CN211144944U

CN211144944U - Hydraulic control system of load-sensitive pump

Info

Publication number: CN211144944U
Application number: CN201922220294.XU
Authority: CN
Inventors: 姜伟; 姜洪; 王震山; 张晓磊; 刘占远; 李贺; 史浙安; 柯稳
Original assignee: Shanghai Shengbang Hydraulic Co ltd; Xuzhou Shengbang Machinery Co Ltd; Zhejiang Sunbun Technology Co Ltd; Sunbun Group Co Ltd
Current assignee: Shanghai Shengbang Hydraulic Co ltd; Xuzhou Shengbang Machinery Co Ltd; Zhejiang Sunbun Technology Co Ltd; Sunbun Group Co Ltd
Priority date: 2019-12-12
Filing date: 2019-12-12
Publication date: 2020-07-31
Anticipated expiration: 2029-12-12

Abstract

A load-sensitive pump hydraulic control system. The problem of current hydraulic control system receive other hydraulic component easily in the course of the work and influence its stability is solved. The control valve comprises a control cavity and a spring cavity, an oil outlet of the check valve is communicated with the control cavity of the control valve through a control oil path, a feedback oil path on the load-sensitive multi-way valve is communicated with the spring cavity of the control valve, the control oil cylinder comprises a piston, a rod cavity and a rodless cavity, pressure oil at the oil outlet of the variable pump is input into the rodless cavity of the control oil cylinder through the safety oil path and the rod cavity of the control oil cylinder and pressure oil in the control oil path through the control valve, and output flow of the variable pump is adjusted through the piston under the mutual action of the pressure oil and the rod cavity of the control oil cylinder. The utility model discloses simple structure still has, convenient assembling, and the action is reliable, advantages such as long service life.

Description

Hydraulic control system of load-sensitive pump

Technical Field

The utility model relates to a hydraulic control system, concretely relates to sensitive pump hydraulic control system of load.

Background

The platform for high-altitude operation features flexible operation, large working span and wide range. The hydraulic lifting platform is arranged on the vehicle, so that fire fighters can ascend to rescue high-rise buildings and high facilities, rescue trapped people, rescue valuable materials and complete other rescue tasks. Due to the particularity of the working application of the elevating platform fire truck, the elevating platform fire truck has very high requirements on the reliability, the stability and the cooperativity of the action of an actuating mechanism.

The existing hydraulic control system of the high-meter-number ascending operation platform basically consists of a variable pump and a load sensitive valve. The load sensitive valve has two forms of pre-valve compensation and post-valve compensation, when two or more loads act simultaneously, the flow provided by the main pump is enough to meet the flow required by the system, and the pre-valve compensation and the post-valve compensation have the same effect; if the flow provided by the main pump cannot meet the flow required by the system, the system adopting the pre-valve compensation can preferentially meet the flow required by a small load, and the residual flow can flow to a larger load; and the case of post-valve compensation is: the opening of the proportional valve reduces the flow supply of each load, and the effect of action coordination is achieved. Namely: when the flow provided by the main pump cannot meet the requirement of the system, the flow distribution compensated before the valve is related to the load, and the flow distribution compensated after the valve is not related to the load and is only related to the opening amount of the main valve. Because the compensation before the valve does not have the capacity of resisting flow saturation, in order to ensure the continuity and stability of each load during the composite action, the hydraulic control system of the ascending operation platform adopts a variable pump and valve post-compensation control system.

In the variable pump post-valve compensation control hydraulic system of the existing ascending operation platform, pressure oil at the outlet of a variable pump in a variable control system directly acts on a control valve, namely the pressure oil at the outlet of the variable pump is used as the pressure of a control oil way and is balanced with the pressure fed back by a load and the pressure set by a spring of the control valve, so that the variable pump is maintained to output a constant flow. The output pressure of the pump is determined by the load, which is higher than the pressure of the load. This higher load pressure is dissipated in the filter, check valve, load sensitive multiplex valve and hydraulic line.

In practical applications, the pressure in the hydraulic line is relatively constant due to the constant spring setting of the control valve, and the pressure loss in the line is only related to the magnitude of the flow rate. In the working process of the hydraulic system, the phenomena of pressure fluctuation and hydraulic impact are inevitably generated, so that the pressure loss of pressure oil flowing through the one-way valve is changed along with the pressure fluctuation; along with the circulation work of a hydraulic system, the amount of dirt contained in the filter is increased, when the pressure oil with the same flow rate passes through the filter with the increased amount of dirt contained, a large pressure loss is necessarily formed on the filter with the increased amount of dirt contained, the pressure loss of a pipeline is usually relatively fixed, and when the pressure loss of the filter or the pressure loss of the one-way valve changes, the pressure loss of the load-sensitive valve is necessarily changed along with the pressure loss of the load-sensitive valve. When the load-sensitive multi-way valve executes a certain action in the working process, the opening area of the valve rod is fixed, and the flow formula shows that: the flow coefficient C, the flow area A and the density rho of the hydraulic oil are all unchanged, so that the factors influencing the change from the load sensitive valve to the action flow are only related to the pressure difference between the front and the rear of the valve port. The pressure difference of a multi-way valve throttling opening of a load-sensitive multi-way valve and variable pump system commonly used at present is determined by the pressure difference of an inlet of the multi-way valve and a feedback oil opening, but the pressure difference from the pressure at the outlet of the pump to the pressure at the feedback oil opening can only be determined according to a pressure difference control unit. Three throttling influences pressure loss from the pressure at the outlet of the pump to the oil inlet of the load sensitive valve, and the throttling opening comprises 1 and a pipeline from the outlet of the pump to the inlet of the multi-way valve; 2. a high pressure filter; 3. a one-way valve. Therefore, the differential pressure of the throttling opening of the multi-way valve has uncertainty, and is more obvious particularly in the field of small flow of high-altitude vehicles. The magnitude of the pump flow and the temperature of the oil liquid can influence the differential pressure of the throttling port of the multi-way valve, so that the movement speed of the actuating mechanism cannot be accurately controlled. As described above, the pressure loss of the filter or the pressure loss of the check valve may cause the pressure loss of the load sensitive valve to change, which may cause unstable flow output to the actuator through the load sensitive multi-way valve, which may cause the shaking of the load operation, and may make the stability of the vehicle operation difficult to be ensured.

SUMMERY OF THE UTILITY MODEL

For solving the problem that current hydraulic control system receives other hydraulic component easily and influences its stability among the background art in the course of the work, the utility model provides a sensitive pump hydraulic control system of load.

The technical scheme of the utility model is that: a hydraulic control system of a load sensitive pump comprises a variable control system and a load sensitive multi-way valve, wherein the variable control system comprises a variable pump, a control valve, a pressure cut-off valve and a control oil cylinder, an oil outlet of the variable pump is connected with the load sensitive multi-way valve through a filter and a one-way valve, the control valve comprises a control cavity and a spring cavity, the oil outlet of the one-way valve is communicated with the control cavity of the control valve through a control oil way, a feedback oil way on the load sensitive multi-way valve is communicated with the spring cavity of the control valve, the spring force in the spring cavity of the control valve, the oil pressure in the feedback oil way and the oil pressure of the control oil way in the control cavity are interacted to adjust a control valve opening, the control oil cylinder comprises a piston, a rod cavity and a rodless cavity, pressure oil at the oil outlet of the variable pump is input to the rodless cavity of the control oil cylinder through a safety oil way and pressure oil in the control oil way is The output flow of the variable displacement pump.

As an improvement of the utility model, the oil inlet and the control oil way of control valve communicate mutually, the oil-out of control valve is linked together with the rodless chamber of control cylinder.

As a further improvement, the control cylinder has a first state in which the pressure oil in the rod chamber is reduced by the control valve opening when the sum of the pressure of the oil pressure in the spring force in the control valve spring chamber and the feedback oil path is greater than the oil pressure of the control oil path in the control chamber, the output flow of the variable pump is increased by the piston, a second state in which the output of the variable pump is stabilized by the variable pump when the sum of the pressure of the oil pressure in the spring force in the control valve spring chamber and the feedback oil path is equal to the oil pressure of the control oil path in the control chamber, and a third state in which the pressure oil in the control oil path is increased by the control valve opening when the sum of the pressure of the oil pressure in the spring force in the control valve spring chamber and the feedback oil path is less than the oil pressure of the control oil path in the control chamber and the output flow of the variable pump is decreased by the.

As a further improvement, the pressure trip valve locate between control valve and the control cylinder, the pressure trip valve have the first position that makes the oil-out of control valve and the no pole chamber of control cylinder be linked together and the second position that the no pole chamber of safety oil circuit and control cylinder is linked together is made in the switching-over when the pressure oil of safety oil circuit surpasss the settlement of pressure trip valve.

As a further improvement, the pressure cut-off valve include pressure control chamber and pressure spring chamber, the safety oil circuit link to each other with the pressure control chamber of pressure cut-off valve, the oil inlet of pressure cut-off valve respectively, the pressure cut-off valve when being in the second position the pressure oil of safety oil circuit link to each other through the oil inlet of pressure cut-off valve, the oil-out of pressure cut-off valve and the rodless chamber of control cylinder.

As a further improvement, the rodless chamber of pressure trip valve and control cylinder between be equipped with first passageway, pressure trip valve and control valve between be equipped with second passageway, third passageway and oil tank be linked together, the pressure trip valve be in when the second position safe oilway be linked together through the rodless chamber of first passageway with control cylinder.

As a further improvement of the utility model, still be equipped with the throttling element, the throttling element locate between first passageway and the third passageway, the throttling element on be equipped with the orifice.

As a further improvement, the sensitive multiple unit valve of load link and an at least work link including control, the control link and the work link splice mutually, the sensitive multiple unit valve of load include main oil inlet and oil return opening, the control link on be equipped with flow divider and off-load valve, the flow divider locate between main oil inlet and the oil return opening, the off-load valve locate between feedback oil circuit and the oil return opening.

As a further improvement, the work antitorque couplet on be equipped with control switching-over valve and guide's proportional solenoid valve, the sensitive multiple unit valve of load include the guide's oil circuit that is linked together with guide's proportional solenoid valve, guide's proportional solenoid valve's oil-out is linked together with the switching-over control chamber of control switching-over valve.

As a further improvement of the utility model, the utility model also comprises an auxiliary pump, the auxiliary pump is communicated with the load-sensitive multi-way valve.

The beneficial effects of the utility model are that, the control chamber of control valve gets oil from the oil-out of check valve to avoid filter, check valve etc. to cause the pressure variation of the sensitive valve of load in system work because pressure loss, thereby make the executor operate unstably, avoid the executor shake, control cylinder has the pole chamber still to get oil from the variable pump oil-out, makes variable pump control reliable, and the security is high. The utility model discloses simple structure still has, convenient assembling, and the action is reliable, advantages such as long service life.

Drawings

Fig. 1 is a hydraulic schematic diagram of an embodiment of the present invention.

Fig. 2 is a hydraulic schematic diagram of the variable control system 10 of fig. 1.

Fig. 3 is a hydraulic schematic diagram of the load sensitive multiplex valve 4 of fig. 1.

Fig. 4 is a schematic structural diagram of an embodiment of the present invention.

In the figure, 1 is a variable pump, 2 is a filter, 3 is a one-way valve, 4 is a load-sensitive multi-way valve, 41 is a flow dividing valve, 42 is an unloading valve, 43 is a pilot proportional solenoid valve, 44 is a pilot oil path, 45 is a control link, 46 is a working link, 47 is a control reversing valve, 5 is a control valve, 51 is a control cavity, 52 is a spring cavity, 6 is a pressure cut-off valve, 61 is a pressure control cavity, 62 is a pressure spring cavity, 7 is a control oil cylinder, 71 is a piston, 72 is a rod cavity, 73 is a rodless cavity, 8 is a control oil path, 9 is a safety oil path, 10 is a variable control system, 11 is an auxiliary pump, 12 is a first channel, 13 is a second channel, 14 is a third channel, 15 is an oil tank, 16 is a throttling element, 17 is a throttling hole, P is a main oil path, T is an oil inlet, L S is an oil return port, and is.

Detailed Description

The embodiments of the present invention will be further explained with reference to the accompanying drawings:

as shown by fig. 1 in combination with fig. 2-4, a hydraulic control system for a load-sensitive pump includes a variable control system 10 and a load-sensitive multi-way valve 4, the variable control system 10 includes a variable pump 1, a control valve 5, a pressure cut-off valve 6 and a control cylinder 7, an oil outlet of the variable pump 1 is connected with the load-sensitive multi-way valve 4 through a filter 2 and a check valve 3, the control valve 5 includes a control chamber 51 and a spring chamber 52, an oil outlet of the check valve is connected with the control chamber of the control valve through a control oil path 8, a feedback oil path L S on the load-sensitive multi-way valve is connected with the spring chamber of the control valve, a spring force in the spring chamber of the control valve, an oil pressure in the feedback oil path and an oil pressure interacting control valve opening of the control oil path in the control chamber, the control cylinder 7 includes a piston 71, a rod chamber 72 and a rodless chamber 73, pressure oil at the oil outlet of the variable pump is input to the rodless chamber 73 of the control oil path 8 through the control valve 5, the rod chamber 73 and the rod chamber 73, thereby, the pressure oil from the control cylinder 71 is prevented from being reliably lost, the pump is a pressure loss caused by a simple and a beneficial effect of a control cylinder, a simple and a control valve, a beneficial effect of a control valve, a control system, a control valve, a control system for a control system.

An oil inlet of the control valve 5 is communicated with a control oil path 8, and an oil outlet of the control valve is communicated with a rodless cavity of the control oil cylinder. Therefore, the pressure oil of the control oil way can reliably enter the rodless cavity of the control oil cylinder, the piston of the control oil cylinder drives the variable pump to act, the output flow is changed, and the rod cavity of the control oil cylinder is directly input through the safety oil way to change the output flow of the variable pump in the actual production process.

The control cylinder 7 has a first state in which the control valve opening reduces the pressure oil in the rodless chamber 73 and the rod chamber 72 receives the pressure oil in the safety oil passage 9 and increases the output flow rate of the variable displacement pump by the piston 71 when the sum of the spring force in the spring chamber 52 of the control valve 5 and the pressure of the oil pressure in the feedback oil passage L S is greater than the oil pressure in the control oil passage 8 in the control chamber 51, a second state in which the variable displacement pump 1 stably outputs when the sum of the spring force in the spring chamber 52 of the control valve 5 and the pressure of the oil pressure in the feedback oil passage L S is equal to the oil pressure in the control oil passage 8 in the control chamber 51, and a third state in which the opening of the control valve 5 increases the rodless chamber 73 and the pressure oil in the control oil passage 8 increases and decreases the output flow rate of the variable displacement pump 1 by the piston 71 when the sum of the spring force in the control oil passage 52 of the control oil passage 51 and the pressure in the control oil passage 8 is less than the oil pressure in the control oil passage 51, and more specifically, when the sum of the pressure of the control valve opening of the control oil passage 54 and the control oil pressure in the control oil passage 54 is greater than the right end of the control oil passage, and the control oil passage L, when the control valve, the pressure of the control oil passage L, the control valve is greater than the pressure of the control oil pressure of the control valve, the control oil passage, the control valve, and the pressure of the control oil passage L, and the control oil pressure of the control oil passage.

The pressure cut-off valve 6 is arranged between the control valve and the control oil cylinder, and the pressure cut-off valve is provided with a first position enabling an oil outlet of the control valve 5 to be communicated with a rodless cavity 73 of the control oil cylinder 7 and a second position enabling a safety oil path 9 to be communicated with the rodless cavity 73 of the control oil cylinder 7 through reversing when pressure oil of the safety oil path exceeds the setting of the pressure cut-off valve. Specifically, pressure trip valve 6 include pressure control chamber 61 and pressure spring chamber 62, the safe oil circuit link to each other with the pressure control chamber of pressure trip valve, the oil inlet of pressure trip valve respectively, the pressure trip valve be in when the second position pressure oil of safe oil circuit link to each other with the rodless chamber of control cylinder through the oil inlet of pressure trip valve, the oil-out of pressure trip valve. The utility model discloses well control valve control oil selects the pressure oil of check valve oil outlet department, and the pressure oil of pressure trip valve intercepting variable pump oil outlet department, make pressure differential control unit (control valve) and maximum pressure control unit (pressure trip valve) just keep apart and realize its new principle like this, thereby make the control chamber of control valve get oil from the oil-out of check valve, thereby avoid the filter, check valve etc. cause the pressure variation of the sensitive valve of load because pressure loss in system work, thereby make the executor operate unstably, avoid the executor shake, the pole chamber of control cylinder still gets oil from the variable pump oil-out, make variable pump control reliable, the security is high. The left end and the safe oil circuit of pressure trip valve are linked together, and the right-hand member is the spring of high pressure, and when the output pressure of variable pump was greater than the spring force of pressure trip valve right-hand member, the left position work of pressure trip valve, and pressure oil reachs the no pole chamber of control cylinder through the pressure trip valve this moment, thereby the swash plate pivot angle of push pump diminishes and reduces the flow output of variable pump, reduces the output pressure of pump, prevents that the pump from lasting overload operation for system security, stability are higher.

A first channel 12 is arranged between the pressure cut-off valve and a rodless cavity of the control oil cylinder, a second channel 13 and a third channel 14 are arranged between the pressure cut-off valve and the control valve, the third channel is communicated with an oil tank 15, and the safety oil path is communicated with the rodless cavity of the control oil cylinder through the first channel when the pressure cut-off valve is at the second position. Specifically speaking, the utility model discloses still be equipped with throttling element 16, throttling element 16 locate between first passageway and the third passageway, throttling element on be equipped with orifice 17. Particularly, the second channel is also connected with the third channel and the oil tank through a throttling hole in the throttling piece, and the structure enables the throttling hole to play a role in pressure relief and variable pump stability control for the system.

The load-sensitive multi-way valve 4 comprises a control link 45 and at least one working link 46, the control link is spliced with the working link, the load-sensitive multi-way valve comprises a main oil inlet P and an oil return port T, the control link is provided with a diverter valve 41 and an unloading valve 42, the diverter valve 41 is arranged between the main oil inlet and the oil return port, and the unloading valve is arranged between a feedback oil path and the oil return port. The structure enables a plurality of work couples to be spliced as required, and the product has wider expansibility and wider adaptation range. The function of the flow divider is that when the output flow of the pump is larger than the flow required by executing action, the redundant flow returns from the flow divider under the load pressure, so that high-pressure overflow oil return is avoided, and the energy consumption and the heat productivity are reduced. The unloading valve is an electromagnetic unloading valve, and when the electromagnetic unloading valve does not need to act in each execution action, the electromagnetic unloading valve can enable the oil way to be in a low-pressure unloading state, so that unnecessary energy consumption loss is reduced.

The working connection 46 is provided with a control reversing valve 47 and a pilot proportional solenoid valve 43, the load sensitive multi-way valve comprises a pilot oil path 44 communicated with the pilot proportional solenoid valve 43, and an oil outlet of the pilot proportional solenoid valve is communicated with a reversing control cavity of the control reversing valve 47. The pilot proportional solenoid valve outputs different flow rates by giving different current values so as to control the reversing displacement of the valve rod of the load sensitive multi-way valve.

The utility model discloses still include auxiliary pump 11, auxiliary pump and the sensitive multiple unit valve of load be linked together. The auxiliary pump, which is generally a fixed displacement pump, can also supply pressurized oil, resulting in higher safety of the product.

In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for convenience of description and simplification of the description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art. In addition, in the description of the present invention, "a plurality" means two or more unless otherwise specified.

The skilled person should understand that: although the present invention has been described in accordance with the above embodiments, the inventive concept is not limited to this embodiment, and any modification of the inventive concept will be included in the scope of the patent claims.

Claims

1. A load-sensitive pump hydraulic control system comprises a variable control system (10) and a load-sensitive multi-way valve (4), and is characterized in that the variable control system (10) comprises a variable pump (1), a control valve (5), a pressure cut-off valve (6) and a control oil cylinder (7), an oil outlet of the variable pump (1) is connected with the load-sensitive multi-way valve (4) through a filter (2) and a one-way valve (3), the control valve (5) comprises a control cavity (51) and a spring cavity (52), an oil outlet of the one-way valve is communicated with the control cavity of the control valve through a control oil path (8), a feedback oil path (L S) on the load-sensitive multi-way valve is communicated with the spring cavity of the control valve, the spring force in the spring cavity of the control valve, the oil pressure in the feedback oil path and the oil pressure interaction of the control oil path in the control cavity adjust the control valve opening, the control oil cylinder (7) comprises a piston (71), a rod cavity (72) and a rodless cavity (73), and pressure oil at the oil outlet of the variable pump passes through a safety oil path (9) and enters the control oil chamber (7) through the control rod cavity (71) and the control oil cylinder (73).

2. The hydraulic control system of a load-sensitive pump according to claim 1, wherein an oil inlet of the control valve (5) is communicated with a control oil path (8), and an oil outlet of the control valve is communicated with a rodless cavity of the control cylinder.

3. The load-sensitive pump hydraulic control system according to claim 1, wherein the control cylinder (7) has a first state in which the control valve opening decreases the pressure oil in the rodless chamber (73) and the pressure of the oil pressure in the feedback oil passage (L S) decreases the pressure oil in the rod chamber (72) receiving the pressure oil in the relief oil passage (9) and increases the output flow rate of the variable pump by the piston (71) when the sum of the spring force in the spring chamber (52) of the control valve (5) and the pressure of the oil pressure in the feedback oil passage (L S) is equal to the oil pressure in the control oil passage (8) in the control chamber (51) so that the variable pump (1) outputs stably, and a second state in which the sum of the spring force in the spring chamber (52) of the control valve (5) and the pressure of the oil pressure in the feedback oil passage (L S) is less than the pressure of the control oil passage (8) in the control chamber (51) so that the flow rate of the control valve (5) increases the flow rate of the control valve opening (73) through the control oil passage (71).

4. A load-sensitive pump hydraulic control system according to claim 1, characterized in that the pressure-cut off valve (6) is provided between the control valve and the control cylinder, said pressure-cut off valve having a first position in which the outlet of the control valve (5) is in communication with the rodless chamber (73) of the control cylinder (7) and a second position in which the safety oil path (9) is in communication with the rodless chamber (73) of the control cylinder (7) by reversing when the pressure oil of the safety oil path exceeds the setting of the pressure-cut off valve.

5. The hydraulic control system of the load-sensitive pump according to claim 4, wherein the pressure cut-off valve (6) comprises a pressure control cavity (61) and a pressure spring cavity (62), the safety oil path is respectively connected with the pressure control cavity of the pressure cut-off valve and an oil inlet of the pressure cut-off valve, and when the pressure cut-off valve is at the second position, the pressure oil of the safety oil path is connected with the rodless cavity of the control oil cylinder through the oil inlet of the pressure cut-off valve and the oil outlet of the pressure cut-off valve.

6. The load-sensitive pump hydraulic control system according to claim 4, wherein a first passage (12) is provided between the pressure cut-off valve and the rodless chamber of the control cylinder, a second passage (13) and a third passage (14) are provided between the pressure cut-off valve and the control cylinder, the third passage is communicated with an oil tank (15), and the safety oil path is communicated with the rodless chamber of the control cylinder through the first passage when the pressure cut-off valve is in the second position.

7. The load sensitive pump hydraulic control system of claim 6, further comprising a throttling element (16), wherein the throttling element (16) is disposed between the first passage and the third passage, and wherein the throttling element is provided with a throttling orifice (17).

8. The hydraulic control system of a load-sensitive pump according to claim 1, wherein the load-sensitive multi-way valve (4) comprises a control link (45) and at least one working link (46), the control link is spliced with the working link, the load-sensitive multi-way valve comprises a main oil inlet (P) and an oil return port (T), the control link is provided with a diverter valve (41) and an unloading valve (42), the diverter valve (41) is arranged between the main oil inlet and the oil return port, and the unloading valve is arranged between a feedback oil path and the oil return port.

9. The load-sensitive pump hydraulic control system according to claim 8, wherein the working link (46) is provided with a control reversing valve (47) and a pilot proportional solenoid valve (43), the load-sensitive multi-way valve comprises a pilot oil path (44) communicated with the pilot proportional solenoid valve (43), and an oil outlet of the pilot proportional solenoid valve is communicated with a reversing control cavity of the control reversing valve (47).

10. A load sensitive pump hydraulic control system as claimed in claim 1 further comprising an auxiliary pump (11) in communication with the load sensitive multiplex valve.