Hydraulic control operation system and hydraulic control operation method of engineering machinery and engineering machinery

Abstract

A hydraulic control operation system of engineering machinery comprises a control valve group, a control handle, an execution element, a pilot control oil way and a controller, and the control valve group is connected with the control handle and the execution element. The pilot control oil way comprises a pilot oil source, a switching valve and a pilot oil control valve, an oil inlet of the switching valve is connected with the pilot oil source, two working oil ports are connected with the control handle through a first oil way and a second oil way respectively, and the pilot oil control valve is arranged on the second oil way; the switching valve and the pilot oil control valve are connected with the controller, the controller controls the switching-on of the first oil way or the second oil way by controlling the switching valve, and when the second oil way is switched on, the controller is further used for receiving the action signal and adjusting the pressure of the hydraulic oil passing through the pilot oil control valve according to the received action signal. The hydraulic control operation system can solve the problem of large speed reduction proportion difference of different actions during speed reduction, and is simple in structure, low in cost and easy to implement. The invention further relates to a hydraulic control operation method of the engineering machinery and the engineering machinery.

Description

Technical Field

[0001] The present invention relates to the technical field of engineering machinery, and in particular to a hydraulic control operating system of engineering machinery, a hydraulic control operating method and engineering machinery. Background Art

[0002] Engineering machinery is an important part of the equipment industry. All mechanical equipment required for earthwork construction, road construction and maintenance, mobile lifting and loading and unloading operations, and comprehensive mechanized construction projects required for various construction projects are called engineering machinery.

[0003] Mobile cranes are commonly used in mobile lifting and loading and unloading operations. Mobile cranes mainly include truck cranes, tire cranes, crawler cranes, and special mobile cranes. Their operating mechanisms mainly include: a luffing mechanism that changes the boom angle, a telescopic mechanism that changes the boom length, a winch mechanism for lifting and lowering, and a slewing mechanism for horizontal circular motion of the vehicle. The operating mechanism usually controls the luffing, telescopic, winching, and slewing actions through the control handle and pedal, and can be divided into electric control and hydraulic control according to the form of the operating handle.

[0004] In the hydraulic control system of a mobile crane, the hoisting action is driven by the hoisting motor, the luffing action is driven by the luffing cylinder, and the slewing action is driven by the slewing motor. The pump that provides hydraulic oil to the hoisting motor and the luffing cylinder is usually a variable displacement pump, and the pump that provides hydraulic oil to the slewing motor is usually a fixed displacement pump. The prior art usually sets a pressure reducing valve on the pilot oil circuit to decelerate each action, so that the pilot control pressure is reduced by the pressure reducing valve before being supplied to the operating handle. However, due to differences in driving methods and hydraulic system principles, the pilot control pressure-flow output characteristics of each action are different, that is, at the same pilot control pressure, the hydraulic oil flow obtained when each operating mechanism is in action is different.

[0005] In practical applications, the actions with the largest differences in pilot control pressure-flow output characteristics are winching, luffing and slewing. In the existing deceleration scheme, the pressure set by the pressure reducing valve is a fixed value. When the winch speed is used as the deceleration target, the luffing and slewing speeds will be very slow, or even no action; when the luffing or slewing speed is used as the deceleration target, the winch speed is not significantly reduced and the deceleration requirements cannot be met; in summary, in the existing hydraulic control operating system, each action has a large difference in the deceleration ratio when decelerating. Summary of the invention

[0006] In view of this, the present invention provides a hydraulic control system for engineering machinery and engineering machinery having the hydraulic control system, which can solve the problem of large differences in speed reduction ratios of different actions during deceleration, and has a simple structure, low cost and easy implementation.

[0007] A hydraulic control system for engineering machinery provided by an embodiment of the present invention comprises a control valve group, a control handle and an actuator, wherein the control valve group is connected to the control handle and the actuator respectively. It also comprises a pilot control oil circuit and a controller, wherein the pilot control oil circuit comprises a pilot oil source, a switching valve and a pilot oil control valve, wherein the oil inlet of the switching valve is connected to the pilot oil source, and the two working oil ports of the switching valve are connected to the control handle through a first oil circuit and a second oil circuit respectively, and the pilot oil control valve is arranged on the second oil circuit; the switching valve and the pilot oil control valve are both connected to the controller, and the controller controls the conduction of the first oil circuit or the second oil circuit by controlling the switching valve, and when the second oil circuit is conducted, the controller is also used to receive an action signal and adjust the pressure of the hydraulic oil passing through the pilot oil control valve according to the received action signal.

[0008] Further, the control valve group includes a rotary valve and a multi-way valve, the actuator includes a rotary motor and a boom cylinder, the control handle is connected to the two oil inlets of the rotary valve through a left rotary pilot oil circuit and a right rotary pilot oil circuit, the two oil outlets of the rotary valve are connected to the rotary motor, the control handle is connected to the two oil inlets of the multi-way valve through a boom drop pilot oil circuit and a boom start pilot oil circuit, the two oil outlets of the multi-way valve are connected to the boom cylinder; the action signal includes a rotary action signal and a boom drop action signal, when the controller receives the rotary action signal, the hydraulic oil passing through the pilot oil control valve is controlled to have a first pressure, when the controller receives the boom drop action signal, the hydraulic oil passing through the pilot oil control valve is controlled to have a second pressure, wherein the first pressure is less than the second pressure.

[0009] Further, when the controller receives the swing action signal and the amplitude drop action signal at the same time, the controller controls the hydraulic oil passing through the pilot oil control valve to have a third pressure, wherein the third pressure is greater than or equal to the second pressure.

[0010] Furthermore, the hydraulic control system of the engineering machinery also includes a first sensor, a second sensor and a third sensor; the first sensor is connected to the left swing pilot oil circuit, the second sensor is connected to the right swing pilot oil circuit, and the third sensor is connected to the amplitude change drop pilot oil circuit; the first sensor, the second sensor and the third sensor are also connected to the controller; the first sensor is used to detect the hydraulic oil pressure of the left swing pilot oil circuit / the second sensor is used to detect the hydraulic oil pressure of the right swing pilot oil circuit to form the swing action signal and send it to the controller, and the third sensor is used to detect the hydraulic oil pressure of the amplitude change drop pilot oil circuit to form the amplitude change drop action signal and send it to the controller.

[0011] Furthermore, the hydraulic control system of the engineering machinery also includes a shuttle valve, a fourth sensor and a fifth sensor; the two oil inlets of the shuttle valve are respectively connected to the left swing pilot oil circuit and the right swing pilot oil circuit, the oil outlet of the shuttle valve is connected to the fourth sensor, and the fifth sensor is connected to the amplitude change pilot oil circuit; the fourth sensor is used to detect the hydraulic oil pressure of the left swing pilot oil circuit or the right swing pilot oil circuit to form the swing action signal and send it to the controller, and the fifth sensor is used to detect the hydraulic oil pressure of the amplitude change pilot oil circuit to form the amplitude change action signal and send it to the controller.

[0012] Furthermore, the control handle is connected to the controller, and the control handle generates the rotation action signal and / or the amplitude change action signal and sends them to the controller.

[0013] Furthermore, the actuator also includes a winch motor, and the control handle is connected to the two oil inlets of the multi-way valve through the winch-falling pilot oil circuit and the winch-lifting pilot oil circuit, and the two oil outlets of the multi-way valve are connected to the winch motor; when the controller does not receive the rotation action signal and / or the variable amplitude falling action signal, the controller controls the hydraulic oil through the pilot oil control valve to have a fourth pressure, and the fourth pressure is less than the first pressure.

[0014] Furthermore, the pilot oil control valve has an electric drive end Y S1 The controller controls the electric drive end Y S1 Different current values ​​are input to control the pressure of the hydraulic oil passing through the pilot oil control valve. The greater the current value input by the controller, the greater the pressure of the hydraulic oil passing through the pilot oil control valve.

[0015] Furthermore, a one-way valve is provided on the second oil circuit, and the one-way valve is connected between the pilot oil control valve and the control handle.

[0016] The present invention also provides a hydraulic control operation method for engineering machinery, which is used to operate the hydraulic control operating system. When the hydraulic control operating system of the engineering machinery does not need to decelerate, the controller controls the first oil circuit to be connected. When the hydraulic control operating system of the engineering machinery needs to decelerate, the controller controls the second oil circuit to be connected.

[0017] The action signal includes a variable amplitude drop action signal and a rotation action signal, and when controlling the conduction of the second oil circuit, it also includes:

[0018] When the controller receives the swing action signal, the controller controls the hydraulic oil passing through the pilot oil control valve to have a first pressure; when the controller receives the amplitude change and drop action signal, the controller controls the hydraulic oil passing through the pilot oil control valve to have a second pressure; when the controller receives the swing action signal and the amplitude change and drop action signal at the same time, the controller controls the hydraulic oil passing through the pilot oil control valve to have a third pressure; when the controller does not receive the swing action signal and / or the amplitude change and drop action signal, the controller controls the hydraulic oil passing through the pilot oil control valve to have a fourth pressure; wherein, the first pressure is less than the second pressure, the third pressure is greater than or equal to the second pressure, and the fourth pressure is less than the first pressure.

[0019] Furthermore, the switching valve has an electric control terminal Y1, and the pilot oil control valve has an electric drive terminal Y S1 ;

[0020] When the electric control terminal Y1 of the controller and the electric drive terminal Y S1 When no electricity is available, the first oil circuit is connected;

[0021] When the controller controls the electric control terminal Y1 of the switching valve to be energized, the current value I1 is input to the electric drive terminal Y1 of the pilot oil control valve. S1 , at this time, the hydraulic oil passing through the pilot oil control valve has the fourth pressure;

[0022] When the controller controls the electric control terminal Y1 of the switching valve to be energized, the current value I2 is input to the electric drive terminal Y S1 At this time, the hydraulic oil passing through the pilot oil control valve has the first pressure;

[0023] When the controller controls the electric control terminal Y1 of the switching valve to be energized, the current value I3 is input to the electric drive terminal Y S1 , at this time, the hydraulic oil passing through the pilot oil control valve has the second pressure;

[0024] When the controller controls the electric control terminal Y1 of the switching valve to be energized, the current value I4 is input to the electric drive terminal Y S1 At this time, the hydraulic oil passing through the pilot oil control valve has the third pressure;

[0025] Among them, the current value I4≥I3>I2>I1.

[0026] The present invention also provides an engineering machine, comprising the above-mentioned hydraulic control operating system.

[0027] In summary, the hydraulic control system of the engineering machinery of the present invention includes a control valve group, a control handle and an actuator, and the control valve group is connected to the control handle and the actuator respectively. It also includes a pilot control oil circuit and a controller, the pilot control oil circuit includes a pilot oil source, a switching valve and a pilot oil control valve, the oil inlet of the switching valve is connected to the pilot oil source, the two working oil ports of the switching valve are connected to the control handle through the first oil circuit and the second oil circuit respectively, and the pilot oil control valve is arranged on the second oil circuit; the switching valve and the pilot oil control valve are both connected to the controller, and the controller controls the conduction of the first oil circuit or the second oil circuit by controlling the switching valve. When the second oil circuit is conducted, the controller is also used to receive an action signal and adjust the pressure of the hydraulic oil passing through the pilot oil control valve according to the received action signal; the hydraulic control system of the engineering machinery of the present invention can solve the problem of large differences in the deceleration ratios of different actions during deceleration, and has a simple structure, low cost and is easy to implement.

[0028] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, the following specifically cites a preferred embodiment and describes it in detail with the accompanying drawings as follows. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 It is a schematic diagram of a hydraulic control system for an engineering machine according to a first embodiment of the present invention.

[0030] Figure 2 It is a connection relationship diagram of some electronic control components in the hydraulic control operating system of the engineering machinery according to the first embodiment of the present invention.

[0031] Figure 3 It is the pilot control pressure-flow curve in the hydraulic control system of engineering machinery.

[0032] Figure 4 It is a schematic diagram of a hydraulic control system for engineering machinery according to a second embodiment of the present invention.

[0033] Figure 5 It is a connection relationship diagram of some electronic control components in the hydraulic control operating system of the engineering machinery according to the second embodiment of the present invention.

[0034] Figure 6 It is a schematic diagram of a hydraulic control system for engineering machinery according to a third embodiment of the present invention.

[0035] Figure 7 It is a connection relationship diagram of some electronic control components in the hydraulic control operating system of the engineering machinery according to the third embodiment of the present invention. DETAILED DESCRIPTION

[0036] In order to further explain the technical means and effects adopted by the present invention to achieve the predetermined invention purpose, the present invention is described in detail below in conjunction with the accompanying drawings and preferred embodiments.

[0037] Figure 1 is a schematic diagram of a hydraulic control system for an engineering machine according to a first embodiment of the present invention, Figure 2 This is a connection diagram of some electronic control components in the hydraulic control operating system of the engineering machinery of the first embodiment of the present invention. Please refer to Figure 1 and Figure 2 The hydraulic control system of the engineering machinery of this embodiment includes a control valve group 10, a control handle 20, an actuator 30, a pilot control oil circuit 40 and a controller 50. The control valve group 10 is connected to the control handle 20 and the actuator 30 respectively.

[0038] Among them, the pilot control oil circuit 40 includes a pilot oil source 41, a switching valve 42 and a pilot oil control valve 43. The oil inlet of the switching valve 42 is connected to the pilot oil source 41. The two working oil ports of the switching valve 42 are respectively connected to the control handle 20 through the first oil circuit 101 and the second oil circuit 102. The pilot oil control valve 43 is arranged on the second oil circuit 102; the switching valve 42 and the pilot oil control valve 43 are both connected to the controller 50. The controller 50 controls the conduction of the first oil circuit 101 or the second oil circuit 102 by controlling the switching valve 42. When the second oil circuit 102 is connected, the controller 50 is also used to receive an action signal and adjust the pressure of the hydraulic oil passing through the pilot oil control valve 43 according to the received action signal.

[0039] In this embodiment, the control handle 20 includes a first handle 21 and a second handle 22 . The first handle 21 is, for example, a left handle, and the second handle 22 is, for example, a right handle. The user can perform corresponding actions by operating the first handle 21 and the second handle 22 .

[0040] Further, the control valve group 10 includes a rotary valve 11, the actuator 30 includes a rotary motor 31, the control handle 20 is connected to the two oil inlets of the rotary valve 11 through the left rotary pilot oil circuit 103 and the right rotary pilot oil circuit 104, and the two oil outlets of the rotary valve 11 are connected to the rotary motor 31. The rotary motor 31 can perform a left rotary action or a right rotary action when it is running. When the left rotary pilot oil circuit 103 is connected, the rotary motor 31 performs a left rotary action, and when the right rotary pilot oil circuit 104 is connected, the rotary motor 31 performs a right rotary action.

[0041] The control valve group 10 further includes a multi-way valve 12, and the actuator 30 further includes a luffing oil cylinder 32. The control handle 20 is connected to the two oil inlets of the multi-way valve 12 through the luffing down pilot oil circuit 105 and the luffing up pilot oil circuit 106, and the two oil outlets of the multi-way valve 12 are connected to the luffing oil cylinder 32. The luffing oil cylinder 32 can perform the luffing down action and the luffing up action when it is in operation. When the luffing down pilot oil circuit 105 is connected, the luffing oil cylinder 32 performs the luffing down action, and when the luffing up pilot oil circuit 106 is connected, the luffing oil cylinder 32 performs the luffing up action.

[0042] Since the actions with the largest difference in pilot control pressure-flow output characteristics are winching, luffing and slewing actions, such as Figure 3 As shown in the figure, curve A is the pilot control pressure-flow curve when performing the variable-luffing action, curve B is the pilot control pressure-flow curve when performing the rotation action, and curve C is the pilot control pressure-flow curve when performing the winch action (including the winch lifting action and the winch lowering action). It can be seen from the figure that when the pilot control pressure is the same, the flow output obtained by the variable-luffing action, the rotation action, and the winch action becomes larger in turn, and the smaller the pilot control pressure, the greater the flow difference. In other words, if you want to ensure that each action runs smoothly, different pilot control pressures are required when performing different actions, especially when performing variable-luffing and rotation actions. Furthermore, the action signal received by the controller 50 includes a rotation action signal and a variable amplitude drop action signal. When the controller 50 receives the rotation action signal, the hydraulic oil passing through the pilot oil control valve 43 is controlled to have a first pressure. When the controller 50 receives the variable amplitude drop action signal, the hydraulic oil passing through the pilot oil control valve 43 is controlled to have a second pressure. The first pressure is less than the second pressure, that is, the pilot control pressure when performing the variable amplitude drop action is greater than the pilot control pressure when performing the rotation action.

[0043] Further, when the controller 50 receives the rotation action signal and the amplitude drop action signal at the same time, the controller 50 controls the hydraulic oil passing through the pilot oil control valve 43 to have a third pressure, wherein the third pressure is greater than or equal to the second pressure, that is, when the amplitude drop action and the rotation action are performed at the same time, the pilot control pressure must be greater than or equal to the pilot control pressure when the amplitude drop action is performed alone.

[0044] In this embodiment, the hydraulic control system of the engineering machinery includes a first sensor 1031, a second sensor 1041 and a third sensor 1051. The first sensor 1031 is connected to the left slewing pilot oil circuit 103, the second sensor 1041 is connected to the right slewing pilot oil circuit 104, and the third sensor 1051 is connected to the variable amplitude drop pilot oil circuit 105; the first sensor 1011, the second sensor 1021 and the third sensor 1031 are also connected to the controller 50.

[0045] In this embodiment, the first sensor 1031 , the second sensor 1041 , and the third sensor 1051 are all pressure sensors.

[0046] The first sensor 1031 is used to detect the hydraulic oil pressure of the left swing pilot oil circuit 103 to form a swing action signal and send it to the controller 50. The second sensor 1041 is used to detect the hydraulic oil pressure of the right swing pilot oil circuit 104 to form a swing action signal and send it to the controller 50. That is to say, when a left swing action or a right swing action is performed, a swing action signal will be generated.

[0047] The third sensor 1051 is used to detect the hydraulic oil pressure of the luffing pilot oil circuit 105 to generate a luffing action signal and send it to the controller 50 .

[0048] When the controller 50 receives a swing action signal or a luffing action signal, it controls the second oil circuit 102 to be connected, and adjusts the pressure of the hydraulic oil passing through the pilot oil control valve 43 according to different action signals. In this way, when performing the luffing action, the pressure of the hydraulic oil passing through the pilot oil control valve 43 will be greater than when performing the swing action, which solves the problem of large differences in the deceleration ratios of different actions during the deceleration action.

[0049] Furthermore, the actuator 30 also includes a hoisting motor 33, and the control handle 20 is connected to the two oil inlets of the multi-way valve 12 through the hoisting lowering pilot oil circuit 107 and the hoisting lifting pilot oil circuit 108, and the two oil outlets of the multi-way valve 12 are connected to the hoisting motor 33; when the controller 50 does not receive the rotary action signal and / or the variable amplitude lowering action signal, the controller 50 controls the hydraulic oil through the pilot oil control valve 43 to have a fourth pressure, and the fourth pressure is less than the first pressure. When the controller 50 does not receive the rotary action signal and / or the variable amplitude lowering action signal, it means that other actions other than the rotary action and / or the variable amplitude lowering action are executed at this time, such as the hoisting lifting action, the hoisting lowering action, etc. At this time, the pilot control pressure required to execute these actions is smaller than that when executing the rotary action.

[0050] In this embodiment, the pilot oil control valve 43 is, for example, an electric proportional reversing valve, but is not limited thereto. The pilot oil control valve 43 has an electric drive terminal Y S1 ; The controller 50 controls the electric drive terminal Y S1 Different current values ​​are input to control the pressure of the hydraulic oil passing through the pilot oil control valve 43 . The greater the current value input by the controller 50 , the greater the pressure of the hydraulic oil passing through the pilot oil control valve 43 .

[0051] Furthermore, a one-way valve 44 is provided on the second oil circuit 102, and the one-way valve 44 is connected between the pilot oil control valve 43 and the control handle 20. When the first oil circuit 101 is connected, the one-way valve 44 can prevent the pilot oil from the second oil circuit 102 from reversely entering the pilot oil control valve 43.

[0052] Furthermore, a balancing valve 34 is provided between the boom cylinder 32 and the multi-way valve 12, and a pilot control end of the balancing valve 34 is connected to the boom drop pilot oil circuit 105 through the boom balancing valve opening oil circuit 109. A balancing valve 35 is provided between the hoisting motor 33 and the multi-way valve 12.

[0053] Furthermore, the hydraulic control operating system further includes a first pump 61 and a second pump 62. The first pump 61 is connected to the multi-way valve 12 for pumping hydraulic oil to the multi-way valve 12, and the second pump 62 is connected to the rotary valve 11 for pumping hydraulic oil to the rotary valve 11. The first pump 61 is a variable displacement pump, and the second pump 62 is a fixed displacement pump.

[0054] The following is the specific control principle of the hydraulic control operating system of this embodiment:

[0055] 1. The deceleration condition is not triggered: When the controller 50 controls the electric control terminal Y1 of the switching valve 42 and the electric drive terminal Y S1 When no electricity is supplied, the first oil circuit 101 in the pilot control oil circuit 40 is connected, the pilot control pressure is not limited, and the pilot control oil circuit 40 does not decelerate.

[0056] 2. Deceleration condition trigger:

[0057] a: When there is no pressure signal from the first sensor 1031, the second sensor 1041, and the third sensor 1051, it means that the rotary action and / or the variable amplitude action are not operated. At this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I1 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a fourth pressure through the pilot oil control valve 43;

[0058] b: When the first sensor 1031 or the second sensor 1041 has a pressure signal and the third sensor 1051 has no pressure signal, it means that the rotary action is operated and the variable amplitude action is not operated; at this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I2 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a first pressure through the pilot oil control valve 43;

[0059] c: When there is no pressure signal from the first sensor 1031 or the second sensor 1041, and there is a pressure signal from the third sensor 1051, it means that the luffing action is operated, and the rotation action is not operated; at this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I3 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a second pressure through the pilot oil control valve 43;

[0060] d: When the first sensor 1031 and the third sensor 1051 have pressure signals at the same time, or when the second sensor 1031 and the third sensor 1051 have pressure signals at the same time, it means that the rotary action and the variable amplitude action are operated at the same time. At this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I4 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a third pressure through the pilot oil control valve 43;

[0061] Among them, the current value I4≥I3>I2>I1, and the specific current value can be theoretically calculated according to the control pilot pressure-flow curve and the characteristics of the pilot oil control valve 43, or can be debugged and calibrated through experiments.

[0062] [Second embodiment]

[0063] Figure 4 is a schematic diagram of a hydraulic control system for engineering machinery according to a second embodiment of the present invention, Figure 5 This is a connection diagram of some electronic control components in the hydraulic control operating system of the engineering machinery of the second embodiment of the present invention. Please refer to Figure 4 and Figure 5 The hydraulic control operating system of the second embodiment is different from that of the first embodiment in that the hydraulic control operating system of the present embodiment includes a shuttle valve 1032, a fourth sensor 1033 and a fifth sensor 1052. The two oil inlets of the shuttle valve 1032 are respectively connected to the left rotation pilot oil circuit 103 and the right rotation pilot oil circuit 104, the oil outlet of the shuttle valve 1032 is connected to the fourth sensor 1033, and the fifth sensor 1052 is connected to the variable amplitude drop pilot oil circuit 105.

[0064] The fourth sensor 1033 and the fifth sensor 1052 are both pressure sensors. The fourth sensor 1033 is used to detect the hydraulic oil pressure of the left swing pilot oil circuit 103 or the right swing pilot oil circuit 104 to form a swing action signal to be sent to the controller 50, and the fifth sensor 1052 is used to detect the hydraulic oil pressure of the variable amplitude drop pilot oil circuit 105 to form a variable amplitude drop action signal to be sent to the controller 50.

[0065] The following is the specific control principle of the hydraulic control operating system of this embodiment:

[0066] 1. The deceleration condition is not triggered: When the controller 50 controls the electric control terminal Y1 of the switching valve 42 and the electric drive terminal Y S1 When no electricity is supplied, the first oil circuit 101 in the pilot control oil circuit 40 is connected, the pilot control pressure is not limited, and the pilot control oil circuit 40 does not decelerate.

[0067] 2. Deceleration condition trigger:

[0068] a: When there is no pressure signal from the fourth sensor 1033 and the fifth sensor 1052, it means that the rotary action and / or the variable amplitude action are not operated. At this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I1 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a fourth pressure through the pilot oil control valve 43;

[0069] b: When the fourth sensor 1033 has a pressure signal and the fifth sensor 1052 has no pressure signal, it means that the rotary action is operated and the variable amplitude drop action is not operated; at this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I2 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a first pressure through the pilot oil control valve 43;

[0070] c: When the fourth sensor 1033 has no pressure signal and the fifth sensor 1052 has a pressure signal, it means that the variable amplitude drop action is operated and the rotation action is not operated; at this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I3 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a second pressure through the pilot oil control valve 43;

[0071] d: When the fourth sensor 1033 and the fifth sensor 1052 have pressure signals at the same time, it means that the rotary action and the variable amplitude drop action are operated at the same time. At this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I4 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a third pressure through the pilot oil control valve 43;

[0072] Among them, the current value I4≥I3>I2>I1.

[0073] [Third embodiment]

[0074] Figure 6 is a schematic diagram of a hydraulic control system for engineering machinery according to a third embodiment of the present invention, Figure 7 This is a connection diagram of some electronic control components in the hydraulic control operating system of the engineering machinery of the third embodiment of the present invention. Please refer to Figure 6 and Figure 7The hydraulic control operating system of the third embodiment is different from that of the first embodiment in that:

[0075] The control handle 20 of this embodiment is connected to the controller 50, and the control handle 20 generates a rotation action signal and / or a luffing action signal and sends it to the controller 50. The control handle 20 is a handle with direction and position detection, and the action currently performed by the engineering machinery is directly identified by the control handle 20, and the action control signal is sent to the controller 50 to adjust the pressure of the hydraulic oil passing through the pilot oil control valve 43.

[0076] The following is the specific control principle of the hydraulic control operating system of this embodiment:

[0077] 1. The deceleration condition is not triggered: When the controller 50 controls the electric control terminal Y1 of the switching valve 42 and the electric drive terminal Y S1 When no electricity is supplied, the first oil circuit 101 in the pilot control oil circuit 40 is connected, the pilot control pressure is not limited, and the pilot control oil circuit 40 does not decelerate.

[0078] 2. Deceleration condition trigger:

[0079] a: When the control handle 20 does not send a rotation action and / or a variable amplitude drop action signal, at this time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I1 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a fourth pressure through the pilot oil control valve 43;

[0080] b: When the control handle 20 sends a rotation action signal, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I2 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a first pressure through the pilot oil control valve 43;

[0081] c: When the control handle 20 sends a variable amplitude drop action signal, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I3 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a second pressure through the pilot oil control valve 43;

[0082] d: When the control handle 20 sends the rotation action and the variable amplitude drop action signals at the same time, the controller 50 controls the electric control terminal Y1 of the switching valve 42 to be energized, and at the same time inputs the current value I4 to the electric drive terminal Y1 of the pilot oil control valve 43. S1 , the hydraulic oil has a third pressure through the pilot oil control valve 43;

[0083] Among them, the current value I4≥I3>I2>I1.

[0084] The present invention also relates to an engineering machine, comprising the above-mentioned hydraulic control system. The engineering machine is preferably a mobile crane, and other structures of the engineering machine are well known to those skilled in the art and will not be described in detail here.

[0085] The hydraulic control system of the engineering machinery of the present invention comprises a control valve group 10, a control handle 20, an actuator 30, a pilot control oil circuit 40 and a controller 50. The control valve group 10 is connected to the control handle 20 and the actuator 30 respectively. The pilot control oil circuit 40 includes a pilot oil source 41, a switching valve 42 and a pilot oil control valve 43. The oil inlet of the switching valve 42 is connected to the pilot oil source 41. The two working oil ports of the switching valve 42 are respectively connected to the control handle 20 through the first oil circuit 101 and the second oil circuit 102. The pilot oil control valve 43 is arranged on the second oil circuit 102. The switching valve 42 and the pilot oil control valve 43 are both connected to the controller 50. The controller 50 controls the conduction of the first oil circuit 101 or the second oil circuit 102 by controlling the switching valve 42. When the second oil circuit 102 is connected, the controller 50 is also used to receive an action signal and adjust the pressure of the hydraulic oil passing through the pilot oil control valve 43 according to the received action signal. The hydraulic control operating system of the engineering machinery of the present invention can solve the problem of large differences in the deceleration ratios of different actions during deceleration, and has a simple structure, low cost and is easy to implement.

[0086] The above description is only a preferred embodiment of the present invention and does not limit the present invention in any form. Although the present invention has been disclosed as a preferred embodiment as above, it is not used to limit the present invention. Any technician familiar with this profession can make some changes or modifications to equivalent embodiments of equivalent changes using the technical contents disclosed above without departing from the scope of the technical solution of the present invention. However, any simple modification, equivalent change and modification made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention still fall within the scope of the technical solution of the present invention.

Claims

1. A hydraulic control system for engineering machinery, comprising a control valve group (10), a control handle (20) and an actuator (30), wherein the control valve group (10) is connected to the control handle (20) and the actuator (30), respectively, and characterized in that: The invention also comprises a pilot control oil circuit (40) and a controller (50), wherein the pilot control oil circuit (40) comprises a pilot oil source (41), a switching valve (42) and a pilot oil control valve (43), wherein an oil inlet of the switching valve (42) is connected to the pilot oil source (41), two working oil ports of the switching valve (42) are respectively connected to the control handle (20) via a first oil circuit (101) and a second oil circuit (102), and the pilot oil control valve (43) is arranged at the second oil circuit. (102); the switching valve (42) and the pilot oil control valve (43) are both connected to the controller (50), and the controller (50) controls the conduction of the first oil circuit (101) or the second oil circuit (102) by controlling the switching valve (42). When the second oil circuit (102) is conducted, the controller (50) is also used to receive an action signal and adjust the pressure of the hydraulic oil passing through the pilot oil control valve (43) according to the received action signal.

2. The hydraulic control system of engineering machinery according to claim 1, characterized in that: The control valve group (10) comprises a rotary valve (11) and a multi-way valve (12); the actuator (30) comprises a rotary motor (31) and a luffing oil cylinder (32); the control handle (20) is connected to two oil inlets of the rotary valve (11) via a left rotary pilot oil circuit (103) and a right rotary pilot oil circuit (104); the two oil outlets of the rotary valve (11) are connected to the rotary motor (31); the control handle (20) is connected to the multi-way valve (31) via a luffing down pilot oil circuit (105) and a luffing up pilot oil circuit (106). The two oil inlets of the multi-way valve (12) are connected, and the two oil outlets of the multi-way valve (12) are connected to the boom cylinder (32); the action signal includes a rotation action signal and a boom drop action signal, and when the controller (50) receives the rotation action signal, the hydraulic oil passing through the pilot oil control valve (43) is controlled to have a first pressure, and when the controller (50) receives the boom drop action signal, the hydraulic oil passing through the pilot oil control valve (43) is controlled to have a second pressure, wherein the first pressure is less than the second pressure.

3. The hydraulic control system of engineering machinery according to claim 2, characterized in that: When the controller (50) receives the swing action signal and the amplitude drop action signal at the same time, the controller (50) controls the hydraulic oil passing through the pilot oil control valve (43) to have a third pressure, wherein the third pressure is greater than or equal to the second pressure.

4. The hydraulic control system of engineering machinery according to claim 2 or 3, characterized in that: The hydraulic control system of the engineering machinery further comprises a first sensor (1031), a second sensor (1041) and a third sensor (1051); the first sensor (1031) is connected to the left rotation pilot oil circuit (103), the second sensor (1041) is connected to the right rotation pilot oil circuit (104), and the third sensor (1051) is connected to the variable amplitude drop pilot oil circuit (105); the first sensor (1011), the second sensor (1021) and the third sensor (1031) are also connected to the controller (50); The first sensor (1031) is used to detect the hydraulic oil pressure of the left swing pilot oil circuit (103) / the second sensor (1041) is used to detect the hydraulic oil pressure of the right swing pilot oil circuit (104) to form the swing action signal and send it to the controller (50), and the third sensor (1051) is used to detect the hydraulic oil pressure of the amplitude change falling pilot oil circuit (105) to form the amplitude change falling action signal and send it to the controller (50).

5. The hydraulic control system of engineering machinery according to claim 2 or 3, characterized in that: The hydraulic control system of the engineering machinery further comprises a shuttle valve (1032), a fourth sensor (1033) and a fifth sensor (1052); the two oil inlets of the shuttle valve (1032) are respectively connected to the left-swing pilot oil circuit (103) and the right-swing pilot oil circuit (104); the oil outlet of the shuttle valve (1032) is connected to the fourth sensor (1033); and the fifth sensor (1052) is connected to the luffing pilot oil circuit (105); The fourth sensor (1033) is used to detect the hydraulic oil pressure of the left swing pilot oil circuit (103) or the right swing pilot oil circuit (104) to form the swing action signal and send it to the controller (50), and the fifth sensor (1052) is used to detect the hydraulic oil pressure of the variable amplitude drop pilot oil circuit (105) to form the variable amplitude drop action signal and send it to the controller (50).

6. The hydraulic control system of engineering machinery according to claim 2 or 3, characterized in that: The control handle (20) is connected to the controller (50), and the control handle (20) generates the rotation action signal and / or the amplitude change action signal and sends them to the controller (50).

7. The hydraulic control system for engineering machinery according to claim 2 or 3, characterized in that: The actuator (30) also includes a hoisting motor (33), and the control handle (20) is connected to the two oil inlets of the multi-way valve (12) through the hoisting lowering pilot oil circuit (107) and the hoisting raising pilot oil circuit (108), and the two oil outlets of the multi-way valve (12) are connected to the hoisting motor (33); when the controller (50) does not receive the rotary action signal and / or the variable amplitude falling action signal, the controller (50) controls the hydraulic oil through the pilot oil control valve (43) to have a fourth pressure, and the fourth pressure is less than the first pressure.

8. The hydraulic control system of engineering machinery according to claim 2 or 3, characterized in that: The pilot oil control valve (43) has an electric drive end Y S1 The controller (50) controls the electric drive terminal Y S1 Different current values ​​are input to control the pressure of the hydraulic oil passing through the pilot oil control valve (43); the greater the current value input by the controller (50), the greater the pressure of the hydraulic oil passing through the pilot oil control valve (43).

9. The hydraulic control system for engineering machinery according to claim 1, characterized in that: A one-way valve (44) is also provided on the second oil circuit (102), and the one-way valve (44) is connected between the pilot oil control valve (43) and the control handle (20).

10. A hydraulic control operation method for engineering machinery, characterized in that: Used to operate the hydraulic control operating system according to any one of claims 1 to 9, when the hydraulic control operating system of the engineering machinery does not need to decelerate, the controller (50) controls the first oil circuit (101) to be connected, and when the hydraulic control operating system of the engineering machinery needs to decelerate, the controller (50) controls the second oil circuit (101) to be connected; The action signal includes a variable amplitude drop action signal and a rotation action signal, and when controlling the conduction of the second oil circuit (101), it also includes: When the controller (50) receives the swing action signal, the controller (50) controls the hydraulic oil passing through the pilot oil control valve (43) to have a first pressure; when the controller (50) receives the amplitude change drop action signal, the controller (50) controls the hydraulic oil passing through the pilot oil control valve (43) to have a second pressure; when the controller (50) receives the swing action signal and the amplitude change drop action signal at the same time, the controller (50) controls the hydraulic oil passing through the pilot oil control valve (43) to have a third pressure; when the controller (50) does not receive the swing action signal and / or the amplitude change drop action signal, the controller (50) controls the hydraulic oil passing through the pilot oil control valve (43) to have a fourth pressure; wherein the first pressure is less than the second pressure, the third pressure is greater than or equal to the second pressure, and the fourth pressure is less than the first pressure.

11. The hydraulic control operation method of engineering machinery according to claim 10, characterized in that: The switching valve (42) has an electric control terminal Y1, and the pilot oil control valve (43) has an electric drive terminal Y S1 ; When the controller (50) controls the electric control terminal Y1 of the switching valve (42) and the electric drive terminal Y2 of the pilot oil control valve (43), S1 When no electricity is available, the first oil circuit (101) is connected; When the controller (50) controls the electric control terminal Y1 of the switching valve (42) to be energized, a current value I1 is input to the electric drive terminal Y1 of the pilot oil control valve (43). S1 At this time, the hydraulic oil passing through the pilot oil control valve (43) has the fourth pressure; When the controller (50) controls the electric control terminal Y1 of the switching valve (42) to be energized, a current value I2 is input to the electric drive terminal Y1 of the pilot oil control valve (43). S1 At this time, the hydraulic oil passing through the pilot oil control valve (43) has the first pressure; When the controller (50) controls the electric control terminal Y1 of the switching valve (42) to be energized, a current value I3 is input to the electric drive terminal Y1 of the pilot oil control valve (43). S1 At this time, the hydraulic oil passing through the pilot oil control valve (43) has the second pressure; When the controller (50) controls the electric control terminal Y1 of the switching valve (42) to be energized, a current value I4 is input to the electric drive terminal Y1 of the pilot oil control valve (43). S1 At this time, the hydraulic oil passing through the pilot oil control valve (43) has the third pressure; Among them, the current value I4≥I3>I2>I1.

12. An engineering machine, characterized in that: Comprising the hydraulic control operating system as described in any one of claims 1 to 9.

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