CN116716944A - Main valve of excavator, hydraulic system of excavator and excavator - Google Patents

Abstract

The application belongs to the field of excavators and discloses an excavator main valve, an excavator hydraulic system and an excavator, wherein the excavator main valve comprises a multi-way valve group, a first multi-way valve and a second multi-way valve, wherein the multi-way valve comprises a first oil inlet and a second oil inlet; and the external breaking valve is connected with the inner bypass oil way and used for controlling the pressure oil of the inner bypass oil way to be conducted and driving a breaking hammer of the excavator to work. The excavator hydraulic system comprises an excavator main valve; the first main pump is used for pumping oil towards the first oil inlet of the multi-way valve group; the second main pump is used for pumping oil towards a second oil inlet of the multi-way valve group; and the breaking hammer is connected to the breaking hammer valve plate and the external breaking valve through oil ways respectively. The external crushing valve is small in size and can be connected to the multi-way valve group through bolts, so that the main valve is small in size, pipelines are convenient to arrange, oil supply modes are diversified, and the flexibility of crushing control is improved.

Description

Main valve of excavator, hydraulic system of excavator and excavator

Technical Field

The application belongs to the field of excavators, and particularly relates to an excavator, a hydraulic system thereof and a main valve.

Background

The conventional control system of the breaking hammer of the excavator is shown in fig. 1, the hydraulic breaking hammer works by utilizing hydraulic energy provided by the hydraulic system of the excavator, namely, energy output by a main pump is transmitted to the breaking hammer through the control of a main valve, so that the breaking hammer is driven to work. For conventional hydraulic breaking hammer control systems, one pump is typically used for control and the other pump is used as auxiliary control, but the auxiliary pump cannot control the hydraulic hammer alone. When one pump control is used, the crushing efficiency is high, but the service life of the pump is reduced. There is a large energy loss when working with two pumps.

For large breaking hammers, there is also proposed a breaking control system shown in fig. 2, comprising a first main pump 5, a second main pump 6, a main valve 7, wherein an additional breaking control valve 8 is required. Considering that the large breaking hammer generally needs larger flow and higher pressure, the breaking control valve 8 has larger volume and is arranged on one side of the main valve 7 externally, so that the occupied space is larger, the pipeline arrangement is difficult, and meanwhile, the cost is increased more. The external crushing control mode has larger volume and difficult pipeline arrangement.

Disclosure of Invention

The application aims to provide a main valve of an excavator, an excavator hydraulic system and the excavator, so that oil supply modes are diversified, and the flexibility of crushing control is improved.

To achieve the above object, according to one aspect of the present application, there is provided a main valve of an excavator, comprising:

the multi-way valve group comprises a first multi-way valve provided with a first oil inlet and a second multi-way valve provided with a second oil inlet, the first multi-way valve comprises a breaking hammer valve plate, and the second multi-way valve is provided with an inner bypass oil way led out from the second oil inlet;

and the external crushing valve is connected with the inner bypass oil way and used for controlling the pressure oil of the inner bypass oil way to be conducted and driving a crushing hammer of the excavator to work.

In some embodiments, the first multiple-way valve includes a plurality of first working valve plates and a first main oil supply path sequentially connected to each of the first working valve plates from the first oil inlet, the second multiple-way valve includes a plurality of second working valve plates and a second main oil supply path sequentially connected to each of the second working valve plates from the second oil inlet, and the inner bypass path is disposed in parallel with the second main oil supply path;

the second working valve plate comprises a breaking confluence valve, and the breaking confluence valve is used for controlling pressure oil of the second main oil supply oil way to flow to the breaking hammer valve plate.

In some embodiments, the excavator main valve comprises:

the controller is used for respectively controlling the breaking hammer valve plate, the external breaking valve and the breaking confluence valve and is configured to:

in a first working mode, controlling to independently open the breaking hammer valve plate, so that pressure oil of the first main oil supply way is conducted and drives the breaking hammer to work;

in a second working mode, the external breaking valve is controlled to be independently opened, so that the pressure oil of the inner bypass oil way is conducted and the breaking hammer is driven to work;

and in a third working mode, controlling to jointly open the breaking hammer valve plate and the external breaking valve, so that the breaking hammer is jointly driven to work by the pressure oil of the first main oil supply oil way and the pressure oil of the inner bypass oil way.

