CN213682287U - Steering hydraulic system and loader - Google Patents
Steering hydraulic system and loader Download PDFInfo
- Publication number
- CN213682287U CN213682287U CN202022015621.0U CN202022015621U CN213682287U CN 213682287 U CN213682287 U CN 213682287U CN 202022015621 U CN202022015621 U CN 202022015621U CN 213682287 U CN213682287 U CN 213682287U
- Authority
- CN
- China
- Prior art keywords
- valve
- port
- pilot
- pump
- signal control
- 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 relates to a hydraulic system, in order to solve the energy-conserving problem that the existing quantitative steering system has throttling loss and overflow loss, is unfavorable for the complete machine, the utility model discloses construct a steering hydraulic system and loader, wherein turn to the hydraulic system signal control valve, the main valve load signal delivery outlet of flow amplification valve communicates with the spring chamber of priority valve, LS1 mouth communicates with the spring chamber of priority valve, the load signal delivery outlet communicates with hydraulic tank through the meso position oil circuit of main valve when the main valve is in the meso position, the spring chamber opposite end of priority valve communicates with CF mouth; the LS1 port, the pump port of the variable pump and the LS port are all connected with a signal control valve, and the LS port of the variable pump is communicated with the LS1 port or the pump port of the variable pump through the signal control valve. Utility model can make the sensitive variable pump of load provide the flow as required according to turning to when turning to, do not have throttle and overflow loss simultaneously to reach energy-conserving purpose.
Description
Technical Field
The utility model relates to a hydraulic system, more specifically say, relate to a turn to hydraulic system and loader.
Background
The steering hydraulic systems of most existing loaders are quantitative systems, and because the discharge capacity of the quantitative systems is invariable, the redundant flow inevitably has throttling loss and overflow loss in the steering process, so that the energy conservation of the whole loader is not facilitated. A high-pressure load sensing system is used in a steering system of part of the high-end loader, the high-pressure load sensing system is advanced in principle, high in loop efficiency and steering comfort, but high in system cost, and in the popularization process of the high-pressure steering system, due to the fact that steering core elements are high-pressure, the phenomena of steering stagnation, steering heaviness and the like often occur. Therefore, at least at the present stage of high-voltage operation of the steering system of the loader, matched core elements cannot completely meet the use requirements, and a low-voltage control load sensing steering system is urgently needed, so that the energy conservation of the whole machine can be realized, and the requirements of domestic working conditions can be met.
SUMMERY OF THE UTILITY MODEL
The to-be-solved technical problem of the utility model is to there are throttling loss and overflow loss, be unfavorable for the energy-conserving problem of complete machine to current ration a steering system, and provide a turn to hydraulic system and loader, eliminate throttling loss and overflow loss so that the complete machine is energy-conserving.
The utility model discloses a realize that the technical scheme of its purpose is like: the steering hydraulic system is characterized by further comprising a signal control valve, wherein the flow amplifying valve comprises a priority valve and a main valve which are connected between the port P and the ports A and B, the oil inlet end of the priority valve is communicated with the port P, the CF port is connected with the main valve, and a working oil port of the main valve is communicated with the ports A and B; the L port and the R port of the steering gear are connected with a pilot control end of a main valve; the load signal output port of the main valve is communicated with the spring cavity of the priority valve, the LS1 port of the flow amplifying valve is communicated with the spring cavity of the priority valve, the load signal output port is communicated with the hydraulic oil tank through a middle oil way of the main valve when the main valve is in a middle position, and the opposite end of the spring cavity of the priority valve is communicated with the CF port; the LS1 port of the flow amplifying valve, the pump port and the LS port of the variable pump are all connected with the signal control valve, when no effective pressure is input at the hydraulic control end of the signal control valve, the LS1 port of the flow amplifying valve is communicated with the LS port of the variable pump through the signal control valve, and when the effective pressure is input at the hydraulic control end of the signal control valve, the pump port of the variable pump is communicated with the LS port of the variable pump through the signal control valve.
In the steering hydraulic system, the signal control valve is a two-position three-way valve, a port P2 of the signal control valve is connected with a port LS1 of the flow amplification valve, a port P3 of the signal control valve is connected with a pump port of the variable pump, a port P4 of the signal control valve is connected with a port LS of the variable pump, and when no effective pressure is input at a hydraulic control end of the signal control valve, a port P2 and a port P4 of the signal control valve are communicated; the port P3 communicates with the port P4 when the pilot port of the signal control valve has a valid pressure input.
In the above-mentioned hydraulic steering system, the pilot oil source includes a pilot oil supply valve, an oil inlet end of the pilot oil supply valve is connected to the pump port of the variable displacement pump, and an oil outlet end of the pilot oil supply valve is connected to the P port of the steering gear.
The technical scheme for realizing the purpose of the invention is as follows: the loader comprises a working hydraulic system and the steering hydraulic system, wherein an EF port of a priority valve is connected with a distribution valve in the working hydraulic system, a hydraulic control end of a signal control valve is connected with a pilot control oil path of the working hydraulic system through a shuttle valve group, an oil outlet end of the shuttle valve group is connected with the hydraulic control end of the signal control valve, and each oil inlet end of the shuttle valve group is connected with the pilot control oil path of the working hydraulic system.
The loader further comprises a two-position two-way switch valve, an EF port of the priority valve is connected with a distribution valve in a working hydraulic system through the two-position two-way switch valve, a hydraulic control end of the two-position two-way switch valve is connected with an oil outlet end of the shuttle valve group, and when the oil outlet end of the shuttle valve group has effective pressure output, the two-position two-way switch valve is switched on or switched off.
In the loader, the pilot oil source comprises a pilot oil supply valve, the oil inlet end of the pilot oil supply valve is connected with the pump port of the variable pump, the first oil outlet end of the pilot oil supply valve is connected with the P port of the steering gear, and the second oil outlet end of the pilot oil supply valve is connected with the pilot valve of the working hydraulic system.
Compared with the prior art, the utility model can provide the flow for the load sensitive variable pump according to the steering requirement when steering, and simultaneously has no throttling and overflow loss, thereby achieving the purpose of energy saving; compared with a high-end high-voltage load sensing variable system, the system can solve the problem of frequent steering jamming, heavy steering and other fault feedbacks in the application process, and greatly saves the cost while meeting the domestic working condition requirements.
Drawings
Fig. 1 is a schematic diagram of the hydraulic system of the loader of the present invention.
Fig. 2 is a schematic diagram of a flow amplifying valve in the steering system of the loader of the present invention.
Part names and serial numbers in the figure:
the hydraulic control system comprises a hydraulic oil tank 1, a variable displacement pump 2, a steering gear 3, a flow amplification valve 4, a main valve 41, a priority valve 42, a load signal output port 43, a steering oil cylinder 5, a signal control valve 6, a pilot oil supply valve 7, a distribution valve 8, a shuttle valve group 9, a pilot valve 10 and a two-position two-way switch valve 11.
Detailed Description
The following description of the embodiments refers to the accompanying drawings.
As shown in fig. 1, in the loader of the present embodiment, the hydraulic system includes a steering hydraulic system and a working hydraulic system.
The steering hydraulic system comprises a flow amplifying valve 4, a steering oil cylinder 5 connected with an A port and a B port of the flow amplifying valve 4, a steering gear 3, a pilot oil source connected with a P port of the steering gear 3, a hydraulic oil tank 1, a variable pump 2 of which the oil inlet end is connected with the hydraulic oil tank 1 and the pump port is connected with the P port of the flow amplifying valve 4, and a signal control valve 6.
As shown in fig. 2, the flow amplifying valve 4 includes a priority valve 42 and a main valve 41 connected between port P and ports a and B, an oil inlet end of the priority valve 42 is connected to port P, a CF port is connected to the main valve 41, and a working port of the main valve 41 is connected to ports a and B. The load signal output port 43 of the main valve 41 and the LS1 port of the flow amplifying valve are both in communication with the spring chamber of the priority valve 42; the opposite end of the spring chamber of the priority valve 42 communicates with the CF port of the priority valve 42. When the main valve is in the middle position, the LS1 port is communicated with the hydraulic oil tank through the load signal output port 43 of the main valve and the middle position of the main valve, when the main valve is in the non-middle position (when the main valve is in the left position or the right position during steering), the steering load signal is extracted through the load signal extraction throttling groove and is output through the load signal output port 43 and the LS1 port.
As shown in fig. 1, the LS1 port of the flow amplifying valve, the pump port of the variable displacement pump and the LS port are connected with the signal control valve. The L port and the R port of the steering gear 3 are connected to the pilot control end of the main valve 41; the signal control valve 6 is a two-position three-way valve, a P2 port of the signal control valve is connected with an LS1 port of the flow amplifying valve 4, a P3 port of the signal control valve is connected with a pump port of the variable pump, a P4 port of the signal control valve is connected with an LS port of the variable pump, when no effective pressure is input at a hydraulic control end of the signal control valve 6 (namely, when the pilot valve 10 does not operate, a P2 port and a P4 port are connected, and a P3 port is cut off; when the pilot control end of the signal control valve has effective pressure input (when the pilot valve 10 has operation action), the P3 port and the P4 port are communicated, and the P2 port is cut off. The pilot oil source comprises a pilot oil supply valve 7, the oil inlet end of the pilot oil supply valve 7 is connected with the pump port of the variable displacement pump 2, the first oil outlet end (A1 port) is connected with the P port of the steering gear 3, and the second oil outlet end (A port) is connected with a pilot valve 10 of the working hydraulic system.
As shown in fig. 1, the EF port of the priority valve 42 is connected to the distribution valve 8 in the working hydraulic system through a two-position two-way switching valve 11, the hydraulic control end of the two-position two-way switching valve is connected to the oil outlet end of the shuttle valve group, and when the effective pressure output at the oil outlet end of the shuttle valve group is that the two-position two-way valve is opened, and vice versa. The oil outlet end of the shuttle valve group 9 is also connected with the hydraulic control end of the signal control valve 6, and each oil inlet end of the shuttle valve group 9 is connected with the pilot control oil path of the working hydraulic system.
The four output ports (a1 port, b1 port, a2 port, b2 port) of the pilot valve 10 are connected with the hydraulic control end of the corresponding reversing valve of the distribution valve 8 in the working hydraulic system through a pilot control oil path, and by operating the pilot valve, the corresponding pilot pressure output port of the pilot valve outputs effective pilot pressure to act on the hydraulic control end of the corresponding reversing valve in the distribution valve, so that the effective pilot pressure is reversed to realize the corresponding action in the lifting of the movable arm of the loader or the retraction of the bucket. The effective pilot pressure enables it to drive the reversal of the direction change valve in the distribution valve.
The working principle of the loader in the embodiment is as follows:
1. the whole machine is in idle no-action working condition, the pilot valve 10 has no pilot pressure signal output, the pressure of each input end of the shuttle valve group 9 is zero, the pressure of the output end is also zero, the signal control valve 6 is in left position, and the P2 port is communicated with the P4 port; the two-position two-way switch valve 11 is in an upper cut-off state. The LS port of the variable pump 2 is communicated with the LS1 port of the flow amplifying valve 4 through a P4 port and a P2 port of the signal control valve 6, and flows back to the oil tank through the load signal output port 43 of the main valve 41 and a middle oil path, so that the LS port of the variable pump 2 and the LS1 port of the main valve 41 are ensured to be decompressed when the middle position is reached; the pressures at the left and right ends of the priority valve 42 are equal, and the priority valve 42 is in the right position, so that the variable displacement pump 2 is ensured to be in the closed middle position, and no flow is output.
2. Under the working condition of independent steering, the pilot valve 10 has no pilot pressure signal output, the pressure of each input end of the shuttle valve group 9 is zero, the pressure of the output end is also zero, the signal control valve 6 is positioned at the left position, and the two-position two-way switch valve 11 is positioned at the upper stop; when steering, the main valve 41 is switched to the left or right position, and a steering load signal is taken out through the throttle groove of the main valve and applied to the spring chamber of the priority valve through the load signal output port 43. The opposite end of the spring cavity of the priority valve is connected with the CF port, the pressure of the CF port is higher than the pressure of the load signal, the priority valve moves to the right position, the opening from the P port to the CF port is reduced until the pressure difference between the variable displacement pump and the steering load signal is equal to the standby pressure delta P, and the priority valve is in the middle position and is communicated with the CF port and the EF port simultaneously. And an LS port of the variable displacement pump receives a steering load signal through a signal control valve 6, and outputs the flow required by a steering system.
3. Under the independent working condition, the pilot valve 10 has pilot pressure signal output, the pressure of at least one input end in each input end of the shuttle valve group 9 is not zero, the pressure is output from the output end of the shuttle valve group 9 through the shuttle valve group 9 and acts on a hydraulic control end P1 port of the signal control valve 6, and the signal control valve 6 is in the right position; the two-position two-way switch valve 11 is at the lower position and is conducted; at this time, the pump port of the variable pump and the LS port of the variable pump are communicated through a P3 port and a P4 port of the signal control valve 6, and the variable pump is changed into a constant pressure pump with a pressure cut-off function from a load sensitive pump. The pressure signal of the spring cavity of the priority valve flows back to the oil tank through the middle position of the main valve, and the priority valve is positioned at the leftmost position. The variable displacement pump outputs flow to the working system at maximum displacement until the pressure reaches the cut-off pressure, and the variable displacement pump becomes minimum displacement without high-pressure overflow loss.
4. When the steering system and the working system act simultaneously, the pilot valve 42 outputs a pilot pressure signal, the pressure at least one of the input ends of the shuttle valve group 9 is not zero, the pressure is output from the output end of the shuttle valve group through the shuttle valve group 9 and acts on a hydraulic control end P1 port of the signal control valve 6, the signal control valve 6 is in the right position, and the two-position two-way switch valve 11 is in the lower position and is conducted. At this time, the variable pump port and the LS port of the variable pump are connected through the P3 port and the P4 port of the signal control valve 6, and the variable pump is changed from a load-sensitive pump to a constant pressure pump with a pressure cutoff function. Since the steering load signal pressure is less than the CF port pressure, the priority valve is in the neutral position communicating with both the CF port and the EF port. The variable displacement pump outputs flow in a maximum displacement state, the output flow meets the steering requirement preferentially, and the rest flow is supplied to a working system through an EF port. The minimum displacement is not achieved until the operating system pressure reaches the cut-off pressure.
Compared with the traditional quantitative steering system, the hydraulic system in the embodiment can enable the load sensitive variable pump to provide flow according to the steering requirement during steering, and meanwhile, throttling and overflow losses are avoided, so that the energy-saving purpose is achieved; compared with a high-end high-voltage load sensing variable system, the system can solve the problem of frequent steering jamming, heavy steering and other fault feedbacks in the application process, and greatly saves the cost while meeting the domestic working condition requirements.
Claims (6)
1. A steering hydraulic system comprises a flow amplifying valve, a steering oil cylinder connected with an A port and a B port of the flow amplifying valve, a steering gear, a pilot oil source connected with a P port of the steering gear, a hydraulic oil tank and a variable pump, wherein the oil inlet end of the variable pump is connected with the hydraulic oil tank, and the pump port of the variable pump is connected with the P port of the flow amplifying valve; the L port and the R port of the steering gear are connected with a pilot control end of a main valve; the load signal output port of the main valve is communicated with the spring cavity of the priority valve, the load signal output port is communicated with the hydraulic oil tank through a middle oil way of the main valve when the main valve is in a middle position, the LS1 port of the flow amplifying valve is communicated with the spring cavity of the priority valve, and the opposite end of the spring cavity of the priority valve is communicated with the CF port; the LS1 port of the flow amplifying valve, the pump port and the LS port of the variable pump are all connected with the signal control valve, when no effective pressure is input at the hydraulic control end of the signal control valve, the LS1 port of the flow amplifying valve is communicated with the LS port of the variable pump through the signal control valve, and when the effective pressure is input at the hydraulic control end of the signal control valve, the pump port of the variable pump is communicated with the LS port of the variable pump through the signal control valve.
2. The steering hydraulic system according to claim 1, characterized in that the signal control valve is a two-position three-way valve, a port P2 of the signal control valve is connected with a port LS1 of the flow amplification valve, a port P3 of the signal control valve is connected with a pump port of the variable pump, a port P4 of the signal control valve is connected with a port LS of the variable pump, and when no effective pressure is input at a hydraulic control end of the signal control valve, a port P2 and a port P4 of the signal control valve are communicated; the port P3 communicates with the port P4 when the pilot port of the signal control valve has a valid pressure input.
3. The steering hydraulic system according to claim 1, characterized in that the pilot oil source includes a pilot oil supply valve, an oil inlet end of the pilot oil supply valve is connected to a pump port of the variable displacement pump, and an oil outlet end of the pilot oil supply valve is connected to a P port of the steering gear.
4. A loader comprising a working hydraulic system, characterized by further comprising the steering hydraulic system of claim 1 or 2, wherein the EF port of the priority valve is connected to a distribution valve in the working hydraulic system, the pilot control end of the signal control valve is connected to the pilot control oil path of the working hydraulic system through a shuttle valve group, the oil outlet end of the shuttle valve group is connected to the pilot control end of the signal control valve, and each oil inlet end of the shuttle valve group is connected to the pilot control oil path of the working hydraulic system.
5. The loader of claim 4, further comprising a two-position two-way switching valve, wherein the EF port of the priority valve is connected to a distribution valve in the working hydraulic system through the two-position two-way switching valve, the hydraulic control end of the two-position two-way switching valve is connected to the oil outlet end of the shuttle valve set, and when the effective pressure output at the oil outlet end of the shuttle valve set is that the two-position two-way valve is opened and the other is closed.
6. The loader according to claim 4 or 5, wherein said pilot oil source comprises a pilot oil supply valve, an oil inlet end of said pilot oil supply valve is connected to a pump port of said variable displacement pump, a first oil outlet end is connected to a P port of said steering gear, and a second oil outlet end is connected to a pilot valve of said working hydraulic system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022015621.0U CN213682287U (en) | 2020-09-15 | 2020-09-15 | Steering hydraulic system and loader |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022015621.0U CN213682287U (en) | 2020-09-15 | 2020-09-15 | Steering hydraulic system and loader |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN213682287U true CN213682287U (en) | 2021-07-13 |
Family
ID=76747791
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202022015621.0U Active CN213682287U (en) | 2020-09-15 | 2020-09-15 | Steering hydraulic system and loader |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN213682287U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113482090A (en) * | 2021-07-27 | 2021-10-08 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| CN113494111A (en) * | 2021-07-27 | 2021-10-12 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
-
2020
- 2020-09-15 CN CN202022015621.0U patent/CN213682287U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113482090A (en) * | 2021-07-27 | 2021-10-08 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| CN113494111A (en) * | 2021-07-27 | 2021-10-12 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| CN113494111B (en) * | 2021-07-27 | 2022-08-05 | 柳州柳工液压件有限公司 | Main control valve, fixed variable hydraulic system and loader |
| CN113482090B (en) * | 2021-07-27 | 2023-12-12 | 广西中源机械有限公司 | Main control valve, constant-variable hydraulic system and loader |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108412829B (en) | Load sensitive type multi-way valve with independently adjustable inlet and outlet throttling edges | |
| CN213682287U (en) | Steering hydraulic system and loader | |
| CN208346897U (en) | Loader hydraulic system | |
| CN104806588A (en) | Two-pump confluence hydraulic control system | |
| CN111255007B (en) | Loader constant-variable hydraulic system based on load signal direct control | |
| CN111733921A (en) | Loader hydraulic system and engineering machinery | |
| CN113482090B (en) | Main control valve, constant-variable hydraulic system and loader | |
| CN107724454B (en) | Loading machine determines variable delivery hydraulic system | |
| CN214423459U (en) | Constant-variable flow converging hydraulic system for loader | |
| CN210034023U (en) | Hydraulic control system of quick-change device | |
| CN106812752B (en) | Multiple directional control valve | |
| CN112109801B (en) | Steering hydraulic system and loader | |
| CN113494111B (en) | Main control valve, fixed variable hydraulic system and loader | |
| CN110985458B (en) | Multistage differential pressure control hydraulic system | |
| CN106762903B (en) | Multiple directional control valve | |
| CN212924200U (en) | Novel crane hydraulic valve group | |
| CN111720376A (en) | Flow dividing valve, hydraulic system thereof and engineering machinery | |
| CN111994807A (en) | Novel crane hydraulic valve group | |
| CN114857121B (en) | Fixed-variable multi-way valve and hydraulic system thereof | |
| CN220037116U (en) | High-low pressure double-pump converging multi-way valve | |
| CN114183426B (en) | Regenerative hydraulic valve with pressure selection function | |
| CN218148627U (en) | Semi-variable confluence hydraulic system of loader | |
| CN217974568U (en) | Constant-variable flow-converging control hydraulic system of loader | |
| CN215444559U (en) | Energy-saving loader hydraulic system | |
| CN114909351B (en) | Quantitative closed-center hydraulic system and working method and control method thereof |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |