Hydraulic control system for excavator attachments and excavator

Abstract

The present application discloses a hydraulic control system for an excavator attachment and an excavator. The system includes a main pump; a control main valve, which includes a breaker main valve plate, a plurality of auxiliary mechanism main valve plates, and a double-pump confluence cut-off valve; a controller configured to: determine that the breaker main valve plate is in the working valve position and the plurality of auxiliary mechanism main valve plates are in the cut-off valve positions; control the double-pump confluence cut-off valve to conduct, and control the engine to operate at a first set speed, so that the main pump operates at a first maximum output power; determine that the breaker main valve plate is in the cut-off valve position and at least one of the auxiliary mechanism main valve plates is in the working valve position; control the double-pump confluence cut-off valve to cut off, and control the main pump to operate at a second maximum output power and / or control the engine to operate at a second set speed; wherein, the second set speed is greater than the first set speed, and the second maximum output power is greater than the first maximum output power. The control hydraulic system of the present application can improve the overall efficiency of the breaking operation.

Description

Technical Field

[0001] This application belongs to the excavator control system. Specifically, it relates to an excavator and its attachment hydraulic control system. Background Art

[0002] Currently, the breaker on an excavator basically operates with dual-pump confluence. Specifically, the output powers of the two pumps are equal, and the engine runs at a relatively low speed. Although the output flow of the main pumps can meet the requirements of the breaking operation, at the same time, other auxiliary operations, such as left and right sweeping or front and back piling, etc., are relatively slow. However, the auxiliary operations account for about 30% of the time during the breaking operation, which to a certain extent affects the overall efficiency of the breaking operation and thus affects the overall rate of return.

[0003] In addition, when the breaking action and the auxiliary action are operated simultaneously, the dual-pump confluence needs to be cancelled. Since the powers of the two pumps are set to be equal, the breaking action will become slower, reducing the efficiency of the breaking operation. Summary of the Invention

[0004] To overcome at least one of the above technical defects, this application provides an attachment hydraulic control system for an excavator and an excavator to improve the overall efficiency of the breaking operation.

[0005] To achieve the above object, in the first aspect of this application, an attachment hydraulic control system for an excavator is provided, including:

[0006] A main pump, including a first variable pump and a second variable pump driven by an engine;

[0007] A control main valve, including a breaker main valve plate for controlling a breaker, a plurality of auxiliary mechanism main valve plates for correspondingly controlling a plurality of auxiliary action actuators, and a dual-pump confluence cut-off valve for controlling the realization of the dual-pump confluence function; and

[0008] A controller, configured to:

[0009] Determine that the breaker main valve plate is in the working valve position and a plurality of the auxiliary mechanism main valve plates are in the cut-off valve position;

[0010] Control the dual-pump confluence cut-off valve to conduct for dual-pump confluence, and control the engine to operate at a first set speed; wherein, the engine operating at the first set speed drives the main pump to operate at a first maximum output power;

[0011] Determine that the breaker main valve plate is in the cut-off valve position and at least one of the auxiliary mechanism main valve plates is in the working valve position;

[0012] Control the dual-pump confluence cut-off valve to cut off to stop dual-pump confluence, and control the main pump to operate at a second maximum output power and / or control the engine to operate at a second set speed;

[0013] Wherein, the second set rotational speed is greater than the first set rotational speed, and the second maximum output power is greater than the first maximum output power.

[0014] In some embodiments, the controller may further be configured to:

[0015] Determine that the breaker main valve plate and at least one of the auxiliary mechanism main valve plates are in the working valve position;

[0016] Control the double-pump confluence cut-off valve to be closed to stop double-pump confluence;

[0017] Control the main pump such that the output power of the second variable pump that supplies oil to the breaker is greater than the output power of the first variable pump.

[0018] In some embodiments, the controller is further configured to:

[0019] Determine that the breaker main valve plate and at least one of the auxiliary mechanism main valve plates are in the working valve position;

[0020] Control to increase the rotational speed of the engine.

[0021] In some embodiments, both the breaker main valve plate and the auxiliary mechanism main valve plates are hydraulic control directional valves. Pilot control valves and pressure detection units for detecting the oil pressure in the oil circuit are respectively provided in the respective pilot control oil circuits of the breaker main valve plate and each of the auxiliary mechanism main valve plates. The controller is electrically connected to each of the pressure detection units to determine the respective current valve positions of the breaker main valve plate and the auxiliary mechanism main valve plates.

[0022] In some embodiments, the hydraulic control system of the excavator attachment includes:

[0023] A third hydraulic pump for supplying oil to each of the pilot control oil circuits;

[0024] Wherein, the first variable pump, the second variable pump, and the third hydraulic pump are configured as a triple pump uniformly driven by the engine.

[0025] In some embodiments, the pilot control oil circuit is connected to an accumulator or to the oil outlet of the first variable pump or the second variable pump.

[0026] In some embodiments, both the breaker main valve plate and the auxiliary mechanism main valve plates are electromagnetic directional valves and are electrically connected to the controller.

[0027] In some embodiments, the main pump includes:

[0028] A first pump control valve for controlling the output power of the first variable pump; and

[0029] A second pump control valve for controlling the output power of the second variable pump;

[0030] Wherein, the controller is electrically connected to and respectively controls the first pump control valve and the second pump control valve.

[0031] In some embodiments, the control main valve includes:

[0032] A first pumping working oil circuit supplied with oil by the first variable pump;

[0033] A second pumping working oil circuit supplied with oil by the second variable pump;

[0034] Wherein, the breaker main valve plate is arranged in the second pumping working oil circuit, and the double-pump confluence cut-off valve is used to control the connection or cut-off between the first pumping working oil circuit and the second pumping working oil circuit.

[0035] In some embodiments, a plurality of the auxiliary mechanism main valve plates are arranged in series in the first pumping working oil circuit.

[0036] In some embodiments, the double-pump confluence cut-off valve and the auxiliary mechanism main valve plate are reversely interlocked.

[0037] In some embodiments, the hydraulic control system for an excavator attachment includes:

[0038] An accelerator knob for adjusting the working gear of the engine to determine the engine speed corresponding to the working gear.

[0039] According to a second aspect of the present application, there is also provided an excavator, which includes the hydraulic control system for an excavator attachment according to the above of the present application.

[0040] In the present application, by the controller judging the current valve positions of the breaker main valve plate and the auxiliary mechanism main valve plate, it can be determined that the current working condition is one of three working conditions: only the breaking action, only the auxiliary action, or both actions coexist. Furthermore, the double-pump confluence cut-off valve, the engine speed, and the main pump output power can be correspondingly controlled, so that when there is a breaking action, the engine speed is low and the main pump output power is low, and when there are other auxiliary actions, the engine speed is high and the main pump power output increases, improving the speed of the auxiliary action, thereby improving the overall efficiency of the breaking operation.

[0041] Other features and advantages of the embodiments of the present application will be described in detail in the subsequent specific embodiment part. Description of the Drawings

[0042] The accompanying drawings are used to provide a further understanding of the embodiments of the present application, and constitute a part of the specification. Together with the following specific embodiments, they are used to explain the embodiments of the present application, but do not constitute a limitation to the embodiments of the present application. In the accompanying drawings:

[0043] Figure 1 is a hydraulic schematic diagram of a hydraulic control system for an excavator attachment according to a specific embodiment of the present application; and

[0044] Figure 2 is a flowchart of a control method of a controller in a hydraulic control system for an excavator attachment according to a specific embodiment of the present application.

[0045] Description of reference numerals

[0046] 1 Hydraulic oil tank 2 Engine

[0047] 3 Main pump 4 Controller

[0048] 5 Throttle knob 6 Control main valve

[0049] 7 Detection module 8 Breaker

[0050] 9 Right pilot valve 10 Left pilot valve

[0051] 11 Hydraulic hammer valve 12 Foot valve

[0052] 31 First pump control valve 32 Second pump control valve

[0053] 61 Double pump confluence cut-off valve 62 Breaker main valve plate

[0054] 63 Auxiliary mechanism main valve plate L0 Pilot control oil circuit

[0055] P1 First variable pump P2 Second variable pump

[0056] P3 Third hydraulic pump Specific embodiments

[0057] The following describes in detail the specific embodiments of the present application with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are only used to illustrate and explain the present application, and are not used to limit the present application.

[0058] The following describes a hydraulic control system for an excavator attachment according to the present application with reference to the accompanying drawings.

[0059] See Figure 1 , Figure 2 , in a specific embodiment of the present application, a hydraulic control system for an excavator attachment is disclosed, including:

[0060] The main pump 3 includes a first variable pump P1 and a second variable pump P2 driven by the engine 2;

[0061] The control main valve 6 includes a breaker main valve piece 62 for controlling the breaker 8, a plurality of auxiliary mechanism main valve pieces 63 for correspondingly controlling a plurality of auxiliary action actuators, and a double-pump confluence cut-off valve 61 for controlling the realization of the double-pump confluence function; and

[0062] The controller 4 is configured to:

[0063] Determine that the breaker main valve piece 62 is in the working valve position and the plurality of auxiliary mechanism main valve pieces 63 are in the cut-off valve position;

[0064] Control the double-pump confluence cut-off valve 61 to conduct for double-pump confluence, and control the engine 2 to operate at a first set speed; wherein, the engine 2 operating at the first set speed drives the main pump 3 to operate at a first maximum output power;

[0065] Determine that the breaker main valve piece 62 is in the cut-off valve position and at least one auxiliary mechanism main valve piece 63 is in the working valve position;

[0066] Control the double-pump confluence cut-off valve 61 to cut off to stop double-pump confluence, and control the main pump 3 to operate at a second maximum output power and / or control the engine 2 to operate at a second set speed;

[0067] Wherein, the second set speed is greater than the first set speed, and the second maximum output power is greater than the first maximum output power.

[0068] In the control system of the present application, for the defects in the prior art that the same engine speed and main pump power are set for the crushing action and other auxiliary actions (i.e., other actions except the crushing action) to meet the needs of the crushing action, but the other auxiliary actions are slower, affecting the overall operation efficiency, or when meeting the needs of other auxiliary actions, it will cause the power of the crushing action to be redundant and waste fuel, etc., the present application particularly improves the overall efficiency of the crushing operation by increasing the speed of the auxiliary actions.

[0069] For this reason, referring to Figure 2 the control process, steps S100 and S200 are the working conditions of only the crushing operation. At this time, it is necessary to control the double-pump confluence cut-off valve 61 to conduct to achieve double-pump confluence, and confluence the pumping oil of the first variable pump P1 and the second variable pump P2 and pump it to the working oil circuit of the breaker 8. Steps S300 and S400 are the working conditions of only the auxiliary actions. At this time, on the basis of canceling the double-pump confluence, the engine 2 can be controlled to increase the speed, or the main pump 3 can be controlled to increase the pump output power, or both the engine speed and the pump output power can be controlled to increase respectively, so as to increase the speed of the auxiliary actions.

[0070] In contrast, in the prior art, the engine speed is usually determined by determining the working gear, and thus the maximum output power of the main pump is also determined. In this application, the engine speed and the output power of the main pump are controlled separately. In this way, in the working conditions of only crushing operation or only auxiliary actions, the corresponding pump output power can be adjusted according to different working conditions, and the auxiliary action speed can be increased to improve the overall efficiency.

[0071] More importantly, since the engine speed and the output power of the main pump can be controlled separately, at the same working gear, that is, at the same engine speed, the output powers of the two variable pumps can be adjusted differently. Therefore, in the working conditions where crushing operation and other auxiliary actions exist simultaneously, without adjusting the working gear, that is, without adjusting the speed, the internal flow distribution can be optimized, that is, the output power ratio of the two variable pumps can be adjusted separately to preferentially meet the requirements of the crushing action. Therefore, the controller 4 is further configured to:

[0072] Determine that the main valve plate 62 of the breaker and the main valve plate 63 of at least one auxiliary mechanism are in the working valve position;

[0073] Control the double-pump confluence cut-off valve 61 to cut off to stop the double-pump confluence;

[0074] Control the main pump 3 so that the output power of the second variable pump P2 supplying oil to the breaker 8 is greater than the output power of the first variable pump P1.

[0075] It can be seen that in the third working condition where crushing operation and other auxiliary actions exist simultaneously, since the double-pump confluence is stopped and the single pump supplies oil to the breaker 8, there may be a problem of insufficient oil supply. Therefore, the output power of the second variable pump P2 supplying oil to the breaker 8 is increased, so as to preferentially meet the crushing action in terms of flow distribution.

[0076] Furthermore, in the working conditions where crushing operation and other auxiliary actions exist simultaneously, if the engine speed meets the requirements, that is, it can provide enough flow of pumped oil to meet the requirements of multi-action operation, the output power adjustment of the pump can be provided, so that both the breaker 8 and the auxiliary action actuator can meet the hydraulic flow requirements of the working oil. However, if the engine speed is too low, resulting in insufficient overall pumped hydraulic flow, the engine speed can also be increased. Therefore, the controller 4 can also be configured to:

[0077] Determine that the main valve plate 62 of the breaker and the main valve plate 63 of at least one auxiliary mechanism are in the working valve position;

[0078] Control to increase the speed of the engine 2.

[0079] From the above control logic of the control valve 4, it can be seen that in three different working conditions, the controller 4 can correspondingly control the double-pump confluence cut-off valve 61, the main pump 3 and the engine 2, so as to improve the working efficiency of the auxiliary actions while meeting the requirements of the crushing operation.

[0080] See Figure 1 , in a hydraulic control system of an excavator attachment in a specific embodiment, the breaker main valve plate 62 serving as the control main valve of the breaker 8 and the auxiliary mechanism main valve plate 63 correspondingly controlling the auxiliary action actuator are both hydraulic control directional valves. As Figure 1 shown, pilot control valves and respective pressure detection units SE1 to SE10 for detecting the oil pressure of the oil circuit are respectively provided in the respective pilot control oil circuits L0 of the breaker main valve plate 62 and each auxiliary mechanism main valve plate 63, and the respective pressure detection units SE1 to SE10 constitute a detection module 7. The controller 4 is electrically connected to the respective pressure detection units SE1 to SE10 to determine the respective current valve positions of the breaker main valve plate 62 and the auxiliary mechanism main valve plate 63.

[0081] Those skilled in the art can understand that these auxiliary action actuators can be swing cylinders, boom cylinders, rotary pumps, etc. on the working attachments of the excavator. Figure 1 For clear display and to avoid clutter, only the connection of the breaker main valve plate 62 and its pilot control oil circuit is illustrated, while the connection of other auxiliary action actuators and their auxiliary mechanism main valve plates 63 and their pilot control oil circuits is omitted.

[0082] Among them, the hydraulic hammer valve 11 is a switch valve on the pilot control oil circuit of the breaker main valve plate 62, which controls the on or off state of the pilot control oil circuit, thereby controlling the valve position switching of the breaker main valve plate 62 and finally controlling the action of the breaker 8. Similarly, Figure 1 as shown, the right pilot valve 9, the left pilot valve 10, the foot valve 12, etc. also control the on and off of the pilot control oil circuits of the corresponding auxiliary mechanism main valve plates 63, thereby controlling the valve position switching of the auxiliary mechanism main valve plates 63 and finally controlling the actions of the auxiliary action actuators.

[0083] In this embodiment, the respective pressure detection units SE1 to SE10 can be various types of oil pressure detection sensors. When the detected oil pressure is large, it indicates that the pilot control oil circuit is in a conducting state, otherwise it is in an oil circuit disconnected state.

[0084] During operation, the controller 4 receives the pressure detection signals from each of the pressure detection units SE1 to SE10, thereby correspondingly determining the current valve positions of the breaker main valve plate 62 and each of the auxiliary mechanism main valve plates 63. Then, it determines whether it is in the working condition of single breaker operation through the control step S100, or determines whether it is in the working condition of single auxiliary action through the step S300, or determines whether it is in the working condition where the breaker operation and the auxiliary action coexist by determining that the breaker main valve plate 62 and at least one auxiliary mechanism main valve plate 63 are in the working valve positions. Then, it executes the control steps under the judged working condition, such as the control step S200 or the control step S400, etc.

[0085] In Figure 1 the hydraulic control system for excavator attachments further includes a third hydraulic pump P3 for supplying oil to each of the pilot control oil circuits L0. Among them, the pumped hydraulic oil of the third hydraulic pump P3 is directed to a plurality of pilot control oil circuits connected in parallel. Correspondingly, each of the pilot control valves (i.e., the illustrated right pilot valve 9, left pilot valve 10, hydraulic hammer valve 11, foot valve 12) is also connected in parallel.

[0086] Further, the third hydraulic pump P3 can be set separately, or as Figure 1 shown, since the oil pumping requirement of the third hydraulic pump P3 is small, in order to save energy, the first variable pump P1, the second variable pump P2, and the third hydraulic pump P3 can be configured as a triple pump uniformly driven by the engine 2.

[0087] Optionally, the pilot oil can be provided not only by sucking the hydraulic oil tank 1 through the third hydraulic pump P3, but also by other means, such as an accumulator or other hydraulic working oil circuits, such as the pumping oil circuits of the first variable pump P1 and the second variable pump P2 connected to the control main valve 6. Therefore, in other embodiments, the pilot control oil circuit L0 can be connected to the accumulator or to the pump oil outlet of the first variable pump P1 or the second variable pump P2.

[0088] In a feasible embodiment, the valve position of the main valve plate can also be switched by an electromagnetic valve, that is, both the breaker main valve plate 62 and the auxiliary mechanism main valve plate 63 are electromagnetic reversing valves and are electrically connected to the controller 4. In this way, the working valve positions of the breaker main valve plate 62 and each of the auxiliary mechanism main valve plates 63 can be confirmed by the energized and de-energized states of the electromagnets of each main valve plate.

[0089] See Figure 1 , the main pump 3 in this embodiment includes:

[0090] A first pump control valve 31 for controlling the output power of the first variable pump P1; and

[0091] A second pump control valve 32 for controlling the output power of the second variable pump P2;

[0092] Among them, the controller 4 is electrically connected to and controls the first pump control valve 31 and the second pump control valve 32 respectively.

[0093] Those skilled in the art know that variable pumps and the pump control valves for controlling their output power are known technologies. The pump control valves can control the opening degree of the pump oil outlet, etc., so as to control the output power of the variable pump. Therefore, the specific structures of the first pump control valve 31 and the second pump control valve 32 will not be elaborated here one by one.

[0094] See Figure 1 , the control main valve 6 includes:

[0095] The first pumping working oil circuit, which is supplied with oil by the first variable pump P1; and

[0096] The second pumping working oil circuit, which is supplied with oil by the second variable pump P2;

[0097] Among them, the breaker main valve plate 62 is arranged in the second pumping working oil circuit, and the double-pump confluence cut-off valve 61 is used to control the connection or cut-off between the first pumping working oil circuit and the second pumping working oil circuit.

[0098] As can be seen from the figure, the breaker main valve plate 62 is arranged in the second pumping working oil circuit, that is, the breaker 8 is supplied with oil by the second variable pump P2. The double-pump confluence cut-off valve 61 is a switching valve. When it is in the left position shown in the figure, the pressure oil pumped by the first variable pump P1 returns oil through the first pumping working oil circuit, so that the pumping pressure oil of the first variable pump P1 and the second variable pump P2 of the main pump 3 all flows to the breaker main valve plate 62 of the control main valve 6, realizing the double-pump confluence function.

[0099] When it is in the right cut-off position of the double-pump confluence cut-off valve 61, the pressure oil pumped by the first variable pump P1 passes through the first pumping working oil circuit and flows through the connecting oil circuit to the oil inlet of the breaker main valve plate 62, thereby realizing double-pump confluence and jointly driving the breaker 8 to act.

[0100] In this embodiment, a plurality of auxiliary mechanism main valve plates 63 are arranged in series in the first pumping working oil circuit, that is, the first variable pump P1 supplies oil to the auxiliary action execution mechanism. In this way, in the third working condition where the breaker 8 and the auxiliary action coexist, by increasing the output power of the second variable pump P2 and ensuring the output power of the first variable pump P1, it can not only ensure the pressure oil demand for the breaker operation, but also meet the required oil supply for improving the auxiliary action speed through single-pump oil supply. It should be noted that the auxiliary mechanism main valve plate 63 can also be arranged in series in the second pumping working oil circuit, and the present application does not limit this.

[0101] In addition, a reverse interlock is generally formed between the double-pump confluence cut-off valve 61 and the main valve disc 63 of the auxiliary mechanism, that is, when any main valve disc 63 of the auxiliary mechanism is in the working valve position, the double-pump confluence cut-off valve 61 is correspondingly locked in the left position shown in the figure, canceling the double-pump confluence function.

[0102] In addition, the hydraulic control system of the excavator attachment further includes:

[0103] The throttle knob 5 is used to adjust the working gear of the engine 2 to determine the engine speed corresponding to the working gear.

[0104] Among them, the excavator operator can determine the working gear through the throttle knob 5, thereby setting the engine speed of the engine 2. In the prior art, the throttle knob 5 selects the working gear, and then determines the unique corresponding main pump working efficiency. However, in this application, one working gear can correspond to multiple main pump powers, that is, the main pump powers corresponding to the crushing action and the auxiliary action are different. During the crushing operation, the engine speed is no longer fixed and can automatically match different engine speeds according to the crushing action and the auxiliary action. During the crushing operation, if the crushing action and the auxiliary action are carried out simultaneously, the controller 4 will give different control information to the first variable pump P1 and the second variable pump P2, so that the output power of the second variable pump P2 supplying oil to the breaker 8 is greater than that of the first variable pump P1, giving priority to satisfying the crushing action.

[0105] On the above basis, this application also discloses an excavator, including the above-mentioned hydraulic control system of the excavator attachment. In the control of the breaker operation of this excavator, when there is a crushing action, the engine speed is low and the main pump output power is low. When there are other auxiliary actions, the engine speed is high and the main pump power output increases, improving the speed of the auxiliary action, thereby improving the overall efficiency of the crushing operation.

[0106] In the description of this application, it should be understood that the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one of these features. In the description of this application, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise specifically defined.

[0107] In this application, unless otherwise clearly specified or limited, terms such as "installed", "connected", "coupled", "fixed", etc. shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection, an electrical connection, or communicable with each other; it may be directly connected, or indirectly connected through an intermediate medium, and it may be the communication inside two components or the interaction relationship between two components, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0108] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "example", "specific example", or "some examples", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of this application. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples. In addition, without contradiction, those skilled in the art can combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples.

[0109] Although the embodiments of this application have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting this application. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of this application.

Claims

1. An excavator attachment hydraulic control system, characterized in that, the excavator attachment hydraulic control system includes: a main pump (3), including a first variable pump (P1) and a second variable pump (P2) driven by an engine (2); a control main valve (6), including a breaker main valve plate (62) for controlling a breaker (8), a plurality of auxiliary mechanism main valve plates (63) for correspondingly controlling a plurality of auxiliary action actuators, and a double-pump confluence cut-off valve (61) for controlling the realization of the double-pump confluence function; and a controller (4), configured to: determine that the breaker main valve plate (62) is in the working valve position and the plurality of auxiliary mechanism main valve plates (63) are in the cut-off valve position; control the double-pump confluence cut-off valve (61) to conduct for double-pump confluence, and control the engine (2) to operate at a first set speed; wherein, the engine (2) operating at the first set speed drives the main pump (3) to operate at a first maximum output power; determine that the breaker main valve plate (62) is in the cut-off valve position and at least one of the auxiliary mechanism main valve plates (63) is in the working valve position; control the double-pump confluence cut-off valve (61) to cut off to stop double-pump confluence, and control the main pump (3) to operate at a second maximum output power and / or control the engine (2) to operate at a second set speed; wherein, the second set speed is greater than the first set speed, and the second maximum output power is greater than the first maximum output power; wherein, the controller (4) is further configured to: determine that the breaker main valve plate (62) and at least one of the auxiliary mechanism main valve plates (63) are in the working valve position; control the double-pump confluence cut-off valve (61) to cut off to stop double-pump confluence; control the main pump (3) such that the output power of the second variable pump (P2) supplying oil to the breaker (8) is greater than the output power of the first variable pump (P1).

2. The excavator attachment hydraulic control system according to claim 1, characterized in that, the controller (4) is further configured to: determine that the breaker main valve plate (62) and at least one of the auxiliary mechanism main valve plates (63) are in the working valve position; control to increase the speed of the engine (2).

3. The excavator attachment hydraulic control system according to claim 1 or 2, characterized in that, the breaker main valve plate (62) and the auxiliary mechanism main valve plates (63) are both hydraulic control reversing valves, and pilot control valves and pressure detection units (SE1~SE10) for detecting the oil pressure of the oil circuit are respectively provided in the respective pilot control oil circuits (L0) of the breaker main valve plate (62) and each of the auxiliary mechanism main valve plates (63), and the controller (4) is electrically connected to each of the pressure detection units (SE1~SE10) to determine the respective current valve positions of the breaker main valve plate (62) and the auxiliary mechanism main valve plates (63).

4. The excavator attachment hydraulic control system according to claim 3, characterized in that, the excavator attachment hydraulic control system includes: a third hydraulic pump (P3) for supplying oil to each of the pilot control oil circuits (L0); Among them, the first variable pump (P1), the second variable pump (P2), and the third hydraulic pump (P3) are configured as a triple pump uniformly driven by the engine (2).

5. The hydraulic control system for an excavator attachment according to claim 3, characterized in that the pilot control oil circuit (L0) is connected to an accumulator or to the pump oil outlet of the first variable pump (P1) or the second variable pump (P2).

6. The hydraulic control system for an excavator attachment according to claim 1 or 2, characterized in that both the breaker main valve plate (62) and the auxiliary mechanism main valve plate (63) are electromagnetic directional control valves and are electrically connected to the controller (4).

7. The hydraulic control system for an excavator attachment according to claim 1 or 2, characterized in that the main pump (3) includes: a first pump control valve (31) for controlling the output power of the first variable pump (P1); and a second pump control valve (32) for controlling the output power of the second variable pump (P2); wherein, the controller (4) is electrically connected to and respectively controls the first pump control valve (31) and the second pump control valve (32).

8. The hydraulic control system for an excavator attachment according to claim 7, characterized in that the control main valve (6) includes: a first pumping working oil circuit supplied with oil by pumping of the first variable pump (P1); a second pumping working oil circuit supplied with oil by pumping of the second variable pump (P2); wherein, the breaker main valve plate (62) is arranged in the second pumping working oil circuit, and the double-pump confluence cut-off valve (61) is used to control the connection or cut-off between the first pumping working oil circuit and the second pumping working oil circuit.

9. The hydraulic control system for an excavator attachment according to claim 8, characterized in that a plurality of the auxiliary mechanism main valve plates (63) are arranged in series in the first pumping working oil circuit.

10. The hydraulic control system for an excavator attachment according to claim 8, characterized in that a reverse interlock is provided between the double-pump confluence cut-off valve (61) and the auxiliary mechanism main valve plate (63).

11. The hydraulic control system for an excavator attachment according to claim 1 or 2, characterized in that the hydraulic control system for an excavator attachment includes: a throttle knob (5) for adjusting the working gear of the engine (2) to determine the engine speed corresponding to the working gear.

12. An excavator, characterized in that the excavator includes the hydraulic control system for an excavator attachment according to any one of claims 1 to 11.

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