In some embodiments, the controller is further configured to:

and under a fourth working mode, alternately controlling and opening the breaking hammer valve plate and the external breaking valve, so that the pressure oil of the first main oil supply oil way and the pressure oil of the inner bypass oil way alternately drive the breaking hammer to work.

In some embodiments, in the fourth mode of operation, the controller is further configured to repeatedly cycle the following control steps:

controlling to open the breaking hammer valve plate and closing the external breaking valve;

for a first time interval T1;

controlling to open the external breaking valve and closing the breaking hammer valve plate;

for a second time interval T2.

In some embodiments, the breaking hammer valve plate, the external breaking valve and the breaking confluence valve are all hydraulic pilot reversing valves, and the main valve of the excavator comprises:

the first pilot switching valve is connected with a control oil port of the external crushing valve through a first pilot control oil path, the second pilot switching valve is connected with a control oil port of the crushing hammer valve plate through a second pilot control oil path, and the third pilot switching valve is connected with a control oil port of the crushing converging valve through a third pilot control oil path;

the controller is also used for respectively switching and controlling the first pilot switching valve, the second pilot switching valve and the third pilot switching valve.

In some embodiments, the breaking hammer valve plate, the external breaking valve and the breaking confluence valve are all electromagnetic directional valves.

In some embodiments, the external breaker valve comprises:

the first main oil port of the cartridge valve is connected with the inner bypass oil way, and the second main oil port is used for connecting an oil way to the breaking hammer;

the reversing control valve comprises a first side working oil port connected to a control cavity of the cartridge valve, a second side working oil port positioned on the other side and connected to a valve core cavity of the cartridge valve, and a control valve oil return port;

the reversing control valve is used for switching and connecting the first side working oil port to the second side working oil port or the control valve oil return port.

In some embodiments, the cartridge valve is a cone valve; and/or the second main oil port of the cartridge valve is provided with a one-way valve, and the one-way valve is used for enabling pressure oil to flow from a valve core cavity of the cartridge valve to the breaking hammer and to be blocked reversely.

According to a second aspect of the present application, there is provided an excavator hydraulic system comprising:

the main valve of the excavator;

the first main pump is used for pumping oil towards a first oil inlet of the multi-way valve group;

the second main pump is used for pumping oil towards a second oil inlet of the multi-way valve group;

and the breaking hammer is connected to the breaking hammer valve plate and the external breaking valve through oil ways respectively.

In some embodiments, the first and second main pumps are each a proportional variable pump.

According to a third aspect of the present application, there is provided an excavator comprising the excavator hydraulic system described above.

In some embodiments, the rated tonnage of the excavator is not less than 50t.

According to the scheme, the external crushing valve for controlling the crushing hammer is additionally arranged on the outer side of the multi-way valve group of the excavator, the external crushing valve can be connected to the multi-way valve group through bolts, the main valve is small in size, and the pipeline arrangement is convenient. Meanwhile, an inner bypass oil way is additionally arranged in the multi-way valve group, the external crushing valve is connected with the inner bypass oil way, pressure oil can flow to the crushing hammer through the first oil inlet and the crushing hammer valve plate, and can also flow to the crushing hammer through the second oil inlet, the inner bypass oil way and the external crushing valve, so that the oil supply mode is more flexible. Further, oil can be alternately supplied by the double pumps, so that the flexibility of crushing control and the service life of the pumps are improved.

Additional features and advantages of embodiments of the application will be set forth in the detailed description which follows.

Drawings

The accompanying drawings are included to provide a further understanding of embodiments of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain, without limitation, the embodiments of the application. In the drawings:

FIG. 1 is a hydraulic schematic diagram of a prior art excavator hydraulic system;

FIG. 2 is a hydraulic schematic diagram of another excavator hydraulic system of the prior art;

FIG. 3 is a hydraulic schematic of a main valve of an excavator according to an embodiment of the present application;

FIG. 4 is a hydraulic schematic diagram of an excavator hydraulic system employing the main valve of the excavator of FIG. 3; and

fig. 5 is a hydraulic schematic of the external breaker valve of fig. 4.

Description of the reference numerals

1. First multiplex valve 2 second multiplex valve

3. External 4 guide valve groups of crushing valve

5. First main pump 6 second main pump

7. Main valve 8 crushing control valve

10. Valve plate of breaking hammer of controller 11

21. Breaking confluence valve 31 cartridge valve

32. Breaking hammer of reversing control valve 100

P1 first oil inlet P2 second oil inlet

P3 third oil outlet L1 first main oil supply way

L2 second main oil supply oil way L3 inner bypass oil way

Detailed Description

The following describes specific embodiments of the present application in detail with reference to the drawings. It should be understood that the detailed description and specific examples, while indicating and illustrating the application, are not intended to limit the application.

The main valve of the excavator, the excavator hydraulic system and the excavator according to the present application are described below with reference to the accompanying drawings.

The application discloses a novel main valve of an excavator. As shown in fig. 3, in one embodiment, an excavator main valve includes:

the multi-way valve group comprises a first multi-way valve 1 provided with a first oil inlet P1 and a second multi-way valve 2 provided with a second oil inlet P2, wherein the first multi-way valve 1 comprises a breaking hammer valve plate 11, and the second multi-way valve 2 is provided with an inner bypass oil way L3 led out from the second oil inlet P2;

the external breaking valve 3 is connected with the inner bypass oil way L3 and is used for controlling the pressure oil of the inner bypass oil way L3 to be conducted and driving the breaking hammer 100 of the excavator to work.

It can be seen that, in the scheme of the present application, the external crushing valve 3 for controlling the crushing hammer 100 is additionally arranged at the outer side of the multi-way valve group of the excavator, meanwhile, the internal bypass oil path L3 led out from the second oil inlet P2 is additionally arranged in the second multi-way valve 2, and the external crushing valve 3 is connected with the internal bypass oil path L3, i.e. is connected with the third oil outlet P3 of the internal bypass oil path L3 on the valve body of the multi-way valve group. In this way, the pressure oil can flow to the breaking hammer 100 through the first oil inlet P1 and the breaking hammer valve plate 11, and can also flow to the breaking hammer 100 through the second oil inlet P2, the inner bypass oil path L3, the third oil outlet P3 and the external breaking valve 3, so that the oil supply mode is more flexible.

Referring to fig. 3, the first multiple-way valve 1 includes a plurality of first working valve plates and a first main oil supply oil path L1 sequentially connected to each of the first working valve plates from the first oil inlet P1 (the breaking hammer valve plate 11 is one of the first working valve plates), the second multiple-way valve 2 includes a plurality of second working valve plates and a second main oil supply oil path L2 sequentially connected to each of the second working valve plates from the second oil inlet P2, and the inner bypass oil path L3 is arranged in parallel with the second main oil supply oil path L2; the second working valve plate comprises a breaking confluence valve 21, and the breaking confluence valve 21 is used for controlling pressure oil of the second main oil supply oil way L2 to flow to the breaking hammer valve plate 11.

It can be seen that the pressure oil can flow to the breaking hammer 100 through the second oil inlet P2, the second main oil supply oil path L2, the breaking confluence valve 21 and the breaking hammer valve plate 11, so that the breaking hammer 100 can be independently controlled by two pumps respectively, the confluence of the two pumps can be realized, and the flexibility of breaking control is improved. The main valve of the excavator with the novel structure can be mounted, so that single and double pumps can be flexibly controlled.

Referring to fig. 4, the main valve of the excavator of the present embodiment may further include:

a controller 10 for controlling the breaking hammer valve plate 11, the external breaking valve 3 and the breaking confluence valve 21, respectively, and configured to:

in the first working mode, the breaking hammer valve plate 11 is controlled to be independently opened, so that the pressure oil of the first main oil supply oil way L1 is conducted and the breaking hammer 100 is driven to work;

in the second working mode, the external breaking valve 3 is controlled to be independently opened, so that the pressure oil of the inner bypass oil way L3 is conducted and the breaking hammer 100 is driven to work;

in the third working mode, the breaking hammer valve plate 11 and the external breaking valve 3 are controlled to be opened together, so that the breaking hammer 100 is driven to work by the pressure oil of the first main oil supply oil path L1 and the inner bypass oil path L3 together.

Therefore, only the breaking hammer valve plate 11, the external breaking valve 3 and the breaking confluence valve 21 are controlled by the controller 10 in an electric control and/or liquid control mode respectively, so that different oil supply modes of the breaking hammer 100 can be simply realized. As can be seen from fig. 4, in the first operating mode, the pressure oil flows to the breaking hammer 100 via the first oil inlet P1, the breaking hammer valve plate 11; in the second working mode, the pressure oil flows to the breaking hammer 100 from the second oil inlet P2, the inner bypass oil path L3 and the external breaking valve 3; in the third working mode, one path of pressure oil flows to the breaking hammer valve plate 11 through the first oil inlet P1 and the first main oil supply oil path L1, and the other path of pressure oil flows to the breaking hammer 100 after converging through the second oil inlet P2 and the second main oil supply oil path L2, the breaking converging valve 21 and the breaking hammer valve plate 11, so as to drive the breaking hammer to work together.

In particular, the controller 10 of the present embodiment may be further configured to:

in the fourth operation mode, the breaking hammer valve plate 11 and the external breaking valve 3 are alternately controlled to be opened, so that the breaking hammer 100 is alternately driven to work by the pressure oil of the first main oil supply oil path L1 and the pressure oil of the inner bypass oil path L3.

In other words, through the periodic control of the controller 10, the breaking hammer 100 can be alternately driven to work in the first working mode and the second working mode, so that the double pumps can be alternately operated, and the service life of the single pump can be prolonged.

Specifically, as an example, in the fourth operation mode, the controller 10 may be configured to repeatedly perform the following control steps:

the breaking hammer valve plate 11 is controlled to be opened and the external breaking valve 3 is controlled to be closed;

for a first time interval T1;

controlling to open the external breaking valve 3 and close the breaking hammer valve plate 11;

for a second time interval T2.

During operation, the values of T1 and T2 can be preset according to the needs, so that the independent running time of the single pump can be adjusted, and the operation is flexible and convenient. It should be noted that, the matching between the controller 10 and the solenoid valve is important, and the quality of the matching relationship directly affects the striking effect of the breaking hammer and the service life of the main pump.

The control valve associated with the controller 10 may be an electromagnetic valve, a pilot-operated valve, or the like, and in the embodiment shown in fig. 4, the breaking hammer valve plate 11, the external breaking valve 3, and the breaking confluence valve 21 are all hydraulic pilot-operated directional valves, and the main valve of the excavator includes:

the pilot valve group 4 comprises a first pilot switching valve, a second pilot switching valve and a third pilot switching valve which are arranged in parallel, wherein the first pilot switching valve is connected with a control oil port of the external crushing valve 3 through a first pilot control oil path, the second pilot switching valve is connected with a control oil port of the crushing hammer valve plate 11 through a second pilot control oil path, and the third pilot switching valve is connected with a control oil port of the crushing confluence valve 21 through a third pilot control oil path;

wherein the controller 10 is further configured to switch and control the first pilot switching valve, the second pilot switching valve, and the third pilot switching valve, respectively.

Referring to fig. 4, the pilot valve group 4 includes a first pilot switching valve, a second pilot switching valve, and a third pilot switching valve, which are sequentially disposed in parallel from left to right, and each controls on/off of a respective pilot control oil path, thereby controlling reversing operation of a corresponding control valve. Of course, it will be appreciated by those skilled in the art that the first pilot switching valve, the second pilot switching valve, and the third pilot switching valve may be electromagnetic switching valves, and in other embodiments, the breaking hammer valve plate 11, the external breaking valve 3, and the breaking confluence valve 21 may be electromagnetic switching valves.

