CN216922714U - Hydraulic system for controlling flow - Google Patents
Hydraulic system for controlling flow Download PDFInfo
- Publication number
- CN216922714U CN216922714U CN202122791304.2U CN202122791304U CN216922714U CN 216922714 U CN216922714 U CN 216922714U CN 202122791304 U CN202122791304 U CN 202122791304U CN 216922714 U CN216922714 U CN 216922714U
- Authority
- CN
- China
- Prior art keywords
- hydraulic
- oil
- valve
- oil port
- flow
- Prior art date
- 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.)
- Active
Links
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The utility model provides a hydraulic system for controlling flow, which comprises a main oil way and a flow control system, wherein the main oil way comprises a small-flow signal oil port and a large-flow signal oil port, and the pressure of the large-flow signal oil port is greater than that of the small-flow signal oil port; the flow control system comprises a shuttle valve, a pressure reducing valve, a hydraulic reversing valve, a variable hydraulic pump and an oil tank; one input end of the shuttle valve is connected with the small-flow signal oil port, the other input end of the shuttle valve is connected with the large-flow signal oil port, the output end of the shuttle valve is connected with the input end of the pressure reducing valve, the output end of the pressure reducing valve is connected with the signal oil port of the hydraulic reversing valve, the input end of the hydraulic reversing valve is connected with the oil tank, the output end of the hydraulic reversing valve is connected with the signal oil port of the variable reversing pump, the input end of the variable reversing pump is connected with the oil tank, and the output end of the variable reversing pump is connected with the input oil port of the main oil way; the utility model meets the use requirement that the flow rate difference required by different actions is large, and the situation of excessive flow rate overflow heating can not occur; the cost is low.
Description
Technical Field
The utility model relates to the technical field of hydraulic pressure, in particular to a hydraulic system for controlling flow.
Background
Along with the improvement of the requirement of a user on the operating efficiency of the crane, the oil pump is required to provide enough flow to meet the requirement of the system; however, when the flow rate required by one action of the crane is much larger than that required by other actions, the small-flow action can overflow due to the residual flow rate to generate great heat when using a quantitative pump system, and the design and use requirements cannot be met; although the above problems can be solved by using the load sensitive variable system in which the output of the oil pump is only related to the opening of the multi-way valve at the flow rate required for the operation and excessive flow rate overflows and heats up, the use of the load sensitive variable system has problems of complicated system control and high component cost.
For the telescopic action of some telescopic cranes, the difference between the hydraulic flow rates required before and after the telescopic action of the crane is large, so a hydraulic system which is low in cost and meets the use requirement that the difference between the required flow rates is large between different actions needs to be designed.
Disclosure of Invention
The utility model provides a hydraulic system for controlling flow, which meets the use requirement of different actions with larger flow difference and does not generate more flow overflow heating by utilizing the structure of the utility model; the cost is low.
In order to achieve the purpose, the technical scheme of the utility model is as follows: a hydraulic system for controlling flow comprises a main oil way and a flow control system, wherein the main oil way comprises a small-flow signal oil port, a large-flow signal oil port and a main oil way input oil port, and the pressure of the large-flow signal oil port is greater than that of the small-flow signal oil port.
The flow control system comprises a shuttle valve, a pressure reducing valve, a hydraulic reversing valve, a variable hydraulic pump and an oil tank; one input end of the shuttle valve is connected with the small-flow signal oil port, the other input end of the shuttle valve is connected with the large-flow signal oil port, the output end of the shuttle valve is connected with the input end of the pressure reducing valve, the output end of the pressure reducing valve is connected with the signal oil port of the hydraulic reversing valve, the input end of the hydraulic reversing valve is connected with the oil tank, the output end of the hydraulic reversing valve is connected with the signal oil port of the variable reversing pump, the input end of the variable reversing pump is connected with the oil tank, and the output end of the variable reversing pump is connected with the input oil port of the main oil way.
When the small flow signal oil port outputs hydraulic oil, the oil pressure of the small flow signal oil port is not enough to enable the hydraulic reversing valve to change the direction; when the large-flow signal oil port outputs hydraulic oil, the hydraulic oil of the large-flow signal oil port is processed by the pressure reducing valve, so that the hydraulic reversing valve is reversed.
