CN212337754U - Flow dividing valve, hydraulic system thereof and engineering machinery - Google Patents
Flow dividing valve, hydraulic system thereof and engineering machinery Download PDFInfo
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- CN212337754U CN212337754U CN202021226482.XU CN202021226482U CN212337754U CN 212337754 U CN212337754 U CN 212337754U CN 202021226482 U CN202021226482 U CN 202021226482U CN 212337754 U CN212337754 U CN 212337754U
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Abstract
The utility model discloses a flow divider valve and hydraulic system, engineering machine tool thereof, the flow divider valve includes choke valve, first liquid accuse valve, second liquid accuse valve, check valve, sequence valve, third liquid accuse valve, shuttle valve, the oil inlet of flow divider valve communicates with the confluence mouth through choke valve, check valve in proper order, the pressure before the choke valve, the back pressure of choke valve communicate each one end control chamber of second liquid accuse valve respectively; the outlet end of the throttle valve is respectively connected with the oil return port T2 through a first hydraulic control valve and a third hydraulic control valve which are positioned at a working position, and is used for unloading through the first hydraulic control valve and the third hydraulic control valve; the first hydraulic control valve control cavity is communicated with the oil return port T3 through a second hydraulic control valve in a first working position; control port c1 and control port c2 are each connected to an inlet of the shuttle valve; the working port of the shuttle valve is communicated with the control cavity of the first hydraulic control valve through a second hydraulic control valve at a second working position; the confluence port P2 is connected to the control end of the third pilot controlled valve through a sequence valve. The flow of the confluence oil inlet and the unloading oil inlet or the pressure of the confluence opening is realized.
Description
Technical Field
The utility model belongs to the technical field of engineering machine tool, concretely relates to flow divider valve and hydraulic system, engineering machine tool thereof.
Background
At present, a power source part of a hydraulic system adopts an internal combustion engine, if a fixed displacement pump is adopted as a power element, the flow of the system changes along with the change of the rotating speed of the internal combustion engine, which has great influence on the performance of the hydraulic system, and particularly when the rotating speed of the internal combustion engine is low, the efficiency of the hydraulic system is obviously reduced. If the displacement of the fixed displacement pump is increased to ensure that the system flow is sufficient when the internal combustion engine rotates at a low speed, the fixed displacement pump can provide a large amount of redundant flow or throttle or overflow when the internal combustion engine rotates at a high speed, which causes energy waste, and meanwhile, when the pressure of the system is high, the required torque of the fixed displacement pump is increased to influence the output of a power source. Generally, a hydraulic system has more than one actuator, the demand flow of the actuators is different, and the design is based on the actuator with the maximum flow, so that the flow of the actuator with low demand flow is wasted, and the flow exceeding the demand flow is possibly harmful. In order to solve the contradiction, the technical scheme adopted in the market at present adopts a variable pump to provide corresponding flow according to the requirement of an actuating element, but the variable pump has higher cost and complex system.
SUMMERY OF THE UTILITY MODEL
The purpose is as follows: in order to overcome the deficiencies in the prior art, the utility model provides a flow dividing valve and hydraulic system, engineering machine tool thereof. According to the change of the pump flow of the hydraulic system, the flow converging to the system is automatically adjusted, the flow of different execution elements of the system is ensured, the energy waste is avoided, the harm caused by overlarge flow is eliminated, and meanwhile, the flow of the system is adjusted according to the system pressure, so that the overlarge torque required by the first pump and the second pump is avoided, and the influence on the output of a power source is avoided.
The technical scheme is as follows: in order to solve the technical problem, the utility model discloses a technical scheme does:
in a first aspect, a flow dividing valve is provided, which comprises a throttle valve, a first hydraulic control valve, a second hydraulic control valve, a one-way valve, a sequence valve, a third hydraulic control valve and a shuttle valve, wherein the flow dividing valve is provided with a control port c1, a control port c2, a flow merging port P2, an oil inlet P3, an oil return port T2 and an oil return port T3;
an oil inlet P3 of the flow divider is communicated with a flow merging port P2 through a throttle valve and a one-way valve in sequence, the front pressure of the throttle valve is communicated with a control cavity at one end of a second hydraulic control valve, the rear pressure of the throttle valve is communicated with a control cavity at the other end of the second hydraulic control valve and is used for controlling the position of a valve core of the second hydraulic control valve;
the outlet end of the throttle valve is respectively connected with an oil return port T2 through a first hydraulic control valve in one working position and a third hydraulic control valve in one working position, and is used for unloading through the first hydraulic control valve and the third hydraulic control valve; the first hydraulic control valve control cavity is communicated with the oil return port T3 through a second hydraulic control valve in a first working position;
one of the control port c1 and the control port c2 is connected to one inlet of the shuttle valve, and the other of the control port c1 and the control port c2 is connected to the other inlet of the shuttle valve; the working port of the shuttle valve is communicated with the control cavity of the first hydraulic control valve through a second hydraulic control valve at a second working position and is used for controlling the position of the valve core of the first hydraulic control valve;
one end of the sequence valve is connected with the confluence port P2, and the other end of the sequence valve is connected with the control end of the third hydraulic control valve for controlling the position of the valve core of the third hydraulic control valve.
In some embodiments, the control port c1 of the flow divider valve is connected to the lower inlet of the shuttle valve, the control port c2 is connected to the upper inlet of the shuttle valve, and the outlet end of the throttle valve is connected with the oil return port T2 through the first hydraulic control valve at the right position and the third hydraulic control valve at the right position respectively;
when the flow of the oil inlet P3 does not exceed a set value, the first hydraulic control valve control cavity is communicated with the oil return port T3 through the second hydraulic control valve which is at the upper position, the first hydraulic control valve is at the right position under the force of the return spring, the flow of the oil inlet P3 cannot be unloaded through the first hydraulic control valve in the flow dividing valve, and the flow of the oil inlet P3 flows to the confluence port P2 to be converged;
when the flow of the oil inlet P3 exceeds a set value, a working port of the shuttle valve is communicated with a control port of a first hydraulic control valve through a second hydraulic control valve at a lower position, the first hydraulic control valve moves left, and the flow of the oil inlet P3 is unloaded through the first hydraulic control valve in the flow dividing valve;
when the pressure of the confluence port P2 exceeds a preset value, the sequence valve is opened to push the third hydraulic control valve to be reversed to the left position, the flow of the confluence port P2 is unloaded back to the hydraulic oil tank through the third hydraulic control valve, and the pressure of the confluence port P2 is unloaded.
In a second aspect, a hydraulic system is provided, which comprises a hydraulic oil tank, a first pump, a second pump, a pilot valve, a multi-way valve, a first actuating element, a second actuating element and the flow dividing valve; the first pump and the second pump are both fixed displacement pumps;
the first pump comprises a front pump and a rear pump; the oil inlets of the front pump, the rear pump and the second pump are all connected with a hydraulic oil tank, the oil outlet of the front pump is connected with an oil inlet P1 of the multi-way valve and a confluence port P2 of the diverter valve, the oil outlet of the second pump is connected with an oil inlet P3 of the diverter valve, and the oil outlet of the rear pump is connected with an oil inlet P4 of the pilot valve; the control port a1 of the pilot valve is connected with the control port b1 of the multi-way valve and the control port c1 of the shunt valve, the control port a2 of the pilot valve is connected with the control port b2 of the multi-way valve and the control port c2 of the shunt valve, the control port a3 of the pilot valve is connected with the control port b3 of the multi-way valve, and the control port a4 of the pilot valve is connected with the control port b4 of the multi-way;
a working oil port A1 of the multi-way valve is connected with an oil port of a rodless cavity of the first actuating element, a working oil port B1 of the multi-way valve is connected with an oil port of a rod cavity of the first actuating element, a working oil port A2 of the multi-way valve is connected with a rodless cavity of the second actuating element, and a working oil port B2 of the multi-way valve is connected with an oil port of a rod cavity of the second actuating element;
the oil return port T1 of the multi-way valve and the oil return ports T2 and T3 of the flow dividing valve are connected with a hydraulic oil tank.
In some embodiments, the first actuator is a hydraulic ram.
In some embodiments, the second actuator is a hydraulic ram.
In some embodiments, the multiplex valve is a pilot controlled multiplex valve.
In some embodiments, an overflow valve is further arranged at the oil outlet of the rear pump, and the overflow valve flows back to the hydraulic oil tank through the overflow port.
The third aspect of the present invention also provides an engineering machine, including the above hydraulic system.
Has the advantages that: the utility model provides a flow divider and hydraulic system, engineering machine tool thereof increases a pump two, the flow divider is according to two flow changes of pump, and control the executive component action, the flow of automatic adjustment confluence system, thereby guarantee that an executive component is the large-traffic demand of double pump confluence all the time, it is stable to guarantee that executive component two-phase flows, pump two flow is one oil supply when big, two off-loads of pump, double pump confluence when pump two flow is not enough, energy waste has been reduced, the harm that large-traffic brought has been avoided. When the system pressure exceeds a certain value, the two-way pump is unloaded through the throttling valve, so that the torque required by the first pump and the second pump is controlled within a certain range, and the output of a power source is not influenced.
Drawings
FIG. 1 is a schematic diagram of a diverter valve according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a hydraulic system according to an embodiment of the present invention;
FIG. 3 is a schematic diagram of a first pump in an embodiment;
in the figure: the hydraulic control system comprises a hydraulic oil tank 1, a first pump 2, a second pump 3, a pilot valve 4, a multi-way valve 5, a flow dividing valve 6, a first actuating element 7 and a second actuating element 8; a front pump 21, a rear pump 22, and an overflow valve 23; a throttle valve 61, a first pilot operated valve 62, a second pilot operated valve 63, a check valve 64, a sequence valve 65, a third pilot operated valve 66, a shuttle valve 67.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.
Unless specifically stated otherwise, the relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present invention. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.
Example 1
As shown in fig. 1, a flow dividing valve includes a throttle valve 61, a first pilot-controlled valve 62, a second pilot-controlled valve 63, a check valve 64, a sequence valve 65, a third pilot-controlled valve 66, and a shuttle valve 67, and the flow dividing valve is provided with a control port c1, a control port c2, a flow merging port P2, an oil inlet P3, an oil return port T2, and an oil return port T3;
an oil inlet P3 of the flow divider 6 is communicated with a confluence port P2 through a throttle valve 61 and a check valve 64 in sequence, the front pressure of the throttle valve 61 is communicated with a control cavity at one end of a second hydraulic control valve 63, the rear pressure of the throttle valve 61 is communicated with a control cavity at the other end of the second hydraulic control valve 63, and the control cavity is used for controlling the valve core position of the second hydraulic control valve 63;
the outlet end of the throttle valve 61 is connected with an oil return port T2 through a first hydraulic control valve 62 in one working position and a third hydraulic control valve 66 in one working position respectively, and is used for unloading through the first hydraulic control valve 62 and the third hydraulic control valve 66; the control cavity of the first hydraulic control valve 62 is communicated with the oil return port T3 through the second hydraulic control valve 63 in the first working position;
one of the control ports c1 and c2 is connected to one inlet of the shuttle valve 67, and the other of the control ports c1 and c2 is connected to the other inlet of the shuttle valve 67; the working port of the shuttle valve 67 is communicated with the control cavity of the first hydraulic control valve 62 through the second hydraulic control valve 63 at the second working position and is used for controlling the valve core position of the first hydraulic control valve 62;
the sequence valve 65 has one end connected to the merging port P2 and the other end connected to the pilot port of the third pilot-controlled valve 66 for controlling the spool position of the third pilot-controlled valve 66.
In some embodiments, as shown in fig. 1, the pilot port c1 of the flow divider valve 6 is connected to the lower inlet of the shuttle valve 67, the pilot port c2 is connected to the upper inlet of the shuttle valve 67, and the outlet of the throttle valve 61 is connected to the return port T2 through the first pilot-controlled valve 62 in the right position and the third pilot-controlled valve 66 in the right position, respectively;
when the flow of the oil inlet P3 does not exceed a set value, the control cavity of the first hydraulic control valve 62 is communicated with the oil return port T3 through the second hydraulic control valve 63 which is at the upper position, the first hydraulic control valve 62 is at the right position under the force of the return spring, the flow of the oil inlet P3 cannot be unloaded through the first hydraulic control valve 62 in the flow dividing valve 6, and the flow of the oil inlet P3 flows to the confluence port P2 to be converged;
when the flow of the oil inlet P3 exceeds a set value, the working port of the shuttle valve 67 is communicated with the control port of the first hydraulic control valve 62 through the second hydraulic control valve 63 at the lower position, the first hydraulic control valve 62 moves to the left, and the flow of the oil inlet P3 is unloaded through the first hydraulic control valve 62 in the flow dividing valve 6;
when the pressure of the confluence port P2 exceeds a preset value, the sequence valve 65 is opened to push the third hydraulic control valve 66 to be switched to the left position, the flow of the confluence port P2 is unloaded back to the hydraulic oil tank 1 through the third hydraulic control valve 66, and the pressure of the confluence port P2 is unloaded.
Example 2
As shown in fig. 2, a hydraulic system includes a hydraulic oil tank 1, a first pump 2, a second pump 3, a pilot valve 4, a multi-way valve 5, a first actuator 7, a second actuator 8, and the above-mentioned flow dividing valve 6; the first pump 2 and the second pump 3 are fixed displacement pumps;
as shown in fig. 3, the first pump 2 comprises a front pump 21, a rear pump 22 and an overflow valve 23; the oil inlets of the front pump 21, the rear pump 22 and the second pump 3 are all connected with the hydraulic oil tank 1, the oil outlet of the front pump 21 is connected with the oil inlet P1 of the multi-way valve 5 and the confluence port P2 of the diverter valve 6, the oil outlet of the second pump 3 is connected with the oil inlet P3 of the diverter valve 6, and the oil outlet of the rear pump 22 is connected with the oil inlet P4 of the pilot valve 4; the control port a1 of the pilot valve 4 is connected with the control port b1 of the multi-way valve 5 and the control port c1 of the flow dividing valve 6, the control port a2 of the pilot valve 4 is connected with the control port b2 of the multi-way valve 5 and the control port c2 of the flow dividing valve 6, the control port a3 of the pilot valve 4 is connected with the control port b3 of the multi-way valve 5, and the control port a4 of the pilot valve 4 is connected with the control port b4 of the multi-way valve 5;
a working oil port A1 of the multi-way valve 5 is connected with an oil port of a rodless cavity of the first actuating element 7, a working oil port B1 of the multi-way valve 5 is connected with an oil port of a rod cavity of the first actuating element 7, a working oil port A2 of the multi-way valve 5 is connected with a rodless cavity of the second actuating element 8, and a working oil port B2 of the multi-way valve 5 is connected with an oil port of a rod cavity of the second actuating element 8;
the return port T1 of the multiplex valve 5 and the return ports T2 and T3 of the flow dividing valve 6 are connected to the hydraulic oil tank 1.
In some embodiments, the first and second actuators include, but are not limited to, hydraulic rams.
In some embodiments, the multiplex valve 5 is a pilot controlled multiplex valve.
In some embodiments, as shown in fig. 3, a relief valve 23 is further provided at the oil outlet of the rear pump 22, and flows back to the hydraulic oil tank 1 through the relief port.
The flow of the second pump 3 passes through the flow divider 6, and the flow of the flow divider 6 merged into the system is controlled according to different flow of the second pump 3 and different operation requirements.
On the basis of the structure, the oil inlets of the first pump 2 and the second pump 3 can be respectively connected with the hydraulic oil tank 1, or the oil inlets of the two pumps can be connected with the hydraulic oil tank 1 after being connected. The first pump 2 and the second pump 3 can be directly connected with the hydraulic oil tank 1, and can also be connected with the hydraulic oil tank 1 through the filter element to filter impurities in hydraulic oil.
The utility model discloses the working process is as follows: when the system does not operate, the control ports of the pilot valve 4, the multi-way valve 5 and the flow divider 6 have no pressure, the valve core of the multi-way valve 5 is positioned at the middle position, the flow of the pump I2 flows in through the oil port P1 of the multi-way valve 5, and directly returns to the oil tank from the oil return port T1 of the multi-way valve 5; the flow of the second pump 3 flows from the flow divider valve 6 port P3 through the internal check valve 64, then flows through the multiplex valve 5 port P1, and also returns to the tank directly from the multiplex valve 5 return port T1.
When the system operates the second actuator 8 to extend, the pilot valve 4 communicates with the oil inlet P4 and the control port a2, the oil at the outlet of the rear pump 22 in the first pump 2 enters the control port b2 of the multi-way valve 5 through the pilot valve 4, the control valve core of the second actuator 8 in the multi-way valve 5 moves to the left, the surplus oil at the outlet of the rear pump 22 overflows from the overflow valve 23 back to the hydraulic oil tank 1, the oil at the outlet of the second pump 3 passes through the flow dividing valve 6, and enters the rodless cavity of the second actuator 8 through the multi-way valve 5 after being converged with the front pump 21 of the first pump 2, and the. When the second actuator 8 is operated to extend, the pressure of the control port a2 of the pilot valve 4 is simultaneously transmitted to the control port c2 of the flow divider 6, the upper position of the shuttle valve 67 in the flow divider 6 is opened, the lower position of the shuttle valve is closed, the pressure of the control port c2 enters the oil inlet of the second hydraulic valve 63, the oil at the outlet of the second pump 3 generates pressure loss when passing through the throttle valve 61 in the flow divider 6, the pressure loss is proportional to the flow of the second pump 3, the pressure in front of the throttle valve 61 is communicated with the control cavity at the lower end of the second hydraulic valve 63, and the pressure in the rear of the throttle valve 61 is communicated with. When the flow of the second pump 3 is small, the pressure difference between the two ends of the throttle valve 61 is not enough to overcome the return spring force of the second hydraulic control valve 63, the second hydraulic control valve 63 works in an upper position, the control cavity of the first hydraulic control valve 62 is communicated with the hydraulic oil tank 1 through the second hydraulic control valve 63, the first hydraulic control valve 62 is in a right position under the return spring force, the second pump 3 cannot be unloaded through the first hydraulic control valve 62 in the flow dividing valve 6, double-pump confluence is realized, and a large flow is supplied to the second execution element 8. When the flow of the second pump 3 exceeds a certain value, the pressure at the two ends of the throttle valve 61 is enough to overcome the return spring force of the second hydraulic control valve 63, the second hydraulic control valve 63 works at the lower position, the pressure of the control port c2 of the flow dividing valve is communicated with the control port of the first hydraulic control valve 62 through the second hydraulic control valve 63, the first hydraulic control valve 62 moves leftwards, and the second pump 3 is unloaded through the first hydraulic control valve 62 in the flow dividing valve 6, so that the second pump 3 is unloaded. When the system pressure is higher than a certain value along with the load change of the second execution element 8, the sequence valve 65 in the flow dividing valve 6 is opened to push the third hydraulic control valve 66 to be reversed to the left position, and the second pump 3 is unloaded back to the hydraulic oil tank 1 through the third hydraulic control valve 66, so that the required torques of the second pump 3, the first control pump 2 and the second control pump 3 are controlled below a certain value when the system pressure is high.
When the system operates the second actuator 8 to retract, the pilot valve 4 communicates with the oil inlet P4 and the control port a1, oil at the outlet of the rear pump 22 in the first pump 2 enters the control port b1 of the multi-way valve 5 through the pilot valve 4, the control valve core of the second actuator 8 in the multi-way valve 5 moves to the right, redundant oil at the outlet of the rear pump 22 overflows from the overflow valve 23 to the hydraulic oil tank 1, oil at the outlet of the second pump 3 passes through the flow dividing valve 6, is converged with the first pump 2 and then enters the rod cavity of the second actuator 8 through the multi-way valve 5, and the second actuator 8 retracts. When the second actuator 8 is operated to retract, the pressure of the control port a1 of the pilot valve 4 is transmitted to the control port c1 of the flow dividing valve 6, the lower position of the shuttle valve 67 in the flow dividing valve 6 is opened, the upper position of the shuttle valve is closed, the pressure of the control port c1 enters the oil inlet of the second hydraulic valve 63, pressure loss is generated when oil at the outlet of the second pump 3 flows through the throttle valve 61 in the flow dividing valve 6, the pressure loss is in direct proportion to the flow of the second pump 3, the pressure in front of the throttle valve 61 is communicated with the control cavity at the lower end of the second hydraulic valve 63, and the pressure in the rear of. When the flow of the second pump 3 is small, the pressure difference between the two ends of the throttle valve 61 is not enough to overcome the return spring force of the second hydraulic control valve 63, the second hydraulic control valve 63 works in an upper position, the control cavity of the first hydraulic control valve 62 is communicated with the hydraulic oil tank 1 through the second hydraulic control valve 63, the first hydraulic control valve 62 is in a right position under the return spring force, the second pump 3 cannot be unloaded through the first hydraulic control valve 62 in the flow dividing valve 6, double-pump confluence is realized, and a large flow is supplied to the second execution element 8. When the flow of the second pump 3 exceeds a certain value, the pressure at the two ends of the throttle valve 61 is enough to overcome the return spring force of the second hydraulic control valve 63, the second hydraulic control valve 63 works at the lower position, the pressure of the control port c1 of the flow dividing valve is communicated with the control port of the first hydraulic control valve 62 through the second hydraulic control valve 63, the first hydraulic control valve 62 moves leftwards, and the second pump 3 is unloaded through the first hydraulic control valve 62 in the flow dividing valve 6, so that the second pump 3 is unloaded. When the system pressure is higher than a certain value along with the load change of the second execution element 8, the sequence valve 65 in the flow dividing valve 6 is opened to push the third hydraulic control valve 66 to be reversed to the left position, and the second pump 3 is unloaded back to the hydraulic oil tank 1 through the third hydraulic control valve 66, so that the required torques of the second pump 3, the first control pump 2 and the second control pump 3 are controlled below a certain value when the system pressure is high.
When the system operates the first actuator 7 to extend, the pilot valve 4 communicates with the oil inlet P4 and the control port a4, oil at the outlet of the rear pump 22 in the first pump 2 enters the control port b4 of the multi-way valve 5 through the pilot valve 4, the control valve core of the first actuator 7 in the multi-way valve 5 moves to the left, redundant oil at the outlet of the rear pump 22 overflows from the overflow valve 23 back to the hydraulic oil tank 1, oil at the outlet of the second pump 3 passes through the flow dividing valve 6, is converged with the first pump 2 and then enters the rodless cavity of the first actuator 7 through the multi-way valve 5, and the first actuator 7 extends. When the first actuator 7 is operated to extend, the control ports a1 and a2 of the pilot valve 4 are not pressurized, so the control ports c1 and c2 of the flow dividing valve 6 are also not pressurized, no matter how much the flow of the second pump 3 is, the position of the second hydraulic control valve 63 in the flow dividing valve 6 is caused, the first hydraulic control valve 62 is always in the right position, the second pump 3 cannot be unloaded through the first hydraulic control valve 62 in the flow dividing valve 6, double-pump confluence is realized, and large flow is supplied to the first actuator 7. When the system pressure is higher than a certain value along with the load change of the first actuator 7, the sequence valve 65 in the flow dividing valve 6 is opened to push the third hydraulic control valve 66 to be reversed to the left position, and the second pump 3 is unloaded back to the hydraulic oil tank 1 through the third hydraulic control valve 66, so that the required torques of the second pump 3, the first control pump 2 and the second control pump 3 are controlled below a certain value when the system pressure is high.
When the system operates the first actuator 7 to retract, the pilot valve 4 communicates with the oil inlet P4 and the control port a3, oil at the outlet of the rear pump 22 in the first pump 2 enters the control port b3 of the multi-way valve 5 through the pilot valve 4, the control valve core of the first actuator 7 in the multi-way valve 5 moves to the right, redundant oil at the outlet of the rear pump 22 overflows from the overflow valve 23 back to the hydraulic oil tank 1, oil at the outlet of the second pump 3 passes through the flow dividing valve 6, is converged with the first pump 2 and then enters the rod cavity of the first actuator 7 through the multi-way valve 5, and the first actuator 7. When the first actuator 7 is operated to retract, the control ports a1 and a2 of the pilot valve 4 are not pressurized, so the control ports c1 and c2 of the flow dividing valve 6 are also not pressurized, no matter what the flow of the second pump 3 is, the position of the second hydraulic control valve 63 in the flow dividing valve 6 is caused, the first hydraulic control valve 62 is always in the right position, the second pump 3 cannot be unloaded through the first hydraulic control valve 62 in the flow dividing valve 6, double-pump confluence is realized, and a large flow is supplied to the first actuator 7. When the system pressure is higher than a certain value along with the load change of the first actuator 7, the sequence valve 65 in the flow dividing valve 6 is opened to push the third hydraulic control valve 66 to be reversed to the left position, and the second pump 3 is unloaded back to the hydraulic oil tank 1 through the third hydraulic control valve 66, so that the required torques of the second pump 3, the first control pump 2 and the second control pump 3 are controlled below a certain value when the system pressure is high.
In the working process of the system, when the system pressure is higher than the set value of the safety valve of the multi-way valve 5, the safety valve of the multi-way valve 5 is opened, and the flow of the pump I2 is unloaded through the safety valve of the multi-way valve 5.
Example 3
In another aspect, a working machine is also provided, which comprises the hydraulic system.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the scope of the present invention.
The above description is only a preferred embodiment of the present invention, and it should be noted that: for those skilled in the art, without departing from the principle of the present invention, several improvements and modifications can be made, and these improvements and modifications should also be considered as the protection scope of the present invention.
Claims (8)
1. A flow dividing valve is characterized by comprising a throttling valve, a first hydraulic control valve, a second hydraulic control valve, a one-way valve, a sequence valve, a third hydraulic control valve and a shuttle valve, wherein the flow dividing valve is provided with a control port c1, a control port c2, a flow merging port P2, an oil inlet P3, an oil return port T2 and an oil return port T3;
an oil inlet P3 of the flow divider is communicated with a flow merging port P2 through a throttle valve and a one-way valve in sequence, the front pressure of the throttle valve is communicated with a control cavity at one end of a second hydraulic control valve, the rear pressure of the throttle valve is communicated with a control cavity at the other end of the second hydraulic control valve and is used for controlling the position of a valve core of the second hydraulic control valve;
the outlet end of the throttle valve is respectively connected with an oil return port T2 through a first hydraulic control valve in one working position and a third hydraulic control valve in one working position, and is used for unloading through the first hydraulic control valve and the third hydraulic control valve; the first hydraulic control valve control cavity is communicated with the oil return port T3 through a second hydraulic control valve in a first working position;
one of the control port c1 and the control port c2 is connected to one inlet of the shuttle valve, and the other of the control port c1 and the control port c2 is connected to the other inlet of the shuttle valve; the working port of the shuttle valve is communicated with the control cavity of the first hydraulic control valve through a second hydraulic control valve at a second working position and is used for controlling the position of the valve core of the first hydraulic control valve;
one end of the sequence valve is connected with the confluence port P2, and the other end of the sequence valve is connected with the control end of the third hydraulic control valve for controlling the position of the valve core of the third hydraulic control valve.
2. The flow divider valve of claim 1 wherein control port c1 is connected to the lower inlet port of the shuttle valve, control port c2 is connected to the upper inlet port of the shuttle valve, and the throttle valve outlet port is connected to the return port T2 via a first pilot operated valve at right position and a third pilot operated valve at right position, respectively;
when the flow of the oil inlet P3 does not exceed a set value, the first hydraulic control valve control cavity is communicated with the oil return port T3 through the second hydraulic control valve which is at the upper position, the first hydraulic control valve is at the right position under the force of the return spring, the flow of the oil inlet P3 cannot be unloaded through the first hydraulic control valve in the flow dividing valve, and the flow of the oil inlet P3 flows to the confluence port P2 to be converged;
when the flow of the oil inlet P3 exceeds a set value, a working port of the shuttle valve is communicated with a control port of a first hydraulic control valve through a second hydraulic control valve at a lower position, the first hydraulic control valve moves left, and the flow of the oil inlet P3 is unloaded through the first hydraulic control valve in the flow dividing valve;
when the pressure of the confluence port P2 exceeds a preset value, the sequence valve is opened to push the third hydraulic control valve to be reversed to the left position, the flow of the confluence port P2 is unloaded back to the hydraulic oil tank through the third hydraulic control valve, and the pressure of the confluence port P2 is unloaded.
3. A hydraulic system comprising a hydraulic tank, a first pump, a second pump, a pilot valve, a multi-way valve, a first actuator, a second actuator and a flow divider valve according to claim 1 or 2; the first pump and the second pump are both fixed displacement pumps;
the first pump comprises a front pump and a rear pump; the oil inlets of the front pump, the rear pump and the second pump are all connected with a hydraulic oil tank, the oil outlet of the front pump is connected with an oil inlet P1 of the multi-way valve and a confluence port P2 of the diverter valve, the oil outlet of the second pump is connected with an oil inlet P3 of the diverter valve, and the oil outlet of the rear pump is connected with an oil inlet P4 of the pilot valve; the control port a1 of the pilot valve is connected with the control port b1 of the multi-way valve and the control port c1 of the shunt valve, the control port a2 of the pilot valve is connected with the control port b2 of the multi-way valve and the control port c2 of the shunt valve, the control port a3 of the pilot valve is connected with the control port b3 of the multi-way valve, and the control port a4 of the pilot valve is connected with the control port b4 of the multi-way;
a working oil port A1 of the multi-way valve is connected with an oil port of a rodless cavity of the first actuating element, a working oil port B1 of the multi-way valve is connected with an oil port of a rod cavity of the first actuating element, a working oil port A2 of the multi-way valve is connected with a rodless cavity of the second actuating element, and a working oil port B2 of the multi-way valve is connected with an oil port of a rod cavity of the second actuating element;
the oil return port T1 of the multi-way valve and the oil return ports T2 and T3 of the flow dividing valve are connected with a hydraulic oil tank.
4. The hydraulic system of claim 3, wherein the first actuator is a hydraulic ram.
5. The hydraulic system of claim 3, wherein the second actuator is a hydraulic ram.
6. The hydraulic system of claim 3, wherein the multiplex valve is a pilot controlled multiplex valve.
7. The hydraulic system as claimed in claim 3, characterized in that an overflow valve is further provided at the oil outlet of the rear pump, and flows back to the hydraulic oil tank through an overflow port.
8. A working machine, characterized in that it comprises a hydraulic system according to any one of claims 3-7.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202021226482.XU CN212337754U (en) | 2020-06-29 | 2020-06-29 | Flow dividing valve, hydraulic system thereof and engineering machinery |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021226482.XU CN212337754U (en) | 2020-06-29 | 2020-06-29 | Flow dividing valve, hydraulic system thereof and engineering machinery |
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| CN212337754U true CN212337754U (en) | 2021-01-12 |
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