CN116771743A

CN116771743A - Hydraulic control system, counterweight weight detection and pressure debugging method

Info

Publication number: CN116771743A
Application number: CN202310951906.0A
Authority: CN
Inventors: 常刘平; 刘永平; 陈海生
Original assignee: Hunan Sany Medium Lifting Machinery Co Ltd
Current assignee: Hunan Sany Medium Lifting Machinery Co Ltd
Priority date: 2023-07-31
Filing date: 2023-07-31
Publication date: 2023-09-19

Abstract

The invention relates to the technical field of hydraulic systems, and provides a hydraulic control system, a counterweight weight detection method and a pressure debugging method. The hydraulic control system comprises a balance weight oil cylinder group, a balance weight control valve group, a pressure oil control valve, a pressure regulating valve, a control device, a pressure oil source and an oil tank. The pressure oil control valve controls the communication state of the pressure oil source and the balance weight control valve group, and the balance weight control valve group controls the communication state of the pressure oil control valve, the oil tank and the balance weight oil cylinder group, wherein the balance weight control valve group is provided with a rod cavity and a rodless cavity. The embodiment of the invention can reduce the high-pressure overflow waste in the working process of the hydraulic control system and can also improve the stability of the load lifting operation of the counterweight cylinder group.

Description

Hydraulic control system, counterweight weight detection and pressure debugging method

Technical Field

The invention relates to the technical field of hydraulic systems, in particular to a hydraulic control system, a counterweight weight detection method and a pressure debugging method.

Background

In order to ensure the safety of the crane operation process, a counterweight is usually arranged on the crane. Currently, hydraulic control systems are mostly used as power drive systems for installing and releasing balancing weights. In order to improve the operational stability and reliability of the hydraulic control system, pressure regulating valves are often provided. The pressure regulating valve in the existing hydraulic control system is usually an empirical fixed value, and cannot meet the accurate pressure supply requirements under different use conditions, and the problems of large high-pressure overflow waste and poor operation stability of the counterweight cylinder inevitably occur in the use process.

Disclosure of Invention

The invention provides a hydraulic control system, a counterweight weight detection and pressure debugging method, which are used for solving the problems that the existing hydraulic control system is easy to cause larger high-pressure overflow waste and the operation stability of an oil cylinder is relatively poor.

According to a first aspect of the present invention, there is provided a hydraulic control system including a counterweight cylinder group, a counterweight control valve group, a pressure oil control valve, a pressure regulating valve, a control device, a pressure oil source, and an oil tank.

Wherein, the pressure oil source is connected with the pressure oil control valve. The pressure oil control valve and the oil tank are connected with the counterweight control valve group. The balance weight control valve group is connected with a rod cavity and a rodless cavity of the balance weight oil cylinder group. The pressure oil control valve is used for controlling the communication state between the pressure oil source and the counterweight control valve group. The balance weight control valve group is used for controlling the communication state among the pressure oil control valve, the oil tank and the rod cavity and the rodless cavity of the balance weight oil cylinder group.

The pressure regulating valve is connected between the pressure output oil port of the pressure oil control valve and the counterweight control valve group. The control device is connected with the counterweight control valve group, the pressure oil control valve and the pressure regulating valve. The control device is used for determining the weight of the balancing weight based on the working state of the balancing weight oil cylinder group, the pressures of the rodless cavity and the rod-containing cavity of the balancing weight oil cylinder group and the action areas of the rodless cavity and the rod-containing cavity of the balancing weight oil cylinder group, and adapting and setting the set pressure of the pressure regulating valve of the balancing weight oil cylinder group in different working states based on the pressures of the rod-containing cavity and the rodless cavity of the balancing weight oil cylinder group.

According to the hydraulic control system provided by the invention, the counterweight cylinder group comprises a first counterweight cylinder and a second counterweight cylinder. The counterweight control valve group includes a first counterweight control valve and a second counterweight control valve.

The pressure oil output port of the pressure oil control valve and the oil tank are connected with the first counterweight control valve and the second counterweight control valve. The first counterweight control valve is connected with a rod cavity and a rodless cavity of the first counterweight oil cylinder. The first counterweight control valve is used for controlling the communication state among a pressure output oil port of the pressure oil control valve, the oil tank, a rod cavity and a rodless cavity of the first counterweight oil cylinder. The second counterweight control valve is connected with a rod cavity and a rodless cavity of the second counterweight oil cylinder. The second counterweight control valve is used for controlling the communication state among the pressure oil output port of the pressure oil control valve, the oil tank, the rod cavity and the rodless cavity of the second counterweight oil cylinder.

According to the hydraulic control system provided by the invention, the pressure oil control valve is at least provided with an oil supply level and an unloading level. And an oil inlet of the pressure oil control valve is connected with the pressure oil source. And an oil return port of the pressure oil control valve is connected with the oil tank. In the oil supply level state, an oil inlet of the pressure oil control valve is communicated with a pressure output oil port of the pressure oil control valve; and in the unloading position state, an oil inlet of the pressure oil control valve is communicated with an oil return port of the pressure oil control valve.

According to the hydraulic control system provided by the invention, the first counterweight control valve is at least provided with a first counterweight lifting position and a first counterweight falling position. And under the state that the pressure oil control valve is switched to the oil supply position and the first balance weight control valve is switched to the first balance weight lifting position, the pressure oil source is communicated with a rod cavity of the first balance weight oil cylinder, and a rodless cavity of the first balance weight oil cylinder is communicated with the oil tank. And under the state that the pressure oil control valve is switched to the oil supply position and the first balance weight control valve is switched to the first balance weight falling position, the pressure oil source is communicated with the rodless cavity of the first balance weight oil cylinder, and the rod cavity of the first balance weight oil cylinder is communicated with the oil tank.

The second counterweight control valve is provided with at least a second counterweight lifting position and a second counterweight dropping position. And in the state that the pressure oil control valve is switched to the oil supply position and the second balance weight control valve is switched to the second balance weight lifting position, the pressure oil source is communicated with a rod cavity of the second balance weight oil cylinder, and a rodless cavity of the second balance weight oil cylinder is communicated with the oil tank. And under the state that the pressure oil control valve is switched to the oil supply position and the second balance weight control valve is switched to the second balance weight falling position, the pressure oil source is communicated with a rodless cavity of the second balance weight oil cylinder, and a rod cavity of the second balance weight oil cylinder is communicated with the oil tank.

According to the hydraulic control system provided by the invention, the first pressure sensor is arranged in the rod cavity of the first counterweight cylinder. A second pressure sensor is arranged in the rodless cavity of the first counterweight cylinder. And a third pressure sensor is arranged in a rod cavity of the second counterweight oil cylinder. And a fourth pressure sensor is arranged in the rodless cavity of the second counterweight oil cylinder. The control device is connected with the first balance weight control valve, the second balance weight control valve, the first pressure sensor, the second pressure sensor, the third pressure sensor and the fourth pressure sensor.

The control device is used for determining the weight of the first balancing weight based on the working position of the first balancing weight control valve, the detection results of the first pressure sensor and the second pressure sensor and the acting areas of the rod cavity and the rodless cavity of the first balancing weight oil cylinder, or determining the weight of the second balancing weight based on the working position of the second balancing weight control valve, the detection results of the third pressure sensor and the fourth pressure sensor and the acting areas of the rod cavity and the rodless cavity of the second balancing weight oil cylinder.

And the set pressure of the pressure regulating valve in different action states of the first counterweight cylinder under the weight of the corresponding first counterweight cylinder is adapted and set based on the working positions of the first counterweight control valve, the pressure oil control valve and the first counterweight cylinder with and without rod cavities, or the set pressure of the pressure regulating valve in different action states of the second counterweight cylinder under the weight of the corresponding second counterweight cylinder is adapted and set based on the working positions of the second counterweight control valve, the pressure oil control valve and the second counterweight cylinder with and without rod cavities.

According to the hydraulic control system provided by the invention, the hydraulic control system further comprises a swing oil cylinder and a swing control valve. The swing oil cylinder is connected with the counterweight oil cylinder group and used for adjusting the position of the counterweight oil cylinder group. The swing control valve is connected with a pressure output oil port of the pressure oil control valve, the oil tank and a rod cavity and a rodless cavity of the swing oil cylinder.

The swing control valve is at least provided with a swing extension position and a swing retraction position. And the pressure oil source is communicated with the rodless cavity of the swing oil cylinder, and the rod cavity of the swing oil cylinder is communicated with the oil tank in a state that the pressure oil control valve is switched to the oil supply position and the swing control valve is switched to the swing extending position. And when the pressure oil control valve is switched to the oil supply position and the swing control valve is switched to the swing contraction position, the pressure oil source is communicated with a rod cavity of the swing oil cylinder, and a rodless cavity of the swing oil cylinder is communicated with the oil tank.

According to the hydraulic control system provided by the invention, the fifth pressure sensor is arranged in the rod cavity and/or the rodless cavity of the swing oil cylinder. The control device is connected with the swing control valve and the fifth pressure sensor and is used for adjusting the set pressure of the pressure regulating valve in the contracted and/or stretched state of the swing oil cylinder under the weight of the corresponding balancing weight based on the working state of the balance weight oil cylinder group, the working position of the swing control valve and the detection result of the fifth pressure sensor.

According to a second aspect of the present invention, there is provided a method for weight detection and pressure adjustment of a counterweight based on the hydraulic control system described above, comprising the steps of:

switching working states of the counterweight control valve group and the pressure oil control valve to enable the counterweight oil cylinder group to fall in an idle load;

the counterweight oil cylinder group is connected with the counterweight block, and the working states of the counterweight control valve group and the pressure oil control valve are switched so as to lift the counterweight oil cylinder group in a loaded manner;

the control device determines the weight of the balancing weight and determines the set pressure of the pressure regulating valve in the load lifting state of the balancing weight oil cylinder group under the corresponding weight of the balancing weight;

switching working states of the counterweight control valve group and the pressure oil control valve to enable the counterweight oil cylinder group to fall under load;

the control device determines the set pressure of the pressure regulating valve in the load falling state of the counterweight cylinder group under the weight of the corresponding counterweight block.

According to the method for detecting the weight of the counterweight and adjusting the pressure, the control device determines the weight of the counterweight and determines the set pressure of the pressure regulating valve in the load lifting state of the counterweight cylinder group under the weight of the corresponding counterweight, and the method specifically comprises the following steps:

the control device judges that the counterweight cylinder group is in a loaded lifting state according to the pressure difference between the rod cavity and the rodless cavity of the counterweight cylinder group and the working states of the counterweight control valve group and the pressure oil control valve, and determines the weight of the counterweight block based on the pressure difference between the rodless cavity and the rod cavity of the counterweight cylinder group and the acting area difference between the rodless cavity and the rod cavity of the counterweight cylinder group;

And determining the set pressure of the pressure regulating valve in the load lifting state of the counterweight cylinder group under the weight of the corresponding counterweight block based on the pressure difference of the rodless cavity and the rod cavity of the counterweight cylinder group.

The step of determining the set pressure of the pressure regulating valve in the load falling state of the counterweight cylinder group under the weight of the corresponding counterweight by the control device specifically comprises the following steps:

the control device judges that the counterweight cylinder group is in a loaded falling state according to the pressure difference between the rod cavity and the rodless cavity of the counterweight cylinder group and the working states of the counterweight control valve group and the pressure oil control valve, and determines the set pressure of the pressure regulating valve in the loaded falling state of the counterweight cylinder group under the weight of the corresponding counterweight block based on the pressure difference between the rodless cavity and the rod cavity of the counterweight cylinder group.

According to the method for detecting the weight of the counterweight and debugging the pressure, provided by the invention, the method for detecting the weight of the counterweight and debugging the pressure further comprises the following steps:

the control device judges that the counterweight cylinder group is in a loaded state according to the pressure difference of the rod cavity and the rodless cavity of the counterweight cylinder group;

the control device determines the set pressure of the pressure regulating valve of the swing oil cylinder in the contracted and/or extended state under the weight of the corresponding balancing weight according to the working position of the swing control valve and the pressure difference of the rod cavity and the rodless cavity of the swing oil cylinder.

In the hydraulic control system provided by the invention, a pressure oil source is connected with an oil inlet of a pressure oil control valve, a pressure output oil port and an oil tank of the pressure oil control valve are connected with a counterweight control valve group, and the counterweight control valve group is connected with a rod cavity and a rodless cavity of a counterweight oil cylinder. When the oil inlet of the pressure oil control valve is communicated with the pressure output oil port, the pressure oil source can supply oil to the rod cavity or the rodless cavity of the counterweight oil cylinder group through the counterweight control valve group, and the rodless cavity or the oil in the rod cavity of the counterweight oil cylinder group can flow back to the oil tank through the counterweight control valve group.

A pressure regulating valve is arranged between the pressure output port of the pressure oil control valve and the counterweight control valve group. The control device is connected with the balance weight control valve group and the pressure oil control valve, and can determine the working state of the balance weight oil cylinder group according to the working states of the balance weight control valve group and the pressure oil control valve and the pressure difference of the rod cavity and the rodless cavity of the balance weight oil cylinder group. The working state of the counterweight cylinder group at least comprises no-load extending and falling, load shrinkage lifting and load extending and falling. For example, when the pressure oil source supplies oil to the rodless cavity of the counterweight cylinder group through the pressure oil control valve and the counterweight control valve and the rod cavity and the rodless cavity of the counterweight cylinder group have no pressure difference, the counterweight cylinder group is indicated to be in an idle-load extending and falling state; when the pressure oil source supplies oil to the rod cavity of the counterweight oil cylinder group through the pressure oil control valve and the counterweight control valve and the pressure difference exists between the rod cavity and the rodless cavity of the counterweight oil cylinder group, the counterweight oil cylinder group is indicated to be in a load shrinkage lifting state; when the pressure oil source supplies oil to the rodless cavity of the counterweight oil cylinder group through the pressure oil control valve and the counterweight control valve and the pressure difference exists between the rod cavity and the rodless cavity of the counterweight oil cylinder group, the counterweight oil cylinder group is indicated to be in a loaded extending and falling state.

In the working process, the counterweight cylinder group firstly needs to extend out and fall to the counterweight block in an idle mode, and then is connected with the counterweight block and then is contracted and lifted to the limit position in a load mode so as to finish counterweight installation. After the operation of the operation machine is finished, the counterweight cylinder group extends out and falls under load and releases the counterweight block. In the process of carrying, contracting and lifting the counterweight cylinder group, the control device can determine the weight of the counterweight block based on the pressure of the rodless cavity and the rod cavity of the counterweight cylinder group and the action area of the rodless cavity and the rod cavity of the counterweight cylinder group. Specifically, the weight of the balancing weight=the pressure of the rod cavity of the balance weight oil cylinder group×the acting area of the rod cavity of the balance weight oil cylinder group-the pressure of the rodless cavity of the balance weight oil cylinder group×the acting area of the rodless cavity of the balance weight oil cylinder group.

In the process of carrying, contracting and lifting the counterweight cylinder group, the control device can determine the set pressure value of the pressure regulating valve under the weight of the counterweight block based on the pressure of the rod cavity of the counterweight cylinder group. The control device can accurately adapt to the set pressure of the pressure regulating valve in the load shrinkage lifting state of the counterweight cylinder group under the weight of the counterweight cylinder group based on the pressure of the rod cavity of the counterweight cylinder group. In the subsequent working process, when the counterweight blocks with corresponding weight are mounted on the counterweight cylinder group to perform lifting action, the control device is convenient to automatically adjust the working pressure of the pressure regulating valve to a corresponding set pressure value. Similarly, in the process of the load extension and falling of the counterweight cylinder group, the control device can accurately adapt the set pressure of the pressure regulating valve in the load extension and falling state of the counterweight cylinder group based on the rodless cavity pressure of the counterweight cylinder group. In the subsequent working process, when the counterweight blocks with corresponding weight are mounted on the counterweight cylinder group to perform falling actions, the control device is convenient to automatically adjust the working pressure of the pressure regulating valve to a corresponding set pressure value.

Through the structure, the control device can detect the weight of the balancing weight mounted on the balancing weight oil cylinder group, and the set pressure of the pressure regulating valve in the process of lifting and falling under the load of the balancing weight oil cylinder group under the weight of the corresponding balancing weight is relatively accurately adapted, so that the set pressure of the pressure regulating valve can be accurately matched and set according to different working conditions in the subsequent working process. Therefore, high-pressure overflow waste caused in the working process of the hydraulic control system can be reduced, overflow heating is reduced, the service life of hydraulic components is prolonged, and meanwhile, the stability of the counterweight cylinder group in the load lifting process can be improved.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic system diagram of a hydraulic control system provided by the present invention;

FIG. 2 is a flow chart of the method for detecting weight of counterweight and adjusting pressure provided by the invention;

reference numerals:

100. a first counterweight cylinder; 110. a first counterweight control valve; 111. a first counterweight lifting position; 112. a first counterweight falling position; 200. a second counterweight cylinder; 210. a second counterweight control valve; 211. a second counterweight lifting position; 212. a second counterweight falling position; 310. a source of pressurized oil; 320. an oil tank; 330. a pressure oil control valve; 331. oil supply level; 332. unloading position; 400. a pressure regulating valve; 510. a first pressure sensor; 520. a second pressure sensor; 530. a third pressure sensor; 540. a fourth pressure sensor; 600. swinging the oil cylinder; 610. a swing control valve; 611. swinging the extension position; 612. and (5) swinging and shrinking.

Detailed Description

Embodiments of the present invention are described in further detail below with reference to the accompanying drawings and examples. The following examples are illustrative of the invention but are not intended to limit the scope of the invention.

In the description of the embodiments of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "first", "second", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the embodiments of the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the embodiments of the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

In describing embodiments of the present invention, it should be noted that, unless explicitly stated and limited otherwise, the terms "coupled," "coupled," and "connected" should be construed broadly, and may be either a fixed connection, a removable connection, or an integral connection, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the embodiments of the present invention will be understood by those of ordinary skill in the art according to specific circumstances.

In embodiments of the invention, unless expressly specified and limited otherwise, a first feature "up" or "down" on a second feature may be that the first and second features are in direct contact, or that the first and second features are in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the embodiments of the present invention. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples, as well as features of various embodiments or examples, described in this specification may be combined and combined to further clarify the objects, aspects and advantages of embodiments of the present invention, without departing from the spirit and scope of the invention, and it should be apparent that the described embodiments are some, but not all, embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

A hydraulic control system, a counterweight weight detection method, and a pressure adjustment method according to embodiments of the invention are described below with reference to fig. 1 and 2. It should be understood that the following description is only illustrative of the embodiments of the invention and is not intended to limit the invention in any way.

An embodiment of the first aspect of the present invention provides a hydraulic control system, as shown in fig. 1, which includes a counterweight cylinder group, a counterweight control valve group, a pressure oil control valve 330, a pressure regulating valve 400, a control device, a pressure oil source 310, and a tank 320.

Wherein the pressure oil source 310 is connected to a pressure oil control valve 330. The pressure oil control valve 330 and the oil tank 320 are connected to the balance weight control valve group. The balance weight control valve group is connected with the rod cavity and the rodless cavity of the balance weight oil cylinder group. The pressure oil control valve 330 is used to control the communication state between the pressure oil source 310 and the balance weight control valve group. The balance weight control valve group is used for controlling the communication state among the pressure oil control valve 330, the oil tank 320 and the rod cavity and the rodless cavity of the balance weight oil cylinder group.

The pressure regulating valve 400 is connected between the pressure output port of the pressure oil control valve 330 and the counterweight control valve group. The control device is connected to the balance weight control valve group, the pressure oil control valve 330, and the pressure regulating valve 400. The control device is used for determining the weight of the balancing weight based on the working state of the balancing weight oil cylinder group, the pressure of the rodless cavity and the rod-containing cavity of the balancing weight oil cylinder group and the action area of the rodless cavity and the rod-containing cavity of the balancing weight oil cylinder group, and adapting and adjusting the set pressure of the pressure regulating valve 400 of the balancing weight oil cylinder group in different working states based on the pressure of the rod-containing cavity and the rodless cavity of the balancing weight oil cylinder group.

In the hydraulic control system provided by the invention, a pressure oil source 310 is connected with an oil inlet of a pressure oil control valve 330, a pressure output oil port of the pressure oil control valve 330 and an oil tank 320 are connected with a counterweight control valve group, and the counterweight control valve group is connected with a rod cavity and a rodless cavity of a counterweight oil cylinder. When the oil inlet of the pressure oil control valve 330 is communicated with the pressure output oil port, the pressure oil source 310 can supply oil to the rod cavity or the rodless cavity of the counterweight cylinder group through the counterweight control valve group, and the rodless cavity or the oil in the rod cavity of the counterweight cylinder group can flow back into the oil tank 320 through the counterweight control valve group.

