valve 31 controls the first piston rod of the first hydraulic cylinder 21 to have a preset working stroke. The second master valve 32 is connected to the second main pump 12 and the second hydraulic cylinder 22 via pipelines. The second master valve 32 controls the second piston rod of the second hydraulic cylinder 22 to have a preset working stroke. In this way, the process in which the first piston rod of the first hydraulic cylinder 21 drives the first cylinder piston in the first cylinder to suck in and push out the slurry, and the process in which the second piston rod of the second hydraulic cylinder 22 drives the second cylinder piston in the second cylinder to suck in and push out the slurry can be matched in a preset manner respectively; thereby avoiding the situation in which the traditional method can only be configured as follows: when the first piston rod of the first hydraulic cylinder 21 drives the first cylinder piston in the first cylinder to finish sucking in the slurry and start pushing out the slurry, the second piston rod of the second hydraulic cylinder 22 drives the second cylinder piston in the second cylinder to finish pushing out the slurry and start sucking in the slurry, and when the first piston rod of the first hydraulic cylinder 21 drives the first cylinder piston in the first cylinder to finish pushing out the slurry and start sucking in the slurry, the second piston rod of the second hydraulic cylinder 22 drives the second cylinder piston in the second cylinder to finish sucking in the slurry and start pushing out the slurry, causing the slurry transported to the filling pipeline to be instantly cut off.

[0024] In addition, the third main valve 33 is connected to the third main pump 13, the first main valve 31, and the second main valve 32 through pipelines respectively. The third main valve 33 is used to switch to the first hydraulic cylinder 21 and the second hydraulic cylinder 22 to supply hydraulic oil to increase the propulsion force, so that the first piston rod of the first hydraulic cylinder 21 drives the first cylinder piston in the first cylinder to have more sufficient propulsion force and response speed in the process of pushing out the slurry, and matches the action stroke of the second piston rod of the second hydraulic cylinder 22 driving the second cylinder piston in the second cylinder, so that the second piston rod of the second hydraulic cylinder 22 drives the second cylinder piston in the second cylinder to have more sufficient propulsion force and response speed in the process of pushing out the slurry, and matches the action stroke of the first piston rod of the first hydraulic cylinder 21 driving the first cylinder piston in the first cylinder.

[0025] The filling industrial pump hydraulic system 100 provided in an embodiment of the present application includes: a first main pump 11, a second main pump 12, a third main pump 13, a first hydraulic cylinder 21, a second hydraulic cylinder 22, a first main valve 31, a second main valve 32, and a third main valve 33; the first main valve 31 is connected to the first main pump 11 and the first hydraulic cylinder 21 respectively, so that the hydraulic oil of the first main pump 11 can flow into the first hydraulic cylinder 21 through the first main valve 31; the second main valve 32 is connected to the second main pump 12 and the second hydraulic cylinder 22 respectively, so that the hydraulic oil of the second main pump 12 can flow into the second hydraulic cylinder 22 through the second main valve 32; the third main valve 33 is connected to the third main pump 13, the first main valve 31, and the second main valve 32 respectively, so that the hydraulic oil of the third main pump 13 can flow into the first hydraulic cylinder 21 through the third main valve 33 and the first main valve 31, or the hydraulic oil of the third main pump 13 can flow into the second hydraulic cylinder 22 through the third main valve 33 and the second main valve 32. The hydraulic system uses the first main valve 31 to control the first hydraulic cylinder 21, uses the second main valve 32 to control the second hydraulic cylinder 22, and uses the third main valve 33 to switch the supply of hydraulic oil to the first hydraulic cylinder 21 and the second hydraulic cylinder 22 to increase the propulsion force. The action strokes of the first piston rod of the first hydraulic cylinder 21 and the second piston rod of the second hydraulic cylinder 22 can be matched to avoid the interruption of slurry flow due to reversal of the filling industrial pump, thereby reducing the impact of the reversal of the filling industrial pump on slurry transportation.

[0026] Optionally, in one embodiment of the present application, the filling industrial pump hydraulic system 100 is configured as follows: the hydraulic oil of the first main pump 11 flows into the rodless chamber of the first hydraulic cylinder 21 through the first master valve 31 at a first front-end outward flow rate, the hydraulic oil of the second main pump 12 flows into the rodless chamber of the second hydraulic cylinder 22 through the second master valve 32 at a second rear-end outward flow rate, and the hydraulic oil of the third main pump 13 flows into the rodless chamber of the first hydraulic cylinder 21 through the third master valve 33 and the first master valve 31, so that the first piston of the first hydraulic cylinder 21 moves from the first proximal position to the first transition position, and the second piston of the second hydraulic cylinder 22 moves from the second transition position to the second distal position; and, if the second piston of the second hydraulic cylinder 22 moves from the second transition position to the second distal position, the hydraulic oil of the second main pump 12 flows into the rod chamber of the second hydraulic cylinder 22 through the second master valve 32, so that the second piston of the second hydraulic cylinder 22 moves from the second distal position to the second proximal position.

[0027] The hydraulic oil of the first master pump 11 flows into the rodless chamber of the first hydraulic cylinder 21 through the first master valve 31 at the first rear-end outward flow rate, the hydraulic oil of the second master pump 12 flows into the rodless chamber of the second hydraulic cylinder 22 through the second master valve 32 at the second front-end outward flow rate, and the hydraulic oil of the third master pump 13 flows into the rodless chamber of the second hydraulic cylinder 22 through the third master valve 33 and the second master valve 32, so that the first piston of the first hydraulic cylinder 21 moves from the first transition position to the first distal position, and the second piston of the second hydraulic cylinder 22 moves from the second proximal position to the second transition position; and, if the first piston of the first hydraulic cylinder 21 moves from the first transition position to the first distal position, the hydraulic oil of the first master pump 11 flows into the rod chamber of the first hydraulic cylinder 21 through the first master valve 31, so that the first piston of the first hydraulic cylinder 21 moves from the first distal position to the first proximal position.

[0028] Among them, the first transition position is located between the first proximal position and the first distal position; the second transition position is located between the second proximal position and the second distal position; the first front section outbound flow rate is greater than the first rear section outbound flow rate; the second front section outbound flow rate is greater than the second rear section outbound flow rate.

[0029] It can be understood that based on the above configuration, the piston and piston rod of at least one of the first hydraulic cylinder 21 and the second hydraulic cylinder 22 can drive the cylinder piston in the corresponding cylinder to be in the stroke of pushing out the slurry, thereby avoiding the situation where the slurry transported to the filling pipeline is instantly interrupted.

[0030] In addition, the stroke positions of the first piston of the first hydraulic cylinder 21 include a first proximal position, a first transition position, and a first distal position, so that the stroke for pushing out the slurry can be divided into a first front stroke from the first proximal position to the first transition position, and a first rear stroke from the first transition position to the first distal position. In the first front stroke, there is more slurry in the first cylinder and the resistance is greater. The hydraulic oil of the first main pump 11 flows into the rodless cavity of the first hydraulic cylinder 21 at a higher first front stroke flow rate, thereby making the first hydraulic cylinder 21 have a higher propulsion force; in the first rear stroke, there is less slurry in the first cylinder and the resistance is smaller. The hydraulic oil of the first main pump 11 flows into the rodless cavity of the first hydraulic cylinder 21 at a lower first rear stroke flow rate, thereby making the first hydraulic cylinder 21 have an appropriate propulsion force.

[0031] Similarly, the stroke positions of the second piston of the second hydraulic cylinder 22 include a second proximal position, a second transition position, and a second distal position, so that the stroke for pushing out the slurry can be divided into a second front stroke from the second proximal position to the second transition position, and a second rear stroke from the second transition position to the second distal position. In the second front stroke, the slurry in the second cylinder is more and the resistance is greater, and the hydraulic oil of the second main pump 12 flows into the rodless cavity of the second hydraulic cylinder 22 at a higher second front stroke flow rate, thereby making the second hydraulic cylinder 22 have a higher propulsion force; in the second rear stroke, the slurry in the second cylinder is less and the resistance is smaller, and the hydraulic oil of the second main pump 12 flows into the rodless cavity of the second hydraulic cylinder 22 at a lower second rear stroke flow rate, thereby making the second hydraulic cylinder 22 have an appropriate propulsion force.

[0032] Optionally, in one embodiment of the present application, the first hydraulic cylinder 21 is provided with at least a first transition position detection member 211 and a first remote position detection member 212; the first transition position detection member 211 is used to detect whether the first piston of the first hydraulic cylinder 21 moves to the first transition position; the first remote position detection member 212 is used to detect whether the first piston of the first hydraulic cylinder 21 moves to the first remote position; the second hydraulic cylinder 22 is provided with at least a second transition position detection member 221 and a second remote position detection member 222; the second transition position detection member 221 is used to detect whether the second piston of the second hydraulic cylinder 22 moves to the second transition position; the second remote position detection member 222 is used to detect whether the second piston of the second hydraulic cylinder 22 moves to the second remote position.

[0033] The first transition position detection component 211 and the first remote position detection component 212 can be used to detect whether the first piston of the first hydraulic cylinder 21 moves to the first transition position or the first remote position. The second transition position detection component 221 and the second remote position detection component 222 can be used to detect whether the second piston of the second hydraulic cylinder 22 moves to the second transition position or the second remote position. In this way, corresponding signals can be sent according to the detection results to control the first main pump 11, the second main pump 12, the first main valve 31, the second main valve 32, and the third main valve 33, so that the first main pump 11 and the second main pump 12 respectively supply hydraulic oil according to the preset flow rate, and the first main valve 31, the second main valve 32, and the third main valve 33 are switched to the corresponding working positions to form a preset hydraulic flow path.

[0034] For example, if the first transition position detection component 211 detects that the first piston of the first hydraulic cylinder 21 moves from the first proximal position to the first transition position, a corresponding signal can be sent to control the hydraulic oil supplied by the first main pump 11 to be reduced from the first front-end outward flow rate to the first rear-end outward flow rate, and control the third main valve 33 to switch the working position, so that the hydraulic oil supplied by the third main pump 13 no longer flows to the rodless chamber of the first hydraulic cylinder 21 through the first main valve 31, but flows to the rodless chamber of the second hydraulic cylinder 22 through the second main valve 32, and controls the hydraulic oil supplied by the second main pump 12 to flow to the rodless chamber of the second hydraulic cylinder 22 through the second main pump 12, so that the second piston of the second hydraulic cylinder 22 moves from the second proximal position to the second transition position. If the first distal position detection member 212 detects that the first piston of the first hydraulic cylinder 21 moves from the first transition position to the first distal position, a corresponding signal can be sent to control the first main valve 31 to switch the working position, so that the hydraulic oil supplied by the first main pump 11 no longer flows to the rodless chamber of the first hydraulic cylinder 21, but flows to the rod chamber of the first hydraulic cylinder 21, so that the first piston of the first hydraulic cylinder 21 quickly retreats from the first distal position to the first proximal position. Similarly, the second transition position detection member 221 and the second distal position detection member 222 can also be used to achieve corresponding action stroke control, so that the first piston of the first hydraulic cylinder 21 and the second piston of the second hydraulic cylinder 22 can work alternately according to the preset action stroke, so that the piston and piston rod of at least one of the first hydraulic cylinder 21 and the second hydraulic cylinder 22 drive the cylinder piston in the corresponding cylinder to be in the stroke of pushing out the slurry, thereby avoiding the situation where the slurry transported to the filling pipeline is instantly cut off.

[0035] Optionally, in one embodiment of the present application, the first hydraulic cylinder 21 is provided with a first rod chamber oil port 213 and a first rodless chamber oil port 214; the second hydraulic cylinder 22 is provided with a second rod chamber oil port 223 and a second rodless chamber oil port 224; the first main valve 31 is provided with a first oil inlet 311, a first oil outlet 312, a first reversing oil port 313, and a first mutual oil port 314; the first oil inlet 311 is connected to the oil supply port of the first main pump 11, the first oil outlet 312 is connected to the oil tank 40, and the first reversing oil port 313 is connected to the oil tank 40. 13 is connected to the first rodless chamber oil port 214, and the first mutual oil port 314 is connected to the first rod chamber oil port 213; the second main valve 32 is provided with a second oil inlet 321, a second oil outlet 322, a second reversing oil port 323, and a second mutual oil port 324; the second oil inlet 321 is connected to the oil supply port of the second main pump 12, the second oil outlet 322 is connected to the oil tank 40, the second reversing oil port 323 is connected to the second rodless chamber oil port 224, and the second mutual oil port 324 is connected to the second rod chamber oil port 223.

[0036] For example, the first main valve 31 can be a three-position, four-way reversing valve controlled by a pilot valve. The second main valve 32 can also be a three-position, four-way reversing valve controlled by a pilot valve. The third main valve 33 can be a two-position, four-way reversing valve controlled by a pilot valve. The first and second main valves 31, 32 can each be a three-position, four-way reversing valve with a DN63 diameter, while the third main valve 33 can be a two-position, four-way reversing valve with a DN50 diameter.

[0037] Hydraulic oil flows out of one of the first reversing oil port 313 and the first interlocking oil port 314 of the first main valve 31, while hydraulic oil flows in. When the first main valve 31 is in the left position, the first oil inlet 311 is connected to the first reversing oil port 313, and the first oil outlet 312 is connected to the first interlocking oil port 314. When the first main valve 31 is in the middle position, the first oil inlet 311, the first oil outlet 312, the first reversing oil port 313, and the first interlocking oil port 314 are closed. When the first main valve 31 is in the right position, the first oil inlet 311 is connected to the first interlocking oil port 314, and the first oil outlet 312 is connected to the first reversing oil port 313. Hydraulic oil flows out of one of the second reversing oil port 323 and the second interlocking oil port 324 of the second main valve 32, while hydraulic oil flows in the other. When the second main valve 32 is in the left position, the second oil inlet 321 is connected to the second reversing oil port 323, and the second oil outlet 322 is connected to the second mutual oil port 324; when the second main valve 32 is in the middle position, the second oil inlet 321, the second oil outlet 322, the second reversing oil port 323, and the second mutual oil port 324 are closed; when the second main valve 32 is in the right position, the second oil inlet 321 is connected to the second mutual oil port 324, and the second oil outlet 322 is connected to the second reversing oil port 323.

[0038] Optionally, in one embodiment of the present application, the third master valve 33 is provided with a third oil inlet 331, a third oil outlet 332, a third reversing oil port 333, and a third mutual oil port 334; the third oil inlet 331 is connected to the oil supply port of the third main pump 13, the third oil outlet 332 is connected to the oil tank 40, the third reversing oil port 333 is connected to the first oil inlet 311 of the first master valve 31, and the third mutual oil port 334 is connected to the second oil inlet 321 of the second main valve 32.

[0039] Hydraulic oil flows out of one of the third reversing oil port 333 and the third interlocking oil port 334 of the third main valve 33, while hydraulic oil flows in. When the third main valve 33 is in the left position, the third oil inlet 331 is connected to the third reversing oil port 333, and the third oil outlet 332 is connected to the third interlocking oil port 334. When the third main valve 33 is in the right position, the third oil inlet 331 is connected to the third interlocking oil port 334, and the third oil outlet 332 is connected to the third reversing oil port 333.

[0040] Optionally, in one embodiment of the present application, it also includes a first supply pump 51, a first reversing valve 61, a first pressure valve cylinder 71, and a first suction valve cylinder 81; the first reversing valve 61 is respectively connected to the first supply pump 51, the first pressure valve cylinder 71, and the first suction valve cylinder 81, so that the hydraulic oil of the first supply pump 51 can flow into the first pressure valve cylinder 71 and the first suction valve cylinder 81 through the first reversing valve 61; it also includes a second supply pump 52, a second reversing valve 62, a second pressure valve cylinder 72, and a second suction valve cylinder 82; the second reversing valve 62 is respectively connected to the second supply pump 52, the second pressure valve cylinder 72, and the second suction valve cylinder 82, so that the hydraulic oil of the second supply pump 52 can flow into the second pressure valve cylinder 72 and the first suction valve cylinder 81 through the second reversing valve 62.

[0041] The first pressure valve cylinder 71 can be configured with a first pressure valve piston and a first pressure valve piston rod. One end of the first pressure valve piston rod is connected to the first pressure valve piston, and the other end of the first pressure valve piston rod can be connected to the first pressure valve. The first pressure valve can be used to control the opening and closing of the discharge port of the first material cylinder; the first suction valve cylinder 81 can be configured with a first suction valve piston and a first suction valve piston rod. One end of the first suction valve piston rod is connected to the first suction valve piston, and the other end of the first suction valve piston rod can be connected to the first suction valve. The first suction valve can be used to control the opening and closing of the feed port of the first material cylinder.

[0042] Similarly, the second pressure valve cylinder 72 can be configured with a second pressure valve piston and a second pressure valve piston rod, one end of the second pressure valve piston rod is connected to the second pressure valve piston, and the other end of the second pressure valve piston rod can be connected to the second pressure valve, and the second pressure valve can be used to control the opening and closing of the discharge port of the second material cylinder; the second suction valve cylinder 82 can be configured with a second suction valve piston and a second suction valve piston rod, one end of the second suction valve piston rod is connected to the second suction valve piston, and the other end of the second suction valve piston rod can be connected to the second suction valve, and the second suction valve can be used to control the opening and closing of the feed port of the second material cylinder.

[0043] The first reversing valve 61 is used to control the oil supply from the first supply pump 51 to the first pressure valve cylinder 71 and the first suction valve cylinder 81 , and the second reversing valve 62 is used to control the oil supply from the second supply pump 52 to the second pressure valve cylinder 72 and the second suction valve cylinder 82 .

[0044] Optionally, in one embodiment of the present application, the first pressure valve cylinder 71 is provided with a first pressure valve rod chamber oil port 711 and a first pressure valve rodless chamber oil port 712; the first suction valve cylinder 81 is provided with a first suction valve rod chamber oil port 811 and a first suction valve rodless chamber oil port 812; the second pressure valve cylinder 72 is provided with a second pressure valve rod chamber oil port 721 and a second pressure valve rodless chamber oil port 722; the second suction valve cylinder 82 is provided with a second suction valve rod chamber oil port 821 and a second suction valve rodless chamber oil port 822.

[0045] The first reversing valve 61 is provided with a first reversing valve oil inlet 611, a first reversing valve oil outlet 612, a first reversing valve reversing oil port 613, and a first reversing valve mutual oil port 614; the first reversing valve oil inlet 611 is connected to the oil supply port of the first supply pump 51, the first reversing valve oil outlet 612 is connected to the oil tank 40, the first reversing valve reversing oil port 613 is respectively connected to the first pressure valve rodless chamber oil port 712 and the first suction valve rod chamber oil port 811, and the first reversing valve mutual oil port 614 is respectively connected to the first pressure valve rod chamber oil port 711 and the first suction valve rodless chamber oil port 812.

[0046] The second reversing valve 62 is provided with a second reversing valve oil inlet 621, a second reversing valve oil outlet 622, a second reversing valve reversing oil port 623, and a second reversing valve mutual oil port 624; the second reversing valve oil inlet 621 is connected to the oil supply port of the second supply pump 52, the second reversing valve oil outlet 622 is connected to the oil tank 40, the second reversing valve reversing oil port 623 is respectively connected to the second pressure valve rodless chamber oil port 722 and the second suction valve rod chamber oil port 821, and the second reversing valve mutual oil port 624 is respectively connected to the second pressure valve rod chamber oil port 721 and the second suction valve rodless chamber oil port 822.

[0047] The first reversing valve 61 and the second reversing valve 62 can each be a three-position, four-way reversing valve, each controlled by a pilot valve. Hydraulic oil flows out of one of the first reversing valve reversing port 613 and the first reversing valve mutual oil port 614 of the first reversing valve 61, while hydraulic oil flows into the other. When the first reversing valve 61 is in the left position, the first reversing valve oil inlet 611 is connected to the first reversing valve reversing oil port 613, and the first reversing valve oil outlet 612 is connected to the first reversing valve interposition oil port 614. When the first reversing valve 61 is in the middle position, the first reversing valve oil inlet 611, the first reversing valve oil outlet 612, the first reversing valve reversing oil port 613, and the first reversing valve interposition oil port 614 are closed. When the first reversing valve 61 is in the right position, the first reversing valve oil inlet 611 is connected to the first reversing valve interposition oil port 614, and the first reversing valve oil outlet 612 is connected to the first reversing valve reversing oil port 613. Hydraulic oil flows out of one of the second reversing valve reversing oil port 623 and the second reversing valve interposition oil port 624 of the second reversing valve 62, while hydraulic oil flows into the other. When the second reversing valve 62 is in the left position, the second reversing valve oil inlet 621 is connected with the second reversing valve reversing oil port 623, and the second reversing valve oil outlet 622 is connected with the second reversing valve mutual oil port 624; when the second reversing valve 62 is in the middle position, the second reversing valve oil inlet 621, the second reversing valve oil outlet 622, the second reversing valve reversing oil port 623, and the second reversing valve mutual oil port 624 are closed; when the second reversing valve 62 is in the right position, the second reversing valve oil inlet 621 is connected with the second reversing valve mutual oil port 624, and the second reversing valve oil outlet 622 is connected with the second reversing valve reversing oil port 623.

[0048] Optionally, in one embodiment of the present application, a first accumulator 91 and a second accumulator 92 are further included, and the first accumulator 91 is respectively connected to the oil supply port of the first supply pump 51 and the oil inlet 611 of the first reversing valve; the second accumulator 92 is respectively connected to the oil supply port of the second supply pump 52 and the oil inlet 621 of the second reversing valve.

[0049] In this embodiment, Figure 1As shown, the first accumulator 91 can be composed of two first accumulators 91A and 91B, each with a volume of 10 L. The second accumulator 92 can also be composed of two second accumulators 92A and 92B, each with a volume of 10 L. The first supply pump 51 can be used to supply oil to the pilot valve of the first main valve 31, the pilot valve of the third main valve 33, the pilot valve of the first reversing valve 61, and the first accumulator 91. The second supply pump 52 can be used to supply oil to the pilot valve of the second main valve 32, the pilot valve of the second reversing valve 62, and the second accumulator 92. The first supply pump 51 can be an oil pump with a displacement of 45 mL / h, and the second supply pump 52 can also be an oil pump with a displacement of 45 mL / h. When the piston rod of the first pressure valve cylinder 71 and the piston rod of the first suction valve cylinder 81 need to reverse, the first accumulator 91 can quickly release hydraulic energy for rapid reversal; when the piston rod of the second pressure valve cylinder 72 and the piston rod of the second suction valve cylinder 82 need to reverse, the second accumulator 92 can quickly release hydraulic energy for rapid reversal.

[0050] In the description of the embodiments of the present application, it should be noted that, unless otherwise clearly specified and limited, the terms "installation" and "connection" should be understood in a broad sense. For example, "connection" can be a detachable connection or a non-detachable connection; it can be a direct connection or an indirect connection through an intermediate medium. Among them, "fixed connection" means that the two are connected to each other and the relative position relationship after connection remains unchanged. The directional terms mentioned in the embodiments of the present application, such as "upper", "lower", "inside", "outside", etc., are only reference to the directions of the accompanying drawings. Therefore, the directional terms used are for better and clearer explanation and understanding of the embodiments of the present application, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the embodiments of the present application. "Multiple" means at least two.

[0051] In the embodiments of this application, the terms "first," "second," "third," and "fourth" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, a feature specified as "first," "second," "third," or "fourth" may explicitly or implicitly include one or more of the features.

[0052] In the embodiments of this application, "and / or" is simply a description of the association relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A exists alone, A and B exist simultaneously, and B exists alone. In addition, the character " / " in this document generally indicates that the related objects are in an "or" relationship.

[0053] References to "one embodiment" or "some embodiments" in this specification mean that a particular feature, structure, or characteristic described in conjunction with the embodiment is included in one or more embodiments of the present application. Thus, phrases such as "in one embodiment," "in some embodiments," "in some other embodiments," and "in another embodiment" appearing in various places in this specification do not necessarily refer to the same embodiment, but rather mean "one or more but not all embodiments," unless otherwise specifically emphasized. The terms "including," "comprising," "having," and variations thereof all mean "including but not limited to," unless otherwise specifically emphasized.

[0054] The above content has briefly described the embodiments of the present application in detail. Those skilled in the art can design and modify the device and its usage within the scope of the present application according to the on-site construction conditions.

[0055] Each embodiment in this specification is described in a related manner. The same or similar parts between the embodiments can be referred to each other. Each embodiment focuses on the differences from other embodiments.

[0056] The above description is merely a specific embodiment of the present application, but the scope of protection of the present application is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present application should be included in the scope of protection of the present application. Therefore, the scope of protection of the present application should be based on the scope of protection of the claims.

Claims

1. A filling industrial pump hydraulic system, characterized in that, include: A first main pump, a second main pump, a third main pump, a first hydraulic cylinder, and a second hydraulic cylinder; a first main valve and a second main valve; the first main valve is connected to the first main pump and the first hydraulic cylinder respectively, so that the hydraulic oil of the first main pump can flow into the first hydraulic cylinder through the first main valve; the second main valve is connected to the second main pump and the second hydraulic cylinder respectively, so that the hydraulic oil of the second main pump can flow into the second hydraulic cylinder through the second main valve; The third main valve is respectively connected to the third main pump, the first main valve, and the second main valve, so that the hydraulic oil of the third main pump can flow into the first hydraulic cylinder through the third main valve and the first main valve, or the hydraulic oil of the third main pump can flow into the second hydraulic cylinder through the third main valve and the second main valve.

2. The filling industrial pump hydraulic system according to claim 1, characterized in that: Configured to: The hydraulic oil of the first master pump flows into the rodless chamber of the first hydraulic cylinder through the first master valve at a first front-end outward flow rate, the hydraulic oil of the second master pump flows into the rodless chamber of the second hydraulic cylinder through the second master valve at a second rear-end outward flow rate, and the hydraulic oil of the third master pump flows into the rodless chamber of the first hydraulic cylinder through the third master valve and the first master valve, so that the first piston of the first hydraulic cylinder moves from the first proximal position to the first transition position, and the second piston of the second hydraulic cylinder moves from the second transition position to the second distal position; and, if the second piston of the second hydraulic cylinder moves from the second transition position to the second distal position, the hydraulic oil of the second master pump flows into the rod chamber of the second hydraulic cylinder through the second master valve, so that the second piston of the second hydraulic cylinder moves from the second distal position to the second proximal position; The hydraulic oil of the first master pump flows into the rodless chamber of the first hydraulic cylinder through the first master valve at a first rear-end outward flow rate, the hydraulic oil of the second master pump flows into the rodless chamber of the second hydraulic cylinder through the second master valve at a second front-end outward flow rate, and the hydraulic oil of the third master pump flows into the rodless chamber of the second hydraulic cylinder through the third master valve and the second master valve, so that the first piston of the first hydraulic cylinder moves from the first transition position to the first distal position, and the second piston of the second hydraulic cylinder moves from the second proximal position to the second transition position; and, if the first piston of the first hydraulic cylinder moves from the first transition position to the first distal position, the hydraulic oil of the first master pump flows into the rod chamber of the first hydraulic cylinder through the first master valve, so that the first piston of the first hydraulic cylinder moves from the first distal position to the first proximal position; Among them, the first transition position is located between the first proximal position and the first distal position; the second transition position is located between the second proximal position and the second distal position; the first front-end outbound flow rate is greater than the first rear-end outbound flow rate; the second front-end outbound flow rate is greater than the second rear-end outbound flow rate.

3. The filling industrial pump hydraulic system according to claim 2, characterized in that: The first hydraulic cylinder is provided with at least a first transition position detection member and a first distal position detection member; the first transition position detection member is used to detect whether the first piston of the first hydraulic cylinder has moved to the first transition position; the first distal position detection member is used to detect whether the first piston of the first hydraulic cylinder has moved to the first distal position; The second hydraulic cylinder is provided with at least a second transition position detection component and a second remote position detection component; the second transition position detection component is used to detect whether the second piston of the second hydraulic cylinder moves to the second transition position; the second remote position detection component is used to detect whether the second piston of the second hydraulic cylinder moves to the second remote position.

4. The filling industrial pump hydraulic system according to claim 3, characterized in that: The first hydraulic cylinder is provided with a first rod chamber oil port and a first rodless chamber oil port; the second hydraulic cylinder is provided with a second rod chamber oil port and a second rodless chamber oil port; The first main valve is provided with a first oil inlet, a first oil outlet, a first reversing oil port, and a first mutual oil port; the first oil inlet is connected to the oil supply port of the first main pump, the first oil outlet is connected to the oil tank, the first reversing oil port is connected to the first rodless chamber oil port, and the first mutual oil port is connected to the first rod chamber oil port; The second main valve is provided with a second oil inlet, a second oil outlet, a second reversing oil port, and a second mutual oil port; the second oil inlet is connected to the oil supply port of the second main pump, the second oil outlet is connected to the oil tank, the second reversing oil port is connected to the second rodless chamber oil port, and the second mutual oil port is connected to the second rod chamber oil port.

5. The filling industrial pump hydraulic system according to claim 4, characterized in that: The third main valve is provided with a third oil inlet, a third oil outlet, a third reversing oil port, and a third mutual oil port; the third oil inlet is connected to the oil supply port of the third main pump, the third oil outlet is connected to the oil tank, the third reversing oil port is connected to the first oil inlet of the first main valve, and the third mutual oil port is connected to the second oil inlet of the second main valve.

6. The filling industrial pump hydraulic system according to claim 5, characterized in that: The system further includes a first supply pump, a first reversing valve, a first pressure valve cylinder, and a first suction valve cylinder; the first reversing valve is connected to the first supply pump, the first pressure valve cylinder, and the first suction valve cylinder, respectively, so that the hydraulic oil of the first supply pump can flow into the first pressure valve cylinder and the first suction valve cylinder through the first reversing valve; It also includes a second supply pump, a second reversing valve, a second pressure valve cylinder, and a second suction valve cylinder; the second reversing valve is respectively connected to the second supply pump, the second pressure valve cylinder, and the second suction valve cylinder, so that the hydraulic oil of the second supply pump can flow into the second pressure valve cylinder and the first suction valve cylinder through the second reversing valve.

7. The filling industrial pump hydraulic system according to claim 6, characterized in that: The first pressure valve oil cylinder is provided with a first pressure valve rod chamber oil port and a first pressure valve rodless chamber oil port; the first suction valve oil cylinder is provided with a first suction valve rod chamber oil port and a first suction valve rodless chamber oil port; The second pressure valve oil cylinder is provided with a second pressure valve rod chamber oil port and a second pressure valve rodless chamber oil port; the second suction valve oil cylinder is provided with a second suction valve rod chamber oil port and a second suction valve rodless chamber oil port; The first reversing valve is provided with a first reversing valve oil inlet, a first reversing valve oil outlet, a first reversing valve reversing oil port, and a first reversing valve mutual oil port; the first reversing valve oil inlet is connected to the oil supply port of the first supply pump, the first reversing valve oil outlet is connected to the oil tank, the first reversing valve reversing oil port is respectively connected to the first pressure valve rodless chamber oil port and the first suction valve rod chamber oil port, and the first reversing valve mutual oil port is respectively connected to the first pressure valve rod chamber oil port and the first suction valve rodless chamber oil port; The second reversing valve is provided with a second reversing valve oil inlet, a second reversing valve oil outlet, a second reversing valve reversing oil port, and a second reversing valve mutual oil port; the second reversing valve oil inlet is connected to the oil supply port of the second supply pump, the second reversing valve oil outlet is connected to the oil tank, the second reversing valve reversing oil port is respectively connected to the second pressure valve rodless chamber oil port and the second suction valve rod chamber oil port, and the second reversing valve mutual oil port is respectively connected to the second pressure valve rod chamber oil port and the second suction valve rodless chamber oil port.

8. The filling industrial pump hydraulic system according to claim 7, characterized in that: It also includes a first accumulator and a second accumulator, the first accumulator is respectively connected to the oil supply port of the first supply pump and the oil inlet of the first reversing valve; the second accumulator is respectively connected to the oil supply port of the second supply pump and the oil inlet of the second reversing valve.

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