Loader-digger with lateral moving function and control method thereof

Abstract

The backhoe loader with the lateral moving function comprises a machine frame, a lateral moving frame is arranged on a cross beam, close to one end of an excavator bucket, of the machine frame, a lateral moving mechanism for driving the lateral moving frame to move is further arranged on the machine frame, the lateral moving mechanism comprises an auxiliary oil cylinder and a main oil cylinder which are connected in series, and the auxiliary oil cylinder and the main oil cylinder are connected in parallel. The auxiliary oil cylinder and the main oil cylinder are arranged in a stepped mode, a power output rod of the main oil cylinder is hinged to a vertical leg of the machine frame, a power output rod of the auxiliary oil cylinder is hinged to the side moving frame, and the side moving device further comprises a fixing block which is used for fixedly connecting the tail end of the auxiliary oil cylinder and the tail end of the main oil cylinder. The main oil cylinder drives the auxiliary oil cylinder and the lateral moving frame to move along a cross beam of the machine frame. The range-extended double oil cylinders are connected in series, so that the requirements on the oil cylinders are reduced, the capacity of coping with loads is improved, the convenience of the whole system is improved, and the service life of the whole system is prolonged.

Description

Technical Field

[0001] The present invention relates to the technical field of loaders, and in particular to an excavator loader with a side shift function and a control method thereof. Background Art

[0002] An excavator loader is a multifunctional engineering machinery. As it combines the functions of a loader and an excavator, it is also called a "two-timing machine". It is flexible and convenient to operate, has good economic and use benefits, and is suitable for various engineering operations in construction, mining, ports and other places.

[0003] From a structural perspective, backhoe loaders are mainly classified into those with side-shift frames or those without side-shift frames. When a backhoe loader is equipped with a side-shift frame, it can improve its adaptability to different sites, making it more convenient to operate in special sites. However, the excavator loader of this type has poor stability during excavation, and the movement of the side shift frame is inconvenient. For this reason, the Chinese patent document "Excavator Loader" with application number CN201911293270.5 discloses a technical solution: a drive structure is set on the frame of the excavator loader, so that it can use one drive mechanism to simultaneously realize the movement of the leg assembly and the side shift frame, thereby simplifying the operation of the excavator loader, and at the same time, the spacing of the legs can be adjusted to achieve stable support, and this drive structure can be a double-headed structure cylinder as recorded, or a gear rack drive mechanism, or a worm gear drive mechanism; further, the Chinese patent document "A Power Side Shift Device for an Excavator Loader" with application number CN202410668313.8 records: the driver can easily drive the side shift of the sliding frame by controlling the extension and retraction of the first cylinder and the second cylinder installed on the frame and the sliding frame respectively, and the first cylinder and the second cylinder have different formation lengths, thereby achieving the purpose of driving the excavation working device to move left and right.

[0004] Among the above schemes, the defect of Scheme 1 is that it has very high requirements for the double-headed cylinder. In the process of balancing and distributing the load, high requirements are put forward for the double-headed cylinder, otherwise it is very easy to affect the efficiency and stability during operation, and when used for a long time, it is also easy to increase the wear and pressure of the double-headed cylinder, which will affect the service life of the cylinder and the entire system. When other mechanisms such as gear rack drive mechanisms or worm gear drive mechanisms are used, it is easy to make the structure too complicated, increasing the difficulty of subsequent maintenance; the two cylinders in Scheme 2 are independently set during setting, and a structural connection needs to be established through the installation tube, which makes the structure quite complicated. It is difficult to control the synchronization when the two cylinders are operated, which is easy to cause mechanical failures and uneven load distribution, and is not convenient for flexible response to the adjustment of large loads. Therefore, we need an excavator loader with a simple structure, better adaptability to the environment and load, and better stability. Summary of the invention

[0005] In order to overcome the defects of the prior art, the technical problem to be solved by the present invention is to propose an excavator loader with a side shift function and a control method thereof. By using extended-range dual cylinders in series, the requirements for the cylinders are reduced, the ability to cope with loads is improved, and the convenience and life of the overall system are improved.

[0006] To achieve this object, the present invention adopts the following technical solutions:

[0007] The present invention provides an excavator loader with a side shift function, comprising a frame, wherein a side shift frame is arranged on a cross beam near one end of the bucket, and a side shift mechanism is also arranged on the frame to drive the side shift frame to move, and the side shift mechanism comprises an auxiliary oil cylinder and a main oil cylinder connected in series, and specifically, the side shift mechanism also comprises a connecting block, and the connecting block is arranged at one end of the auxiliary oil cylinder away from the fixed block, and the auxiliary oil cylinder and the main oil cylinder are fixedly connected to the connecting block, and an oil inlet and an oil return port are also arranged on the top of the connecting block, and the inlet and the return port are provided. The oil port is connected to the oil inlet of the main oil cylinder, the oil outlet of the main oil cylinder is connected to the oil inlet of the auxiliary oil cylinder, and the oil outlet of the auxiliary oil cylinder is connected to the oil return port; the auxiliary oil cylinder and the main oil cylinder are arranged in a stepped manner, the power output rod of the main oil cylinder is hinged to the vertical leg of the frame, the power output rod of the auxiliary oil cylinder is hinged to the side shift frame, and also includes a fixing block that fixes the tail ends of the auxiliary oil cylinder and the main oil cylinder. When side shifting, the main oil cylinder drives the auxiliary oil cylinder and the side shift frame to move along the crossbeam of the frame.

[0008] During side shifting, the side shift frame moves along the crossbeam of the frame, a guide rail cooperating with the side shift frame is arranged on the side of the frame, a slideway cooperating with the fixed block and the connecting block is arranged on the top of the frame, and a clamping cylinder is arranged on the side shift frame near the four top corners so that when the auxiliary cylinder and the main cylinder move the side shift frame into place, the clamping cylinder is used to fix the position.

[0009] The auxiliary oil cylinder and the main oil cylinder are provided with articulated rings on their power output rods, the frame legs and the side shift frame are provided with articulated parts that cooperate with the articulated rings, and the axes of the articulated rings of the auxiliary oil cylinder and the main oil cylinder are vertically arranged.

[0010] In order to ensure efficient use of the power of the dual cylinders, the stroke length of the main cylinder is greater than the stroke length of the auxiliary cylinder. In this way, the main cylinder and the auxiliary cylinder can be protected to extend their service life while achieving a greater range increase.

[0011] The legs of the frame are provided with supporting oil cylinders and supporting feet. When the frame is in operation, the supporting oil cylinder drives the supporting feet to extend out of the legs of the frame to support the ground, so as to further ensure the stability during operation.

[0012] A method for controlling an excavator loader, controlling the excavator loader as described above, comprises the following steps: S00: before operation, checking the hydraulic oil level to ensure that the oil volume is sufficient, and at the same time checking whether the oil cylinder, pipeline and joints are leaking or damaged, preheating the loader to ensure that the oil temperature of the hydraulic system is appropriate, starting the engine of the loader, running the hydraulic system oil pump, and performing preliminary test operation to ensure that there is no abnormality in the system; S10: the operator uses the control panel or the joystick to extend and retract the main oil cylinder, drive the auxiliary oil cylinder and the side shift frame to start moving to one side, and when the side shift frame moves to a certain position and needs more precise adjustment, the operator Operate the hydraulic control valve to allow the hydraulic oil to flow into the auxiliary cylinder for precise adjustment; S20: The main cylinder continues to extend and retract, using its longer stroke to drive the auxiliary cylinder and the side shift frame to complete the remaining moving distance, ensuring that the side shift frame and the bucket reach the target position for operation; S30: Operate the hydraulic control valve to allow the hydraulic oil to flow back from the return oil port to the oil tank, the cylinder contracts, and the side shift frame and the bucket return to their initial positions or prepare for the next side shift; S40: After the operation is completed, the operator should check whether there is any abnormal sound or leakage in the hydraulic system, check whether the cylinder has abnormal wear or damage, and perform daily maintenance work.

[0013] In step S10, when the side shift position is short, the auxiliary oil cylinder is used to move the side shift frame initially to quickly respond to the formation. When more detailed adjustments or greater thrust are required later, the main oil cylinder starts to work.

[0014] The beneficial effects of the present invention are:

[0015] The present invention uses extended-range dual cylinders in series, so that the cylinders can ensure that the bucket can move sideways smoothly, thereby improving work efficiency; at the same time, the pressure requirements on the cylinders can be reduced, and a larger load and change can be withstand under the same hydraulic pressure. The series design can adapt to larger eccentric loads because the two cylinders can share the load, reducing mechanical failures and improving load unevenness, thereby ensuring stable operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a structural schematic diagram of an excavator loader with a side shift function provided in a specific embodiment of the present invention;

[0017] Figure 2 It is a structural schematic diagram of an excavator loader with a side shift function provided in a specific embodiment of the present invention after removing the bucket;

[0018] Figure 3 It is a structural schematic diagram of a frame with a side shift frame provided in a specific embodiment of the present invention;

[0019] Figure 4 It is a schematic diagram of the principle of a rack with a side shift rack provided in a specific embodiment of the present invention;

[0020] Figure 5 It is a structural schematic diagram of a side shift frame provided in a specific embodiment of the present invention;

[0021] Figure 6 is a schematic structural diagram of a side shift frame provided in a specific embodiment of the present invention from another perspective;

[0022] Figure 7 is a structural schematic diagram of a side shift mechanism provided in a specific embodiment of the present invention;

[0023] Figure 8 is a schematic structural diagram of a side shift mechanism provided in a specific embodiment of the present invention from another perspective;

[0024] Fig. 9 It is a schematic diagram of the side shift mechanism provided in a specific embodiment of the present invention when the main oil cylinder between the cross beams is extended and the auxiliary oil cylinder is retracted;

[0025] Fig.10 It is a schematic diagram of the side shift mechanism provided in a specific embodiment of the present invention when the main oil cylinder and the auxiliary oil cylinder between the cross beams are extended;

[0026] Fig.11 It is a schematic diagram of the side shift mechanism provided in a specific embodiment of the present invention when the main oil cylinder between the cross beams is retracted and the auxiliary oil cylinder is extended;

[0027] Fig.12 It is a schematic diagram of the side shift mechanism provided in a specific embodiment of the present invention when the main oil cylinder and the auxiliary oil cylinder between the cross beams are retracted;

[0028] Fig.13 is a schematic diagram of the travel of the side shift mechanism provided in a specific embodiment of the present invention;

[0029] In the figure:

[0030] 1. Frame; 2. Side shift frame; 3. Side shift mechanism; 31. Auxiliary oil cylinder; 32. Main oil cylinder; 33. Fixed block; 34. Connecting block; 341. Oil inlet; 342. Oil return port; 11. Guide rail; 12. Slide; 21. Clamping cylinder; 35. Articulated ring; 13. Articulated part; 14. Support foot. DETAILED DESCRIPTION

[0031] The technical solution of the present invention is further described below with reference to the accompanying drawings and through specific implementation methods.

[0032] As shown in the figure, the present invention provides an excavator loader with a side shift function, including a frame 1, a side shift frame 2 is arranged on the cross beam near one end of the bucket of the frame 1, and a side shift mechanism 3 for driving the side shift frame 2 to move is also arranged on the frame 1, and the side shift mechanism 3 includes an auxiliary oil cylinder 31 and a main oil cylinder 32 connected in series. Specifically, the side shift mechanism 3 also includes a connecting block 34, and the connecting block 34 is arranged at the end of the auxiliary oil cylinder 31 away from the fixed block 33. The auxiliary oil cylinder 31 and the main oil cylinder 32 are fixedly connected to the connecting block 34, and an oil inlet 341 and an oil return port 342 are also arranged on the top of the connecting block 34. The oil inlet 341 is connected to the oil inlet of the main oil cylinder 32, the oil outlet of the main oil cylinder 32 is connected to the oil inlet of the auxiliary oil cylinder 31, and the oil outlet of the auxiliary oil cylinder 31 is connected to the oil return port 342. In this way, the auxiliary oil cylinder 31 and the main oil cylinder 32 are connected in series, and the extension and retraction of the auxiliary oil cylinder 31 will directly affect the action of the main oil cylinder 32, and its synchronization performance is high. The auxiliary oil cylinder 31 and the main oil cylinder 32 can jointly bear the load of the mobile side shift frame 2, making the movement more stable and reducing the system vibration caused by load changes or the load offset caused by uneven speed, that is, achieving a higher thrust output with a smaller hydraulic system hydraulic oil pressure, thereby achieving efficient use of energy efficiency with a relatively simple structure, and can fundamentally and in principle improve and cope with the ability to withstand larger loads during operation. This configuration allows the system to provide a larger torque output while maintaining a compact structure, and the dual oil cylinders designed in series can better adapt to the eccentric load situation (according to the situation, an additional oil replenishment or oil release device can be designed to eliminate the accumulated error during synchronous control, which is a common method used by technicians in this field and will not be repeated here), and can distribute the load more reasonably, so that it has better adaptability to different working environments and loads, and provides better stability and controllability during side shift drive;

[0033] Furthermore, the auxiliary oil cylinder 31 and the main oil cylinder 32 are arranged in a stepped manner, the power output rod of the main oil cylinder 32 is hinged to the leg of the frame 1, and the power output rod of the auxiliary oil cylinder 31 is hinged to the side shift frame 2. Specifically, the power output rods of the auxiliary oil cylinder 31 and the main oil cylinder 32 are provided with hinge rings 35, and the leg of the frame 1 and the side shift frame 2 are fixed with hinge parts 13 that cooperate with the hinge ring 35. The axes of the hinge rings 35 of the auxiliary oil cylinder 31 and the main oil cylinder 32 are arranged vertically; in this way, the use of hinge at the connection is convenient for assembly and later maintenance, and can also eliminate and weaken the stress at the node. At the same time, the vertical arrangement of the axes of the hinge rings 35 of the auxiliary oil cylinder 31 and the main oil cylinder 32 can also keep the structure stable during movement to avoid the force from shifting toward one side.

[0034] It also includes a fixed block 33 that fixes the tail ends of the auxiliary cylinder 31 and the main cylinder 32. When side shifting, the main cylinder 32 drives the auxiliary cylinder 31 and the side shift frame 2 to move along the crossbeam of the frame 1. At the same time, the stroke length of the main cylinder 32 is greater than the stroke length of the auxiliary cylinder 31.

[0035] Definition: The telescopic stroke of the main cylinder 32 is S1. When the piston of the main cylinder 32 is fully retracted, the length dimension from the hinge ring 35 of the main cylinder 32 to the rear end of the cylinder is L1; the telescopic stroke of the auxiliary cylinder 31 is S2. When the piston of the auxiliary cylinder 31 is fully retracted, the length dimension from the hinge ring 35 of the auxiliary cylinder 31 to the rear end of the cylinder is L2; ​​and the total stroke of the side shift frame 2 is S (taking the movement from the far right to the far left as an example, Figures 9 to 11 As shown, in the commonly used specifications of oil cylinders on the market, the standard ratio of the oil cylinder stroke to the cylinder length is approximately 60%. Therefore, the cylinder length and stroke ratio of the main oil cylinder 32 is 3:2, and the cylinder length and stroke ratio of the auxiliary oil cylinder 31 is 2:1.

[0036] Therefore, in order to maximize the stroke S of the side shift frame 2, the following conditions need to be met:

[0037] When the side shift frame 2 is at the far right:

[0038] Condition 1: S = S1 + L1 - L2;

[0039] In order to enable the side shift frame 2 to move to the left and to fully utilize the stroke of each cylinder without causing waste, the following conditions should be met:

[0040] Condition 2: L1=S2+L2, and L1>L2, S1>S2, L1>S1, L2>S2 (side shift frame 2 moves to the left);

[0041] That is, the side shift frame 2 moves to the extreme positions on both sides to meet the above conditions to maximize the stroke S. The transformation formula gives condition 3: S = S1 + L1 - (L1 - S2) = S1 + S2, that is, the stroke S of the side shift frame 2 is mainly determined by the strokes of the two cylinders. Therefore, how to choose the stroke ratio of the two cylinders is particularly important.

[0042] For example, take the stroke of S=1000mm as an example. If S1 is much larger than S2, for example, S1=800mm, S2=200mm, then it means that the cylinder length of the main cylinder 32 must reach about 1200mm or larger (the cylinder length and stroke ratio of the main cylinder 32 is 3:2), which means that a cylinder with larger size and thrust is required, which significantly increases the cost, and due to the limitation of the loader beam, an overly large cylinder cannot be used; and in this case, according to condition 2, the stroke of the auxiliary cylinder 31 and the cylinder length of the auxiliary cylinder 31 must reach 200mm and 1000mm respectively, that is, the cylinder length and stroke ratio of the auxiliary cylinder 31 is 5:1. This configuration is not a standard cylinder ratio and requires additional customization, which further greatly increases the cost of the auxiliary cylinder 31, or when other standard cylinders are used, it will cause waste of stroke;

[0043] If S1 is close to S2, for example, S1=550mm, S2=450mm, then the cylinder length of the main cylinder 32 must reach about 825mm or larger (the cylinder length and stroke ratio of the main cylinder 32 is 3:2); then according to condition 2, the cylinder length of the auxiliary cylinder 31 must reach 375mm (less than S2), which is obviously impossible.

[0044] Preferably, in the present invention, the ratio of S1 to S2 is about 7-6.5:3-3.5 (the cylinder length and stroke ratio of the main oil cylinder 32 and the auxiliary oil cylinder 31 are the standard ratio of 3:2 or 2:1), that is, taking the stroke of S=1000mm as an example, the size of S1 is about 650-700mm (the size and stroke ratio of the oil cylinder is 3:2), and the size of S2 is about 300-350mm (the size and stroke ratio of the oil cylinder is 2:1); in one embodiment, the stroke length S1 of the main oil cylinder 32 is 665mm, and the stroke length S2 of the auxiliary oil cylinder 31 is 314mm; the tail ends of the auxiliary oil cylinder 31 and the main oil cylinder 32 are fixedly connected, which ensures that the relative position and movement between the two are synchronized, thereby ensuring better stability and reducing system vibration caused by load changes;

[0045] To sum up, the solution adopted in this case is to use the auxiliary cylinder 31 and the main cylinder 32 with different strokes connected in series through a hydraulic oil pipe to form a side shift mechanism 3, and then drive the side shift frame 2 to move along the crossbeam of the frame 1, thereby causing the bucket installed on the side shift frame 2 to shift sideways, thereby realizing the side shift function of the excavator loader. In this way, different cylinders are used to provide power in different operation stages, that is, to achieve segmented power output. Through the coordinated use of the auxiliary cylinder 31 and the main cylinder 32, different forces and speeds can be provided at different stages, thereby optimizing the performance and efficiency of the entire system. It should be noted that the segmented output mentioned in this case is different from the means and effects of cooperating with two independently operating cylinders to side shift the bucket. The segmented output of this case is the auxiliary cylinder 31 and the main cylinder 32 designed in series through hydraulic oil pipes, and the two independently operating cylinders are connected together through an external mechanical structure. The series design of this case is better in coping with higher loads and operating stability. Specifically, during use, the auxiliary cylinder 31 can be used for quick response and initial movement in the initial stage. This is because the auxiliary cylinder 31 has a shorter stroke and can provide faster action; subsequently, when more detailed adjustments or greater thrust are needed, the main cylinder 32 starts working. Since the main cylinder 32 has a longer stroke, it can provide more lasting power output to ensure that the side shift frame can move smoothly into place, or finally the short-stroke auxiliary cylinder 31 will make fine adjustments when the side shift frame 2 approaches the target position to ensure the accuracy and stability of the bucket side shift, provide more refined control, and make the operation more flexible; from the perspective of the entire use stroke, in most of the stroke of the side shift frame 2, the main cylinder 32 bears the main load when it is longer, which can reduce the wear of the auxiliary cylinder 31; in short strokes, the auxiliary cylinder 31 bears the main load, which can reduce the wear of the main cylinder 32; and in the process of large loads, they can share the load, thereby reducing the pressure of the hydraulic system, reducing the wear of the cylinder, and extending the service life.

[0046] In order to facilitate the movement of the connecting block 34 along the cross beam on the top of the frame 1, a guide rail 11 cooperating with the side shift frame 2 is arranged on the side of the frame 1, so that after the side shift frame 2 is installed on the frame 1, it can be moved along the cross beam on the top of the frame 1, and a slideway 12 cooperating with the fixed block 33 and the connecting block 34 is arranged on the top of the frame 1. Clamping cylinders 21 are arranged on the side shift frame 2 near the four top corners, so that when the auxiliary cylinder 31 and the main cylinder 32 move the side shift frame 2 into place, the clamping cylinder 21 is used to fix the position.

[0047] Preferably, in order to enhance the supporting effect during operation, a supporting cylinder (not shown) and a supporting foot 14 are provided in the vertical leg of the frame 1. During operation, the supporting cylinder drives the supporting foot 14 to extend from the vertical leg of the frame 1 to support the ground, so as to provide auxiliary support, thereby preventing the load from acting on the frame 1 alone for a long time during operation, and avoiding excessive damage to the frame 1.

[0048] A method for controlling an excavator loader, controlling the excavator loader as described above, comprises the following steps: S00: before operation, checking the hydraulic oil level to ensure that the oil is sufficient, and at the same time checking whether the oil cylinder, pipeline and joints are leaking or damaged, preheating the loader to ensure that the oil temperature of the hydraulic system is appropriate, starting the engine of the loader, running the hydraulic system oil pump, and performing preliminary test operation to ensure that there is no abnormality in the system; S10: the operator uses the control panel or the joystick to extend and retract the main oil cylinder 32, driving the auxiliary oil cylinder 31 and the side shift frame 2 to start moving to one side. When the side shift frame 2 moves to a certain position and needs more precise adjustment, the hydraulic Control valve to allow hydraulic oil to flow into auxiliary cylinder 31 for precise adjustment; S20: main cylinder 32 continues to extend and retract, using its longer stroke to drive auxiliary cylinder 31 and side shift frame 2 to complete the remaining moving distance, ensuring that side shift frame 2 and bucket reach the target position for operation; S30: operate the hydraulic control valve to allow hydraulic oil to flow back to the oil tank from return oil port 342, the cylinder contracts, and the side shift frame 2 and bucket return to the initial position or prepare for the next side shift; S40: after the operation is completed, the operator should check whether there is any abnormal sound or leakage in the hydraulic system, check whether the cylinder has abnormal wear or damage, and perform daily maintenance work.

[0049] Preferably, in step S10, when the lateral shift position is short, the auxiliary oil cylinder 31 is initially used to move the lateral shift frame 2 to quickly respond to the formation. When more detailed adjustments or greater thrust are required later, the main oil cylinder 32 starts working; in step S10, in order to achieve precise control of the speed and force of the auxiliary oil cylinder 31 and the main oil cylinder 32, a hydraulic control valve (such as a throttle valve, a reversing valve, an overflow valve, etc.) can be used to accurately control the flow direction and pressure of the hydraulic oil; or an electronic control system, such as a proportional servo valve, can adjust the speed and position of the cylinder according to the real-time feedback signal; or a synchronous control loop (such as a series synchronous loop, a diverter valve synchronous loop, etc.) is used to ensure the action of the two cylinders; or feedback devices such as displacement sensors and pressure sensors can monitor the position and load of the cylinder in real time, and adjust them through the control system to ensure precise synchronous control. These are all control means in this field and will not be described in detail in this case.

[0050] In summary, during the process of adjusting the side shift frame 2 and the bucket side shift, if Figures 9 to 12As shown, taking the initial bucket at the rightmost side as an example, the main cylinder 32 is in the extended state with the longest stroke, and the auxiliary cylinder 31 is in the retracted state with the shortest stroke. At this time, to adjust the bucket from the rightmost side to the leftmost side, the auxiliary cylinder 31 can be extended to move the bucket first, and then when the auxiliary cylinder 31 reaches the maximum stroke, the main cylinder 32 can be retracted. When the main cylinder 32 is fully retracted, the side shift frame 2 and the bucket move from the rightmost side to the leftmost side; conversely, the side shift frame 2 and the bucket can be moved from the leftmost side back to the rightmost side. In this way, not only the above-mentioned technical effects can be achieved, but also the stroke can be increased by one step compared to a single cylinder, so that the side shift frame 2 and the bucket have a larger side shift range. (The above describes the method of first extending the auxiliary cylinder 31 and then retracting the main cylinder 32. It is also possible to first retract the main cylinder 32 and then extend the auxiliary cylinder 31 as recorded in this case.)

[0051] The present invention is described by preferred embodiments, and those skilled in the art will appreciate that various changes or equivalent substitutions may be made to these features and embodiments without departing from the spirit and scope of the present invention. The present invention is not limited to the specific embodiments disclosed herein, and other embodiments falling within the claims of this application are within the scope of protection of the present invention.

Claims

1. An excavator loader with a side shift function, comprising a frame (1), wherein the frame (1) is provided with a side shift frame (2) on a cross beam near one end of a bucket, and the frame (1) is also provided with a side shift mechanism (3) for driving the side shift frame (2) to move, wherein: The side shift mechanism (3) comprises an auxiliary oil cylinder (31) and a main oil cylinder (32) connected in series, wherein the auxiliary oil cylinder (31) and the main oil cylinder (32) are arranged in a stepped manner, the power output rod of the main oil cylinder (32) is hinged to the standing leg of the frame (1), the power output rod of the auxiliary oil cylinder (31) is hinged to the side shift frame (2), and further comprises a fixing block (33) that fixes the tail ends of the auxiliary oil cylinder (31) and the main oil cylinder (32). When side shifting, the main oil cylinder (32) drives the auxiliary oil cylinder (31) and the side shift frame (2) to move along the crossbeam of the frame (1).

2. The backhoe loader with side shift function according to claim 1, characterized in that: The side shift mechanism (3) further comprises a connecting block (34), wherein the connecting block (34) is arranged at one end of the auxiliary oil cylinder (31) away from the fixed block (33), the auxiliary oil cylinder (31) and the main oil cylinder (32) are fixedly connected to the connecting block (34), and an oil inlet (341) and an oil return port (342) are also arranged on the top of the connecting block (34), the oil inlet (341) is connected to the oil inlet of the main oil cylinder (32), the oil outlet of the main oil cylinder (32) is connected to the oil inlet of the auxiliary oil cylinder (31), and the oil outlet of the auxiliary oil cylinder (31) is connected to the oil return port (342).

3. The backhoe loader with side shift function according to claim 2, characterized in that: A guide rail (11) cooperating with the side shift frame (2) is arranged on the side of the frame (1), a slideway (12) cooperating with the fixing block (33) and the connecting block (34) is arranged on the top of the frame (1), and a clamping cylinder (21) is arranged near the four top corners on the side shift frame (2) so that when the auxiliary cylinder (31) and the main cylinder (32) move the side shift frame (2) into position, the clamping cylinder (21) is used to fix the position.

4. The backhoe loader with side shift function according to claim 3, characterized in that: The power output rods of the auxiliary oil cylinder (31) and the main oil cylinder (32) are provided with hinged rings (35); the legs of the frame (1) and the side shift frame (2) are fixed with hinged parts (13) that cooperate with the hinged ring (35); the axes of the hinged rings (35) of the auxiliary oil cylinder (31) and the main oil cylinder (32) are vertically arranged.

5. The backhoe loader with side shift function according to claim 3, characterized in that: The stroke length of the main oil cylinder (32) is greater than the stroke length of the auxiliary oil cylinder (31).

6. The backhoe loader with side shift function according to claim 5, characterized in that: A supporting oil cylinder and a supporting foot (14) are arranged inside the standing leg of the frame (1). During operation, the supporting oil cylinder drives the supporting foot (14) to extend out of the standing leg of the frame (1) to support the ground.

7. A backhoe loader control method, characterized in that: Controlling the backhoe loader according to any one of claims 1 to 6 comprises the following steps: S00: Before operation, check the hydraulic oil level to ensure that the oil volume is sufficient. At the same time, check whether the oil cylinder, pipelines and joints are leaking or damaged. Preheat the loader to ensure that the hydraulic system oil temperature is appropriate. Start the loader engine, let the hydraulic system oil pump run, and conduct preliminary test operations to ensure that there is no abnormality in the system. S10: The operator uses the control panel or the joystick to extend and retract the main oil cylinder (32), thereby driving the auxiliary oil cylinder (31) and the side shift frame (2) to start moving to one side. When the side shift frame (2) moves to a certain position and needs more precise adjustment, the operator operates the hydraulic control valve to allow hydraulic oil to flow into the auxiliary oil cylinder (31) for precise adjustment. S20: The main oil cylinder (32) continues to extend and retract, using its longer stroke to drive the auxiliary oil cylinder (31) and the side shift frame (2) to complete the remaining moving distance, ensuring that the side shift frame (2) and the bucket reach the target position for operation; S30: operating the hydraulic control valve to return the hydraulic oil from the oil return port (342) to the oil tank, the oil cylinder contracts, and the side shift frame (2) and the bucket return to the initial position or prepare for the next side shift; S40: After the operation is completed, the operator should check the hydraulic system for abnormal sounds or leaks, check the cylinder for abnormal wear or damage, and perform routine maintenance.

8. The backhoe loader control method according to claim 7, characterized in that: In step S10, when the side shift position is short, the auxiliary oil cylinder (31) is initially used to move the side shift frame (2) to quickly respond to the formation. When more detailed adjustment or greater thrust is required later, the main oil cylinder (32) starts to work.

Images