CN116576167A - Hydraulic system and hydraulic control method - Google Patents
Hydraulic system and hydraulic control method Download PDFInfo
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- CN116576167A CN116576167A CN202310523842.4A CN202310523842A CN116576167A CN 116576167 A CN116576167 A CN 116576167A CN 202310523842 A CN202310523842 A CN 202310523842A CN 116576167 A CN116576167 A CN 116576167A
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- plunger pump
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- pump
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- 238000000034 method Methods 0.000 title claims abstract description 18
- 238000006073 displacement reaction Methods 0.000 claims abstract description 230
- 239000003921 oil Substances 0.000 claims description 86
- 239000010720 hydraulic oil Substances 0.000 claims description 48
- 230000001502 supplementing effect Effects 0.000 claims description 41
- 230000008569 process Effects 0.000 claims description 4
- 239000000446 fuel Substances 0.000 abstract description 9
- 239000007788 liquid Substances 0.000 abstract description 6
- 239000004576 sand Substances 0.000 description 44
- 239000012530 fluid Substances 0.000 description 8
- 230000007704 transition Effects 0.000 description 7
- 238000010276 construction Methods 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000004134 energy conservation Methods 0.000 description 4
- 239000010705 motor oil Substances 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 3
- 239000000654 additive Substances 0.000 description 3
- 229910052799 carbon Inorganic materials 0.000 description 3
- 230000009977 dual effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000003756 stirring Methods 0.000 description 3
- 230000000996 additive effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000000153 supplemental effect Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- -1 density Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a hydraulic system and a hydraulic control method, comprising the following steps: a first variable displacement plunger pump driven by the first driving section and a second variable displacement plunger pump driven by the second driving section; the driving motor is used for driving the centrifugal pump, the first variable plunger pump and the second variable plunger pump are connected with the driving motor, and the output oil liquid of the first variable plunger pump and/or the output oil liquid of the second variable plunger pump is used for driving the driving motor to operate; the hydraulic system has different displacement working states, and the working conditions of the first variable plunger pump and the second variable plunger pump are controlled according to the condition of the displacement working state of the hydraulic system. By the technical scheme provided by the invention, the technical problem that the fuel consumption of the hydraulic system in the prior art is higher during small-displacement operation can be solved.
Description
Technical Field
The invention relates to the technical field of sand pump driving, in particular to a hydraulic system and a hydraulic control method.
Background
At present, the sand mixing vehicle automatically tracks the fracturing construction process through an automatic control technology, realizes the automatic control of parameters such as liquid level, additives, density, sand pump discharge pressure and the like, and has the functions of mixing, stirring and conveying fracturing media. The power device of the sand mixing vehicle is a chassis vehicle engine on the bench and under the bench, and the chassis vehicle engine on the bench and under the bench respectively control the running of a clean water centrifugal pump, a stirring tank, an auger motor, various additive pumps, a hydraulic system for heat dissipation and the like and a sand pump and adopts hydraulic driving. When in site construction operation, one sand mixing vehicle is matched with a plurality of fracturing trucks to operate, and the sand mixing vehicle plays a role in heart in the whole construction process. The fracturing fluid mixing vehicle is a vehicle-mounted continuous mixing vehicle for the fracturing fluid on an operation site, meets the construction mode of the existing mixing and the existing fracturing, has the functions of realizing accurate continuous uniform feeding and high-quality continuous liquid mixing, and is characterized in that a power device of the fracturing fluid mixing vehicle is a chassis vehicle engine on a bench and a chassis vehicle engine under the bench, and the chassis vehicle engine on the bench and the chassis vehicle engine under the bench respectively control the running of a clean water centrifugal pump, each stirring tank, various additive pumps, a hydraulic system for heat dissipation and the like and a fracturing fluid discharge pump and adopts hydraulic driving. During field operation, the fracturing fluid mixing vehicle can be used for being connected with a sand mixing vehicle to realize pressure mixing. The existing two devices are matched with each other in that a chassis engine drives a hydraulic single pump to drive the sand pump to operate or a hydraulic pump driven by a bench engine to merge to drive the sand pump to operate.
However, when small displacement operations are performed on site, the rotational speed of the sand pump or fracturing fluid discharge pump is required to be substantially fixed due to the operation of the fracturing truck, which results in that even in small displacement operations on site, the on-board engine and the off-board engine are operated simultaneously, resulting in that the fuel consumption on site is still high. Meanwhile, the load of the on-site bench engine is too low, so that the engine oil burning phenomenon of the bench engine is serious.
Disclosure of Invention
The invention mainly aims to provide a hydraulic system and a hydraulic control method, which are used for solving the technical problem that the hydraulic system in the prior art has higher fuel consumption during small-displacement operation.
To achieve the above object, according to one aspect of the present invention, there is provided a hydraulic system including: a first variable displacement plunger pump driven by the first driving section and a second variable displacement plunger pump driven by the second driving section; the driving motor is used for driving the centrifugal pump, the first variable plunger pump and the second variable plunger pump are connected with the driving motor, and the output oil liquid of the first variable plunger pump and/or the output oil liquid of the second variable plunger pump is used for driving the driving motor to operate; the hydraulic system has different displacement working states, and the working conditions of the first variable plunger pump and the second variable plunger pump are controlled according to the condition of the displacement working state of the hydraulic system.
Further, the hydraulic system has a first displacement operating condition and a second displacement operating condition, the displacement of the first displacement operating condition being greater than the displacement of the second displacement operating condition; when the hydraulic system is in a first displacement working state, the first variable plunger pump and the second variable plunger pump are both in working states, and the working displacement of the driving motor is kept at the maximum displacement; when the hydraulic system is in the second displacement working state, the first variable plunger pump is in a non-working state, the second variable plunger pump is in a working state, and the working displacement of the driving motor is reduced to a preset displacement.
Further, the drive motor is a variable motor; when the hydraulic system is in a first displacement working state, the inclination angle of a swash plate of the driving motor is kept at the maximum displacement; when the hydraulic system is in the second displacement working state, the inclination angle of the swash plate of the driving motor is adjusted so as to adjust the working displacement of the driving motor to the preset displacement.
Further, the driving motor is an electric control motor; when the hydraulic system is in the first displacement working state, the electric control motor is in a power-off state; when the hydraulic system is in the second displacement working state, the electric control motor is in a power-on state, so that the electric control motor adjusts the inclination angle of the swash plate of the driving motor through electric control.
Further, the driving motor is a hydraulic control motor, the first variable plunger pump is driven by a power takeoff of the chassis, and the hydraulic system further comprises:
the first reversing valve is connected with the driving motor; when the hydraulic system is in a first displacement working state, the first reversing valve is in a first reversing position; when the hydraulic system is in the second displacement operating state, the first reversing valve is in a first initial position.
Further, the hydraulic system also comprises a pressure reducing valve which is connected with the first reversing valve; and/or the number of the groups of groups,
the first reversing valve is a pneumatic reversing valve, an electromagnetic reversing valve or a manual reversing valve.
Further, the drive motor includes a first dosing motor and a second dosing motor; when the hydraulic system is in a first displacement working state, the first quantitative motor and the second quantitative motor are connected in parallel, and the first quantitative motor and the second quantitative motor are both in a working state;
when the hydraulic system is in the second displacement working state, the second variable plunger pump is in zero displacement, and the first variable plunger pump is in a working state; or alternatively, the process may be performed,
when the hydraulic system is in the second displacement operating state, the second variable displacement plunger pump is connected in series with the first variable displacement plunger pump.
Further, the first variable displacement plunger pump is driven by the power takeoff of the chassis, and the hydraulic system further comprises:
the second reversing valve is connected with a second variable plunger pump;
the second reversing valve and the second quantitative motor are connected with the third reversing valve;
when the hydraulic system is in the first displacement working state, the second reversing valve is in a second reversing position; when the hydraulic system is in the second displacement working state, the second reversing valve is in the second initial position, and the third reversing valve is in the third reversing position, so that the oil inlet of the second quantitative motor is communicated with the oil outlet of the second quantitative motor.
Further, the second reversing valve is a pneumatic reversing valve, an electromagnetic reversing valve or a manual reversing valve; and/or the number of the groups of groups,
the third reversing valve is a hydraulic control reversing valve.
Further, the first variable displacement plunger pump is driven by the power takeoff of the chassis, and the hydraulic system further comprises:
the fourth reversing valve is connected with the second variable plunger pump;
the fifth reversing valve, the fourth reversing valve, the first quantitative motor and the second quantitative motor are all connected with the fifth reversing valve;
when the hydraulic system is in the first displacement working state, the fourth reversing valve is in a fourth reversing position; when the hydraulic system is in the second displacement working state, the fourth reversing valve is in the fourth initial position, and the fifth reversing valve is in the fifth initial position, so that the first metering motor and the second metering motor are connected in series through adjustment of the fifth reversing valve.
Further, the hydraulic system further includes:
a hydraulic oil tank;
the first oil supplementing pump, the hydraulic oil tank and the first variable plunger pump are connected with the first oil supplementing pump, and the first oil supplementing pump operates to generate suction so as to suck hydraulic oil in the hydraulic oil tank into an oil suction port of the first variable plunger pump for supplementing oil;
the second oil supplementing pump, the hydraulic oil tank and the second variable plunger pump are connected with the second oil supplementing pump, and the second oil supplementing pump operates to generate suction so as to suck hydraulic oil in the hydraulic oil tank into an oil suction port of the second variable plunger pump for supplementing oil.
Further, a first overflow valve is arranged in the first variable plunger pump, so that oil entering the first variable plunger pump overflows in a shell of the first variable plunger pump through the first overflow valve; and/or the number of the groups of groups,
the second variable plunger pump is internally provided with a second overflow valve so that oil entering the second variable plunger pump overflows in a shell of the second variable plunger pump through the second overflow valve.
According to another aspect of the present invention, there is provided a hydraulic control method employing the hydraulic system provided above; the hydraulic control method comprises the following steps: the first variable plunger pump is driven to work by the first driving part, and the second variable plunger pump is driven to work by the second driving part; driving a driving motor through a first variable plunger pump and/or a second variable plunger pump, and driving a centrifugal pump through the driving motor; and controlling the working condition of the first variable plunger pump and the working condition of the second variable plunger pump according to the condition of the displacement working state of the hydraulic system.
By applying the technical scheme of the application, the working condition of the first variable plunger pump and the working condition of the second variable plunger pump are controlled according to the condition of the displacement working state of the hydraulic system. Specifically, the working condition of the first variable plunger pump can be conveniently controlled through the adjustment of the first driving part, the working condition of the second variable plunger pump can be conveniently controlled through the adjustment of the second driving part, and therefore the driving conditions of the first driving part and the second driving part can be conveniently and reasonably controlled, one of the first driving part and the second driving part can be reasonably selected to drive when the small-displacement operation is performed, the amount of engine oil needed by driving can be effectively reduced, the energy consumption can be conveniently reduced, and energy conservation, emission reduction and low carbon emission are realized.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:
FIG. 1 shows a schematic diagram of a hydraulic system provided in accordance with a first embodiment of the present application;
Fig. 2 shows a schematic view of a hydraulic system provided according to a second embodiment of the application;
FIG. 3 shows a schematic diagram of a hydraulic system provided in accordance with a third embodiment of the present application;
fig. 4 shows a schematic view of a hydraulic system provided according to a fourth embodiment of the application.
Wherein the above figures include the following reference numerals:
10. a first variable displacement plunger pump;
20. a second variable displacement plunger pump;
30. a drive motor; 31. a first metering motor; 32. a second quantitative motor;
41. a first reversing valve; 42. a second reversing valve; 43. a third reversing valve; 44. a fourth reversing valve; 45. a fifth reversing valve;
50. a hydraulic oil tank;
60. a pressure gauge.
Detailed Description
It should be noted that, without conflict, the embodiments of the present application and features of the embodiments may be combined with each other. The application will be described in detail below with reference to the drawings in connection with embodiments.
As shown in fig. 1 to 4, the present application provides a hydraulic system including: a first variable displacement pump 10 and a second variable displacement pump 20, the first variable displacement pump 10 being driven by a first driving unit, the second variable displacement pump 20 being driven by a second driving unit; the driving motor 30, the driving motor 30 is used for driving the centrifugal pump, the first variable plunger pump 10 and the second variable plunger pump 20 are connected with the driving motor 30, and the output oil of the first variable plunger pump 10 and/or the output oil of the second variable plunger pump 20 is used for driving the driving motor 30 to operate; the hydraulic system has different displacement working states, and the working conditions of the first variable plunger pump and the second variable plunger pump are controlled according to the condition of the displacement working states of the hydraulic system.
By adopting the hydraulic system provided by the invention, the working condition of the first variable plunger pump and the working condition of the second variable plunger pump are controlled according to the condition of the displacement working state of the hydraulic system. Specifically, the working condition of the first variable plunger pump can be conveniently controlled through the adjustment of the first driving part, the working condition of the second variable plunger pump can be conveniently controlled through the adjustment of the second driving part, and therefore the driving conditions of the first driving part and the second driving part can be conveniently and reasonably controlled, one of the first driving part and the second driving part can be reasonably selected to drive when the small-displacement operation is performed, the amount of engine oil needed by driving can be effectively reduced, the energy consumption can be conveniently reduced, and energy conservation, emission reduction and low carbon emission are realized.
Specifically, the first driving part is a chassis, and the second driving part is a bench engine.
In this embodiment, the hydraulic system has a first displacement operating condition and a second displacement operating condition, the displacement of the first displacement operating condition being greater than the displacement of the second displacement operating condition; when the hydraulic system is in the first displacement operating state, both the first variable displacement plunger pump 10 and the second variable displacement plunger pump 20 are in the operating state, and the operating displacement of the drive motor 30 is maintained at the maximum displacement; when the hydraulic system is in the second displacement operating state, the first variable displacement plunger pump 10 is in the non-operating state, the second variable displacement plunger pump 20 is in the operating state, and the working displacement of the drive motor 30 is reduced to the preset displacement.
By adopting the technical scheme provided by the embodiment of the invention, the hydraulic system can be in the first displacement working state when working in large displacement. When working with a small displacement, the hydraulic system can be in a second displacement working state, and the first variable displacement plunger pump 10 can be in a non-working state at the moment, correspondingly, the chassis is not required to be started, and meanwhile, the rotating speed of the centrifugal pump is ensured. Therefore, when in small-displacement operation, only the engine on the bench is required to work, and the chassis is not required to be started, so that the fuel consumption can be reduced; and because the bench engine also drives the centrifugal pump, the load rate of the bench engine is effectively improved, the phenomenon that the bench engine burns engine oil is reduced, and the energy conservation, emission reduction and low carbon emission are realized. Therefore, the hydraulic system provided by the invention can solve the technical problem that the hydraulic system in the prior art has higher fuel consumption in the small-displacement operation.
Specifically, the centrifugal pump in the present embodiment may be a sand pump or a fracturing fluid pump.
In the first embodiment of the present invention, the driving motor 30 is a variable motor; maintaining the swash plate angle of the drive motor 30 at maximum displacement when the hydraulic system is in the first displacement operating state; when the hydraulic system is in the second displacement operating state, the swash plate inclination angle of the drive motor 30 is adjusted to adjust the working displacement of the drive motor 30 to a preset displacement. With such an arrangement, it is possible to facilitate adjustment of the working displacement of the drive motor 30 by adjusting the variable of the drive motor 30.
Specifically, the driving motor 30 in the present embodiment is an electronically controlled motor, and it is understood that the driving motor 30 herein is an electronically controlled variable motor. When the hydraulic system is in the first displacement working state, the electric control motor is in a power-off state; when the hydraulic system is in the second displacement operating state, the electric motor is in an energized state such that the electric motor adjusts the swash plate angle of the drive motor 30 by electronically controlling the electric motor. In this way, control and regulation are facilitated.
As shown in fig. 1, in this embodiment, a scheme of driving a sand pump electric control variable motor by combining a chassis hydraulic pump and an on-board hydraulic pump is adopted: the chassis truck drives the first variable displacement pump 10 and the bench engine drives the second variable displacement pump 20, the first variable displacement pump 10 has a first oil supplementing pump (the first oil supplementing pump is arranged in the first variable displacement pump 10 or outside the first variable displacement pump 10), the second variable displacement pump 20 has a second oil supplementing pump (the second oil supplementing pump is arranged in the second variable displacement pump 20 or outside the second variable displacement pump 20), the first oil supplementing pump and the second oil supplementing pump generate suction due to operation, hydraulic oil in the hydraulic oil tank 50 reaches an oil suction port of the first variable displacement pump 10 and an oil suction port of the second variable displacement pump 20, the pipeline of the closed system is supplemented, then overflows in the shell of the first variable displacement pump 10 through a first overflow valve arranged in the first variable displacement pump 10, overflows in the shell of the second variable displacement pump 20 through a second overflow valve arranged in the second variable displacement pump 20, so as to respectively perform cooling effects on rotating components in the shell of the first variable displacement pump 10 and the shell of the second variable displacement pump 20, and then flows back into the hydraulic oil tank 50.
After the control units of the first variable plunger pump 10 and the second variable plunger pump 20 obtain signals, hydraulic oil in the servo oil cylinder of the first variable plunger pump 10 can push the swash plate to act, hydraulic oil in the servo oil cylinder of the second variable plunger pump 20 can push the swash plate to act, and as the inclination angle of the swash plate changes, the first variable plunger pump 10 and the second variable plunger pump 20 have flow output, so that the sand pump driving motor 30 is driven to operate.
When the field operation needs large displacement, the chassis truck and the bench engine work simultaneously, namely the first variable plunger pump 10 and the second variable plunger pump 20 work simultaneously, the driving motor 30 adopts an electric control variable motor, the driving motor 30 cannot be powered, the inclined angle of the inclined plate of the driving motor 30 is kept at the maximum displacement, and the driving motor 30 can drive the sand pump to run at the maximum power.
When the field operation needs small displacement, the chassis vehicle does not work, namely only the second variable plunger pump 20 driven by the bench engine works, at the moment, the driving motor 30 is electrified, the inclination angle of the swash plate of the driving motor 30 is changed and is adjusted to the preset small displacement, and the sand pump adopts a centrifugal pump mode, so that the discharge capacity is small, the input power of the sand pump is not large, and at the moment, the motor with the small displacement is used, so that the sand pump is kept in a reasonable rotating speed range. Thus, the use of the chassis engine is reduced, and the application of reducing emission and fuel economy on site can be satisfied.
The function and function of the hydraulic components in the system: the hydraulic oil tank 50 provides a working medium for transmitting power for the whole hydraulic system; the driving motor 30 is an executing mechanism, and adopts an electric control variable motor to convert pressure energy into mechanical energy; the first variable displacement pump 10 is a power element in a hydraulic system, converts mechanical energy into pressure energy, and transitions a working medium from a low-pressure state to a high-pressure state; the pressure gauge 60 displays the driving oil pressure at the time of operation; the second variable displacement pump 20 is a power element in the hydraulic system, converting mechanical energy into pressure energy, and transitioning the working medium from a low-pressure state to a high-pressure state.
In the second embodiment of the present invention, the driving motor 30 is a hydraulic motor, and the first variable displacement plunger pump 10 is driven by the power take-off of the chassis. The hydraulic system further comprises a first reversing valve 41, the first reversing valve 41 being connected to the drive motor 30; when the hydraulic system is in the first displacement operating state, the first reversing valve 41 is in the first reversing position; when the hydraulic system is in the second displacement operating state, the first directional valve 41 is in the first initial position. With such an arrangement, the displacement can be adjusted adaptively by controlling the commutation of the first reversing valve 41. In the present embodiment, when the first direction valve 41 is in the first initial position, the first direction valve 41 does not perform the direction change; when the first direction valve 41 is in the first direction position, the first direction valve 41 is switched.
Specifically, the hydraulic system further includes a pressure reducing valve connected to the first reversing valve 41. With such an arrangement, when the hydraulic system is in the second displacement operating state, pressure is reduced by the pressure reducing valve.
Specifically, the first reversing valve 41 is a pneumatic reversing valve, or an electromagnetic reversing valve, or a manual reversing valve.
As shown in fig. 2, in the second embodiment, a solution of driving a hydraulic variable motor of a sand pump by combining a chassis hydraulic pump and an on-board hydraulic pump is adopted: the chassis truck drives the first variable plunger pump 10 and the bench engine drives the second variable plunger pump 20, the first variable plunger pump 10 comprises a first oil supplementing pump, the second variable plunger pump 20 comprises a second oil supplementing pump, the first oil supplementing pump and the second oil supplementing pump generate suction force due to operation, hydraulic oil in the hydraulic oil tank 50 reaches an oil suction port of the first variable plunger pump 10 and an oil suction port of the second variable plunger pump 20, a pipeline of a closed system is supplemented, then the hydraulic oil overflows in a shell of the first variable plunger pump 10 through a first overflow valve built in the first variable plunger pump 10, overflows in a shell of the second variable plunger pump 20 through a second overflow valve built in the second variable plunger pump 20, and plays a role of cooling down a rotating part in the shell of the first variable plunger pump 10 and a rotating part in the shell of the second variable plunger pump 20, and then flows back into the hydraulic oil tank 50.
After the control units of the first variable plunger pump 10 and the second variable plunger pump 20 obtain signals, hydraulic oil in the servo oil cylinder of the first variable plunger pump 10 can push the swash plate to act, hydraulic oil in the servo oil cylinder of the second variable plunger pump 20 can push the swash plate to act, and as the inclination angle of the swash plate changes, the first variable plunger pump 10 and the second variable auxiliary pump have flow output, so that the sand pump driving motor 30 is driven to operate.
Because the hydraulic pump driven by the chassis adopts a manner of a chassis full-power takeoff, when the full-power takeoff is hung, pneumatic control hanging is adopted, and the first reversing valve 41 at the moment can adopt a pneumatic control reversing valve (or an electromagnetic reversing valve or a manual reversing valve), namely, the pneumatic control valve can work simultaneously with the power takeoff pneumatic control valve of the chassis, namely, when the chassis works, the full-power takeoff is hung, and meanwhile, the first reversing valve 41 can be reversed together.
When the field operation needs large displacement, the chassis truck and the bench motor work simultaneously, namely the first variable plunger pump 10 and the second variable plunger pump 20 work simultaneously, the first reversing valve 41 reverses, the sand pump driving motor 30 adopts a hydraulic variable motor, the inclined angle of the inclined plate of the sand pump driving motor 30 is kept at the maximum displacement, and at the moment, the sand pump driving motor 30 can drive the sand pump to operate at the maximum power.
When the field operation needs small displacement, the chassis is not operated, the first reversing valve 41 is at a non-reversing position, so that the inclination angle of the sloping cam plate of the sand pump driving motor 30 is changed to be in a set small displacement state (a pressure reducing valve can be added in front of the first reversing valve 41 to reduce pressure so as to proportionally adjust the displacement of the sand pump driving motor 30), namely only the second variable plunger pump 20 driven by the engine on the bench operates at the moment. Because the sand pump adopts a centrifugal pump mode, the discharge capacity is small at the moment, so the input power of the sand pump is not large, and a motor with small displacement is used at the moment, so that the sand pump is kept in a reasonable rotating speed range. Thus, the use of the chassis engine is reduced, and the application of reducing emission and fuel economy on site can be satisfied.
The function and function of the hydraulic components in the system: the hydraulic oil tank 50 provides a working medium for transmitting power for the whole hydraulic system;
the sand pump driving motor 30 is an executing mechanism, and adopts a hydraulic control variable motor to convert pressure energy into mechanical energy; the first variable displacement pump 10 is a power element in a hydraulic system, converts mechanical energy into pressure energy, and transitions a working medium from a low-pressure state to a high-pressure state; the pressure gauge 60 displays the driving oil pressure at the time of operation; the second variable displacement pump 20 is a power element in the hydraulic system, converts mechanical energy into pressure energy, and transitions the working medium from a low-pressure state to a high-pressure state; the first reversing valve 41 is switched and adjusted by reversing to achieve whether the sand pump driving motor 30 is operating at a large displacement or a small displacement.
In the third embodiment of the present invention, the driving motor 30 includes a first metering motor 31 and a second metering motor 32; when the hydraulic system is in the first displacement working state, the first and second dosing motors 31 and 32 are connected in parallel, and the first and second dosing motors 31 and 32 are both in working states. When the hydraulic system is in the second displacement working state, the second variable displacement plunger pump 20 is in zero displacement, and the first variable displacement plunger pump 10 is in a working state, so that the displacement adjustment function is conveniently and effectively achieved.
Specifically, the first variable displacement plunger pump 10 is driven by the power take-off of the chassis, and the hydraulic system further includes a second reversing valve 42 and a third reversing valve 43, and the second reversing valve 42 is connected to the second variable displacement plunger pump 20. The second reversing valve 42 and the second dosing motor 32 are each connected to a third reversing valve 43. Wherein the second reversing valve 42 is in a second reversing position when the hydraulic system is in the first displacement operating state; when the hydraulic system is in the second displacement operating state, the second directional valve 42 is in the second initial position and the third directional valve 43 is in the third directional position so that the oil inlet of the second fixed displacement motor 32 communicates with the oil outlet of the second fixed displacement motor 32. By adopting the arrangement, the adjusting mode is simple, and the adjustment can be conveniently and effectively carried out.
In the present embodiment, the second reversing valve 42 is a pneumatic reversing valve, or an electromagnetic reversing valve, or a manual reversing valve.
Specifically, the third directional valve 43 in the present embodiment is a pilot operated directional valve.
As shown in fig. 3, in the third embodiment, a scheme is adopted in which two fixed-amount motors (a first fixed-amount motor 31 and a second fixed-amount motor 32) are driven by a double pump combination of a chassis hydraulic pump and an on-board hydraulic pump: the chassis truck drives the first variable plunger pump 10 and the bench engine drives the second variable plunger pump 20, the first variable plunger pump 10 comprises a first oil supplementing pump, the second variable plunger pump 20 comprises a second oil supplementing pump, the first oil supplementing pump and the second oil supplementing pump generate suction force due to operation, hydraulic oil in the hydraulic oil tank 50 reaches an oil suction port of the first variable plunger pump 10 and an oil suction port of the second variable plunger pump 20, a pipeline of a closed system is supplemented, then the hydraulic oil overflows in a shell of the first variable plunger pump 10 through a first overflow valve built in the first variable plunger pump 10, overflows in a shell of the second variable plunger pump 20 through a second overflow valve built in the second variable plunger pump 20, and plays a role of cooling a rotating part in the shell of the first variable plunger pump 10 and a rotating part in the shell of the first variable plunger pump 10, and then flows back into the hydraulic oil tank 50.
After the control units of the first variable plunger pump 10 and the second variable plunger pump 20 obtain signals, hydraulic oil in the servo oil cylinder of the first variable plunger pump 10 can push the swash plate to act, hydraulic oil in the servo oil cylinder of the second variable plunger pump 20 can push the swash plate to act, and as the inclination angle of the swash plate changes, the first variable plunger pump 10 and the second variable plunger pump 20 have flow output, so that the sand pump driving motor 30 runs (the first quantitative motor 31 and the second quantitative motor 32 are connected and kept synchronous in a mechanical mode).
Because the hydraulic pump driven by the chassis adopts a mode of a chassis full-power takeoff, when the full-power takeoff is hung, pneumatic control hanging is adopted, and the reversing valve at the moment can adopt a pneumatic control reversing valve (or an electromagnetic reversing valve or a manual reversing valve) and can work simultaneously with the power takeoff pneumatic control valve of the chassis, namely when the chassis works, the full-power takeoff is hung, and the reversing valve can be used for reversing together.
When the field operation requires large displacement, the chassis and the bench motor are simultaneously operated, that is, the first variable displacement plunger pump 10 and the second variable displacement plunger pump 20 are simultaneously operated, the second reversing valve 42 reverses, the first metering motor 31 and the second metering motor 32 are connected in parallel and are both kept at the maximum displacement, and at this time, the first metering motor 31 and the second metering motor 32 can both drive the sand pump to operate at the maximum power.
When the field operation needs small displacement, the second reversing valve 42 is at a non-reversing position when the chassis is not in operation, and the third reversing valve 43 can reverse at this time, so that the oil inlet and outlet of the second quantitative motor 32 are communicated, and zero displacement operation is realized, and only the first quantitative motor 31 drives the sand pump at this time, namely only the second variable plunger pump 20 driven by the bench engine works. Because the sand pump adopts a centrifugal pump mode, the discharge capacity is small at the moment, so the input power of the sand pump is not large, and a motor with small displacement is used at the moment, so that the sand pump is kept in a reasonable rotating speed range. Thus, the use of the chassis engine is reduced, and the application of reducing emission and fuel economy on site can be satisfied.
The function and function of the hydraulic components in the system: the hydraulic oil tank 50 provides a working medium for transmitting power for the whole hydraulic system; the first metering motor 31 is an actuator that converts pressure energy into mechanical energy; the first variable displacement pump 10 is a power element in a hydraulic system, converts mechanical energy into pressure energy, and transitions a working medium from a low-pressure state to a high-pressure state; the pressure gauge 60 displays the driving oil pressure at the time of operation; the second variable displacement pump 20 is a power element in the hydraulic system, converts mechanical energy into pressure energy, and transitions the working medium from a low-pressure state to a high-pressure state; the second reversing valve 42 is a pilot operated reversing valve which is controlled by reversing. The third reversing valve 43 is used for realizing whether the second quantitative motor 32 participates in driving or not through reversing so as to realize the operation of the equipment under the large displacement or the small displacement; the second fixed-amount motor 32 is an actuator that converts pressure energy into mechanical energy.
In the fourth embodiment of the present invention, the drive motor 30 includes the first metering motor 31 and the second metering motor 32; when the hydraulic system is in the first displacement working state, the first and second dosing motors 31 and 32 are connected in parallel, and the first and second dosing motors 31 and 32 are both in working states. When the hydraulic system is in the second displacement working state, the second variable displacement plunger pump 20 is connected with the first variable displacement plunger pump 10 in series, so that the displacement adjustment function is conveniently and effectively achieved.
Specifically, the first variable displacement plunger pump 10 is driven by the power take-off of the chassis, the hydraulic system further comprises a fourth reversing valve 44 and a fifth reversing valve 45, the fourth reversing valve 44 is connected with the second variable displacement plunger pump 20, and the fourth reversing valve 44, the first metering motor 31 and the second metering motor 32 are all connected with the fifth reversing valve 45. Wherein the fourth reversing valve 44 is in a fourth reversing position when the hydraulic system is in the first displacement operating state; when the hydraulic system is in the second displacement operating state, the fourth directional valve 44 is in the fourth initial position and the fifth directional valve 45 is in the fifth initial position, so that the first and second fixed-displacement motors 31 and 32 are connected in series by adjustment of the fifth directional valve 45. By adopting the arrangement, the adjusting mode is simple, and the adjustment can be conveniently and effectively carried out.
As shown in fig. 4, in the fourth embodiment, a scheme is adopted in which two fixed-amount motors (a first fixed-amount motor 31 and a second fixed-amount motor 32) are driven by a double pump combination of a chassis hydraulic pump and an on-board hydraulic pump: the chassis truck drives the first variable plunger pump 10 and the bench engine drives the second variable plunger pump 20, the first variable plunger pump 10 comprises a first oil supplementing pump, the second variable plunger pump 20 comprises a second oil supplementing pump, the first oil supplementing pump and the second oil supplementing pump generate suction force due to operation, hydraulic oil in the hydraulic oil tank 50 reaches the oil absorbing ports of the first variable plunger pump 10 and the second variable plunger pump 20, oil supplementing is carried out on a pipeline of a closed system, then the hydraulic oil overflows in a shell of the first variable plunger pump 10 through an oil supplementing overflow valve arranged in the first variable plunger pump 10, overflows in a shell of the second variable plunger pump 20 through an oil supplementing overflow valve arranged in the second variable plunger pump 20, and plays a role in cooling a rotating part in the shell of the first variable plunger pump 10 and a rotating part in the shell of the first variable plunger pump 10, and then flows back to the hydraulic oil tank 50.
After the control units of the first variable plunger pump 10 and the second variable plunger pump 20 obtain signals, hydraulic oil in the servo oil cylinder of the first variable plunger pump 10 can push the swash plate to act, hydraulic oil in the servo oil cylinder of the second variable plunger pump 20 can push the swash plate to act, and as the inclination angle of the swash plate changes, the first variable plunger pump 10 and the second variable plunger pump 20 have flow output, so that the first quantitative motor 31 and the second quantitative motor 32 run synchronously (are dual quantitative motors or two identical quantitative motors are connected in a mechanical mode to keep synchronous).
Because the hydraulic pump driven by the chassis adopts a mode of a chassis full-power takeoff, when the full-power takeoff is hung, pneumatic control hanging is adopted, and the reversing valve at the moment can adopt a pneumatic control reversing valve (or an electromagnetic reversing valve or a manual reversing valve), namely the pneumatic control valve and the power takeoff pneumatic control valve of the chassis work simultaneously, namely when the chassis works, the full-power takeoff is hung, and the reversing valve can be used for reversing together.
When the field operation needs large displacement, the chassis truck and the bench engine work simultaneously, namely the first variable plunger pump 10 and the second variable plunger pump 20 work simultaneously, the reversing valve reverses, the duplex quantitative motor or the two quantitative motors are kept in parallel at the maximum displacement, and at the moment, the quantitative motors can drive the sand pump to operate with the maximum power.
When the field operation requires small displacement, the fourth reversing valve 44 is in a non-reversing position when the chassis is not in operation, and the fifth reversing valve 45 is not in reversing, so that the oil ports of the dual-metering motor or the two metering motors are kept in series at the minimum displacement to drive the sand pump, namely only the second plunger pump driven by the engine on the bench is operated. Because the sand pump adopts a centrifugal pump mode, the discharge capacity is small at the moment, so the input power of the sand pump is not large, and a motor with small displacement is used at the moment, so that the sand pump is kept in a reasonable rotating speed range. Thus, the use of the chassis engine is reduced, and the application of reducing emission and fuel economy on site can be satisfied.
The function and function of the hydraulic components in the system: the hydraulic oil tank 50 provides a working medium for transmitting power for the whole hydraulic system; the first metering motor 31 is an actuator, and is an actuator for converting pressure energy into mechanical energy by using a dual metering motor or two identical metering motors; the first variable displacement pump 10 is a power element in a hydraulic system, converts mechanical energy into pressure energy, and transitions a working medium from a low-pressure state to a high-pressure state; the pressure gauge 60 displays the driving oil pressure at the time of operation; the second variable displacement pump 20 is a power element in the hydraulic system, converts mechanical energy into pressure energy, and transitions the working medium from a low-pressure state to a high-pressure state; the fourth reversing valve 44 is used for reversing by reversing the hydraulic control reversing valve; the fifth reversing valve 45 realizes whether the duplex quantitative motor or the two quantitative motors are connected in series or in parallel to participate in driving through reversing so as to keep the equipment to work under a large displacement or a small displacement;
in all of the above embodiments, the hydraulic system further includes the hydraulic tank 50, the first supplemental pump, and the second supplemental pump. The hydraulic oil tank 50 and the first variable displacement plunger pump 10 are both connected with a first oil supplementing pump, and the first oil supplementing pump operates to generate suction force so as to suck hydraulic oil in the hydraulic oil tank 50 into an oil suction port of the first variable displacement plunger pump 10 for supplementing oil. The hydraulic oil tank 50 and the second variable displacement plunger pump 20 are both connected with a second oil supplementing pump, and the second oil supplementing pump operates to generate suction force so as to suck hydraulic oil in the hydraulic oil tank 50 into an oil suction port of the second variable displacement plunger pump 20 for supplementing oil.
Specifically, in all of the above embodiments, the first variable displacement pump 10 is provided with the first relief valve therein so that the oil entering the first variable displacement pump 10 overflows into the housing of the first variable displacement pump 10 via the first relief valve. A second relief valve is provided in the second variable displacement pump 20 so that the oil that has entered the second variable displacement pump 20 overflows into the housing of the second variable displacement pump 20 via the second relief valve.
In another embodiment of the present invention, a hydraulic control method is provided, which adopts the hydraulic system provided in all the above embodiments. The hydraulic control method includes: the first variable plunger pump is driven to work by the first driving part, and the second variable plunger pump is driven to work by the second driving part; driving a driving motor through a first variable plunger pump and/or a second variable plunger pump, and driving a centrifugal pump through the driving motor; and controlling the working condition of the first variable plunger pump and the working condition of the second variable plunger pump according to the condition of the displacement working state of the hydraulic system.
From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects: the dual hydraulic pumps or the multiple hydraulic pumps are combined, and the variable motor or the combination mode of two or more motors in series or parallel is adopted to drive the sand pump of the sand mixing vehicle or the fracturing fluid discharge pump of the mixing vehicle respectively, so that the chassis vehicle can stop working during on-site small-displacement construction operation, and the effects of energy conservation and emission reduction can be realized.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present application unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.
In the description of the present application, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present application and simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be constructed and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present application; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
In addition, the terms "first", "second", etc. are used to define the components, and are only for convenience of distinguishing the corresponding components, and the terms have no special meaning unless otherwise stated, and therefore should not be construed as limiting the scope of the present application.
The above description is only of the preferred embodiments of the present application and is not intended to limit the present application, but various modifications and variations can be made to the present application by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.
Claims (13)
1. A hydraulic system, comprising:
a first variable displacement pump (10) and a second variable displacement pump (20), wherein the first variable displacement pump (10) is driven by a first driving part, and the second variable displacement pump (20) is driven by a second driving part;
the driving motor (30) is used for driving the centrifugal pump, the first variable plunger pump (10) and the second variable plunger pump (20) are connected with the driving motor (30), and the output oil of the first variable plunger pump (10) and/or the output oil of the second variable plunger pump (20) is used for driving the driving motor (30) to operate;
The hydraulic system is provided with different displacement working states, and the working conditions of the first variable plunger pump and the working conditions of the second variable plunger pump are controlled according to the conditions of the displacement working states of the hydraulic system.
2. The hydraulic system of claim 1, wherein the hydraulic system has a first displacement operating condition and a second displacement operating condition, the first displacement operating condition having a displacement greater than a displacement of the second displacement operating condition; when the hydraulic system is in the first displacement working state, the first variable displacement plunger pump (10) and the second variable displacement plunger pump (20) are both in working states, and the working displacement of the driving motor (30) is kept at the maximum displacement; when the hydraulic system is in the second displacement working state, the first variable displacement plunger pump (10) is in a non-working state, the second variable displacement plunger pump (20) is in a working state, and the working displacement of the driving motor (30) is reduced to a preset displacement.
3. The hydraulic system according to claim 2, characterized in that the drive motor (30) is a variable motor; maintaining a swash plate angle of the drive motor (30) at a maximum displacement when the hydraulic system is in the first displacement operating state; when the hydraulic system is in the second displacement working state, the inclination angle of the swash plate of the driving motor (30) is adjusted so as to adjust the working displacement of the driving motor (30) to a preset displacement.
4. A hydraulic system according to claim 3, characterized in that the drive motor (30) is an electric motor; when the hydraulic system is in the first displacement working state, the electric control motor is in a power-off state; when the hydraulic system is in the second displacement working state, the electric control motor is in an electric power-on state, so that the electric control motor can adjust the inclination angle of the swash plate of the driving motor (30) through electric control.
5. A hydraulic system according to claim 3, characterized in that the drive motor (30) is a pilot motor, the first variable displacement plunger pump (10) being driven by a power take-off of a chassis, the hydraulic system further comprising:
a first reversing valve (41) connected to the drive motor (30); -the first reversing valve (41) is in a first reversing position when the hydraulic system is in the first displacement operating state; the first reversing valve (41) is in a first initial position when the hydraulic system is in the second displacement operating state.
6. The hydraulic system of claim 5, wherein the hydraulic system is configured to,
the hydraulic system further comprises a pressure reducing valve connected with the first reversing valve (41); and/or the number of the groups of groups,
The first reversing valve (41) is a pneumatic reversing valve, an electromagnetic reversing valve or a manual reversing valve.
7. The hydraulic system according to claim 2, characterized in that the drive motor (30) comprises a first dosing motor (31) and a second dosing motor (32); when the hydraulic system is in the first displacement working state, the first quantitative motor (31) and the second quantitative motor (32) are connected in parallel, and the first quantitative motor (31) and the second quantitative motor (32) are both in working states;
wherein when the hydraulic system is in the second displacement working state, the second variable displacement plunger pump (20) is in zero displacement, and the first variable displacement plunger pump (10) is in a working state; or alternatively, the process may be performed,
the second variable displacement plunger pump (20) is connected in series with the first variable displacement plunger pump (10) when the hydraulic system is in the second displacement operating state.
8. The hydraulic system according to claim 7, wherein the first variable displacement plunger pump (10) is driven by a power take-off of a chassis, the hydraulic system further comprising:
a second reversing valve (42) connected to the second variable displacement plunger pump (20);
a third directional valve (43), the second directional valve (42) and the second dosing motor (32) being connected to the third directional valve (43);
Wherein the second reversing valve (42) is in a second reversing position when the hydraulic system is in the first displacement operating state; when the hydraulic system is in the second displacement working state, the second reversing valve (42) is in a second initial position, and the third reversing valve (43) is in a third reversing position, so that the oil inlet of the second quantitative motor (32) is communicated with the oil outlet of the second quantitative motor (32).
9. The hydraulic system of claim 8, wherein the hydraulic system is configured to,
the second reversing valve (42) is a pneumatic reversing valve, an electromagnetic reversing valve or a manual reversing valve; and/or the number of the groups of groups,
the third reversing valve (43) is a hydraulic control reversing valve.
10. The hydraulic system according to claim 7, wherein the first variable displacement plunger pump (10) is driven by a power take-off of a chassis, the hydraulic system further comprising:
a fourth reversing valve (44) connected to the second variable displacement plunger pump (20);
a fifth directional valve (45), wherein the fourth directional valve (44), the first quantitative motor (31) and the second quantitative motor (32) are all connected with the fifth directional valve (45);
wherein the fourth reversing valve (44) is in a fourth reversing position when the hydraulic system is in the first displacement operating state; when the hydraulic system is in the second displacement working state, the fourth reversing valve (44) is in a fourth initial position, and the fifth reversing valve (45) is in a fifth initial position, so that the first metering motor (31) and the second metering motor (32) are connected in series through adjustment of the fifth reversing valve (45).
11. The hydraulic system according to any one of claims 1 to 10, characterized in that the hydraulic system further comprises:
a hydraulic oil tank (50);
the first oil supplementing pump is connected with the hydraulic oil tank (50) and the first variable plunger pump (10), and the first oil supplementing pump operates to generate suction so as to suck hydraulic oil in the hydraulic oil tank (50) into an oil suction port of the first variable plunger pump (10) for supplementing oil;
the hydraulic oil tank (50) and the second variable plunger pump (20) are connected with the second oil supplementing pump, and the second oil supplementing pump operates to generate suction so as to suck hydraulic oil in the hydraulic oil tank (50) into an oil suction port of the second variable plunger pump (20) for supplementing oil.
12. The hydraulic system of claim 11, wherein the hydraulic system is configured to,
a first overflow valve is arranged in the first variable plunger pump (10) so that oil entering the first variable plunger pump (10) overflows in a shell of the first variable plunger pump (10) through the first overflow valve; and/or the number of the groups of groups,
a second overflow valve is arranged in the second variable plunger pump (20) so that oil entering the second variable plunger pump (20) overflows in a shell of the second variable plunger pump (20) through the second overflow valve.
13. A hydraulic control method, characterized in that the hydraulic control method employs the hydraulic system according to any one of claims 1 to 12; the hydraulic control method includes:
the first variable plunger pump is driven to work by the first driving part, and the second variable plunger pump is driven to work by the second driving part;
driving a driving motor through the first variable plunger pump and/or the second variable plunger pump, and driving a centrifugal pump by adopting the driving motor;
and controlling the working conditions of the first variable plunger pump and the second variable plunger pump according to the condition of the displacement working state of the hydraulic system.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202310523842.4A CN116576167A (en) | 2023-05-06 | 2023-05-06 | Hydraulic system and hydraulic control method |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202310523842.4A CN116576167A (en) | 2023-05-06 | 2023-05-06 | Hydraulic system and hydraulic control method |
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| CN116576167A true CN116576167A (en) | 2023-08-11 |
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