With the arrangement, when the small-flow signal oil port outputs hydraulic oil, the oil pressure of the small-flow signal oil port is not enough to change the direction of the hydraulic reversing valve, and the variable displacement hydraulic pump unloads the variable displacement hydraulic oil; when the large-flow signal oil port outputs hydraulic oil, the hydraulic oil of the large-flow signal oil port is processed by the pressure reducing valve, the hydraulic reversing valve is reversed, the hydraulic oil passing through the hydraulic reversing valve is conveyed to the variable displacement hydraulic pump as signal oil, the variable displacement hydraulic pump outputs the hydraulic oil in a variable displacement mode at the moment, and therefore the variable displacement hydraulic pump can automatically switch the flow of the hydraulic displacement pump to be conveyed to the input oil port of the main oil way according to the required hydraulic flow of the main oil way of the hydraulic system load, the requirement that the main oil way carries out large-flow action is met, overflow heating of the system is avoided when the main oil way carries out small-flow action, and compared with the use of a load sensitive variable system, the cost is reduced and the control of the hydraulic system is simplified.
Further, the hydraulic reversing valve is a two-position two-way hydraulic reversing valve.
Further, when the large-flow signal oil port outputs, the pressure at the output end of the pressure reducing valve is larger than the pressure required by the hydraulic reversing valve for reversing; according to the arrangement, after the hydraulic reversing valve receives the signal oil output by the pressure reducing valve, the hydraulic reversing valve reverses according to the pressure of the signal oil and then outputs the hydraulic oil to the variable displacement hydraulic pump so as to change the hydraulic oil to a large displacement; when the telescopic hydraulic pump is not in action, the hydraulic reversing valve cannot be subjected to pressure for reversing, the hydraulic reversing valve is reset under the action of a spring of the hydraulic valve, the variable displacement hydraulic pump is controlled to discharge the variable displacement oil, and the oil pump is changed to small displacement.
Further, the variable displacement hydraulic pump is a one-way variable displacement hydraulic pump.
Further, the power source of the variable displacement hydraulic pump is an electric motor.
Furthermore, an oil drain port of the hydraulic reversing valve is connected with an oil tank.
Drawings
FIG. 1 is a block diagram of the main oil circuit and flow control system connections of the present invention.
Description of the drawings: 1. a main oil path; 11. a large-flow signal oil port; 12. a small flow signal oil port; 13. a main oil way input oil port; 2. a shuttle valve; 3. a pressure reducing valve; 4. a hydraulically operated directional control valve; 5. and a variable displacement hydraulic pump.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 1, a hydraulic system for controlling flow includes a main oil path 1 for controlling a telescopic hydraulic cylinder and a flow control system, where the main oil path 1 includes a small-flow signal oil port 12, a large-flow signal oil port 11 and an input oil port of the main oil path 1, and a pressure of the large-flow signal oil port 11 is greater than that of the small-flow signal oil port 12.
The flow control system comprises a shuttle valve 2, a pressure reducing valve 3, a hydraulic reversing valve 4, a variable hydraulic pump 5 and an oil tank; one input end of the shuttle valve 2 is connected with a small flow signal oil port 12, the other input end of the shuttle valve 2 is connected with a large flow signal oil port 11, the output end of the shuttle valve 2 is connected with the input end of the pressure reducing valve 3, the output end of the pressure reducing valve 3 is connected with a signal oil port of the hydraulic reversing valve 4, the input end of the hydraulic reversing valve 4 is connected with an oil tank, the output end of the hydraulic reversing valve 4 is connected with a signal oil port of the variable reversing pump, the input end of the variable reversing pump is connected with the oil tank, and the output end of the variable reversing pump is connected with a main oil way input oil port 13.
When the telescopic hydraulic cylinder performs telescopic action, the large-flow signal oil port 11 outputs signal oil to enter the shuttle valve 2; when the telescopic hydraulic cylinder does not perform telescopic action, the small-flow signal oil port 12 outputs signal oil to enter the shuttle valve 2; when the small flow signal oil port 12 outputs hydraulic oil, the oil pressure of the small flow signal oil port 12 is not enough to change the direction of the hydraulic reversing valve 4; when the large-flow signal oil port 11 outputs hydraulic oil, the hydraulic oil of the large-flow signal oil port 11 is processed by the pressure reducing valve 3, so that the hydraulic reversing valve 4 is reversed; the hydraulic flow rate when the crane performs the telescopic action is about 3 times of the hydraulic flow rate of other actions, whether the telescopic action is performed or not is judged through the shuttle valve 2, and the signal oil is output through the shuttle valve 2.
With the above arrangement, when the small-flow signal oil port 12 outputs hydraulic oil, the oil pressure of the small-flow signal oil port 12 is not enough to change the direction of the hydraulic directional control valve 4, and at this time, the variable displacement hydraulic pump 5 unloads the variable displacement hydraulic oil; when the large-flow signal oil port 11 outputs hydraulic oil, the hydraulic oil of the large-flow signal oil port 11 is processed by the pressure reducing valve 3, the hydraulic reversing valve 4 is reversed, the hydraulic oil passing through the hydraulic reversing valve 4 is conveyed to the variable displacement hydraulic pump 5 as signal oil, at the moment, the variable displacement hydraulic pump 5 outputs the hydraulic oil in a variable displacement mode, and therefore the variable displacement hydraulic pump 5 can automatically switch the flow of the hydraulic displacement pump to convey the flow to the main oil path input oil port 13 according to the required hydraulic flow of the main oil path 1 loaded by the hydraulic system, the requirement that the main oil path 1 carries out large-flow action is met, overflow heating of the system is avoided when the main oil path 1 carries out small-flow action, and compared with a load sensitive variable system, the cost is reduced, and the control of the hydraulic system is simplified.
The hydraulic reversing valve 4 is a two-position two-way hydraulic reversing valve 4.
When the large-flow signal oil port 11 outputs, the pressure at the output end of the pressure reducing valve 3 is greater than the pressure required by the hydraulic reversing valve 4 for reversing; the pressure set by the pressure reducing valve 3 is 35bar, and the reversing pressure of the hydraulic reversing valve 4 is 14 bar; the hydraulic reversing valve 4 is reversed according to the pressure of the signal oil after receiving the signal oil output by the pressure reducing valve 3, and then outputs hydraulic oil to the variable displacement hydraulic pump 5 to be converted to large displacement; when the extension is not operated, the hydraulic reversing valve 4 cannot be subjected to pressure for reversing, the hydraulic reversing valve 4 is reset under the action of a spring of the hydraulic reversing valve 4, the variable displacement hydraulic pump 5 is controlled to discharge the variable displacement oil, and the oil pump is changed to small displacement; this valve corresponds to an on-off valve for controlling whether the variable hydraulic pump 5 is variable or not.
The variable hydraulic pump 5 is a one-way variable hydraulic pump 5.
The power source of the variable displacement hydraulic pump 5 is an electric motor.
The oil drain port of the hydraulic reversing valve 4 is connected with an oil tank.
Claims (6)
1. A hydraulic system for controlling flow comprises a main oil way and a flow control system, and is characterized in that: the main oil way comprises a small-flow signal oil port, a large-flow signal oil port and a main oil way input oil port, and the pressure of the large-flow signal oil port is greater than that of the small-flow signal oil port;
the flow control system comprises a shuttle valve, a pressure reducing valve, a hydraulic reversing valve, a variable hydraulic pump and an oil tank; one input end of the shuttle valve is connected with the small-flow signal oil port, the other input end of the shuttle valve is connected with the large-flow signal oil port, the output end of the shuttle valve is connected with the input end of the pressure reducing valve, the output end of the pressure reducing valve is connected with the signal oil port of the hydraulic reversing valve, the input end of the hydraulic reversing valve is connected with the oil tank, the output end of the hydraulic reversing valve is connected with the signal oil port of the variable reversing pump, the input end of the variable reversing pump is connected with the oil tank, and the output end of the variable reversing pump is connected with the input oil port of the main oil way;
when the small flow signal oil port outputs hydraulic oil, the oil pressure of the small flow signal oil port is not enough to enable the hydraulic reversing valve to change the direction; when the large-flow signal oil port outputs hydraulic oil, the hydraulic oil of the large-flow signal oil port is processed by the pressure reducing valve, so that the hydraulic reversing valve is reversed.
2. A hydraulic system for controlling flow according to claim 1, wherein: the hydraulic reversing valve is a two-position two-way hydraulic reversing valve.
3. A hydraulic system for controlling flow according to claim 1, wherein: when the large-flow signal oil port outputs, the pressure of the output end of the pressure reducing valve is larger than the pressure required by the hydraulic reversing valve for reversing.
4. A hydraulic system for controlling flow according to claim 1, wherein: the variable hydraulic pump is a one-way variable hydraulic pump.
5. A hydraulic system for controlling flow according to claim 1, wherein: the power source of the variable hydraulic pump is an electric motor.
6. A hydraulic system for controlling flow according to claim 1, wherein: the oil drain port of the hydraulic reversing valve is connected with an oil tank.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122791304.2U CN216922714U (en) | 2021-11-15 | 2021-11-15 | Hydraulic system for controlling flow |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122791304.2U CN216922714U (en) | 2021-11-15 | 2021-11-15 | Hydraulic system for controlling flow |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN216922714U true CN216922714U (en) | 2022-07-08 |
Family
ID=82248208
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122791304.2U Active CN216922714U (en) | 2021-11-15 | 2021-11-15 | Hydraulic system for controlling flow |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN216922714U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114215797A (en) * | 2021-11-15 | 2022-03-22 | 中船华南船舶机械有限公司 | Method for controlling flow of variable pump by hydraulic system |
-
2021
- 2021-11-15 CN CN202122791304.2U patent/CN216922714U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114215797A (en) * | 2021-11-15 | 2022-03-22 | 中船华南船舶机械有限公司 | Method for controlling flow of variable pump by hydraulic system |
| CN114215797B (en) * | 2021-11-15 | 2024-04-19 | 中船华南船舶机械有限公司 | Method for controlling flow of variable pump by hydraulic system |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103671335B (en) | Load-sensitive electric proportional multi-loop valve | |
| CN102229328B (en) | Vehicle mechanical energy-saving hydraulic system with multi-pump confluence | |
| CN102296665B (en) | Excavator hydraulic system carrying load sensing main valve and positive flow pump | |
| CN103047208A (en) | Load-sensitive electro-hydraulic proportional multi-way valve | |
| CN103174688A (en) | Hydraulic energy-saving system | |
| CN104011399B (en) | Oil pressure control circuit and the oil pressure control circuit of building machinery | |
| CN216922714U (en) | Hydraulic system for controlling flow | |
| CN104863914A (en) | Electrohydraulic joint control flow collecting valve | |
| CN105090141A (en) | Hydraulic variable control system and vehicle | |
| CN114151418A (en) | Variable pump flow control hydraulic system | |
| CN108457926A (en) | Power controls electronic hydrostatic integration pump control asymmetric cylinder actuator | |
| CN102734241B (en) | Opened and closed hydraulic system and engineering machinery | |
| CN105952700A (en) | Loader variable multi-stage power control module and hydraulic system | |
| CN104912136B (en) | A kind of excavator and its Hydraulic slewing system | |
| CN104029721A (en) | Hydraulic steering device for loader | |
| CN213682287U (en) | Steering hydraulic system and loader | |
| CN206017293U (en) | Loading machine variable multiple power levels control module and hydraulic system | |
| CN103290879B (en) | Loader-digger and hydraulic system thereof | |
| CN103031957A (en) | Control system and method for concrete machine | |
| CN203130636U (en) | Engineering mechanical equipment and hydraulic control loop thereof | |
| CN114215797A (en) | Method for controlling flow of variable pump by hydraulic system | |
| CN203670337U (en) | Load-sensitive electric proportional multi-way valve | |
| CN109469656A (en) | Hydraulic system and engineering truck | |
| CN104912857A (en) | Multi-way valve | |
| CN110985458B (en) | Multistage differential pressure control hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |