Integrated control system of pure electric backhoe loader

Abstract

The invention discloses an integrated control system of a pure electric backhoe loader. The integrated control system comprises a hydraulic pump, a control valve group and a hydraulic oil tank, wherein the output end of the hydraulic pump is connected with a port P of the control valve group, and the input end of the hydraulic pump is connected with the hydraulic oil tank; a port B of the control valve set is connected with a port P of the priority valve, a port CF of the priority valve is connected with a port P of the steering gear, a port LS of the priority valve is connected with a port LS of the steering gear, a port T of the priority valve is connected with the hydraulic oil tank, a port L of the steering gear is connected with a left oil cylinder input end of the steering oil cylinder, and a port C of the steering oil cylinder is connected with a right oil cylinder input end of the steering oil cylinder. And an R port of the steering gear is connected with a right oil cylinder input end of the steering oil cylinder. An existing hydraulic pump of a hydraulic system can be used for supplying oil to a gear shifting system and an axle release system of a transfer case and a differential system of a drive axle, the integration level is high, economical efficiency is good, and one hydraulic oil source can meet different control pressure requirements at the same time.

Description

TECHNICAL FIELD

[0001] The present application relates to an integrated control system of a pure electric excavator loader, and belongs to the technical field of excavator loaders. BACKGROUND

[0002] The excavator loader is a multifunctional engineering machinery integrating excavation, loading and walking. The walking system of a conventional fuel oil excavator loader is generally connected by an engine through a torque converter to a gearbox, and the gearbox is connected to a drive axle through a transmission shaft to realize walking. The gearbox is generally a multi-gear gearbox to realize different operation function requirements. The gearbox is generally provided with a variable speed pump, and the following functions are realized through the variable speed pump:

[0003] Oil supply to the gear shifting system to realize gear shifting; oil supply to the bridge disconnecting system to realize two-wheel drive and four-wheel drive switching; and oil supply to the differential system of the drive axle to realize switching of the differential lock and non-lock functions. The control pressures of the above three functions are the same.

[0004] The walking system of a pure electric excavator loader is driven by a walking motor through a simple power divider. In consideration of the maximum traction force and the highest vehicle speed, a simple two-gear power divider is generally used to realize different operation requirements. The simple power divider is connected to the drive axle through a transmission shaft to realize walking. The simple power divider is not provided with a variable speed pump, and thus the simple power divider cannot supply oil to the gear shifting system, the bridge disconnecting system and the differential system of the drive axle connected to the variable speed pump, i.e. cannot realize gear shifting, two-wheel drive and four-wheel drive switching and differential lock. Moreover, the gear shifting control pressure of the simple power divider is different from the bridge disconnecting control pressure, and the bridge disconnecting control pressure is the same as the differential lock control pressure. The structure is more complicated than the original structure. If a pump is separately added to supply oil to the above systems, it is not economical.

[0005] Therefore, how to improve the hydraulic system of the pure electric excavator loader is a technical problem to be solved by those skilled in the art, SUMMARY

[0006] Object: In order to overcome the shortcomings in the prior art, the present application provides an integrated control system of a pure electric excavator loader, which can use the existing hydraulic pump of the hydraulic system to supply oil to the gear shifting system, the bridge disconnecting system and the differential system of the drive axle of the power divider, has high integration and good economy, and one set of hydraulic oil source can meet different control pressure requirements.

[0007] Technical scheme: In order to solve the above technical problems, the technical scheme adopted by the present application is:

[0008] An integrated control system of a pure electric excavator loader, comprising: a hydraulic pump, a control valve group and a hydraulic oil tank.

[0009] The output end of the hydraulic pump is connected with the P port of the control valve group, and the input end of the hydraulic pump is connected with the hydraulic oil tank.

[0010] The input end of the sequence valve is connected with the P port of the control valve group, the output end of the sequence valve is connected with the B port of the control valve group, the oil drain end of the sequence valve is connected with the T2 port of the control valve group, the P port of the control valve group is further connected with the 1 port of the first pressure reducing valve, the 2 port of the first pressure reducing valve is connected with the 1 port of the second pressure reducing valve, the A4 port of the control valve group and the 1 port of the safety electromagnetic valve respectively, the 3 port of the first pressure reducing valve is connected with the 3 port of the second pressure reducing valve, the 2 port of the bridge breaking electromagnetic valve, the 2 port of the differential lock electromagnetic valve, the 2 port of the safety electromagnetic valve and the T1 port of the control valve group respectively, the 2 port of the second pressure reducing valve is connected with the 1 port of the bridge breaking electromagnetic valve and the 1 port of the differential lock electromagnetic valve respectively, the 3 port of the bridge breaking electromagnetic valve is connected with the A3 port of the control valve group, the 3 port of the differential lock electromagnetic valve is connected with the A2 port of the control valve group, and the 3 port of the safety electromagnetic valve is connected with the A1 port of the control valve group.

[0011] As a preferred solution, the 2 port of the first pressure reducing valve is further connected with the M1 port of the control valve group.

[0012] As a preferred solution, the 2 port of the second pressure reducing valve is further connected with the M2 port of the control valve group.

[0013] As a preferred solution, it further comprises a first safety valve, the 2 port of the first pressure reducing valve is further connected with the 1 port of the first safety valve, and the 2 port of the first safety valve is connected with the T1 port of the control valve group.

[0014] As a preferred solution, it further comprises a second safety valve, the 2 port of the second pressure reducing valve is further connected with the 1 port of the second safety valve, and the 2 port of the second safety valve is connected with the T1 port of the control valve group.

[0015] As a preferred solution, it further comprises a check valve and an accumulator, the 1 port of the check valve is connected with the 2 port of the first pressure reducing valve, the 2 port of the check valve is connected with the 1 port of the safety electromagnetic valve, and the 2 port of the check valve is further connected with the accumulator.

[0016] As a preferred solution, it further comprises a throttle valve and a filter, and the P port of the control valve group and the 1 port of the first pressure reducing valve are further connected in series through the throttle valve and the filter.

[0017] As a preferred solution, it further comprises a pressure measuring connector, and the 2 port of the check valve is further connected with one end of the pressure measuring connector on the valve block.

[0018] As a preferred solution, it further comprises a priority valve, a steering gear and a steering cylinder.

[0019] Specifically, the B port of the control valve group is connected to the P port of the priority valve, the CF port of the priority valve is connected to the P port of the steering gear, the LS port of the priority valve is connected to the LS port of the steering gear, the T port of the priority valve is connected to the hydraulic oil tank, the L port of the steering gear is connected to the left cylinder input end of the steering cylinder, and the R port of the steering gear is connected to the right cylinder input end of the steering cylinder.

[0020] As a preferred embodiment, the set pressure of the sequence valve is higher than the set pressure of the first pressure reducing valve; the set pressure of the first safety valve is higher than the set pressure of the first pressure reducing valve; the set pressure of the second pressure reducing valve is lower than the set pressure of the first pressure reducing valve; and the set pressure of the second safety valve is higher than the set pressure of the second pressure reducing valve.

[0021] Beneficial effects: The integrated control system for a pure electric excavator loader provided by this invention has the following advantages compared to the prior art:

[0022] (1) The present invention has high integration and simple pipeline.

[0023] (2) The present invention utilizes existing hydraulic pumps to achieve multiple control functions.

[0024] (3) The present invention can meet different control pressure requirements. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the structure of a first embodiment of the integrated control system for a pure electric excavator loader according to the present invention.

[0026] Figure 2 This is a schematic diagram of the structure of a second embodiment of the integrated control system for a pure electric excavator loader according to the present invention. Detailed Implementation

[0027] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of the present invention.

[0028] The present invention will be further described below with reference to specific embodiments.

[0029] Example 1:

[0030] This embodiment describes an integrated control system for a pure electric excavator loader, such as... Figure 1 As shown, it includes: hydraulic pump 1, control valve group 2, hydraulic oil tank 3.

[0031] The output end of the hydraulic pump 1 is connected to the P port of the control valve group 2, and the input end of the hydraulic pump 1 is connected to the hydraulic oil tank 3.

[0032] The control valve group 2 includes: a valve block 2.14, which is equipped with a sequence valve 2.1, a first pressure reducing valve 2.2, a second pressure reducing valve 2.3, a first safety valve 2.4, a second safety valve 2.5, a one-way valve 2.6, a safety solenoid valve 2.8, a differential lock solenoid valve 2.9, and a bridge disconnect solenoid valve 2.10.

[0033] Specifically, the input end of the sequence valve 2.1 is connected to the P port of the control valve group 2, the output end of the sequence valve 2.1 is connected to the B port of the control valve group 2, the drain end of the sequence valve 2.1 is connected to the T2 port of the control valve group 2, the P port of the control valve group 2 is also connected to the 1 port of the first pressure reducing valve 2.2, the 2 port of the first pressure reducing valve 2.2 is connected to the 1 port of the first safety valve 2.4, the 1 port of the second pressure reducing valve 2.3, the M1 port of the control valve group 2, the A4 port of the control valve group 2, and the 1 port of the safety solenoid valve 2.8, respectively, and the 3 port of the first pressure reducing valve 2.2 is connected to the 2 port of the first safety valve 2.4 and the second pressure reducing valve 2.3, respectively. Port 3 of valve 3, port 2 of the second safety valve 2.5, port 2 of the disconnect solenoid valve 2.10, port 2 of the differential lock solenoid valve 2.9, port 2 of the safety solenoid valve 2.8, and port T1 of control valve group 2 are connected. Port 2 of the second pressure reducing valve 2.3 is connected to port 1 of the second safety valve 2.5, port M2 of control valve group 2, port 1 of the disconnect solenoid valve 2.10, and port 1 of the differential lock solenoid valve 2.9. Port 3 of the disconnect solenoid valve 2.10 is connected to port A3 of control valve group 2. Port 3 of the differential lock solenoid valve 2.9 is connected to port A2 of control valve group 2. Port 3 of the safety solenoid valve 2.8 is connected to port A1 of control valve group 2.

[0034] When the safety solenoid valve is energized, ports 1 and 3 are connected; when de-energized, ports 2 and 3 are connected.

[0035] When the differential lock solenoid valve is energized, ports 1 and 3 of the differential lock solenoid valve are connected; when it is de-energized, ports 2 and 3 of the differential lock solenoid valve are connected.

[0036] When the disconnect solenoid valve is energized, ports 1 and 3 of the disconnect solenoid valve are connected; when de-energized, ports 2 and 3 of the disconnect solenoid valve are connected.

[0037] Port A1 is used to supply pilot oil to the hydraulic system, port A2 is used to supply oil to the differential lock port of the drive axle, port A3 is used to supply oil to the gearbox's disengagement oil circuit, and port A4 is used to supply oil to the transfer case's shifting system.

[0038] The valve block is equipped with pressure testing ports M1 and M2. Port M1 is used to detect the outlet pressure of the first pressure reducing valve, and port M2 is used to detect the outlet pressure of the second pressure reducing valve.

[0039] Furthermore, it also includes a one-way valve 2.6 and an accumulator 2.7. Port 1 of the one-way valve 2.6 is connected to port 2 of the first pressure reducing valve, port 2 of the one-way valve 2.6 is connected to port 1 of the safety solenoid valve, and port 2 of the one-way valve 2.6 is also connected to the accumulator 2.7.

[0040] Furthermore, it also includes: a throttle valve 2.12 and a filter 2.13. The throttle valve 2.12 and the filter 2.13 are connected in series between the P port of the control valve group 2 and the I port of the first pressure reducing valve 2.2.

[0041] Throttle valves are used to reduce the impact of the main oil circuit on the integrated control system, and filters filter the hydraulic oil entering the integrated control system to prevent impurities from contaminating the integrated control system and causing abnormalities such as valve core jamming.

[0042] Furthermore, it also includes a pressure testing connector 2.11, wherein port 2 of the one-way valve 2.6 is connected to one end of the pressure testing connector 2.11 on the valve block 2.14. The pressure testing connector is used to detect the pressure after the one-way valve.

[0043] Furthermore, such as Figure 2 As shown, it also includes: priority valve 4, steering gear 5, steering cylinder 6.

[0044] Specifically, the B port of the control valve group 2 is connected to the P port of the priority valve 4, the CF port of the priority valve 4 is connected to the P port of the steering gear 5, the LS port of the priority valve 4 is connected to the LS port of the steering gear 5, the T port of the priority valve 4 is connected to the hydraulic oil tank 3, the L port of the steering gear 5 is connected to the left cylinder input end of the steering cylinder 6, and the R port of the steering gear 5 is connected to the right cylinder input end of the steering cylinder 6.

[0045] When there is no pressure at the LS port of the priority valve, the P port of the priority valve is connected to the EF port. When there is pressure at the LS port of the priority valve, the P port of the priority valve is connected to the CF port, thus partially satisfying the steering requirements. The T port of the priority valve is always connected to the oil tank. When the pressure at the LS port exceeds the set pressure of the priority valve's safety valve, the pressure at the LS port overflows through the relief valve and returns to the oil tank through the T port of the priority valve.

[0046] When the steering gear is not rotating, the oil supply to the P port is cut off, and the LS port connects to the T port after passing through the internal throttle valve. When the steering gear rotates clockwise, the steering valve enters the left position. At this time, after the internal oil passage is connected, the P and R ports, and the T and L ports, are connected, and the entire machine turns right. When the steering gear rotates counterclockwise, the steering valve enters the right position. At this time, after the internal oil passage is connected, the P and L ports, and the T and R ports, are connected, and the entire machine turns left.

[0047] Furthermore, the set pressure of the sequence valve is higher than the set pressure of the first pressure reducing valve; the set pressure of the first safety valve is higher than the set pressure of the first pressure reducing valve; the set pressure of the second pressure reducing valve is lower than the set pressure of the first pressure reducing valve; and the set pressure of the second safety valve is higher than the set pressure of the second pressure reducing valve.

[0048] Example 2:

[0049] This embodiment describes the working process of an integrated control system for a pure electric excavator loader. The set pressure of the sequence valve 2.1 is 50 bar, the set pressure of the first pressure reducing valve 2.2 is 35 bar, the set pressure of the second pressure reducing valve 2.3 is 20 bar, the set pressure of the first safety valve 2.4 is 45 bar, and the set pressure of the second safety valve 2.5 is 30 bar.

[0050] When hydraulic pump 1 rotates, it supplies oil to port P of control valve group 2 through pipeline. Hydraulic oil flows in from the input end of sequence valve 2.1 and flows out from the output end of sequence valve 2.1 to port B of control valve group 2. Hydraulic oil flows out through the drain end of sequence valve 2.1 to port T2 of control valve group 2, and then flows back to hydraulic oil tank 3 through port T2. Due to the presence of sequence valve 2.1, the output pressure of sequence valve 2.1 is 50 bar. Hydraulic oil flows in from port 1 of first pressure reducing valve 2.2 through throttle valve 2.12 and filter 2.13, and flows out from port 2 of first pressure reducing valve 2.2. Port 3 of first pressure reducing valve 2.2 is connected to hydraulic oil tank 3 through port T1 of control valve group 2. After connection, the pressure at port 2 of the first pressure reducing valve 2.2 is 35 bar, which means the pressure at port 1 of the first safety valve 2.4, port 1 of the second pressure reducing valve 2.3, port M1 of the control valve group 2, port A4 of the control valve group 2, port 1 of the check valve 2.6, and port 1 of the safety solenoid valve 2.8 is all 35 bar. Hydraulic oil at 35 bar flows in from port 1 of the second pressure reducing valve 2.3 and flows out from port 2 of the second pressure reducing valve 2.3. Port 3 of the second pressure reducing valve 2.3 is connected to the hydraulic oil tank 3 via port T1 of the control valve group 2. At this time, the pressure at port 2 of the second pressure reducing valve 2.3 is 20 bar, which means the pressure at port 1 of the second safety valve, port M2 of the control valve group 2, port 1 of the disconnect solenoid valve 2.10, and port 1 of the differential lock solenoid valve 2.9 is all 20 bar. The function of the first safety valve is to protect the pressure after port 2 of the first pressure reducing valve from exceeding 45 bar when the first pressure reducing valve fails, and to prevent excessive pressure on the shifting system connected to port A4 and the pilot system of the working device connected to port A1. The function of the second safety valve is to protect the pressure after port 2 of the second pressure reducing valve from exceeding 30 bar when the second pressure reducing valve fails, and to prevent excessive pressure on the differential lock locking control pressure connected to port A2 and the control pressure on the derailment device connected to port A3.

[0051] When hydraulic pump 1 rotates, the pressure at port A4 of control valve group 2 is 35 bar. The pressurized oil at port A4 supplies the oil inlet of the transfer case shift solenoid valve group. At this time, the transfer case solenoid valve group can switch between different gears by controlling different electrical signals.

[0052] When the enable button is pressed, the safety solenoid valve 2.8 is energized. Hydraulic oil from port 2 of the first pressure reducing valve 2.2 flows through ports 1 and 3 of the safety solenoid valve 2.8 to port A1 of the control valve assembly 2. The pressure at port A1 is the same as the pressure at port 2 of the first pressure reducing valve 2.2, which is 35 bar. Port A1 provides pilot pressure to the pilot system of the working hydraulic system. Operating the handle of the working hydraulic system at this time will achieve the corresponding action. When the enable button is not pressed, the safety solenoid valve 2.8 is not energized. Hydraulic oil from port 2 of the first pressure reducing valve 2.2 flows through ports 1 and 2 of the safety solenoid valve 2.8 to port T1 of the control valve assembly 2, and then flows back to the hydraulic oil tank 3 through port T1. The accumulator acts as a pressure shock for the pump's working chamber. Simultaneously, even when the pump is not working, it can still provide pilot system pressure oil for the working device, allowing the boom, excavator arm, and other working devices to be lowered to the ground while the machine is stopped, thus enhancing safety.

[0053] When the differential lock lock button is pressed, the differential lock solenoid valve 2.9 is energized. Hydraulic oil from port 2 of the second pressure reducing valve 2.3 flows through ports 1 and 3 of the differential lock solenoid valve 2.9 to port A2 of the control valve assembly 2. The pressure at port A2 is the same as the pressure at port 2 of the second pressure reducing valve 2.3, which is 20 bar. Port A2 is connected to the differential lock port of the bridge, and the bridge is in the differential lock locked state. When the differential lock lock button is not pressed, and the differential lock solenoid valve 2.9 is not energized, the hydraulic oil from port 2 of the second pressure reducing valve 2.3 flows through ports 1 and 2 of the differential lock solenoid valve 2.9 to port T1 of the control valve assembly 2, and then flows back to the hydraulic oil tank 3 through port T1.

[0054] When the two-wheel drive / four-wheel drive switch button is pressed, the disengagement solenoid valve 2.10 is energized. Hydraulic oil from port 2 of the second pressure reducing valve 2.3 flows through ports 1 and 3 of the disengagement solenoid valve 2.10 to port A3 of the control valve assembly 2. The pressure at port A3 is the same as the pressure at port 2 of the second pressure reducing valve 2.3, which is 20 bar. Port A3 is connected to the disengagement port of the transfer case, meaning the pressure at the disengagement port is 20 bar. At this time, the transfer case is in four-wheel drive mode. When the two-wheel drive / four-wheel drive switch button is not pressed, the disengagement solenoid valve 2.10 is not energized. Hydraulic oil from port 2 of the second pressure reducing valve 2.3 flows through ports 1 and 2 of the disengagement solenoid valve 2.10 to port T1 of the control valve assembly 2, and then flows back to the hydraulic oil tank 3 through port T1. At this time, the transfer case is in two-wheel drive mode.

[0055] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. An integrated control system for a pure electric excavator loader, characterized in that: include: Hydraulic pump, control valve assembly, hydraulic oil tank; The output end of the hydraulic pump is connected to the P port of the control valve group, and the input end of the hydraulic pump is connected to the hydraulic oil tank. The control valve group includes: the input end of a sequence valve connected to port P of the control valve group; the output end of the sequence valve connected to port B of the control valve group; the drain end of the sequence valve connected to port T2 of the control valve group; port P of the control valve group is also connected to port 1 of the first pressure reducing valve; port 2 of the first pressure reducing valve is connected to port 1 of the second pressure reducing valve, port A4 of the control valve group, and port 1 of the safety solenoid valve; port 3 of the first pressure reducing valve is connected to port 3 of the second pressure reducing valve, port 2 of the disconnect solenoid valve, port 2 of the differential lock solenoid valve, port 2 of the safety solenoid valve, and port T1 of the control valve group; port 2 of the second pressure reducing valve is connected to port 1 of the disconnect solenoid valve and port 1 of the differential lock solenoid valve; port 3 of the disconnect solenoid valve is connected to port A3 of the control valve group; port 3 of the differential lock solenoid valve is connected to port A2 of the control valve group; and port 3 of the safety solenoid valve is connected to port A1 of the control valve group.

2. The integrated control system for a pure electric excavator loader according to claim 1, characterized in that: The second port of the first pressure reducing valve is also connected to the M1 port of the control valve assembly.

3. The integrated control system for a pure electric excavator loader according to claim 1, characterized in that: The second pressure reducing valve's port 2 is also connected to the control valve assembly's port M2.

4. The integrated control system for a pure electric excavator loader according to claim 1, characterized in that: Also includes: The second port of the first safety valve and the first pressure reducing valve are also connected to the first port of the first safety valve, and the second port of the first safety valve is connected to the T1 port of the control valve assembly.

5. The integrated control system for a pure electric excavator loader according to claim 4, characterized in that: Also includes: The second safety valve and the second pressure reducing valve's port 2 are also connected to the second safety valve's port 1, and the second safety valve's port 2 is connected to the control valve group's port T1.

6. The integrated control system for a pure electric excavator loader according to claim 1, characterized in that: It also includes a one-way valve and an accumulator. Port 1 of the one-way valve is connected to port 2 of the first pressure reducing valve, port 2 of the one-way valve is connected to port 1 of the safety solenoid valve, and port 2 of the one-way valve is also connected to the accumulator.

7. The integrated control system for a pure electric excavator loader according to claim 1, characterized in that: Also includes: A throttle valve and a filter are connected in series between the P port of the control valve assembly and the I port of the first pressure reducing valve.

8. The integrated control system for a pure electric excavator loader according to claim 6, characterized in that: It also includes: a pressure test connector, wherein the two ports of the one-way valve are also connected to one end of the pressure test connector on the valve block.

9. The integrated control system for a pure electric excavator loader according to claim 1, characterized in that: Also includes: Priority valve, steering gear, steering cylinder; Specifically, the B port of the control valve group is connected to the P port of the priority valve, the CF port of the priority valve is connected to the P port of the steering gear, the LS port of the priority valve is connected to the LS port of the steering gear, the T port of the priority valve is connected to the hydraulic oil tank, the L port of the steering gear is connected to the left cylinder input end of the steering cylinder, and the R port of the steering gear is connected to the right cylinder input end of the steering cylinder.

10. The integrated control system for a pure electric excavator loader according to claim 5, characterized in that: The set pressure of the sequence valve is higher than the set pressure of the first pressure reducing valve; the set pressure of the first safety valve is higher than the set pressure of the first pressure reducing valve; the set pressure of the second pressure reducing valve is lower than the set pressure of the first pressure reducing valve; and the set pressure of the second safety valve is higher than the set pressure of the second pressure reducing valve.

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