The external crushing valve 3 of the embodiment is the same as the controllable one-way valve and can be connected to the multi-way valve group through bolts. As is well known to those skilled in the art, there are various structural forms and control manners of the external crushing valve 3, and in this embodiment, the external crushing valve 3 of fig. 5 includes, as an example:

the cartridge valve 31, the first main oil port of the cartridge valve 31 is connected with the inner bypass oil path L3 and the second main oil port is used for connecting the oil path to the breaking hammer 100;

the reversing control valve 32 comprises a first side working oil port connected to the control cavity of the cartridge valve 31, and a second side working oil port and a control valve oil return port which are positioned on the other side and connected to the spool cavity of the cartridge valve 31;

the reversing control valve 32 is used for switching and connecting the first side working oil port to the second side working oil port or the control valve oil return port.

In combination with the pilot valve group 4 shown in fig. 4, the external crushing valve 3 is based on a cartridge valve 31, and can allow a large flow to pass through, and is further combined with a reversing control valve 32 to serve as a control valve member of the cartridge valve 31. In fig. 4, one main port of the cartridge valve 31 is connected to the third oil outlet P3 on the valve body of the multiple-way valve group, and the other main port is connected to the breaking hammer 100 through a pipe. To control the opening and closing of the cartridge valve 31, the spring chamber of the cartridge valve 31 (i.e., the left chamber of the cartridge valve 31 shown in the drawing) is connected to the upper working port of the reversing control valve 32, and two lower working ports of the reversing control valve 32 are provided, one of which is an oil return port, and the other of which is connected to the spool chamber of the cartridge valve 31 (i.e., the right chamber of the cartridge valve 31 shown in the drawing).

Thus, when the pilot pressure oil is introduced into the XAo oil port, the reversing control valve 32 is switched to the left position, so that the spring cavity of the cartridge valve 31 is communicated with the oil return port, the cartridge valve 31 is in a conducting state, and the pressure oil in the inner bypass oil path L3 can be led to the breaking hammer 100 through the cartridge valve 31 and the Ao oil port. When the pilot pressure oil is not introduced into the XAo oil port, the reversing control valve 32 is switched to the right position, so that the spring cavity and the valve core cavity of the cartridge valve 31 are communicated, the valve core of the cartridge valve plugs the valve port under the action of spring force, the cartridge valve 31 is in a cut-off state, and the pressure oil of the inner bypass oil path L3 cannot pass through the cartridge valve 31.

In addition, the second main port of the cartridge valve 31 is further provided with a check valve, which is used to enable the pressure oil to flow from the spool cavity of the cartridge valve 31 to the breaking hammer 100 and to be blocked reversely, so as to prevent the oil from flowing back.

In this embodiment, only 1 oil outlet is needed for the crushing function of the excavator, and no micro-action is needed for the crushing function, so that the external crushing valve 3 does not adopt the traditional slide valve core control, but adopts the form of a cone valve.

The application also discloses an excavator hydraulic system, as shown in fig. 4, the excavator hydraulic system of the embodiment comprises:

the main valve of the excavator;

the first main pump 5 is used for pumping oil towards the first oil inlet P1 of the multi-way valve group;

the second main pump 6 is used for pumping oil towards the second oil inlet P2 of the multi-way valve group;

the breaking hammer 100 is respectively connected with the breaking hammer valve plate 11 and the external breaking valve 3 through oil ways.

Therefore, the hydraulic system of the excavator is a double-loop control system, is particularly suitable for the hydraulic system of the medium-large excavator, generally has 2 main pumps, and can independently control the crushing function. In the double-loop control system, the crushing control valve is integrated in the main valve, the size is small, an external pipeline is not needed, and the double pumps can independently drive the crushing hammer to work, so that the single pump control and the double pump control can be realized; meanwhile, according to the requirements of working conditions, the first main pump 5 and the second main pump 6 can be controlled intermittently.

In particular, the first and second main pumps 5, 6 are proportional variable pumps, so that in the intermittent operation mode, the controller 10 can control the power distribution of the first and second main pumps 5, 6, thereby making the control more flexible.

The hydraulic system of the excavator is applied to the excavator, and particularly can be applied to the excavator with rated tonnage not less than 50t.

According to the application, on the basis of a main valve of a conventional excavator, 1 external hydraulic valve, namely the external crushing valve 3, is also a hydraulic control one-way valve, can be connected to a multi-way valve group through bolts, and has the advantages of small main valve volume and convenience in pipeline arrangement. The crushing control system with the novel structure can realize flexible control of single pump and double pumps. The breaking hammer can be independently controlled by the first main pump 5 and the second main pump 6 respectively, double-pump confluence can be realized, the flexibility of breaking control is improved, the external breaking valve 3 which is additionally arranged outside the main valve can be used, the control mode of the breaking hammer 100 is more flexible, the alternate control of 2 pumps can be realized, the energy-saving effect is achieved, and the service life of the pump is greatly prolonged.

According to the different crushing conditions, the following functions can be realized through the control program of the controller 10:

1. the first main pump 5 works alone, and the second main pump 6 does not work;

2. the second main pump 6 works alone, and the first main pump 5 does not work;

3. the first main pump 5 and the second main pump 6 work together in a double-pump manner, and the power between the two pumps is proportionally carried out through a control program;

4. the first and second main pumps 5, 6 alternately operate individually, and the alternate interval time can be controlled by a control program.

In a specific operation, high-pressure oil output by the first main pump 5 and the second main pump 6 enters the multi-way valve group, and when a machine hand performs crushing operation, an electric signal output by the controller 10 controls the pilot valve group 4 to act correspondingly. If the first main pump 5 is required to work independently, the port A2 in the pilot valve group 4 can be controlled to be communicated with pilot pressure oil, and other ports are cut off; if the second main pump 6 is required to work independently, the port A1 in the pilot valve group 4 can be controlled to be communicated with pilot pressure oil, and other ports are cut off; if the first main pump 5 and the second main pump 6 are required to drive the breaking hammer 100 to work, the port A2 and the port A3 in the pilot valve group 4 can be controlled to be communicated with pilot pressure oil, and other oil ports are cut off.

In the description of the present application, it should be understood that the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.

In the present application, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; may be mechanically connected, may be electrically connected or may be in communication with each other; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.

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 present application. 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, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.

While embodiments of the present application have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the application, and that variations, modifications, alternatives and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the application.

Claims (13)

1. An excavator main valve, characterized in that the excavator main valve comprises:

the multi-way valve group comprises a first multi-way valve (1) provided with a first oil inlet (P1) and a second multi-way valve (2) provided with a second oil inlet (P2), wherein the first multi-way valve (1) comprises a breaking hammer valve plate (11), and the second multi-way valve (2) is provided with an inner bypass oil way (L3) led out from the second oil inlet (P2);

and the external breaking valve (3) is connected with the inner bypass oil way (L3) and is used for controlling the pressure oil of the inner bypass oil way (L3) to be conducted and driving a breaking hammer (100) of the excavator to work.

2. The main valve of an excavator according to claim 1, wherein said first multi-way valve (1) comprises a plurality of first working valve plates and a first main oil supply circuit (L1) which is connected to each of said first working valve plates in turn from said first oil inlet (P1), said second multi-way valve (2) comprises a plurality of second working valve plates and a second main oil supply circuit (L2) which is connected to each of said second working valve plates in turn from said second oil inlet (P2), said inner bypass circuit (L3) being arranged in parallel with said second main oil supply circuit (L2);

the second working valve plate comprises a breaking confluence valve (21), and the breaking confluence valve (21) is used for controlling pressure oil of the second main oil supply oil way (L2) to flow to the breaking hammer valve plate (11).

3. The main excavator valve of claim 2 wherein the main excavator valve comprises:

a controller (10) for controlling the breaking hammer valve plate (11), the external breaking valve (3) and the breaking confluence valve (21) respectively, and configured to:

in a first working mode, the breaking hammer valve plate (11) is controlled to be independently opened, so that the pressure oil of the first main oil supply oil way (L1) is conducted and the breaking hammer (100) is driven to work;

in a second working mode, the external breaking valve (3) is controlled to be independently opened, so that the pressure oil of the inner bypass oil way (L3) is conducted and the breaking hammer (100) is driven to work;

under a third working mode, the breaking hammer valve plate (11) and the external breaking valve (3) are controlled to be opened together, so that the breaking hammer (100) is driven to work together by pressure oil of the first main oil supply oil circuit (L1) and the inner bypass oil circuit (L3).

4. The excavator main valve according to claim 3, characterized in that the controller (10) is further configured to:

in a fourth working mode, the breaking hammer valve plate (11) and the external breaking valve (3) are alternately controlled to be opened, so that the pressure oil of the first main oil supply oil way (L1) and the pressure oil of the inner bypass oil way (L3) alternately drive the breaking hammer (100) to work.

5. The excavator main valve according to claim 4, characterized in that in a fourth operating mode the controller (10) is further configured to repeatedly perform the following control steps:

controlling to open the breaking hammer valve plate (11) and close the external breaking valve (3);

for a first time interval T1;

controlling to open the external breaking valve (3) and close the breaking hammer valve plate (11);

for a second time interval T2.

6. The main valve of an excavator according to claim 4, wherein the breaking hammer valve plate (11), the external breaking valve (3) and the breaking confluence valve (21) are all hydraulic pilot reversing valves, the main valve of an excavator comprising:

the pilot valve group (4) comprises a first pilot switching valve, a second pilot switching valve and a third pilot switching valve which are arranged in parallel, the first pilot switching valve is connected with a control oil port of the external crushing valve (3) through a first pilot control oil path, the second pilot switching valve is connected with a control oil port of the crushing hammer valve plate (11) through a second pilot control oil path, and the third pilot switching valve is connected with a control oil port of the crushing confluence valve (21) through a third pilot control oil path;

wherein the controller (10) is further used for respectively switching and controlling the first pilot switching valve, the second pilot switching valve and the third pilot switching valve.

7. The main valve of the excavator according to claim 4, characterized in that the breaking hammer valve plate (11), the external breaking valve (3) and the breaking confluence valve (21) are all electromagnetic directional valves.

8. The excavator main valve according to any one of claims 1 to 7, characterised in that the external crushing valve (3) comprises:

the first main oil port of the cartridge valve (31) is connected with the inner bypass oil path (L3) and the second main oil port is used for connecting an oil path to the breaking hammer (100);

the reversing control valve (32) comprises a first side working oil port connected to the control cavity of the cartridge valve (31), and a second side working oil port and a control valve oil return port which are positioned on the other side and connected to the valve core cavity of the cartridge valve (31);

the reversing control valve (32) is used for switching and connecting the first side working oil port to the second side working oil port or the control valve oil return port.

9. The main valve of claim 8, wherein the cartridge valve is a cone valve; and/or the second main oil port of the cartridge valve (31) is provided with a one-way valve, and the one-way valve is used for enabling pressure oil to flow from a valve core cavity of the cartridge valve (31) to the breaking hammer (100) and be blocked reversely.

10. Excavator hydraulic system, its characterized in that, excavator hydraulic system includes:

the main valve of an excavator according to any one of claims 1 to 9;

the first main pump (5) is used for pumping oil towards a first oil inlet (P1) of the multi-way valve group;

the second main pump (6) is used for pumping oil towards a second oil inlet (P2) of the multi-way valve group;

and the breaking hammer (100) is connected to the breaking hammer valve plate (11) and the external breaking valve (3) through oil ways respectively.

11. The excavator hydraulic system according to claim 10, characterized in that the first main pump (5) and the second main pump (6) are each proportional variable pumps.

12. An excavator, characterized in that the excavator comprises an excavator hydraulic system according to claim 10 or 11.

13. The excavator of claim 12 wherein the excavator has a tonnage of not less than 50t.