A slip system, a regulating method and a working machine

Abstract

This invention relates to the field of slewing drive technology, and discloses a sliding system, adjustment method, and engineering machinery. The sliding system of this invention is applied to the slewing mechanism of engineering machinery, including a hydraulic oil tank, a hydraulic motor, a first pipeline, a second pipeline, and a slewing control module. The hydraulic motor is connected to the hydraulic oil tank, and the two pipelines are respectively connected to its inlet and outlet ends. The slewing control module includes a slewing directional valve, a free-slide proportional valve, and two slewing balance valves. The slewing directional valve can switch between blocking and conducting positions. The slewing balance valve has a load feedback valve core. The free-slide proportional valve is connected in parallel to two pipelines and is connected to a bypass oil circuit and the main machine tilt sensor. Its opening degree is controlled by its current signal. The sliding system of this invention can achieve stepless speed regulation of slewing, reduce hydraulic shock, and prevent slippage by maintaining pressure through the slewing balance valve. Compared with mechanical speed regulation, it is smoother and can achieve independent control of forward and reverse rotation, improving operational safety and stability.

Description

Technical Field

[0001] This invention relates to the field of rotary drive technology, specifically to a sliding system, adjustment method, and engineering machinery. Background Technology

[0002] In related technologies, the slewing system of lifting equipment is mostly an open hydraulic system. This type of system can meet the basic usage requirements for slewing operations on flat ground. However, in slope conditions, because the open hydraulic system is not equipped with a suitable balance valve, it cannot effectively control the pressure and adapt the load to the slewing motor. This easily leads to problems such as weak slewing and reverse slippage, which not only affects construction efficiency but also poses serious operational safety hazards. In the free-slip condition, the engineering machinery in related technologies generally uses a switching valve to achieve the free-slip function. Since the switching valve only has two working states, on and off, and does not have continuous opening adjustment capability, the slewing speed will change abruptly during the switching of the free-slip mode, generating significant slewing impact, which seriously affects the smoothness of operation and causes mechanical wear on the slewing mechanism of the engineering machinery. Summary of the Invention

[0003] This invention provides a sliding system, adjustment method, and engineering machinery to solve the problems of weak rotation and reverse slippage in hydraulic slewing systems under slope conditions due to the lack of a suitable balance valve, and the problem of sudden changes in rotation speed and rotational impact caused by the use of a switching valve when switching modes under free sliding conditions.

[0004] In a first aspect, the present invention provides a sliding system applied to the slewing mechanism of engineering machinery, comprising:

[0005] A hydraulic motor is suitable as a power source for a rotary mechanism. The hydraulic motor includes a motor inlet end and a motor outlet end. The pressure difference between the motor inlet end and the motor outlet end is defined as the motor pressure difference. The hydraulic motor is suitable for controlling the motion state of the rotary mechanism based on the motor pressure difference. A rotary reducer is driven by the output torque of a hydraulic motor. The rotary reducer is suitable for outputting the torque of the hydraulic motor to meet the torque requirements of the rotary mechanism. Slewing bearing, suitable for connecting the upper structure and chassis of a crane; The sliding system is suitable for providing flow to a hydraulic motor and driving the hydraulic motor to work; The sliding system includes: A hydraulic oil tank, suitable for storing pressure media, and connected to the hydraulic motor pipeline; The first and second pipes are connected to the motor inlet and the motor outlet, respectively. The slewing control module is connected between the hydraulic motor and the hydraulic oil tank. The slewing control module includes a slewing directional valve, a free-slip proportional valve, and two slewing balance valves. Beneficial effects: By connecting a free-slip proportional valve in parallel between the first and second pipelines and connecting it to the hydraulic oil tank via a bypass oil line, and electrically connecting the free-slip proportional valve to the main machine tilt sensor, the continuous opening of the valve is controlled by the current signal output by the tilt sensor. This replaces the control method of using a switching valve in related technologies. It can not only adjust the hydraulic oil volume according to the actual tilt angle of the construction machinery to achieve stepless control of the rotation speed, but also avoid the problem of sudden changes in rotation speed caused by the on / off switching of traditional switching valves in related technologies. This effectively reduces the hydraulic shock during mode switching and improves the smoothness of rotation operation.

[0006] The open-type slewing system in related technologies, lacking a suitable balance valve, can only meet basic operational needs under flat ground conditions. When operating on slopes, it is prone to problems such as insufficient slewing power and reverse slippage, making it difficult to guarantee operational stability and safety. The sliding slewing system in this embodiment prevents hydraulic oil backflow through the pressure-holding function of the slewing balance valve, avoiding the problem of reverse slippage of the slewing mechanism and improving the safety of slewing operations.

[0007] Compared to mechanical speed regulation, the hydraulic braking in this embodiment achieves braking and limiting of the rotary mechanism through pressure holding and flow control in the hydraulic circuit. It can adjust the braking force in real time according to the working conditions, effectively avoiding the impact and jamming risks caused by mechanical hard contact. It forms a reliable hydraulic lock-up under complex working conditions such as slopes, avoiding the risk of slippage. Traditional mechanical speed regulation mostly relies on motor speed regulation, which can only complete multi-level step speed adjustment and cannot achieve continuous stepless control of the rotary speed. The smoothness and adaptability of speed regulation are not as good as the control method of hydraulic braking.

[0008] In one optional embodiment, the directional valve has a first open position and a second open position. The directional valve is adapted to be in the first open position so that hydraulic oil flows from the directional valve through the first pipeline into the motor inlet end, or the directional valve is adapted to be in the second open position so that hydraulic oil flows from the directional valve through the second pipeline into the motor outlet end.

[0009] Beneficial effects: By switching the first and second conduction positions of the slewing valve, the input direction of hydraulic oil to the hydraulic motor is changed, thereby achieving independent control of the forward and reverse rotation of the slewing mechanism. Whether the hydraulic motor is operating in forward or reverse rotation, a reliable hydraulic lock can be formed through the pressure-holding action of the slewing balance valve on the corresponding pipeline, effectively preventing the reverse flow of hydraulic oil and avoiding the risk of slippage under forward and reverse operation from the oil circuit level. At the same time, during the forward and reverse hydraulic operation, the slewing valve in the corresponding pipeline can dynamically adjust the valve core opening according to the load feedback valve core change, thereby achieving continuous adjustment of the flow in the first or second pipeline. Combined with the stepless opening control of the free-slip proportional valve, the hydraulic motor can achieve stepless speed regulation of rotation in both forward and reverse rotation, ensuring the smoothness of the slewing action under different directions and loads.

[0010] In one alternative implementation, it further includes: The first pilot proportional valve is adapted to adjust the hydraulic oil flow rate in the first pipeline when the directional valve is in the first open position. In one alternative implementation, it further includes: The second pilot proportional valve is suitable for adjusting the flow rate of hydraulic oil from the second pipeline when the directional valve is in the second open position.

[0011] Beneficial effects: By adjusting the first pilot proportional valve and the second pilot proportional valve, the initial hydraulic oil quantity input to the first and second pipelines can be regulated during the initial oil supply stage of the slewing system when the directional valve is in the first and second conducting positions, respectively. This provides a suitable initial oil supply basis for the forward and reverse rotation of the hydraulic motor, and realizes flow control during the start-up stage of the slewing action.

[0012] In one alternative embodiment, the rotary balance valve includes a check valve, wherein the one-way valve is oriented from the rotary directional valve toward the hydraulic motor.

[0013] Beneficial effects: By installing a check valve in the rotary balance valve and limiting its conduction direction to be from the rotary directional valve to the hydraulic motor, it can ensure that when the hydraulic oil tank actively supplies oil to the hydraulic motor, the hydraulic oil can flow smoothly through the first or second pipeline into the hydraulic motor in the preset direction, providing a stable oil supply path for the rotary mechanism. On the other hand, it can block the reverse flow of hydraulic oil from the hydraulic motor to the rotary directional valve. Under slope conditions, whether the hydraulic motor switches from forward rotation to stop or from reverse rotation to stop, the rotary directional valve can form a reliable hydraulic lock.

[0014] Secondly, the present invention also provides an adjustment method applicable to the sliding system described above, the adjustment method comprising: Obtain instruction information and adjust the slewing reversing valve, free-slide proportional valve and two slewing balance valves based on the instruction information to control the switching of the working mode of the slewing mechanism; The operating modes include stop drift mode, controlled steering mode, and stop anti-slip mode.

[0015] In one optional implementation, command information is acquired, and based on the command information, the slewing reversing valve, the free-slip proportional valve, and the two slewing balance valves are adjusted to control the switching of the slewing mechanism's operating mode, including: Obtain a stop drift signal, control the slewing reversing valve to switch to the blocking position, and control the free-slide proportional valve to be energized so that the hydraulic oil at the motor inlet and outlet of the hydraulic motor flows through the first or second pipeline, and then through the free-slide proportional valve and the bypass oil circuit into the hydraulic oil tank until the motor pressure difference is zero, so that the slewing mechanism is in the stop drift mode.

[0016] Beneficial effects: By acquiring the command information to stop drifting, the slewing reversing valve is switched to the blocking position, and the free-slip proportional valve is energized and opened, allowing the hydraulic oil at the inlet and outlet of the hydraulic motor to flow back to the hydraulic oil tank through the first pipeline, the second pipeline, the free-slip proportional valve, and the bypass oil circuit until the motor pressure difference is zero. At this time, the slewing mechanism slowly decelerates to a stop. Compared with the form of directly braking and forcibly locking the motor, the adjustment method of the stop drifting mode in this embodiment can avoid the hydraulic and mechanical shocks caused by rigid braking, effectively reduce the stress impact and fatigue wear on key components such as the slewing support and the deceleration mechanism, extend the service life of the equipment, make the shutdown process smoother and gentler, significantly improve the overall stability and operational safety, and achieve a stop sliding effect without impact or stress concentration.

[0017] In one optional implementation, the adjustment method further includes: acquiring a speed adjustment signal, adjusting the opening of the free-slip proportional valve to adjust the speed at which the motor pressure difference drops to zero, and thereby adjusting the slip distance of the rotary mechanism.

[0018] Beneficial effects: By acquiring the speed adjustment signal, the opening of the free-slip proportional valve is adjusted in real time, thereby controlling the speed at which the motor pressure difference reaches zero, and thus adjusting the sliding distance of the slewing mechanism. In stop-drift mode, the sliding speed and sliding distance can be controlled according to actual operational needs, avoiding the risks of excessive sliding, failure to rotate, or collisions caused by uncontrolled sliding. The adjustment method of this embodiment retains the advantages of flexible pressure relief and shock-free shutdown, while also achieving controllable and adjustable sliding process, further improving the accuracy of the slewing mechanism's stopping position and operational safety, and enhancing the system's adaptability to different working conditions.

[0019] In one optional implementation, command information is acquired, and based on the command information, the slewing reversing valve, the free-slip proportional valve, and the two slewing balance valves are adjusted to control the switching of the slewing mechanism's operating mode, including: Acquire controlled steering signals and tilt angle signals of construction machinery; If the tilt angle of the construction machinery is 0°, the control slewing valve switches to the first or second conduction position, and the control free-sliding proportional valve is de-energized; based on the load feedback valve core responding to load changes, the opening of the slewing balance valve is adjusted, and the flow rate of the first or second pipeline is adjusted, so that the slewing mechanism is in a controlled steering mode. If the tilt angle of the construction machinery is not 0°, the control slewing valve is switched to the first or second conduction position, the control free-slide proportional valve is energized, and the opening of the free-slide proportional valve is adjusted so that the hydraulic oil from the motor inlet and outlet of a portion of the hydraulic motor flows through the first or second pipeline, and then through the free-slide proportional valve and the bypass oil circuit into the hydraulic oil tank; and based on the load feedback valve core responding to load changes, the opening of the slewing balance valve is adjusted to regulate the flow rate of the first or second pipeline, so that the slewing mechanism is in a controlled steering mode.

[0020] Beneficial effects: When the construction machinery is operating on level ground, the control free proportional valve loses power, cutting off the bypass oil circuit. The slewing system, through the load feedback valve core of the slewing balance valve, adjusts the pipeline opening and hydraulic oil flow according to the load size, so that the slewing speed matches the actual load. This achieves stepless control of the hydraulic oil volume in the first and second pipelines, ensuring that, under the premise of sufficient slewing power, the slewing speed of the hydraulic motor is smoothly adjusted with the load change, and the steering action of the slewing mechanism is smooth and shock-free, meeting the smooth slewing operation requirements under level ground conditions.

[0021] When the construction machinery is in a slope condition, the free-slip proportional valve is energized and adjusts its opening, allowing some hydraulic oil to flow back to the hydraulic oil tank through the bypass oil circuit. At the same time, the load feedback valve core of the slewing balance valve adjusts the pipeline flow according to the load change, so that the slewing mechanism still has stable, controllable and smooth steering performance under slope conditions, significantly improving the safety and reliability under complex working conditions.

[0022] In one optional implementation, command information is acquired, and based on the command information, the slewing reversing valve, the free-slip proportional valve, and the two slewing balance valves are adjusted to control the switching of the slewing mechanism's operating mode, including: Obtain a stop and anti-slip signal, control the slewing reversing valve to switch to the blocking position, and control the free-sliding proportional valve to de-energize, so that the slewing balance valve maintains pressure on the first or second pipeline, and puts the slewing mechanism in the stop and anti-slip mode.

[0023] Beneficial effects: The adjustment method in this embodiment enables the construction machinery to maintain pressure in the first or second pipeline through the rotary balance valve when it is stopped or during work breaks. This stabilizes the pressure and pressure difference at both ends of the hydraulic motor, ensuring that the hydraulic motor does not reverse, swerve, or slip. At the same time, the reverse shut-off function of the check valve prevents hydraulic oil leakage and pressure loss, ensuring that the rotary mechanism always remains reliably locked in the stop, parked, or slope conditions. This avoids safety risks such as brake failure and accidental rotation caused by pressure drop, significantly improving the safety, stability, and parking reliability of the construction machinery when it is stopped.

[0024] Thirdly, the present invention also provides an engineering machine, which includes a slewing mechanism, and the slewing mechanism includes the sliding system as described above. Attached Figure Description

[0025] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0026] Figure 1 This is a schematic diagram of a sliding system according to an embodiment of the present invention; Figure 2 for Figure 1 A schematic diagram of the slewing control module is shown. Figure 3 This is a front view of the entire lifting equipment.

[0027] Explanation of reference numerals in the attached figures: 1. Rotary pump; 101. First pipeline; 102. Second pipeline; 103. Bypass oil circuit; 2. Servo pump; 3. Servo control module; 4. Pilot handle; 5. Rotation control module; 51. Relief valve; 521. First pilot proportional valve; 522. Second pilot proportional valve; 53. Rotation directional valve; 531. First open position; 532. Blocking position; 533. Second open position; 54. Oil replenishing valve; 55. Rotary balance valve; 56. Free-slip proportional valve; 57. Rotary buffer valve; 6. Hydraulic motor; 61. Motor inlet end; 62. Motor outlet end; 7. Slewing reducer; 8. Radiator; 9. Hydraulic oil tank; 10. Slewing bearing. Detailed Implementation

[0028] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments 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, 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 scope of protection of the present invention.

[0029] In the field of construction machinery, the slewing system is the core execution system of equipment such as cranes, excavators, and rotary drilling rigs. Its working performance directly determines the operating accuracy, efficiency, and safety of the equipment, and it is widely used in various complex working conditions such as building construction, bridge construction, and mining.

[0030] In related technologies, the slewing systems of construction machinery are mostly open hydraulic systems. While these systems can meet basic usage requirements for slewing operations on flat ground, they are ineffective in slope conditions due to the lack of suitable balance valves. This results in insufficient pressure control and load matching for the slewing motor, leading to unstable oil pressure on both sides of the motor and a high risk of weak slewing and reverse slippage. This not only affects construction efficiency but also poses serious safety hazards. In free-slip operation, construction machinery in related technologies generally uses on / off valves to achieve this function. However, these valves only have on / off states and lack continuous opening adjustment capabilities. Therefore, during the switching of free-slip modes, the slewing speed changes abruptly, causing significant slewing impacts that severely affect operational stability and cause mechanical wear on the slewing mechanism.

[0031] The existing open hydraulic system and on / off valve control method used in the slewing system of construction machinery are difficult to adapt to the safety operation requirements under slope conditions and the smooth switching requirements under free sliding conditions. They have problems such as weak slewing, reverse slippage, large switching impact, and serious mechanical wear, and cannot meet the reliable operation requirements of construction machinery. Therefore, it is urgent to optimize and improve the existing slewing system.

[0032] The following is combined Figures 1 to 3 The following describes embodiments of the present invention.

[0033] According to an embodiment of the present invention, in one aspect, a sliding system is provided for the slewing mechanism of engineering machinery, the slewing mechanism comprising: The hydraulic motor 6 is suitable as a power source for the rotary mechanism. The hydraulic motor 6 includes a motor inlet end 61 and a motor outlet end 62. The pressure difference between the motor inlet end 61 and the motor outlet end 62 is defined as the motor pressure difference. The hydraulic motor 6 is suitable for controlling the motion state of the rotary mechanism based on the motor pressure difference. The rotary reducer 7 is driven by the output torque of the hydraulic motor 6. The rotary reducer 7 is adapted to convert the high-speed, low-torque output of the hydraulic motor 6 into a low-speed, high-torque output to meet the high torque requirement of the rotary mechanism. Slewing bearing 10 is suitable for connecting the upper structure and chassis of a crane; The sliding system is suitable for providing flow to the hydraulic motor 6 and driving the hydraulic motor 6 to work. The sliding system includes: Hydraulic oil tank 9 is suitable for storing pressure medium and is connected to the hydraulic motor 6 pipeline; The first pipe 101 and the second pipe 102 are respectively connected to the motor inlet end 61 and the motor outlet end 62; The slewing control module 5 is connected between the hydraulic motor 6 and the hydraulic oil tank 9. The slewing control module 5 includes a slewing directional valve 53, a free-slip proportional valve 56, and two slewing balance valves 55. The directional valve 53 is adapted to switch between the blocking position 532 and the opening position. When the directional valve 53 is in the blocking position 532, it is adapted to cut off the active oil supply passage from the hydraulic oil tank 9 to the hydraulic motor 6. When the directional valve 53 is in the opening position, it is adapted to establish a controllable oil supply passage from the hydraulic oil tank 9 to the hydraulic motor 6. Two rotary balancing valves 55 are respectively installed on the first pipeline 101 and the second pipeline 102. The rotary balancing valve 55 includes a load feedback valve core, which is adapted to dynamically adjust the valve core opening in response to load changes, so as to regulate the flow rate of the first pipeline 101 or the second pipeline 102. The free-slide proportional valve 56 is connected in parallel between the first pipeline 101 and the second pipeline 102, and also includes a bypass oil passage 103. The bypass oil passage 103 is adapted to connect the hydraulic oil tank 9 and the free-slide proportional valve 56. The free-slide proportional valve 56 is adapted to connect the first pipeline 101 and the second pipeline 102 with the bypass oil passage 103 when energized, and to cut off the bypass oil passage 103 when de-energized. The free-slide proportional valve 56 is electrically connected to the host tilt sensor, and the valve opening of the free-slide proportional valve 56 is controlled by the current signal output by the host tilt sensor.

[0034] By connecting the free-slip proportional valve 56 in parallel between the first pipeline 101 and the second pipeline 102, and connecting it to the hydraulic oil tank 9 through the bypass oil line 103, and electrically connecting the free-slip proportional valve 56 to the main machine tilt sensor, the valve's continuous opening is controlled by the current signal output by the tilt sensor. This replaces the control method of using a switching valve in related technologies. It can not only adjust the hydraulic oil volume according to the actual tilt angle of the construction machinery and achieve stepless control of the rotation speed, but also avoid the problem of sudden changes in rotation speed caused by the on / off switching of traditional switching valves in related technologies. This effectively reduces the hydraulic shock during mode switching and improves the smoothness of rotation operation.

[0035] The open-type slewing system in related technologies, lacking a suitable balance valve, can only meet basic operational needs under flat ground conditions. However, under incline conditions, it is prone to problems such as insufficient slewing power and reverse slippage, making it difficult to guarantee operational stability and safety. The sliding slewing system in this embodiment prevents hydraulic oil backflow through the pressure-holding function of the slewing balance valve 55, avoiding the problem of reverse slippage of the slewing mechanism and improving the safety of slewing operations.

[0036] Compared to mechanical speed regulation, the hydraulic braking in this embodiment achieves braking and limiting of the rotary mechanism through pressure holding and flow control in the hydraulic circuit. It can adjust the braking force in real time according to the working conditions, effectively avoiding the impact and jamming risks caused by mechanical hard contact. It forms a reliable hydraulic lock-up under complex working conditions such as slopes, avoiding the risk of slippage. Traditional mechanical speed regulation mostly relies on motor speed regulation, which can only complete multi-level step speed adjustment and cannot achieve continuous stepless control of the rotary speed. The smoothness and adaptability of speed regulation are not as good as the control method of hydraulic braking.

[0037] In one embodiment, the directional valve 53 is configured to be in a first directional position 531 and a second directional position 533. The directional valve 53 is adapted to be in the first directional position 531 so that hydraulic oil flows from the directional valve 53 through the first pipeline 101 into the motor inlet end 61. Alternatively, the directional valve 53 is adapted to be in the second directional position 533 so that hydraulic oil flows from the directional valve 53 through the second pipeline 102 into the motor outlet end 62.

[0038] By switching the first conduction position 531 and the second conduction position 533 of the slewing valve 53, the input direction of hydraulic oil to the hydraulic motor 6 is changed, so as to achieve independent control of the slewing mechanism in both forward and reverse directions. Whether the hydraulic motor 6 is operating in forward or reverse, it can form a reliable hydraulic lock through the pressure holding effect of the slewing balance valve 55 on the corresponding pipeline, effectively preventing the reverse flow of hydraulic oil and avoiding the risk of slippage under forward and reverse operation from the oil circuit level. At the same time, during the forward and reverse hydraulic operation, the slewing valve 53 in the corresponding pipeline can dynamically adjust the valve core opening through the load feedback valve core according to the load change, so as to achieve continuous adjustment of the flow of the first pipeline 101 or the second pipeline 102. With the stepless opening control of the free-slip proportional valve 56, the hydraulic motor 6 can achieve stepless speed regulation of the slewing speed in both forward and reverse directions, ensuring the smoothness of the slewing operation under different directions and different loads.

[0039] In one embodiment, it also includes: A first pilot proportional valve 521 and a second pilot proportional valve 522, wherein the first pilot proportional valve 521 is adapted to adjust the hydraulic oil flow rate of the first pipeline 101 when the directional valve 53 is in the first open position 531, and the second pilot proportional valve 522 is adapted to adjust the hydraulic oil flow rate of the second pipeline 102 when the directional valve 53 is in the second open position 533; or, only the first pilot proportional valve 521 is included; or, only the second pilot proportional valve 522 is included.

[0040] By adjusting the first pilot proportional valve 521 and the second pilot proportional valve 522, the initial hydraulic oil input to the first pipeline 101 and the second pipeline 102 can be regulated when the directional valve 53 is in the first open position 531 and the second open position 533, respectively, during the initial oil supply stage of the slewing system. This provides a suitable initial oil supply basis for the forward and reverse rotation of the hydraulic motor 6, and realizes flow control during the start-up stage of the slewing action.

[0041] In one embodiment, the rotary balance valve 55 includes a one-way valve, the one-way valve being oriented from the rotary directional valve 53 toward the hydraulic motor 6.

[0042] By setting a check valve in the rotary balance valve 55 and limiting its conduction direction to be from the rotary reversing valve 53 to the hydraulic motor 6, it can ensure that when the hydraulic oil tank 9 actively supplies oil to the hydraulic motor 6, the hydraulic oil can flow smoothly through the first pipeline 101 or the second pipeline 102 into the hydraulic motor 6 in the preset direction, providing a stable oil supply path for the rotary mechanism; on the other hand, it can block the reverse flow of hydraulic oil from the hydraulic motor 6 to the rotary reversing valve 53. Under the slope condition, whether the hydraulic motor 6 switches from the forward rotation state to the stop state or from the reverse rotation state to the stop state, the rotary reversing valve 53 can form a reliable hydraulic lock.

[0043] In one embodiment, a rotary buffer valve 57 is further included, which is arranged in parallel between the first pipeline 101 and the second pipeline 102.

[0044] When the slewing mechanism starts, reverses, or stops rapidly, the pipeline on one side of the hydraulic motor 6 forms a momentary high pressure due to inertia, while the pipeline on the other side forms a negative pressure. At this time, the pressure oil in the high-pressure side pipeline can be buffered and overflowed to the low-pressure side pipeline through the slewing buffer valve 57, thereby absorbing the inertial impact and pressure peak generated when the slewing mechanism stops or reverses. This avoids the hydraulic system from being damaged by the impact of sudden pressure rise, which could cause damage to the pipeline, seals, and hydraulic components. This makes the slewing action start and stop more smoothly and gently, improving the stability and service life of the system.

[0045] In one embodiment, a rotary reducer 7 is also included, which is connected to the hydraulic motor 6.

[0046] By setting up the slewing reducer 7, the output speed of the hydraulic motor 6 can be reduced and the torque increased. While reducing the speed of the slewing mechanism, the output torque is increased, making the slewing action smoother and more controllable. This meets the slewing operation requirements of engineering machinery with large loads and large torques, and further enhances the load-bearing capacity and operational stability of the slewing mechanism.

[0047] In one embodiment, a servo pump 2 and a servo control module 3 are also included, which are connected by hydraulic lines.

[0048] In one embodiment, a radiator 8 is also included. In this embodiment, the radiator 8 is an air-cooled radiator 8, which is installed in the hydraulic pipeline and is used to dissipate heat and cool the hydraulic oil.

[0049] By installing radiator 8, the heat generated by the hydraulic system during operation can be removed in a timely manner, preventing the hydraulic oil from becoming less viscous, aging of seals, reduced efficiency of components, and shortened lifespan due to excessively high operating temperatures over a long period of time. This ensures stable hydraulic oil performance and allows the entire sliding system to maintain a reliable and stable working state under continuous operating conditions, thus extending the system's service life.

[0050] In one embodiment, an overflow valve 51 is also included, which is connected to the hydraulic line and is used to provide overload protection for the hydraulic system.

[0051] When the hydraulic system pressure exceeds the preset safety value due to sudden load changes, impacts, or misoperation, the relief valve 51 opens and overflows part of the pressurized oil back to the oil tank, limiting the maximum working pressure of the system and preventing damage to the hydraulic pump, hydraulic motor 6, pipelines, and other hydraulic components due to overpressure. This ensures that the sliding system operates within a safe pressure range and improves the safety and reliability of the system.

[0052] In one embodiment, a replenishing valve 54 is also included, which is connected to the hydraulic circuit.

[0053] When the slewing mechanism causes negative pressure, cavitation, or lack of oil in the oil circuit on one side of the hydraulic motor 6 due to inertial rotation, the oil replenishment valve 54 can automatically replenish oil from the oil tank to the low-pressure side oil circuit in a timely manner, avoiding cavitation, impact, and vibration in the oil circuit, ensuring that the hydraulic system is always full of oil, maintaining stable system pressure, thereby protecting the hydraulic motor 6 and various hydraulic components from damage due to cavitation, and improving the smoothness of the slewing action and the reliability of the system operation.

[0054] In one embodiment, a pilot handle 4 is also included. The pilot handle 4 is connected to the servo control module 3 or the hydraulic pilot oil circuit and is used to control the start, stop, steering and speed adjustment of the rotary mechanism.

[0055] The operating principle of the sliding system is as follows: Hydraulic oil tank 9 serves as the storage and replenishment carrier for the system's hydraulic oil, providing clean and sufficient hydraulic oil to the entire rotary system and ensuring its normal operation. During operation, rotary pump 1 starts, converting mechanical energy into hydraulic energy, drawing hydraulic oil from hydraulic oil tank 9, and outputting hydraulic oil to the hydraulic circuit to provide power support for the actuators of the entire sliding system; simultaneously, servo pump 2 starts synchronously, providing power to the servo control system, converting mechanical energy into the hydraulic energy required by the servo system, and delivering it to servo control module 3.

[0056] The operator issues a rotation control command by manipulating the pilot handle 4. The pilot handle 4 transmits the operation signal to the servo control module 3. The servo control module 3 adjusts the pressure and flow of the servo system according to the command signal, thereby controlling the working state of the directional valve 53, so that the directional valve 53 is in the first open position 531, the blocked position 532, or the second open position 533.

[0057] The hydraulic oil, after being regulated by the slewing reversing valve 53, is delivered to the hydraulic motor 6. The hydraulic motor 6 converts hydraulic energy into mechanical energy and outputs slewing power. Since the hydraulic motor 6 has a high output speed and low torque, it cannot directly meet the load requirements of the slewing operation of the construction machinery. Therefore, the hydraulic motor 6 is connected to the slewing reducer 7. The slewing reducer 7 reduces the output speed of the hydraulic motor 6 through the speed ratio of the internal gears, while greatly amplifying the slewing torque, and finally drives the slewing mechanism of the construction machinery to complete a smooth slewing action.

[0058] During the entire system operation, hydraulic oil will generate heat due to energy conversion and pipeline throttling. If the oil temperature is too high, it will affect the performance of hydraulic oil and the life of system components. At this time, the air-cooled radiator 8 cools the circulating hydraulic oil, removes the heat generated by the system in time, maintains the thermal balance of hydraulic oil, and ensures the stability of hydraulic oil viscosity and lubrication performance. After completing the energy transfer, the hydraulic oil flows back to the hydraulic oil tank 9 through the return oil circuit, realizing the recycling of hydraulic oil.

[0059] Throughout the entire oil circuit circulation process, rotary pump 1 provides the main power, servo pump 2 and servo control module 3 ensure control accuracy, pilot handle 4 enables manual operation, rotary balance valve 55 enables stepless speed regulation, hydraulic motor 6 and rotary reducer 7 provide rotary power adapted to the load, radiator 8 maintains system thermal balance, and hydraulic oil tank 9 ensures oil supply and purification, together achieving stable, accurate, and efficient rotary operation of the rotary system.

[0060] According to an embodiment of the present invention, in another aspect, an adjustment method is also provided, applicable to the sliding system as described above, the adjustment method comprising: Obtain instruction information and adjust the slewing reversing valve 53, the free-sliding proportional valve 56, and the two slewing balance valves 55 based on the instruction information to control the switching of the working mode of the slewing mechanism; The operating modes include stop drift mode, controlled steering mode, and stop anti-slip mode.

[0061] In one embodiment, acquiring instruction information and adjusting the slewing reversing valve 53, the free-slip proportional valve 56, and the two slewing balance valves 55 based on the instruction information to control the switching of the slewing mechanism's operating mode includes: Upon receiving a stop drift signal, the slewing reversing valve 53 is switched to the blocking position 532, and the free-slide proportional valve 56 is energized, so that the hydraulic oil at the motor inlet 61 and motor outlet 62 of the hydraulic motor 6 flows through the first pipeline 101 or the second pipeline 102, and then enters the hydraulic oil tank 9 through the free-slide proportional valve 56 and the bypass oil line 103, until the motor pressure difference is zero, so that the slewing mechanism is in the stop drift mode.

[0062] In this embodiment, the stop drift signal can be issued by the operator via a touch-operated lever button. When the control module receives the stop drift signal, the control directional valve 53 switches to the blocking position 532, and the free-slip proportional valve 56 is energized and opened, allowing the hydraulic oil at the inlet and outlet of the hydraulic motor 6 to flow back to the hydraulic oil tank 9 through the first pipeline 101, the second pipeline 102, the free-slip proportional valve 56, and the bypass oil line 103 until the motor pressure difference is zero. At this time, the slewing mechanism slowly decelerates to a stop. Compared with the form of directly braking and forcibly locking the motor, the stop drift mode adjustment method of this embodiment can avoid the hydraulic and mechanical shocks caused by rigid braking, effectively reduce the stress impact and fatigue wear on key components such as the slewing support and deceleration mechanism, extend the service life of the equipment, make the stopping process smoother and gentler, significantly improve the overall stability and operational safety, and achieve a stop sliding effect without impact or stress concentration.

[0063] In one embodiment, the adjustment method further includes: acquiring a speed adjustment signal, adjusting the opening of the free-slip proportional valve 56 to adjust the speed at which the motor pressure difference drops to zero, and thereby adjusting the slip distance of the rotary mechanism.

[0064] By acquiring the speed adjustment signal, the opening of the free-slip proportional valve 56 is adjusted in real time, thereby controlling the speed at which the motor pressure difference reaches zero, and thus adjusting the sliding distance of the slewing mechanism. In stop-drift mode, the sliding speed and sliding distance can be controlled according to actual operational needs, avoiding the risk of excessive sliding, failure to rotate, or collision due to uncontrolled sliding. The adjustment method in this embodiment retains the advantages of flexible pressure relief and impact-free shutdown, while also achieving controllable and adjustable sliding process, further improving the accuracy of the slewing mechanism's stopping position and operational safety, and enhancing the system's adaptability to different working conditions.

[0065] In one embodiment, acquiring instruction information and adjusting the slewing reversing valve 53, the free-slip proportional valve 56, and the two slewing balance valves 55 based on the instruction information to control the switching of the slewing mechanism's operating mode includes: The operator sends a steering signal by touching the buttons on the control lever. The slewing control module 5 receives the controlled steering signal and the tilt angle signal of the construction machinery from the tilt angle sensor. If the tilt angle of the construction machinery is 0°, control the slewing reversing valve 53 to switch to the first conduction position 531 or the second conduction position 533, and control the free sliding proportional valve 56 to de-energize; based on the load feedback valve core responding to load changes, adjust the opening of the slewing balance valve 55, adjust the flow of the first pipeline 101 or the second pipeline 102, so that the slewing mechanism is in the controlled steering mode. If the tilt angle of the construction machinery is not 0°, the control slewing valve 53 is switched to the first conduction position 531 or the second conduction position 533, the control free-slide proportional valve 56 is energized, and the opening of the free-slide proportional valve 56 is adjusted so that the hydraulic oil from the motor inlet end 61 and the motor outlet end 62 of the hydraulic motor 6 flows through the first pipeline 101 or the second pipeline 102, and then enters the hydraulic oil tank 9 through the free-slide proportional valve 56 and the bypass oil circuit 103; and based on the load feedback valve core responding to the load change, the opening of the slewing balance valve 55 is adjusted to adjust the flow rate of the first pipeline 101 or the second pipeline 102, so that the slewing mechanism is in the controlled steering mode.

[0066] Specifically, when the tilt angle of the construction machinery is 0°, under heavy load, the load feedback valve core reduces its opening and flow rate, thereby reducing the rotation speed and ensuring sufficient output torque. Under light load, the load feedback valve core opening increases the hydraulic oil flow rate, thereby appropriately increasing the rotation speed and improving work efficiency.

[0067] When the tilt angle of the construction machinery is not 0°, the free-sliding proportional valve 56 is energized and adjusts its opening, so that part of the hydraulic oil flows back to the hydraulic oil tank 9 through the bypass oil circuit 103, reducing the flow into the hydraulic motor 6. At the same time, the hydraulic motor 6 outlet side is throttled by the load feedback valve core of the rotary balance valve 55, so that a larger pressure difference is formed between the inlet and outlet of the hydraulic motor 6, thereby increasing the output torque of the hydraulic motor 6.

[0068] When the construction machinery is in a flat working condition, the control free proportional valve loses power and cuts off the bypass oil circuit 103. The sliding system adjusts the pipeline opening and hydraulic oil flow according to the load size through the load feedback valve core of the slewing balance valve 55, so that the slewing speed matches the actual load. This achieves stepless control of the hydraulic oil volume in the first pipeline 101 and the second pipeline 102, ensuring that the slewing speed of the hydraulic motor 6 is smoothly adjusted with the load change under the premise of sufficient slewing power. The steering action of the slewing mechanism is smooth and shock-free, meeting the smooth slewing operation requirements under flat working conditions.

[0069] When the construction machinery is in a slope condition, the free-slip proportional valve 56 is energized and adjusts its opening, allowing some hydraulic oil to flow back to the hydraulic oil tank 9 through the bypass oil line 103. At the same time, the load feedback valve core of the slewing balance valve 55 adjusts the pipeline flow according to the load change, so that the slewing mechanism still has stable, controllable and smooth steering performance under slope conditions, significantly improving the safety and reliability under complex working conditions.

[0070] In one embodiment, acquiring instruction information and adjusting the slewing reversing valve 53, the free-slip proportional valve 56, and the two slewing balance valves 55 based on the instruction information to control the switching of the slewing mechanism's operating mode includes: Upon receiving a stop and anti-slip signal, the slewing reversing valve 53 is switched to the blocking position 532, and the free-sliding proportional valve 56 is de-energized, so that the slewing balance valve 55 maintains pressure on the first pipeline 101 or the second pipeline 102, thereby putting the slewing mechanism into the stop and anti-slip mode.

[0071] The adjustment method in this embodiment enables the construction machinery to maintain pressure in the first pipeline 101 or the second pipeline 102 through the rotary balance valve 55 when it is stopped or during work breaks. This stabilizes the pressure and pressure difference at both ends of the hydraulic motor 6, ensuring that the hydraulic motor 6 does not reverse, swerve, or slip. At the same time, in conjunction with the reverse shut-off function of the check valve, it prevents hydraulic oil leakage and pressure loss, ensuring that the rotary mechanism always remains reliably locked in the stop, parked, or slope conditions. This avoids safety risks such as brake failure and accidental rotation caused by pressure drop, significantly improving the safety, stability, and parking reliability of the construction machinery when it is stopped.

[0072] According to an embodiment of the present invention, in another aspect, an engineering machine is also provided, the engineering machine including a slewing mechanism, the slewing mechanism including the sliding system as described above.

[0073] Although embodiments of the invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the invention, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. A sliding system, applied to the slewing mechanism of engineering machinery, characterized in that, The rotary mechanism includes: A hydraulic motor (6) is suitable as a power source for the rotary mechanism; the hydraulic motor (6) includes a motor inlet end (61) and a motor outlet end (62), the pressure difference between the motor inlet end (61) and the motor outlet end (62) is defined as the motor pressure difference, and the hydraulic motor (6) is suitable for controlling the motion state of the rotary mechanism based on the motor pressure difference; a rotary reducer (7) is driven by the output torque of the hydraulic motor (6), and the rotary reducer (7) is suitable for outputting the torque of the hydraulic motor (6) to meet the torque requirements of the rotary mechanism; Slewing bearing (10) is suitable for connecting the upper structure and chassis of a crane; The sliding system is adapted to provide flow to the hydraulic motor (6) and drive the hydraulic motor (6) to work; The sliding system includes: A hydraulic oil tank (9) is suitable for storing pressure medium and is connected to the hydraulic motor (6) via pipeline; The first pipe (101) and the second pipe (102) are respectively connected to the motor inlet end (61) and the motor outlet end (62). The slewing control module (5) is connected between the hydraulic motor (6) and the hydraulic oil tank (9). The slewing control module (5) includes a slewing directional valve (53), a free-slip proportional valve (56), and two slewing balance valves (55).

2. The sliding system according to claim 1, characterized in that, The directional valve (53) has a first open position (531) and a second open position (533). The directional valve (53) is adapted to be in the first open position (531) so that the hydraulic oil flows from the directional valve (53) through the first pipeline (101) into the motor inlet end (61). Alternatively, the directional valve (53) is adapted to be in the second open position (533) so that the hydraulic oil flows from the directional valve (53) through the second pipeline (102) into the motor outlet end (62).

3. The sliding system according to claim 2, characterized in that, Also includes: A first pilot proportional valve (521) is adapted to adjust the hydraulic oil flow rate of the first pipeline (101) when the directional valve (53) is in the first open position (531).

4. The sliding system according to claim 2, characterized in that, Also includes: The second pilot proportional valve (522) is adapted to adjust the hydraulic oil flow rate of the second pipeline (102) when the directional valve (53) is in the second open position (533).

5. An adjustment method, characterized in that, The adjustment method, applicable to the slip system as described in any one of claims 1 to 4, comprises: Obtain instruction information, and adjust the slewing reversing valve (53), the free-sliding proportional valve (56) and the two slewing balance valves (55) based on the instruction information to control the switching of the working mode of the slewing mechanism; The operating modes include stop drift mode, controlled steering mode, and stop anti-slip mode.

6. The adjustment method according to claim 5, characterized in that, The acquisition of instruction information, and the adjustment of the slewing reversing valve (53), the free-slip proportional valve (56), and the two slewing balance valves (55) based on the instruction information to control the switching of the working mode of the slewing mechanism, includes: Obtain a stop drift signal, control the slewing reversing valve (53) to switch to the blocking position (532), control the free-slip proportional valve (56) to be energized, so that the hydraulic oil at the motor inlet end (61) and the motor outlet end (62) of the hydraulic motor (6) flows through the first pipeline (101) or the second pipeline (102), and then enters the hydraulic oil tank (9) through the free-slip proportional valve (56) and the bypass oil line (103) until the motor pressure difference is zero, so that the slewing mechanism is in the stop drift mode.

7. The adjustment method according to claim 5, characterized in that, The adjustment method further includes: acquiring a speed adjustment signal, adjusting the opening of the free-slip proportional valve (56) to adjust the speed at which the motor pressure difference drops to zero, and thereby adjusting the slip distance of the rotary mechanism.

8. The adjustment method according to claim 5, characterized in that, The acquisition of instruction information, and the adjustment of the slewing reversing valve (53), the free-slip proportional valve (56), and the two slewing balance valves (55) based on the instruction information to control the switching of the working mode of the slewing mechanism, includes: Acquire controlled steering signals and tilt angle signals of construction machinery; If the tilt angle of the engineering machinery is 0°, control the slewing reversing valve (53) to switch to the first conduction position (531) or the second conduction position (533), and control the free sliding proportional valve (56) to de-energize; based on the load feedback valve core responding to the load change, adjust the opening of the slewing balance valve (55), adjust the flow of the first pipeline (101) or the second pipeline (102), so that the slewing mechanism is in the controlled steering mode; If the tilt angle of the engineering machinery is not 0°, control the slewing reversing valve (53) to switch to the first conduction position (531) or the second conduction position (533), control the free-slip proportional valve (56) to be energized, and adjust the opening of the free-slip proportional valve (56) so that the hydraulic oil from the motor inlet end (61) and the motor outlet end (62) of part of the hydraulic motor (6) flows through the first pipeline (101) or the second pipeline (102), and then enters the hydraulic oil tank (9) through the free-slip proportional valve (56) and the bypass oil circuit (103); and based on the load feedback valve core responding to the load change, adjust the opening of the slewing balance valve (55) to adjust the flow rate of the first pipeline (101) or the second pipeline (102) so that the slewing mechanism is in the controlled steering mode.

9. The adjustment method according to claim 5, characterized in that, The acquisition of instruction information, and the adjustment of the slewing reversing valve (53), the free-slip proportional valve (56), and the two slewing balance valves (55) based on the instruction information to control the switching of the working mode of the slewing mechanism, includes: Obtain a stop anti-slip signal, control the slewing reversing valve (53) to switch to the blocking position (532), control the free sliding proportional valve (56) to de-energize, so that the slewing balance valve (55) maintains pressure on the first pipeline (101) or the second pipeline (102), so that the slewing mechanism is in the stop anti-slip mode.

10. An engineering machinery, characterized in that, The engineering machinery includes a slewing mechanism, which includes a sliding system as described in any one of claims 1 to 4.

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