CN116906384A - Load-sensitive hydraulic system - Google Patents
Load-sensitive hydraulic system Download PDFInfo
- Publication number
- CN116906384A CN116906384A CN202310904010.7A CN202310904010A CN116906384A CN 116906384 A CN116906384 A CN 116906384A CN 202310904010 A CN202310904010 A CN 202310904010A CN 116906384 A CN116906384 A CN 116906384A
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- Prior art keywords
- control valve
- hydraulic
- port
- valve
- oil
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 5
- 239000003921 oil Substances 0.000 claims description 154
- 239000010720 hydraulic oil Substances 0.000 claims description 33
- 238000004140 cleaning Methods 0.000 abstract description 7
- 230000000694 effects Effects 0.000 abstract description 4
- 230000007547 defect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005265 energy consumption Methods 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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- 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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
-
- 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
- F15B2211/255—Flow control functions
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 belongs to the field of hydraulic control, and particularly relates to a load-sensitive hydraulic system, which comprises a load-sensitive pump, a flow control unit and a driving motor for driving a high-pressure water pump; the flow control unit comprises a first control valve, a hydraulic control valve, a second control valve and a throttle valve, wherein an oil outlet of the load sensitive pump is respectively connected with an oil inlet of the first control valve and a working oil port A of the hydraulic control valve, and the working oil port of the first control valve is connected with a control port of the hydraulic control valve; the working oil port C of the hydraulic control valve is respectively connected with the oil inlet of the driving motor and the oil inlet of the second control valve through the throttle valve, and the working oil port of the second control valve is connected with the feedback control oil port of the load sensitive pump; the control port of the hydraulic control valve is configured to control the on-off of the working oil port A of the hydraulic control valve to the working oil port C of the hydraulic control valve. The flow of the load sensitive hydraulic system is increased or reduced no matter the rotation speed of the chassis, the flow transmitted to the driving motor is almost unchanged, the working pressure of the high-pressure waterway system is maintained, and the cleaning effect is ensured.
Description
Technical Field
The invention belongs to the field of hydraulic control, and particularly relates to a load-sensitive hydraulic system.
Background
The conventional high-pressure cleaning vehicle adopts a main hair and a secondary hair, and the high-pressure cleaning vehicle of the type has large noise, heavy weight and high energy consumption. Therefore, in order to avoid the defect of double-shot, combined with the situation of actual use, part of high-pressure cleaning vehicles in the industry adopt a single-shot design, namely only one main shot is adopted, but the single-shot output rotating speed changes along with the change of the rotating speed of the chassis, so that the pressure of the high-pressure waterway system is unstable, and the cleaning effect is poor.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides the load-sensitive hydraulic system, the flow of which is increased or reduced no matter the rotation speed of the chassis, the flow transmitted to the driving motor is almost unchanged, the working pressure of the high-pressure waterway system is maintained, and the cleaning effect is ensured.
The invention is realized by the following technical scheme: a load-sensitive hydraulic system includes a load-sensitive pump, a flow control unit, and a drive motor for driving a high-pressure water pump;
the flow control unit comprises a first control valve, a hydraulic control valve, a second control valve and a throttle valve, wherein an oil outlet of the load sensitive pump is respectively connected with an oil inlet of the first control valve and a working oil port A of the hydraulic control valve, and the working oil port of the first control valve is connected with a control port B of the hydraulic control valve; the working oil port C of the hydraulic control valve is respectively connected with the oil inlet of the driving motor and the oil inlet of the second control valve through a throttle valve, and the working oil port of the second control valve is connected with the feedback control oil port of the load sensitive pump;
the control port B of the hydraulic control valve is configured to control the on-off of the working oil port A of the hydraulic control valve to the working oil port C of the hydraulic control valve;
and under the working condition that an oil path from the working oil port A of the hydraulic control valve to the working oil port C of the hydraulic control valve is conducted, the second control valve is also configured that an oil inlet of the second control valve is conducted with the working oil port of the second control valve.
In some embodiments, the pilot operated valve is a two-way cartridge valve.
In some embodiments, the first control valve is a solenoid valve comprising an initial station and a right station;
when the first control valve is in the initial station and is in the initial station, an oil inlet of the first control valve is communicated with a working oil port of the first control valve, and at the moment, hydraulic oil provided by a load sensitive pump cannot pass through the working oil port A of the hydraulic control valve to the working oil port C of the hydraulic control valve;
when the first control valve is in the right station and is in the right station, the working oil port of the first control valve is communicated with the hydraulic oil tank, and at the moment, hydraulic oil provided by the load sensitive pump can pass through the working oil port A of the hydraulic control valve to the working oil port C of the hydraulic control valve.
In some embodiments, the second control valve is a solenoid valve comprising an initial station and a right station;
the second control valve is positioned at an initial station when the power is lost, and when the second control valve is positioned at the initial station, an oil inlet of the second control valve and a working oil port of the second control valve are respectively communicated with the hydraulic oil tank;
the second control valve is positioned at the right station when being electrified, and when the second control valve is positioned at the right station, the oil inlet of the second control valve is communicated with the working oil port of the second control valve.
In some embodiments, the flow control unit further comprises a relief valve, an oil inlet of the relief valve is connected with an oil outlet of the throttle valve, and an oil outlet of the relief valve is connected with the hydraulic oil tank.
In some embodiments, the load-sensitive pump is driven by a side power take-off.
In some embodiments, a high pressure filter is also provided at the oil outlet of the load-sensitive pump.
In some embodiments, the flow control unit is integrated within a flow control valve.
The beneficial effects of the invention are as follows: according to the load-sensitive hydraulic system, through the arrangement of the throttle valve and the feedback oil way, no matter whether the rotation speed of the chassis is increased or reduced, the flow transmitted to the driving motor is almost unchanged, the working pressure of the high-pressure waterway system is maintained, and the cleaning effect is ensured.
Drawings
FIG. 1 is a schematic diagram of a hydraulic system of the present invention when the high pressure waterway system is not in operation;
FIG. 2 is a schematic diagram of a hydraulic system of the present invention when the high pressure waterway system is in operation;
in the figure, 1, a load sensitive pump, 2, a high-pressure filter, 3, a flow control unit, 3.1, a first control valve, 3.2, a hydraulic control valve, 3.3, a throttle valve, 3.4, a safety valve, 3.5, a second control valve, 4, a driving motor, 5 and a hydraulic oil tank.
Description of the embodiments
The invention is further described below with reference to the drawings and examples.
As shown in fig. 1 and 2, a load-sensitive hydraulic system includes a load-sensitive pump 1, a flow control unit 3, and a drive motor 4 for driving a high-pressure water pump. In the high-pressure waterway system, the load-sensitive pump 1 is driven by a side power take-off.
The flow control unit 3 comprises a first control valve 3.1, a hydraulic control valve 3.2, a second control valve 3.5 and a throttle valve 3.3. The oil outlet A of the load-sensitive pump 1 is respectively connected with the oil inlet H of the first control valve 3.1 and the working oil port A of the hydraulic control valve 3.2, the working oil port of the first control valve 3.1 is connected with the control port B of the hydraulic control valve 3.2, and the oil return port G of the first control valve 3.1 is connected with the hydraulic oil tank 5. The working oil port C of the hydraulic control valve 3.2 is connected with the oil inlet of the throttle valve 3.3, the oil outlet of the throttle valve 3.3 is respectively connected with the oil inlet D of the driving motor 4 and the oil inlet F of the second control valve 3.5, the oil outlet of the driving motor 4 is connected with the hydraulic oil tank 5, and the working oil port M of the second control valve 3.5 is connected with the feedback control oil port Ls of the load sensitive pump 1.
The control port B of the hydraulic control valve 3.2 is configured to control the on-off of the working port a of the hydraulic control valve 3.2 to the working port C of the hydraulic control valve 3.2. In some embodiments, the hydraulic control valve 3.2 is a two-way cartridge valve, as shown in fig. 1 and 2, where the area of the upper cavity of the two-way cartridge valve is larger than that of the lower cavity, that is, in the load-sensitive hydraulic system, if the hydraulic pressure acting on the working port a of the hydraulic control valve 3.2 is under the working condition that the hydraulic pressure acting on the control port B of the hydraulic control valve 3.2 is not greater than that of the hydraulic pressure, the hydraulic oil of the working port a of the hydraulic control valve 3.2 cannot flow to the working port C of the hydraulic control valve 3.2.
The second control valve 3.5 is also configured such that the oil inlet F of the second control valve 3.5 is communicated with the working oil port M of the second control valve 3.5 when the oil path from the working oil port a of the hydraulic control valve 3.2 to the working oil port C of the hydraulic control valve 3.2 is in a conducting condition. Under the working condition, the driving motor 4 of the load sensitive hydraulic system drives the high-pressure water pump to work after receiving the hydraulic oil from the oil outlet of the throttle valve 3.3, and at the moment, the hydraulic oil from the oil outlet of the throttle valve 3.3 also acts on the feedback control oil port Ls of the load sensitive pump 1 through the second control valve 3.5, as shown in fig. 2, so as to ensure that the difference value between the outlet pressure Pa and the load pressure Pb of the load sensitive pump 1 is constant.
The working principle of applying the load sensitive hydraulic system to the high-pressure waterway system is as follows: 1. when the oil inlet H of the first control valve 3.1 is communicated with the working oil port of the first control valve 3.1, at this time, the hydraulic oil provided by the load-sensitive pump 1 is divided into two paths, one path of hydraulic oil is acted on the control port B of the hydraulic control valve 3.2 after passing through the oil inlet H of the first control valve 3.1 and the working oil port of the first control valve 3.1, the other path of hydraulic oil is directly acted on the working oil port A of the hydraulic control valve 3.2, at this time, the hydraulic pressure acted on the control port B of the hydraulic control valve 3.2 is equal to the hydraulic pressure acted on the working oil port A of the hydraulic control valve 3.2, and because the area of the upper cavity of the two-way cartridge valve is larger than that of the lower cavity, the hydraulic oil of the working oil port A of the hydraulic control valve 3.2 cannot flow to the working oil port C of the hydraulic control valve 3.2, and the driving motor 4 does not work. At this time, the load-sensitive pump 1 is automatically adjusted to a state that the displacement is almost 0, the load-sensitive hydraulic system almost forms no loop, and the power loss is almost zero.
2. When the working oil port of the first control valve 3.1 is communicated with the oil return port G of the first control valve 3.1, at this time, hydraulic oil provided by the load-sensitive pump 1 is divided into two paths, one path acts on the oil inlet H of the first control valve 3.1, the other path acts on the working oil port a of the hydraulic control valve 3.2, but hydraulic oil acting on the oil inlet H of the first control valve 3.1 cannot reach the working oil port of the first control valve 3.1, and at this time, the control port B of the hydraulic control valve 3.2 is communicated with the hydraulic oil tank 5 through the working oil port of the first control valve 3.1 and the oil return port G of the first control valve 3.1, and the control port B of the hydraulic control valve 3.2 has no hydraulic pressure, so the hydraulic pressure acting on the working oil port a of the hydraulic control valve 3.2 can easily push the valve core of the two-way cartridge valve to move upwards, the working oil port a of the hydraulic control valve 3.2 is communicated with the working oil port C of the hydraulic control valve 3.2, the working oil port C of the working oil at the working oil port a of the hydraulic control valve 3.2 cannot flow to the throttle port C of the hydraulic control valve 3.2, and the flow to the driving oil port D of the motor 4 is controlled by adjusting the opening size of the hydraulic valve 3.1. When the oil path from the working oil port A of the hydraulic control valve 3.2 to the working oil port C of the hydraulic control valve 3.2 is in a conducting working condition, the oil inlet F of the second control valve 3.5 is conducted with the working oil port M of the second control valve 3.5, and at the moment, hydraulic oil at the oil outlet of the throttle valve 3.3 also acts on the feedback control oil port Ls of the load sensitive pump 1 through the second control valve 3.5, so that the difference value between the outlet pressure Pa and the load pressure Pb of the load sensitive pump 1 is ensured to be constant. Because the opening of the throttle valve 3.3 is adjusted and then kept unchanged, namely the side power take-off increases or decreases in a certain direction, the flow of the hydraulic system is kept unchanged all the time.
In some embodiments, the hydraulic control valve 3.2 is a two-way cartridge valve, and the first control valve 3.1 is a solenoid valve comprising an initial station and a right station; the coil DT1 of the first control valve 3.1 is positioned at an initial station when power is lost, and the oil inlet of the first control valve 3.1 is communicated with the working oil port of the first control valve 3.1 under the working condition that the first control valve 3.1 is positioned at the initial station; at this time, the hydraulic oil provided by the load-sensitive pump 1 cannot pass through the working port a of the pilot operated valve 3.2 to the working port C of the pilot operated valve 3.2. When the coil DT1 of the first control valve 3.1 is powered on, the coil DT1 is located at a right station, and when the first control valve 3.1 is located at the right station, a working oil port of the first control valve 3.1 is communicated with the hydraulic oil tank 5, and at the moment, hydraulic oil provided by the load sensitive pump 1 can pass through the working oil port A of the hydraulic control valve 3.2 to the working oil port C of the hydraulic control valve 3.2.
In some embodiments, the second control valve 3.5 is a solenoid valve comprising an initial station and a right station; when the coil DT2 of the second control valve 3.5 is in an initial station when the power is lost, the oil inlet F of the second control valve 3.5 and the working oil port M of the second control valve 3.5 are respectively communicated with the hydraulic oil tank 5 when the second control valve 3.5 is in the initial station. When the coil DT2 of the second control valve 3.5 is powered on, the coil is positioned at the right station, and when the second control valve 3.5 is positioned at the right station, the oil inlet F of the second control valve 3.5 is communicated with the working oil port M of the second control valve 3.5. By combining the working principle of the first control valve 3.1, the first control valve 3.1 and the second control valve 3.5 of the load sensitive hydraulic system are controlled to be powered on or powered off simultaneously, so that the work of the high-pressure waterway system can be satisfied.
In some embodiments, the flow control unit 3 further includes a relief valve 3.4, an oil inlet of the relief valve 3.4 is connected to an oil outlet of the throttle valve 3.3, and an oil outlet of the relief valve 3.4 is connected to the hydraulic oil tank 5.
In some embodiments, a high-pressure filter 2 is further arranged at the oil outlet of the load-sensitive pump 1, and the hydraulic oil at the oil outlet of the load-sensitive pump 1 is filtered and then delivered to a flow control unit 3.
In some embodiments, the flow control unit 3 is integrated within a flow control valve. The flow control unit 3 comprises a first control valve 3.1, a hydraulic control valve 3.2, a throttle valve 3.3, a safety valve 3.4 and a second control valve 3.5, and the flow control valve comprises an oil inlet P, an oil return port T, a feedback control oil port Ls and a working oil port A based on the flow control unit 3. In the pair, an oil inlet P of the flow control valve is respectively connected with an oil inlet H of the first control valve 3.1 and a working oil port A of the hydraulic control valve 3.2, an oil return port T of the flow control valve is respectively connected with an oil outlet of the safety valve 3.4, an oil return port G of the first control valve 3.1 and an oil return port of the second control valve 3.5, a feedback control oil port Ls of the flow control valve is connected with a working oil port M of the second control valve 3.5, and the working oil port A of the flow control valve is connected with an oil outlet of the throttle valve 3.3. The oil inlet P of the flow control valve is connected with the oil outlet A of the load sensitive pump 1, the oil return port T of the flow control valve is connected with the hydraulic oil tank 5, the feedback control oil port Ls of the flow control valve is connected with the feedback control oil port Ls of the load sensitive pump 1, and the working oil port A of the flow control valve is connected with the oil inlet D of the driving motor 4.
As another implementation manner, the pilot operated valve 3.2 of the load sensitive hydraulic system of the present invention may also be a pilot operated check valve, where the pilot operated check valve is controlled differently from a two-way cartridge valve, and the control port of the pilot operated check valve may be turned on reversely (i.e. may be turned on in both directions) when hydraulic pressure is obtained, and may be turned on in only one direction when no hydraulic pressure acts on the control port of the pilot operated check valve. Therefore, if the pilot operated check valve 3.2 is adopted, when the first control valve 3.1 is designed to be powered, the oil inlet of the first control valve 3.1 is conducted with the working oil port of the first control valve 3.1, and at this time, the pilot operated check valve is conducted reversely, so that the hydraulic oil provided by the load sensitive pump 1 can be supplied to the driving motor 4; when the first control valve 3.1 is powered off, the working oil port of the first control valve 3.1 is communicated with the oil return port of the first control valve 3.1, and at the moment, the hydraulic control check valve is reversely cut off, so that hydraulic oil provided by the load sensitive pump 1 cannot reach the driving motor 4. Similarly, when the pilot operated check valve is turned on reversely, the second control valve 3.5 is also configured such that the oil inlet of the second control valve 3.5 is turned on with the working oil port of the second control valve 3.5.
The foregoing description is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way, and any simple modification, equivalent variation and modification made to the above embodiments according to the technical principles of the present invention are within the scope of the technical solutions of the present invention.
Claims (8)
1. A load sensitive hydraulic system, characterized by: comprises a load sensitive pump (1), a flow control unit (3) and a driving motor (4) for driving the high-pressure water pump;
the flow control unit (3) comprises a first control valve (3.1), a hydraulic control valve (3.2), a second control valve (3.5) and a throttle valve (3.3), wherein an oil outlet of the load sensitive pump (1) is respectively connected with an oil inlet of the first control valve (3.1) and a working oil port A of the hydraulic control valve (3.2), and a working oil port of the first control valve (3.1) is connected with a control port B of the hydraulic control valve (3.2); the working oil port C of the hydraulic control valve (3.2) is respectively connected with the oil inlet of the driving motor (4) and the oil inlet of the second control valve (3.5) through the throttle valve (3.3), and the working oil port of the second control valve (3.5) is connected with the feedback control oil port of the load sensitive pump (1);
the control port B of the hydraulic control valve (3.2) is configured to control the on-off of the working port A of the hydraulic control valve (3.2) to the working port C of the hydraulic control valve (3.2);
when an oil path from the working oil port A of the hydraulic control valve (3.2) to the working oil port C of the hydraulic control valve (3.2) is in a conducting working condition, the second control valve (3.5) is also configured that an oil inlet of the second control valve (3.5) is conducted with the working oil port of the second control valve (3.5).
2. A load sensitive hydraulic system according to claim 1, wherein: the hydraulic control valve (3.2) is a two-way cartridge valve.
3. A load sensitive hydraulic system according to claim 2, wherein: the first control valve (3.1) is an electromagnetic valve comprising an initial station and a right station;
when the first control valve (3.1) is in an initial station when power is lost, an oil inlet of the first control valve (3.1) is communicated with a working oil port of the first control valve (3.1) when the first control valve (3.1) is in the initial station, and at the moment, hydraulic oil provided by the load sensitive pump (1) cannot pass through the working oil port A of the hydraulic control valve (3.2) to the working oil port C of the hydraulic control valve (3.2);
when the first control valve (3.1) is in a right station when being electrified, a working oil port of the first control valve (3.1) is communicated with the hydraulic oil tank (5) when the first control valve (3.1) is in the right station, and at the moment, hydraulic oil provided by the load sensitive pump (1) can pass through the working oil port A of the hydraulic control valve (3.2) to the working oil port C of the hydraulic control valve (3.2).
4. A load sensitive hydraulic system according to claim 2, wherein: the second control valve (3.5) is an electromagnetic valve comprising an initial station and a right station;
the second control valve (3.5) is positioned at an initial station when power is lost, and when the second control valve (3.5) is positioned at the initial station, an oil inlet of the second control valve (3.5) and a working oil port of the second control valve (3.5) are respectively communicated with the hydraulic oil tank (5);
the second control valve (3.5) is positioned at a right station when being electrified, and when the second control valve (3.5) is positioned at the right station, an oil inlet of the second control valve (3.5) is communicated with a working oil port of the second control valve (3.5).
5. A load sensitive hydraulic system according to claim 1, wherein: the flow control unit (3) further comprises a safety valve (3.4), an oil inlet of the safety valve (3.4) is connected with an oil outlet of the throttle valve (3.3), and an oil outlet of the safety valve (3.4) is connected with a hydraulic oil tank (5).
6. A load sensitive hydraulic system according to claim 1, wherein: the load-sensitive pump (1) is driven by a side power take-off.
7. A load sensitive hydraulic system according to claim 1, wherein: and a high-pressure filter (2) is further arranged at the oil outlet of the load-sensitive pump (1).
8. A load sensitive hydraulic system according to any one of claims 1 to 7, wherein: the flow control unit (3) is integrated in a flow control valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310904010.7A CN116906384A (en) | 2023-07-24 | 2023-07-24 | Load-sensitive hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310904010.7A CN116906384A (en) | 2023-07-24 | 2023-07-24 | Load-sensitive hydraulic system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116906384A true CN116906384A (en) | 2023-10-20 |
Family
ID=88354601
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310904010.7A Pending CN116906384A (en) | 2023-07-24 | 2023-07-24 | Load-sensitive hydraulic system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116906384A (en) |
-
2023
- 2023-07-24 CN CN202310904010.7A patent/CN116906384A/en active Pending
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