A pressure regulating valve 400 is provided between the pressure output port of the pressure oil control valve 330 and the balance weight control valve group. The control device is connected with the balance weight control valve group and the pressure oil control valve 330, and the control device can determine the working state of the balance weight oil cylinder group according to the working states of the balance weight control valve group and the pressure oil control valve 330 and the pressure difference of the rod cavity and the rodless cavity of the balance weight oil cylinder group. The working state of the counterweight cylinder group at least comprises no-load extending and falling, load shrinkage lifting and load extending and falling. For example, when the pressure oil source 310 supplies oil to the rodless cavity of the counterweight cylinder group through the pressure oil control valve 330 and the counterweight control valve, and the rod cavity and the rodless cavity of the counterweight cylinder group have no pressure difference, it indicates that the counterweight cylinder group is in an idle extending and falling state; when the pressure oil source 310 supplies oil to the rod cavity of the counterweight cylinder group through the pressure oil control valve 330 and the counterweight control valve and the pressure difference exists between the rod cavity and the rodless cavity of the counterweight cylinder group, the counterweight cylinder group is indicated to be in a load shrinkage lifting state; when the pressure oil source 310 supplies oil to the rodless cavity of the counterweight cylinder group through the pressure oil control valve 330 and the counterweight control valve, and a pressure difference exists between the rod cavity and the rodless cavity of the counterweight cylinder group, the counterweight cylinder group is indicated to be in a loaded extending and falling state.

In the process of carrying, contracting and lifting the counterweight cylinder group, the control device can determine the set pressure value of the pressure regulating valve 400 under the weight of the counterweight block based on the pressure of the rod cavity of the counterweight cylinder group. Namely, the control device can accurately adapt to the set pressure of the pressure regulating valve 400 in the load shrinkage lifting state of the counterweight cylinder group under the weight of the counterweight cylinder group based on the pressure of the rod cavity of the counterweight cylinder group. In the subsequent working process, when the counterweight cylinder group mounts the counterweight blocks with corresponding weight for lifting action, the control device is convenient to automatically adjust the working pressure of the pressure regulating valve 400 to the corresponding set pressure value. Similarly, in the process of the load extension and falling of the counterweight cylinder group, the control device can accurately adapt the set pressure of the pressure regulating valve 400 in the load extension and falling state of the counterweight cylinder group based on the rodless cavity pressure of the counterweight cylinder group. In the subsequent working process, when the counterweight blocks with corresponding weight are mounted on the counterweight cylinder group to perform the falling action, the control device is convenient to automatically adjust the working pressure of the pressure regulating valve 400 to the corresponding set pressure value.

Through the structure, the control device can detect the weight of the balancing weight mounted on the balancing weight oil cylinder group, and the set pressure of the pressure regulating valve 400 in the process of lifting and falling under the load of the balancing weight oil cylinder group under the weight of the corresponding balancing weight is relatively accurately adapted, so that the set pressure of the pressure regulating valve 400 can be accurately matched and regulated according to different working conditions in the subsequent working process. Therefore, high-pressure overflow waste caused in the working process of the hydraulic control system can be reduced, overflow heating is reduced, the service life of hydraulic components is prolonged, and meanwhile, the stability of the counterweight cylinder group in the load lifting process can be improved.

In one embodiment of the present invention, the set of counterweight cylinders includes a first counterweight cylinder 100 and a second counterweight cylinder 200. The balance weight control valve group includes a first balance weight control valve 110 and a second balance weight control valve 210.

The pressure output port of the pressure oil control valve 330 and the oil tank 320 are connected to the first and second balance weight control valves 110 and 210. The first balance weight control valve 110 is connected to a rod chamber and a rodless chamber of the first balance weight cylinder 100. The first balance weight control valve 110 is used for controlling the communication state among the pressure output port of the pressure oil control valve 330, the oil tank 320, the rod-shaped cavity and the rodless cavity of the first balance weight cylinder 100. The second balance weight control valve 210 is connected to the rod-shaped chamber and the rodless chamber of the second balance weight cylinder 200. The second balance weight control valve 210 is used for controlling the communication state among the pressure output port of the pressure oil control valve 330, the oil tank 320, the rod cavity and the rodless cavity of the second balance weight cylinder 200.

In one embodiment of the invention, the pressure oil control valve 330 is provided with at least a supply oil level 331 and an unloading position 332. An oil inlet of the pressure oil control valve 330 is connected to the pressure oil source 310. The return port of the pressure oil control valve 330 is connected to the oil tank 320. In the state of the oil supply level 331, the oil inlet of the pressure oil control valve 330 is communicated with the pressure output oil port of the pressure oil control valve 330; in the state of the unloading position 332, the oil inlet of the pressure oil control valve 330 communicates with the oil return port of the pressure oil control valve 330.

Further, in one embodiment of the present invention, the first weight control valve 110 is provided with at least a first weight lifting position 111 and a first weight lowering position 112. In a state where the pressure oil control valve 330 is switched to the oil supply position 331 and the first counterweight control valve 110 is switched to the first counterweight lifting position 111, the pressure oil source 310 is communicated with the rod chamber of the first counterweight cylinder 100, and the rodless chamber of the first counterweight cylinder 100 is communicated with the oil tank 320; in a state where the pressure oil control valve 330 is switched to the oil supply position 331 and the first counterweight control valve 110 is switched to the first counterweight drop position 112, the pressure oil source 310 communicates with the rodless chamber of the first counterweight cylinder 100, and the rod chamber of the first counterweight cylinder 100 communicates with the oil tank 320.

The second weight control valve 210 is provided with at least a second weight lifting position 211 and a second weight dropping position 212. In a state where the pressure oil control valve 330 is switched to the oil supply position 331 and the second counterweight control valve 210 is switched to the second counterweight lifting position 211, the pressure oil source 310 is communicated with the rod chamber of the second counterweight cylinder 200, and the rodless chamber of the second counterweight cylinder 200 is communicated with the oil tank 320; in a state where the pressure oil control valve 330 is switched to the oil supply position 331 and the second counterweight control valve 210 is switched to the second counterweight drop position 212, the pressure oil source 310 communicates with the rodless chamber of the second counterweight cylinder 200, and the rod chamber of the second counterweight cylinder 200 communicates with the oil tank 320.

Specifically, as shown in fig. 1, the pressure oil control valve 330 is a two-position three-way electromagnetic directional valve, which includes an oil inlet, an oil return port, and a pressure output port. The first counterweight control valve 110 is a first three-position four-way electromagnetic directional valve, and includes a first working oil port, a second working oil port, a third working oil port, and a fourth working oil port, and the second counterweight control valve 210 includes a second three-position four-way electromagnetic directional valve, and includes a fifth working oil port, a sixth working oil port, a seventh working oil port, and an eighth working oil port. The oil inlet of the two-position three-way electromagnetic directional valve is connected with the pressure oil source 310. The source of pressurized oil 310 includes, but is not limited to, a hydraulic pump. The oil return port of the two-position three-way electromagnetic directional valve is connected with the oil tank 320. The pressure output oil port of the two-position three-way electromagnetic directional valve is respectively connected with the first working oil port of the first three-position four-way electromagnetic directional valve and the fifth working oil port of the second three-position four-way electromagnetic directional valve. The second working oil port of the first three-position four-way electromagnetic directional valve is connected with the oil tank 320, the third working oil port is connected with the rodless cavity of the first counterweight oil cylinder 100, and the fourth working oil port is connected with the rod cavity of the first counterweight oil cylinder 100. The sixth working oil port of the second three-position four-way electromagnetic directional valve is connected with the oil tank 320, the seventh working oil port is connected with the rodless cavity of the second counterweight oil cylinder 200, and the eighth working oil port is connected with the rod cavity of the second counterweight oil cylinder 200.

The two-position three-way electromagnetic directional valve is provided with an oil supply level 331 and an unloading level 332, the electromagnetic control end of the two-position three-way electromagnetic directional valve is DT01, when the DT01 is powered, the two-position three-way electromagnetic directional valve is switched to the oil supply level 331, and the oil inlet of the two-position three-way electromagnetic directional valve is communicated with the pressure output oil port, so that the pressure oil source 310 can be supplied to the first balance weight control valve 110 and the second balance weight control valve 210. When the DT01 is powered off, the two-position three-way electromagnetic directional valve is switched to the unloading position 332, and the pressure oil source 310 is unloaded into the oil tank 320.

The first three-position four-way electromagnetic directional valve may be provided with a first weight stop position in addition to the first weight lifting position 111 and the first weight dropping position 112. Two electromagnetic control ends of the first three-position four-way electromagnetic reversing valve are DT1 and DT2 respectively. When the DT1 is powered on, a first working oil port of the first three-position four-way electromagnetic directional valve is communicated with a fourth working oil port, a second working oil port of the first three-position four-way electromagnetic directional valve is communicated with a third working oil port, if the DT01 is powered on simultaneously at this time, the pressure oil source 310 can be supplied to the rod cavity of the first counterweight cylinder 100 through the two-position three-way electromagnetic directional valve and the first three-position four-way electromagnetic directional valve, and the oil in the rodless cavity of the first counterweight cylinder 100 can flow back into the oil tank 320, so that the piston rod of the first counterweight cylinder 100 is contracted and lifted. When the DT2 is powered on, a first working oil port of the first three-position four-way electromagnetic directional valve is communicated with a third working oil port, a second working oil port of the first three-position four-way electromagnetic directional valve is communicated with a fourth working oil port, if the DT01 is powered on simultaneously at this time, the pressure oil source 310 can be supplied to the rodless cavity of the first counterweight cylinder 100 through the two-position three-way electromagnetic directional valve and the first three-position four-way electromagnetic directional valve, the oil in the rod cavity of the first counterweight cylinder 100 can flow back into the oil tank 320, and the piston rod of the first counterweight cylinder 100 stretches out and falls.

The second balance weight control valve 210 operates similarly and is not described in detail herein. For example, two electromagnetic control ends of the second three-position four-way electromagnetic reversing valve are DT3 and DT4 respectively. When DT3 and DT01 are powered on simultaneously, the pressure oil source 310 can be supplied to the rod cavity of the second counterweight cylinder 200 through the two-position three-way electromagnetic directional valve and the second three-position four-way electromagnetic directional valve, the oil in the rod-free cavity of the second counterweight cylinder 200 can flow back to the oil tank 320, and the piston rod of the second counterweight cylinder 200 is contracted and lifted. When DT2 and DT01 are simultaneously powered on, the pressure oil source 310 can be supplied to the rodless cavity of the second counterweight cylinder 200 through the two-position three-way electromagnetic directional valve and the second three-position four-way electromagnetic directional valve, and the oil in the rod cavity of the second counterweight cylinder 200 can flow back to the oil tank 320, and the piston rod of the second counterweight cylinder 200 stretches out and falls.

As can be seen from the above-described embodiments, in the hydraulic control system, the first balancing weight is connected to the first balancing weight cylinder 100, and the second balancing weight cylinder 200 is connected to the second balancing weight cylinder. The first and second balancing cylinders 100 and 200 are independent of each other to synchronously or independently adjust the height positions of the first and second balancing weights. When the first balancing weight and the second balancing weight are in a state of vertical position deflection, single-side position adjustment and deviation correction are convenient to conduct.

In one embodiment of the present invention, as shown in fig. 1, a rod cavity of the first balance weight cylinder 100 is provided with a first pressure sensor 510, a rod-less cavity of the first balance weight cylinder 100 is provided with a second pressure sensor 520, a rod cavity of the second balance weight cylinder 200 is provided with a third pressure sensor 530, and a rod-less cavity of the second balance weight cylinder 200 is provided with a fourth pressure sensor 540. The control device is connected to the first weight control valve 110, the second weight control valve 210, the first pressure sensor 510, the second pressure sensor 520, the third pressure sensor 530, and the fourth pressure sensor 540.

The control device is used for determining the weight of the first balancing weight based on the working position of the first balancing weight control valve 110, the detection results of the first pressure sensor 510 and the second pressure sensor 520 and the acting areas of the rod cavity and the rodless cavity of the first balancing weight cylinder 100, or determining the weight of the second balancing weight based on the working position of the second balancing weight control valve 210, the detection results of the third pressure sensor 530 and the fourth pressure sensor 540 and the acting areas of the rod cavity and the rodless cavity of the second balancing weight cylinder 200.

And, the set pressure of the pressure regulating valve 400 in different operation states of the first balance weight cylinder 100 under the corresponding weight of the first balance weight is adapted and set based on the working positions of the first balance weight control valve 110 and the pressure oil control valve 330 and the pressure of the rod cavity and the rodless cavity of the first balance weight cylinder 100, or the set pressure of the pressure regulating valve 400 in different operation states of the second balance weight cylinder 200 under the corresponding weight of the second balance weight is adapted and set based on the working positions of the second balance weight control valve 210 and the pressure oil control valve 330 and the pressure of the rod cavity and the rodless cavity of the second balance weight cylinder 200.

For example, the control device determines that the first ram 100 is in the load-lifting state based on the fact that the pressure oil control valve 330 is located at the oil supply level 331, the first ram control valve 110 is located at the first ram lifting position 111, and the product of the detection result of the first pressure sensor 510 and the area of the ram cavity of the first ram 100 is larger than the product of the detection result of the second pressure sensor 520 and the area of the ram cavity of the first ram 100. At this time, the control device determines the weight of the first counterweight based on the detection results of the first pressure sensor 510 and the second pressure sensor 520 and the acting areas of the rod chamber and the rodless chamber of the first counterweight cylinder 100. First balancing weight gravity =

The first weight cylinder 100 has a rod cavity pressure x the first weight cylinder 100 has a rod cavity active area-the first weight cylinder 100 has no rod cavity pressure x the first weight cylinder 100 has no rod cavity active area. In this embodiment, the first weight force=the detection result of the first pressure sensor 510×the rod cavity acting area of the first weight cylinder 100—the second pressure sensor 520 detects the structure×the rod cavity-free acting area of the first weight cylinder 100.

During the load lifting process of the first counterweight cylinder 100, the control device adapts the set pressure value of the pressure regulating valve 400 during the load lifting process of the first counterweight cylinder 100 under the corresponding weight of the first counterweight based on the pressure detection result of the first pressure sensor 510. Here, the pressure regulating valve 400 has a certain pressure loss. When determining the set pressure of the pressure regulating valve 400, the pressure loss of the pressure regulating valve 400 needs to be estimated, and the pressure loss value can be determined empirically. For example, under the above-described working conditions, the set pressure value of the pressure regulating valve 400=the pressure of the rod chamber of the first ram 100+the pressure loss, and in this embodiment, the set pressure value of the pressure regulating valve 400=the detection result of the first pressure sensor 510+the pressure loss.

The control device determines that the first counterweight cylinder 100 is in the loaded drop state based on the fact that the pressure oil control valve 330 is located at the oil supply level 331, the first counterweight control valve 110 is located at the first counterweight drop position 112, and the product of the detection result of the first pressure sensor 510 and the action area of the rod cavity of the first counterweight cylinder 100 is larger than the product of the detection result of the second pressure sensor 520 and the action area of the rod cavity of the first counterweight cylinder 100.

During the first counterweight cylinder 100 is in the load falling process, the control device adapts the set pressure value of the pressure regulating valve 400 when the first counterweight cylinder 100 is in the load falling process under the corresponding first counterweight weight based on the pressure detection result of the second pressure sensor 520. Also, there is some pressure loss of the pressure regulating valve 400. Under the above-described working conditions, the set pressure value of the pressure regulating valve 400=the pressure of the rodless chamber of the first ram 100+the pressure loss, and in this embodiment, the set pressure value of the pressure regulating valve 400=the detection result of the second pressure sensor 520+the pressure loss.

The weight detection process of the second balancing weight and the pressure adaptation and adjustment process of the pressure regulating valve 400 in the load lifting and load falling process of the second balancing weight cylinder 200 are the same as the weight detection process of the first balancing weight and the pressure adaptation and adjustment process of the pressure regulating valve 400 in the load lifting and load falling process of the first balancing weight cylinder 100. In the actual debugging process, the first side may be measured and debugged first, or the second side may be measured and debugged first. Meanwhile, the first balancing weight and the second balancing weight with different weights can be measured and debugged for multiple times, and in the subsequent working process, the control device can automatically set and match the working pressure of the pressure regulating valve 400 under different working conditions.

When the first counterweight cylinder 100 and the second counterweight cylinder 200 act simultaneously, the control device selects the larger set pressure value in the independent debugging process of the first counterweight cylinder 100 and the second counterweight cylinder 200 as the set pressure value of the pressure regulating valve 400 under the current working condition.

For example, the pressure regulating valve 400 is an electric proportional relief valve, and the control device controls the magnitude of the current signal input to the electric proportional relief valve to regulate the magnitude of the pressure required to be set.

In one embodiment of the present invention, the hydraulic control system further includes a swing cylinder 600 and a swing control valve 610. The swing cylinder 600 is connected to the counterweight cylinder group and is used to adjust the position of the counterweight cylinder group. The swing control valve 610 is connected to the pressure output port of the pressure oil control valve 330, the oil tank 320, and the rod-and rodless chambers of the swing cylinder 600.

The swing control valve 610 is provided with at least a swing extension 611 and a swing retraction 612. In a state where the pressure oil control valve 330 is switched to the oil supply position 331 and the swing control valve 610 is switched to the swing extension position 611, the pressure oil source 310 is communicated with the rodless cavity of the swing cylinder 600, and the rod cavity of the swing cylinder 600 is communicated with the oil tank 320; in a state where the pressure oil control valve 330 is switched to the oil supply position 331 and the swing control valve 610 is switched to the swing contraction position 612, the pressure oil source 310 communicates with the rod chamber of the swing cylinder 600, and the rodless chamber of the swing cylinder 600 communicates with the oil tank 320.

Further, in one embodiment of the present invention, the rod-shaped cavity and/or the rodless cavity of the swing cylinder 600 is equipped with a fifth pressure sensor. The control device is connected to the swing control valve 610 and the fifth pressure sensor, and is configured to adjust the set pressure of the pressure regulating valve 400 in the contracted and/or extended state of the swing cylinder 600 according to the weight of the corresponding balancing weight based on the working state of the balancing cylinder group, the working position of the swing control valve 610, and the detection result of the fifth pressure sensor.

For example, as shown in fig. 1, in this embodiment, the swing cylinder 600 includes a first swing cylinder and a second swing cylinder. The rod cavity of the first swing cylinder is communicated with the rod cavity of the second swing cylinder, and the rod-free cavity of the first swing cylinder is communicated with the rod-free cavity of the second swing cylinder. The first and second counterweight cylinders 100 and 200 are symmetrically disposed on the first and second sides of the work machine. The first swing cylinder and the second swing cylinder are symmetrically arranged on the first side and the second side of the working machine, a piston rod of the first swing cylinder is connected with the first counterweight cylinder 100, a piston rod of the second swing cylinder is connected with the second counterweight cylinder 200, and the positions of the first counterweight cylinder 100 and the second counterweight cylinder 200 can be synchronously and symmetrically adjusted by the first swing cylinder 600 and the second swing cylinder 600, and then the positions of the first counterweight block and the second counterweight block are adjusted. The control valve of the swing cylinder 600 is a third three-position four-way electromagnetic reversing valve, which is provided with a swing extension position 611, a swing contraction position 612 and a swing cut-off position. Two electromagnetic control ends of the third three-position four-way electromagnetic reversing valve are DT5 and DT6 respectively, the power-on states of DT5 and DT6 are controlled and controlled, and the working position of the third three-position four-way electromagnetic reversing valve is switched. For example, DT5 is powered, the third three-position four-way electromagnetic directional valve is switched to the swing extended position 611, dt6 is powered, and the third three-position four-way electromagnetic directional valve is switched to the swing retracted position 612. And when the DT5 and the DT6 are powered off simultaneously, the third three-position four-way electromagnetic reversing valve is switched to the swing cut-off position.

The control device can adjust the set pressure of the pressure regulating valve 400 in the contracted and/or extended state of the swing cylinder 600 according to the weight of the corresponding weight block based on the operating state of the weight cylinder group, the operating position of the swing control valve 610, and the detection result of the fifth pressure sensor.

Specifically, the precondition for performing the pressure adaptation process of the pressure control valve in the working state of the telescopic oil cylinder is that the counterweight oil cylinder group is in a loaded state, and the loaded state of the counterweight oil cylinder group is judged according to the method. For example, a fifth pressure sensor is provided in the rod chamber of the swing cylinder 600, and the pressure oil source 310 supplies oil to the rod chamber of the swing cylinder 600 through the pressure oil control valve 330 and the swing control valve 610 to retract the piston rod of the swing cylinder 600. At this time, during the current load-carrying capacity, the set pressure of the pressure regulating valve 400=the rod chamber pressure+the pressure loss of the swing cylinder 600 during the contraction operation of the swing cylinder 600. In this embodiment, the set pressure of the pressure regulating valve 400=the detection result of the fifth pressure sensor+the pressure loss. The set pressure of the pressure regulating valve 400 in the extension operation of the swing cylinder 600 is the same as the set value described above under the same belt load.

In addition, the hydraulic control system is also provided with an alarm system. The alarm system is connected with the control device. For example, in the load lifting process of the first counterweight cylinder 100, if the difference between the pressure of the rod cavity of the first counterweight cylinder 100 and the set pressure of the pressure regulating valve 400 corresponding to the current state is not equal to the preset pressure loss value, the control device starts the alarm system to prompt the staff to reset or adapt to the set pressure of the pressure regulating valve 400.

An embodiment of the second aspect of the present invention provides a method for detecting weight of a counterweight and adjusting pressure based on the hydraulic control system, including the steps of:

switching the working states of the counterweight control valve group and the pressure oil control valve 330 to enable the counterweight cylinder group to fall under no load;

connecting the counterweight cylinder group with the counterweight block, and switching the working states of the counterweight control valve group and the pressure oil control valve 330 so as to lift the counterweight cylinder group in a loaded manner;

the control device determines the weight of the balancing weight and determines the set pressure of the pressure regulating valve 400 in the load lifting state of the balancing weight cylinder group under the corresponding weight of the balancing weight;

switching the working states of the counterweight control valve group and the pressure oil control valve 330 to enable the counterweight cylinder group to fall under load;

The control device determines the set pressure of the pressure regulating valve 400 in the loaded falling state of the counterweight cylinder group under the weight of the corresponding counterweight.

Further, in an embodiment of the present invention, the step of determining the weight of the balancing weight and determining the set pressure of the pressure regulating valve 400 in the on-load lifting state of the balancing cylinder group under the weight of the balancing weight by the control device specifically includes:

the control device judges that the counterweight cylinder group is in a loaded lifting state according to the pressure difference between the rod cavity and the rodless cavity of the counterweight cylinder group and the working states of the counterweight control valve group and the pressure oil control valve 330, and determines the weight of the counterweight block based on the pressure difference between the rodless cavity and the rod cavity of the counterweight cylinder group and the acting area difference between the rodless cavity and the rod cavity of the counterweight cylinder group;

the set pressure of the pressure regulating valve 400 in the load lifting state of the counterweight cylinder group under the weight of the corresponding counterweight block is determined based on the pressure difference of the rodless cavity and the rod cavity of the counterweight cylinder group.

The step of determining the set pressure of the pressure regulating valve 400 in the loaded falling state of the counterweight cylinder group under the weight of the corresponding counterweight by the control device specifically comprises the following steps:

the control device determines that the counterweight cylinder group is in the loaded falling state according to the pressure difference between the rod cavity and the rodless cavity of the counterweight cylinder group and the working states of the counterweight control valve group and the pressure oil control valve 330, and determines the set pressure of the pressure regulating valve 400 in the loaded falling state of the counterweight cylinder group under the weight of the corresponding counterweight block based on the pressure difference between the rodless cavity and the rod cavity of the counterweight cylinder group.

Further, the counterweight weight detection and pressure debugging method further comprises:

the control device determines the set pressure of the pressure regulating valve 400 in the contracted and/or extended state of the swing cylinder 600 under the weight of the corresponding balancing weight according to the working position of the swing control valve 610 and the pressure difference between the rod cavity and the rodless cavity of the swing cylinder 600.

Specifically, for example, the first counterweight side is first debugged, during the debugging process, first, the pressure oil control valve 330 is switched to the oil supply position 331, the first counterweight control valve 110 is switched to the first counterweight falling position 112, at this time, the pressure oil source 310 supplies oil to the rodless cavity of the first counterweight cylinder 100 through the pressure oil control valve 330 and the first counterweight control valve 110, and the first counterweight cylinder 100 falls to the first counterweight position under no load and is connected to the first counterweight.

Subsequently, the first counterweight control valve 110 is switched to the first counterweight lifting position 111, the pressure oil source 310 supplies oil to the rod cavity of the first counterweight cylinder 100 through the pressure oil control valve 330 and the first counterweight control valve 110, and the first counterweight cylinder 100 drives the first counterweight to lift upwards, i.e. the first counterweight cylinder 100 lifts with load.

The control device determines that the first counterweight cylinder 100 is in the load lifting state based on the pressure oil control valve 330 being in the oil supply level 331, the first counterweight cylinder 100 being in the first counterweight lifting position 111, and there being a pressure difference between the rod-shaped chamber and the rodless chamber of the first counterweight cylinder 100. Based on determining that the first counterweight cylinder 100 is in the load lifting state, a first counterweight weight detection process is started. Specifically, in the process of carrying and lifting the first counterweight cylinder 100, the control device determines the weight of the first counterweight through the pressure difference between the rodless cavity and the rod cavity of the first counterweight cylinder 100 and the acting area difference between the rodless cavity and the rod cavity of the first counterweight cylinder 100. I.e. the weight of the first balancing weight = the rod cavity pressure of the first balancing cylinder 100 x the rod cavity area of the first balancing cylinder 100-the rod cavity-free pressure of the first balancing cylinder 100 x the rod cavity-free area of the first balancing cylinder 100.

Based on determining that the first counterweight cylinder 100 is in the load lifting state and determining the weight force of the first counterweight, the set pressure value of the pressure regulating valve 400 in the current state is specifically adapted. Specifically, in the present state, the set value of the pressure regulating valve 400=the pressure of the rod chamber+the pressure loss of the first counterweight cylinder 100.

The first counterweight control valve 110 is switched to the first counterweight falling position 112, the pressure oil source 310 supplies oil to the rodless cavity of the first counterweight cylinder 100 through the pressure oil control valve 330 and the first counterweight control valve 110, and the first counterweight cylinder 100 drives the first counterweight to fall downwards, i.e. the first counterweight cylinder 100 falls under load.

The control device determines that the first counterweight cylinder 100 is in the loaded drop state based on the pressure oil control valve 330 being in the oil supply level 331, the first counterweight cylinder 100 being in the first counterweight drop position 112, and a pressure difference being present between the rod-shaped chamber and the rodless chamber of the first counterweight cylinder 100. Based on the determination that the first counterweight cylinder 100 is in the load-falling state, the set pressure adaptation process of the pressure regulating valve 400 in the current state is started. Specifically, in the current state, the set value of the pressure regulating valve 400=the rodless cavity pressure+pressure loss of the first counterweight cylinder 100.

Thus, the weight detection of the first balancing weight and the set pressure adaptation of the pressure regulating valve 400 in the process of lifting and falling with load of the first balancing weight cylinder 100 under the weight of the balancing weight are completed.

Then, the weight detection of the second balancing weight and the set pressure adaptation of the pressure regulating valve 400 during the load lifting and load falling of the second balancing cylinder 200 under the corresponding balancing weight are performed in a similar manner.

In the following operation, if the first and second counterweight cylinders 100 and 200 are operated simultaneously, the control device selects one of the first and second side pressure adaptations having a larger set value as the pressure set value of the pressure regulating valve 400 in this state.

Thereafter, the control device determines that the counterweight cylinder group is in the loaded state based on the pressure difference between the rod chamber and the rodless chamber of the first counterweight cylinder 100 and/or the pressure difference between the rod chamber and the rodless chamber of the second counterweight cylinder 200, and determines that the swing cylinder 600 is in the swing state based on the swing control valve 610 being in the swing extension position 611 or the swing retraction position 612. In the case where the above-described states are simultaneously satisfied, the set pressure value of the pressure regulating valve 400 in the current state is specifically adapted. Specifically, in the present state, the set value of the pressure regulating valve 400=the pressure of the rod chamber of the swing cylinder 600/the pressure of the rod chamber of the swing cylinder 600+the pressure loss.

Thus, the debugging work of the hydraulic control system is completed. In the subsequent working process, the control device can automatically detect the weight of the balancing weight, and can automatically set the set pressure value of the pressure regulating valve 400 based on different working conditions.

An embodiment of a third aspect of the present invention provides a working machine including the hydraulic control system described above or weight detection and pressure adjustment using the counterweight weight detection and pressure adjustment method described above.

For example, the work machine includes a crane.

Further, since the work machine includes the hydraulic control system as described above, it also has the advantages as described above.

Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present invention, and are not limiting; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. The hydraulic control system is characterized by comprising a counterweight oil cylinder group, a counterweight control valve group, a pressure oil control valve, a pressure regulating valve, a control device, a pressure oil source and an oil tank;

the pressure oil source is connected with the pressure oil control valve, the pressure oil control valve and the oil tank are connected with the balance weight control valve bank, the balance weight control valve bank is connected with a rod cavity and a rodless cavity of the balance weight oil cylinder set, the pressure oil control valve is used for controlling the communication state between the pressure oil source and the balance weight control valve bank, and the balance weight control valve bank is used for controlling the communication state among the pressure oil control valve, the oil tank, the rod cavity and the rodless cavity of the balance weight oil cylinder set;

The pressure oil control valve comprises a pressure oil output port, a pressure oil control valve, a pressure regulating valve, a control device, a balance weight oil cylinder group, a balance weight control valve, a control device and a balance weight oil cylinder group, wherein the pressure oil output port of the pressure oil control valve is connected with the balance weight control valve, the control device is connected with the balance weight control valve, the pressure oil control valve and the pressure regulating valve, the control device is used for determining the weight of the balance weight based on the working state of the balance weight oil cylinder group, the pressure of a rodless cavity and a rod cavity of the balance weight oil cylinder group and the action area of the rodless cavity and the rod cavity of the balance weight oil cylinder group, and setting pressure of the pressure regulating valve in different working states of the balance weight oil cylinder group based on the pressure adaptation of the rod cavity and the rodless cavity of the balance weight oil cylinder group and the pressure regulating valve.

2. The hydraulic control system of claim 1, wherein the set of counterbalance cylinders includes a first counterbalance cylinder and a second counterbalance cylinder, the set of counterbalance control valves includes a first counterbalance control valve and a second counterbalance control valve,

wherein the pressure oil outlet of the pressure oil control valve and the oil tank are connected with the first balance weight control valve and the second balance weight control valve, the first balance weight control valve is connected with a rod cavity and a rodless cavity of the first balance weight oil cylinder, the first balance weight control valve is used for controlling the communication state among the pressure oil outlet of the pressure oil control valve, the oil tank, the rod cavity and the rodless cavity of the first balance weight oil cylinder, the second counterweight control valve is connected with the rod cavity and the rodless cavity of the second counterweight oil cylinder, and is used for controlling the communication state among the pressure output oil port of the pressure oil control valve, the oil tank, the rod cavity and the rodless cavity of the second counterweight oil cylinder.

3. The hydraulic control system according to claim 2, wherein the pressure oil control valve is provided with at least a supply oil level and an unloading position, an oil inlet of the pressure oil control valve is connected with the pressure oil source, an oil return port of the pressure oil control valve is connected with the oil tank, and in the state of the supply oil level, the oil inlet of the pressure oil control valve is communicated with a pressure output oil port of the pressure oil control valve; and in the unloading position state, an oil inlet of the pressure oil control valve is communicated with an oil return port of the pressure oil control valve.

4. The hydraulic control system according to claim 3, wherein the first counterweight control valve is provided with at least a first counterweight lifting position and a first counterweight dropping position, the pressure oil source is communicated with a rod chamber of the first counterweight cylinder, and a rodless chamber of the first counterweight cylinder is communicated with the oil tank in a state in which the pressure oil control valve is switched to the oil supply position and the first counterweight control valve is switched to the first counterweight lifting position; the pressure oil source is communicated with a rodless cavity of the first counterweight oil cylinder in a state that the pressure oil control valve is switched to the oil supply position and the first counterweight control valve is switched to the first counterweight falling position, and a rod cavity of the first counterweight oil cylinder is communicated with the oil tank;

The second counterweight control valve is at least provided with a second counterweight lifting position and a second counterweight falling position, and in the state that the pressure oil control valve is switched to the oil supply position and the second counterweight control valve is switched to the second counterweight lifting position, the pressure oil source is communicated with a rod cavity of the second counterweight oil cylinder, and a rodless cavity of the second counterweight oil cylinder is communicated with the oil tank; and under the state that the pressure oil control valve is switched to the oil supply position and the second balance weight control valve is switched to the second balance weight falling position, the pressure oil source is communicated with a rodless cavity of the second balance weight oil cylinder, and a rod cavity of the second balance weight oil cylinder is communicated with the oil tank.

5. The hydraulic control system of claim 4, wherein a rod cavity of the first counterbalance cylinder is provided with a first pressure sensor, a rodless cavity of the first counterbalance cylinder is provided with a second pressure sensor, a rod cavity of the second counterbalance cylinder is provided with a third pressure sensor, a rodless cavity of the second counterbalance cylinder is provided with a fourth pressure sensor, the control device is connected with the first counterbalance control valve, the second counterbalance control valve, the first pressure sensor, the second pressure sensor, the third pressure sensor and the fourth pressure sensor,

The control device is used for determining the weight of the first balancing weight based on the working position of the first balancing weight control valve, the detection results of the first pressure sensor and the second pressure sensor and the acting areas of the rod cavity and the rodless cavity of the first balancing weight oil cylinder, or determining the weight of the second balancing weight based on the working position of the second balancing weight control valve, the detection results of the third pressure sensor and the fourth pressure sensor and the acting areas of the rod cavity and the rodless cavity of the second balancing weight oil cylinder,

6. The hydraulic control system according to any one of claims 1 to 5, further comprising a swing cylinder connected to the counterweight cylinder group and used for adjusting a position of the counterweight cylinder group, and a swing control valve connected to a pressure output port of the pressure oil control valve, the oil tank, and rod-and rodless chambers of the swing cylinder,

The swing control valve is at least provided with a swing stretching position and a swing shrinking position, the pressure oil source is communicated with a rodless cavity of the swing oil cylinder when the pressure oil control valve is switched to the oil supply position and the swing control valve is switched to the swing stretching position, and a rod cavity of the swing oil cylinder is communicated with the oil tank; and when the pressure oil control valve is switched to the oil supply position and the swing control valve is switched to the swing contraction position, the pressure oil source is communicated with a rod cavity of the swing oil cylinder, and a rodless cavity of the swing oil cylinder is communicated with the oil tank.

7. The hydraulic control system according to claim 6, wherein a fifth pressure sensor is installed in the rod-shaped chamber and/or the rodless chamber of the swing cylinder, and the control device is connected to the swing control valve and the fifth pressure sensor, and is configured to adjust the set pressure of the pressure regulating valve in the contracted and/or extended state of the swing cylinder in the corresponding weight based on the operation state of the counterweight cylinder group, the operation position of the swing control valve, and the detection result of the fifth pressure sensor.

8. A counterweight weight detection and pressure adjustment method based on the hydraulic control system according to any one of claims 1 to 7, characterized by comprising the steps of:

9. The method for detecting and adjusting the weight of a counterweight according to claim 8, wherein the step of determining the weight of the counterweight by the control device and determining the set pressure of the pressure regulating valve in the load lifting state of the counterweight cylinder group under the weight of the corresponding counterweight specifically comprises:

Determining the set pressure of a pressure regulating valve in the load lifting state of the counterweight cylinder group under the weight of the corresponding counterweight block based on the pressure difference of the rodless cavity and the rod cavity of the counterweight cylinder group;

10. The counterweight weight detection and pressure adjustment method of claim 9, wherein the counterweight weight detection and pressure adjustment method further comprises: