Control method for preventing swing tail and tooth breakage of slewing device

Abstract

This invention belongs to the field of hydraulic system technology, and specifically relates to a control method for preventing the swaying of a rotary mechanism and the breakage of gear teeth. The method includes an accumulator and an anti-swaying cartridge valve. The anti-swaying cartridge valve comprises a second shuttle valve, a three-position three-way directional valve, a check valve, a two-position two-way solenoid valve, a two-position two-way directional valve, a first shuttle valve, a brake pressure detection switch, and a pilot pressure transmitter. This invention replenishes pressure on the return oil side of the hydraulic system at the moment the rotary hydraulic motor starts, and charges the accumulator at the moment the rotary hydraulic motor brakes. It also includes a two-position two-way solenoid valve that connects the inlet and return oil circuits at the moment the rotary hydraulic motor starts and stops, thereby preventing the swaying of the rotary mechanism and the breakage of the gear teeth due to impact.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of hydraulic systems, and particularly relates to a control method for preventing a swing device from swinging and preventing a gear from breaking. BACKGROUND

[0002] The existing hydrostatic drive swing system mainly adopts a structure as shown in the figure, and is mainly composed of a hydraulic oil tank 1, a cooler 2, a cooling motor 3, a hydraulic pump 4, a multi-way valve 5, a swing hydraulic motor 6, a shuttle valve 7, a pilot control valve 8, an electromagnetic valve 9 and a pilot integrated block 10. Figure 1 During the working process, an operator controls the pilot control handle to realize the reversing of the valve core in the multi-way valve 5, and the hydraulic oil provided by the main pump drives the swing hydraulic motor 6 to rotate after passing through the multi-way valve 5.

[0003] For example, during the working process of the hydraulic excavator, the swing device is generally in the hydraulic braking state to ensure that the working device effectively performs the digging operation in a determined position, and the swing time accounts for 50% to 70% of the entire working cycle of the hydraulic excavator, and the energy consumption accounts for about 25% to 40%.

[0004] The frequent swing operation causes the start and stop of the swing device to be frequent, the power required when the swing device starts is large, the rotational inertia during the swing process is large, and the required braking energy is also large, therefore, the load-sensitive variable pump is widely used in the current hydraulic excavator, the flow of the load-sensitive variable pump automatically adapts to the flow of the motor during the swing starting process, and the overflow loss is reduced, but due to the large pressure at the starting moment, the impact of the gear teeth of the variable gear on the swing hydraulic motor 6 at the starting moment of the swing hydraulic motor 6 easily causes the gear teeth to break.

[0005] The brake of the swing device is usually in the form of hydraulic braking, the swing motor becomes a pump during the braking process, the oil pumped out flows out through the load valve, the braking energy is completely converted into heat energy, according to statistics, the heat generation of the swing hydraulic oil circuit accounts for about 30% to 40% of the total heat generation of the hydraulic system, which not only causes the temperature of the hydraulic oil to rise, but also requires an additional cooling device to be set to reduce the temperature, which further increases the fuel consumption. However, during the working process, in order to improve the working efficiency, the operator quickly controls the pilot control handle to quickly reverse the valve core in the multi-way valve 5 to close the oil passage, the large rotational inertia of the swing mechanism causes the swing hydraulic motor 6 to continuously rotate, and due to the quick closing of the valve core in the multi-way valve 5, the pressure of the oil return side of the swing hydraulic motor 6 quickly rises, the pressure of the oil supply side quickly decreases, when the pressure of the oil return side is large enough, the swing hydraulic motor 6 reverses, which causes the swing mechanism to swing and easily causes the gear teeth to be damaged due to fatigue. SUMMARY

[0006] The control method for preventing the swing tail of the rotary device and the breaking of the gear tooth can control the communication between the oil return side and the energy accumulator and the communication between the oil inlet and the oil return side of the rotary hydraulic motor when the hydraulic rotary motor is started or stopped, so that the swing tail phenomenon of the rotary mechanism can be effectively solved, and the breaking of the gear tooth due to impact can be prevented.

[0007] To achieve the above object, the technical scheme provided by the application is as follows:

[0008] The control method for preventing the swing tail of the rotary device and the breaking of the gear tooth comprises a rotary hydraulic motor and a multi-way valve, the multi-way valve is realized by the control oil path of a pilot control valve, and further comprises an energy accumulator and an anti-swing tail plug-in valve.

[0009] When the rotary hydraulic motor is started:

[0010] One interface of the three-way directional valve is connected with the energy accumulator, and the other two interfaces are connected with the oil inlet and return paths of the rotary hydraulic motor respectively.

[0011] The two interfaces of the first shuttle valve are connected with the oil inlet and return paths of the rotary hydraulic motor respectively, and the other interface is connected with the energy accumulator through the two-way directional valve, the one-way valve and the energy accumulator in sequence.

[0012] When the rotary hydraulic motor is braked:

[0013] When the rotary hydraulic motor is braked through the pilot control valve, the pilot hydraulic oil in the pilot control cavity of the two-way directional valve in the anti-swing tail plug-in valve returns to the hydraulic oil tank through the two-way directional valve, so that the high-pressure hydraulic oil on the oil return side of the rotary hydraulic motor is charged to the energy accumulator through the first shuttle valve and the two-way directional valve.

[0014] Preferably, the anti-swing tail plug-in valve further comprises a pilot integrated block, a two-position two-way electromagnetic valve, a brake pressure detection switch and a pilot pressure transmitter, two interfaces of the two-position two-way electromagnetic valve are connected with the inlet and return oil circuits of the rotary hydraulic motor respectively; the pilot pressure transmitter is connected to the outlet of the second shuttle valve, the brake pressure detection switch is connected to the outlet of the first shuttle valve, the control circuit of the brake pressure detection switch and the pilot pressure transmitter is connected to the two-position two-way electromagnetic valve respectively, and the two-position two-way electromagnetic valve is turned on and off by detecting the pressure of the control oil circuit and the working oil circuit.

[0015] Preferably, when the pressure detected by the pilot pressure transmitter is higher than 5 Bar and less than 10 Bar, and the electromagnetic valve S6 in the pilot integrated block is electrified, the two-position two-way electromagnetic valve is electrified to realize reversing, the MA1 port of the anti-swing tail plug-in valve is communicated with the MB1 port, the back pressure of the return oil side is rapidly increased at the starting moment, and the pressure difference between the two sides of the hydraulic rotary motor is reduced.

[0016] Preferably, when the pressure detected by the pilot pressure transmitter is less than 5 Bar, the brake pressure detection switch pressure is greater than 100 Bar, and the electromagnetic valve S6 in the pilot integrated block is electrified, the two-position two-way electromagnetic valve is electrified to realize reversing, the MA1 port of the anti-swing tail plug-in valve is communicated with the MB1 port, and the pressure of the working oil ports A1 and B1 of the rotary hydraulic motor is rapidly balanced during braking.

[0017] The application has the following advantages and beneficial effects:

[0018] 1. In the application, the three-position three-way reversing valve is controlled to reverse when the rotary hydraulic motor is started by the pilot control valve, so that the accumulator supplies oil to the return oil side of the rotary hydraulic motor during the starting of the hydraulic rotary motor, the return oil side is pressurized at the starting moment of the hydraulic rotary motor, the return oil resistance is increased, the contact time between the tooth profiles of the variable displacement gear is prolonged, the starting speed of the hydraulic rotary motor is slowed down, and the gear starting impact force is reduced. Therefore, expensive pumps such as load-sensitive variable pumps are not needed, which is economical and energy-saving.

[0019] 2. In the application, the two-position three-way reversing valve is controlled to reverse when the rotary hydraulic motor is started by the pilot control valve, so that the control oil enters the two-position two-way reversing valve through the two-position three-way reversing valve to control the reversing of the two-position two-way reversing valve, the communication between the liquid filling pipeline and the working oil circuit of the rotary hydraulic motor is blocked, and the hydraulic rotary motor is ensured to operate normally.

[0020] Thirdly, in the application, the pilot hydraulic oil in the pilot control cavity of the two-position two-way reversing valve in the anti-swing tail plug-in valve is returned to the hydraulic oil tank through the two-position three-way reversing valve while the pilot operating valve brakes the rotary hydraulic motor, realizing that the high-pressure hydraulic oil on the oil return side of the rotary hydraulic motor is filled into the energy accumulator through the first shuttle valve and the two-position two-way reversing valve, so that the rotary mechanism is continuously driven to rotate under the action of inertia when the rotary mechanism is braked, the high-pressure hydraulic oil with rapidly rising pressure on the oil return side of the hydraulic motor is introduced into the energy accumulator, and the anti-swing tail of the rotary mechanism is avoided. At the same time, the setting of the high-power brake device is also avoided, the brake energy is completely converted into heat energy, the heat generation of the hydraulic system is reduced, the temperature rise of the hydraulic oil is effectively avoided, and no additional cooling device needs to be added, and fuel consumption is reduced.

[0021] Fourthly, in the application, the circuit in which the two-position two-way electromagnetic valve is located is turned on and off by detecting the pressure of the control oil way and the working oil way, so that the two-position two-way electromagnetic valve can be turned on when the rotary hydraulic motor is started and stopped, the inlet and outlet oil ways of the hydraulic rotary motor are connected, the back pressure on the oil return side is rapidly increased at the starting moment, the pressure difference between the two sides of the hydraulic rotary motor is reduced, the purpose of slowly approaching between the gear teeth is achieved, and the gear teeth are prevented from being broken by impact; the pressure of the working oil ports A1 and B1 of the hydraulic motor is rapidly balanced during the braking process, and the anti-swing tail of the rotary mechanism is prevented. BRIEF DESCRIPTION OF DRAWINGS

[0022] Figure 1 A hydraulic principle diagram of a static hydraulic drive rotary system provided by the prior art;

[0023] Figure 2 A hydraulic principle diagram of a hydraulic system for preventing the anti-swing tail and gear breakage of a rotary device provided by the application;

[0024] Figure 3 A hydraulic principle diagram of an anti-swing tail plug-in valve, a rotary hydraulic motor and related control valve bodies provided by the application;

[0025] Figure 4 A hydraulic principle diagram of an anti-swing tail plug-in valve provided by the application;

[0026] Figure: 1-hydraulic oil tank, 2-cooler, 3-cooled motor, 4-hydraulic pump, 5-multi-way valve, 6-energy accumulator, 7-anti-swing tail plug-in valve, 7.1-second shuttle valve, 7.2-three-position three-way reversing valve, 7.3-check valve, 7.4-pilot pressure relief valve, 7.5-two-position two-way electromagnetic valve, 7.6-two-position two-way reversing valve, 7.7-first shuttle valve, 7.8-two-position three-way reversing valve, 7.9-check valve, 8-rotary hydraulic motor, 9-brake pressure detection switch, 10-pilot pressure transmitter, 11-pilot operating valve, 12-electromagnetic valve, 13-pilot integrated block. DETAILED DESCRIPTION

[0027] To make the objectives, technical solutions, and advantages of the embodiments of the invention clearer, the technical solutions of the embodiments of the invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are some embodiments of the invention, but not all embodiments.

[0028] Therefore, the following detailed description of embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention.

[0029] Example

[0030] like Figures 2 to 4 As shown, a hydraulic system for preventing the slewing device from wobbling and the gear teeth from breaking includes: a slewing hydraulic motor 8 and a multi-way valve 5. The multi-way valve 5 is operated by controlling the oil circuit of the pilot control valve 11 to start and stop the rotation of the slewing hydraulic motor 8.

[0031] In this invention, only some of the main oil circuits are labeled (such as main oil circuit L1, main oil circuit L2, etc.), which are represented by solid lines in the figure. The dashed lines not labeled in the figure represent pilot oil circuits, pressure measuring oil circuits, or drain oil circuits. The dotted-line boxes represent several valve bodies integrated into one block, forming an integral component.

[0032] This invention is an improvement on a hydrostatic drive rotary system based on existing technology, such as... Figure 2 As shown, the hydraulic system specifically includes: a hydraulic oil tank 1, a cooler 2, a cooling motor 3, a hydraulic pump 4, a multi-way valve 5, an accumulator 6, an anti-sway cartridge valve 7, a rotary hydraulic motor 8, a pilot control valve 11, a solenoid valve 12, a pilot integrated block 13, and other components. These components are connected through hydraulic working oil circuits and control oil circuits.

[0033] An energy storage device 6 and an anti-sway cartridge valve 7 are installed in the pipeline between the rotary hydraulic motor 8 and the multi-way valve 5.

[0034] Specific connection relationship is: hydraulic oil tank 1 is connected with hydraulic pump 4 through main oil way (working oil way) L1, hydraulic pump 4 is connected with multi-way valve 5 through main oil way (working oil way) L2, multi-way valve 5 is connected with cooler 2 through main oil return way (working oil way) L3, cooler 2 is connected with hydraulic oil tank 1 through main oil return way (working oil way) L4, to constitute a circulation loop. A1 interface of multi-way valve 5 is connected with VA1 port of anti-sway tail plug-in valve 7 through main oil way (working oil way) L5, B1 interface of multi-way valve 5 is connected with VB1 port of anti-sway tail plug-in valve 7 through main oil way (working oil way) L6. MA1 port of anti-sway tail plug-in valve 7 is connected with A1 port of rotary hydraulic motor 8, MB1 port of anti-sway tail plug-in valve 7 is connected with B1 port of rotary hydraulic motor 8, to constitute a drive circuit with the whole hydraulic system. In the working process, the operator can realize the valve core reversing of multi-way valve 5 by operating the handle of pilot control valve 11, and the hydraulic oil provided by hydraulic pump 4 drives rotary hydraulic motor 8 to rotate after passing through multi-way valve 5 and anti-sway tail plug-in valve 7.

[0035] In the application, the anti-sway tail plug-in valve 7 comprises a second shuttle valve 7.1, a three-position three-way reversing valve 7.2, a one-way valve 7.3, an overflow valve 7.4, a two-position two-way electromagnetic valve 7.5, a two-position two-way reversing valve 7.6, a first shuttle valve 7.7, a two-position three-way reversing valve 7.8 and a one-way throttle valve 7.9.

[0036] The A port of the three-position three-way reversing valve 7.2 is communicated with the c1 port of the anti-sway tail plug-in valve 7, the c1 port is communicated with the A2 port of the anti-sway tail plug-in valve 7, and the A2 port is connected with the energy accumulator 6.

[0037] The B port of the three-position three-way reversing valve 7.2 is communicated with the VA1 port of the anti-sway tail plug-in valve 7, and the C port is communicated with the VB1 port. The VA1 port of the anti-sway tail plug-in valve 7 is communicated with the MA1 port, and the VB1 port is communicated with the MB1 port.

[0038] The A port of the first shuttle valve 7.7 is communicated with the MA1 port of the anti-sway tail plug-in valve 7, the B port is communicated with the MB1 port, and the C port of the first shuttle valve 7.7 is communicated with the c1 port of the anti-sway tail plug-in valve 7. The two-position two-way reversing valve 7.6 and the one-way valve 7.3 are sequentially arranged between the C port of the first shuttle valve 7.7 and the c1 port of the anti-sway tail plug-in valve 7, and the one-way valve 7.3 is in the direction from the d1 port of the anti-sway tail plug-in valve 7 to the c1 port.

[0039] Through the above design, when the rotary hydraulic motor 8 starts, the energy accumulator 6 can supply oil to the oil return way through the three-position three-way reversing valve 7.2; when the rotary hydraulic motor 8 stops, the oil return way of the rotary hydraulic motor 8 can supply oil to the energy accumulator 6 through the two-position two-way reversing valve 7.6.

[0040] Further, the anti-swing tail plug-in valve 7 further comprises a two-position two-way electromagnetic valve 7.5, the A port of the two-position two-way electromagnetic valve 7.5 and the MA1 port of the anti-swing tail plug-in valve 7 are communicated, and the B port and the MB1 port are communicated. That is, the two interfaces of the two-position two-way electromagnetic valve 7.5 are connected with the inlet and return oil circuit of the rotary hydraulic motor 8 respectively, and the two-position two-way electromagnetic valve 7.5 is in a communication state when it is electrified when the rotary hydraulic motor 8 starts or stops.

[0041] Further, the two-position two-way reversing valve 7.6 and the energy accumulator 6 are connected with the overflow valve 7.4, one interface of the overflow valve 7.4 is connected with the c1 port of the anti-swing tail plug-in valve 7, and the other interface is communicated with the hydraulic oil tank 1. When the circuit of the hydraulic system supplements oil to the energy accumulator 6, and when the return oil side pressure is higher than a certain value pressure, for example: 12Mpa, the overflow valve 7.4 overflows back to the hydraulic oil tank 1.

[0042] In the present application, the anti-swing tail plug-in valve 7 further comprises a second shuttle valve 7.1, the second shuttle valve 7.1 is connected with the control oil circuit of the rotary hydraulic motor 6, that is, the b1 control oil circuit of the pilot control valve 11 is divided into two parts, one part is used for controlling the multi-way valve 5 and is connected with the b1 of the multi-way valve 5, the a1 port of the multi-way valve 5 is connected with the a1 port of the anti-swing tail plug-in valve 7; the other part is connected with the b1 port of the anti-swing tail plug-in valve 7. The A port of the second shuttle valve 7.1 is connected with the B port of the three-position three-way reversing valve 7.2, the B port of the second shuttle valve 7.1 is connected with the C port of the three-position three-way reversing valve 7.2, and the two ends of the second shuttle valve 7.1 are respectively communicated with the a1 and b1 ports of the anti-swing tail plug-in valve 7 to form a circulating control oil circuit, which is used for controlling the three-position three-way reversing valve 7.2 to realize reversing.

[0043] In the present application, the anti-swing tail plug-in valve 7 further comprises a two-position three-way reversing valve 7.8, the two-position three-way reversing valve 7.8 is connected with the C port of the second shuttle valve 7.1, and is used for controlling the two-position three-way reversing valve 7.8 to realize reversing. The two-position three-way reversing valve 7.8 is provided with a drain pipeline, one interface of the two-position three-way reversing valve 7.8 is connected with the A2 port of the pilot integrated block 13, and the other interface of the two-position three-way reversing valve 7.8 is connected with the two-position two-way reversing valve 7.6. When the two-position three-way reversing valve 7.8 is reversed and opened, the hydraulic oil at the A2 port of the pilot integrated block 13 enters the two-position two-way reversing valve 7.6 from the two-position three-way reversing valve 7.8 and controls the two-position two-way reversing valve 7.6 to realize reversing, and the two-position two-way reversing valve 7.6 is in a closed state.

[0044] Further, the anti-swing tail plug-in valve 7 further comprises a one-way throttle valve 7.9, which is arranged on the pipeline between the two-position three-way reversing valve 7.8 and the two-position two-way reversing valve 7.6. The one-way throttle valve 7.9 plays a role of quickly closing and slowly opening the two-position two-way reversing valve 7.6.

[0045] In the application, the anti-swing tail plug-in valve 7 further comprises a brake pressure detection switch 9 and a pilot pressure transmitter 10, the c port of the second shuttle valve 7.1 is connected with the pilot pressure transmitter 10, and the c port of the first shuttle valve 7.7 is connected with the brake pressure detection switch 9; the control circuits of the brake pressure detection switch 9 and the pilot pressure transmitter 10 are respectively connected to the two-position two-way electromagnetic valve 7.5, so that the circuit in which the two-position two-way electromagnetic valve 7.5 is located can be turned on when the pressure is greater than / less than the set value.

[0046] The control method for preventing the swing tail and the tooth breakage of the rotary device is:

[0047] When the operator starts to operate the pilot control valve 11, there are two cases, that is, the left armrest control valve is operated (left rotation) or the right armrest control valve is operated (right rotation).

[0048] When the rotary hydraulic motor 8 is started (left rotation):

[0049] When the operator manipulates the left handrail control valve, the pilot hydraulic oil flows out from the b1 port of the pilot control valve 11, and is divided into two parts, one of which enters the rotation control link pilot signal port b1 of the multi-way valve 5 to push the spool to move, so that the working oil port B1 of the multi-way valve 5 is connected through the VB1 port of the anti-swing cartridge valve 7, and the high-pressure hydraulic oil enters the working oil port A1, B1 of the rotation hydraulic motor 8 through the anti-swing cartridge valve 7. The other part is again divided into two parts through the b1 port of the anti-swing cartridge valve 7, one of which directly enters the secondary overflow valve pilot control chamber of the rotation hydraulic motor 8 to increase the starting pressure of the rotation hydraulic motor 6, so as to increase the starting acceleration. The other part of the pilot oil enters the anti-swing cartridge valve 7 through the b1 port of the anti-swing cartridge valve 7, and is again divided into two parts, one of which is used to control the three-position three-way directional valve 7.2, and the other part is used to control the second shuttle valve 7.1 B port, and then is again divided into two parts through the C port, one of which is used to open the brake of the rotation hydraulic motor 8, and the other part is used to control the two-position three-way directional valve 7.8 and the pilot pressure transmitter 10 to detect the pilot pressure. When the pressure detected by the pilot pressure transmitter 10 is higher than 5 Bar and lower than 10 Bar, and the electromagnetic valve S6 in the pilot integrated block 13 is electrified, the two-position two-way electromagnetic valve 7.5 is electrified to realize the switching, the MA1 port and the MB1 port of the anti-swing cartridge valve 7 are communicated through the throttle hole to quickly increase the back pressure of the oil return side at the starting moment, reduce the pressure difference between the two sides of the rotation hydraulic motor 8, and reduce the impact force between the driving gear and the driven gear, so as to reduce the starting impact and achieve the purpose of slowly approaching between the gear teeth to prevent the gear teeth from being broken by impact. When the pressure detected by the pilot pressure transmitter 10 is less than 5 Bar, and the pressure of the brake pressure detection switch 9 is greater than 100 Bar, and the electromagnetic valve S6 in the pilot integrated block 13 is electrified, the two-position two-way electromagnetic valve 7.5 is electrified to realize the switching, and the MA1 port and the MB1 port of the anti-swing cartridge valve 7 are communicated through the throttle hole to quickly balance the pressure of the working oil port A1 and B1 of the rotation hydraulic motor 8 during the braking process, so as to prevent the rotation mechanism from swinging.

[0050] The hydraulic oil of the pilot integrated block 13 flows out from the A2 port, enters the A1 port of the anti-swing cartridge valve 7, and when the pilot control valve 11 has a control action, the two-position three-way directional valve 7.8 is switched, and the hydraulic oil provided by the A2 port of the pilot integrated block enters the pilot control chamber of the two-position two-way directional valve 7.6 through the one-way throttle valve 7.9 after the one-way throttle valve 7.9, and pushes the two-position two-way directional valve 7.6 to quickly switch to block the connection between the liquid filling pipeline and the working oil circuit of the rotation hydraulic motor 8. When the rotation hydraulic motor 8 stops, the two-position two-way directional valve 7.6 is in an open state.

[0051] The control of the right rotation and the left rotation is similar and will not be repeated.

[0052] When the rotary hydraulic motor 8 is braked:

[0053] When the operator stops operating the pilot control valve 11, the rotary control spool of the multi-way valve 5 quickly returns to the neutral position under the action of the spring force, and the rotary mechanism continues to drive the rotary hydraulic motor 8 to rotate under the action of inertia, so that the oil return side pressure of the rotary hydraulic motor 8 quickly rises to a relatively high pressure. At the same time, the pilot hydraulic oil in the two-position two-way reversing valve 7.6 of the anti-sway tail plug-in valve 7 slowly returns to the hydraulic oil tank 1 through the hydraulic control check valve 7.8, the two-position two-way reversing valve 7.6 reverses at a relatively slow speed, and the high-pressure hydraulic oil on the oil return side of the rotary hydraulic motor 8 is discharged through the oil port VA1 of the anti-sway tail plug-in valve 7, the A port of the first shuttle valve 7.7, and then through the C port, and then through the hydraulic oil of the two-position two-way reversing valve 7.6 to charge the accumulator 6. When the hydraulic oil pressure at the working oil port end of the rotary hydraulic motor 8 is greater than the sum of the pressure inside the accumulator 6 and the one-way valve 7.3, the one-way valve 7.3 opens to realize the charging of the accumulator 6, so as to store the hydraulic oil on the oil return side and prevent the oil return side pressure from continuously rising, thereby reducing the heat generation of the system. When the oil return side pressure is higher than 12 MPa, the overflow valve 7.4 overflows.

[0054] When there is a rotary action, the two-position two-way reversing valve 7.8 is reversed by the pilot control signal, and then the two-position two-way reversing valve 7.6 is quickly controlled to reverse by the one-way throttle valve 7.9, so as to quickly disconnect the high-pressure pipeline and the oil return pipeline during the rotation of the hydraulic pump 4 driving the hydraulic rotary motor 8. When the operator stops operating, the hydraulic oil in the pilot chamber of the two-position two-way reversing valve 7.6 slowly returns to the hydraulic oil tank 1 through the throttle hole of the one-way throttle valve 7.9, so as to slowly connect the hydraulic oil paths on both sides of the rotary hydraulic motor 8, and give the oil return side of the hydraulic motor enough time to establish pressure, so as to organize the hydraulic rotary motor 8 to continue to rotate and stop. When a certain pressure is established, the hydraulic oil path on the oil return side supplements the accumulator 6.

[0055] The above is only a preferred embodiment of the application and is not intended to limit the application. For those skilled in the art, the application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the application shall be included in the protection scope of the application.

Claims

1. A control method for preventing swing-out and tooth breakage of a slewing device, comprising: The rotary hydraulic motor and the multi-way valve, the multi-way valve realizes switch operation through the control oil way of the pilot control valve, characterized in that further comprising an accumulator and an anti-swing tail plug-in valve; the anti-swing tail plug-in valve comprises a second shuttle valve, a three-position three-way directional valve, a one-way valve, a two-position two-way directional valve, a first shuttle valve and a two-position three-way directional valve; When the rotary hydraulic motor starts: One interface of the three-position three-way directional valve is connected with the accumulator, and the other two interfaces are connected with the inlet and return oil ways of the rotary hydraulic motor; the second shuttle valve is connected with the control oil way of the pilot control valve, and two inlet ports of the second shuttle valve are connected with the three-position three-way directional valve; when the rotary hydraulic motor is started through the pilot control valve, the three-position three-way directional valve is controlled to change direction to realize the accumulator supplementing the return oil side of the rotary hydraulic motor during the starting of the hydraulic rotary motor; Two interfaces of the first shuttle valve are connected with the inlet and return oil ways of the rotary hydraulic motor, and the other interface is connected with the accumulator through the two-position two-way directional valve, the one-way valve and the accumulator in sequence; the two-position two-way directional valve is connected with the two-position three-way directional valve, and the two-position three-way directional valve is connected with the control oil way of the pilot control valve; when the rotary hydraulic motor is started through the pilot control valve, the two-position three-way directional valve is controlled to change direction to open the internal oil way, and the control oil enters the two-position two-way directional valve through the two-position three-way directional valve to control the change direction, thereby blocking the communication between the liquid filling pipeline and the working oil way of the rotary hydraulic motor; When the rotary hydraulic motor brakes: When the rotary hydraulic motor is braked through the pilot control valve, the pilot hydraulic oil in the pilot control cavity of the two-position two-way directional valve in the anti-swing tail plug-in valve returns to the hydraulic oil tank through the two-position three-way directional valve, so that the high-pressure hydraulic oil on the return oil side of the rotary hydraulic motor charges the accumulator through the first shuttle valve and the two-position two-way directional valve.

2. The control method for preventing swing of the slewing device and breaking of the tooth according to claim 1, characterized in that: The anti-swing tail plug-in valve further comprises a pilot integrated block, a two-position two-way electromagnetic valve, a brake pressure detection switch and a pilot pressure transmitter; two interfaces of the two-position two-way electromagnetic valve are connected with the inlet and return oil ways of the rotary hydraulic motor; the outlet of the second shuttle valve is connected with the pilot pressure transmitter, and the outlet of the first shuttle valve is connected with the brake pressure detection switch; the control circuits of the brake pressure detection switch and the pilot pressure transmitter are connected to the two-position two-way electromagnetic valve, so that the two-position two-way electromagnetic valve is turned on or off by detecting the pressure of the control oil way and the working oil way.

3. The control method for preventing swing of the slewing device and breaking of the tooth according to claim 2, characterized in that: When the pressure detected by the pilot pressure transmitter is higher than 5 Bar and lower than 10 Bar, and the electromagnetic valve (S6) in the pilot integrated block is electrified, the two-position two-way electromagnetic valve is electrified to change direction, the MA1 port of the anti-swing tail plug-in valve is communicated with the MB1 port, the back pressure on the return oil side is rapidly increased at the starting moment, and the pressure difference between the two sides of the hydraulic rotary motor is reduced.

4. The control method for preventing swing of the slewing device and breaking of the tooth according to claim 2, characterized in that: When the pressure detected by the pilot pressure transmitter is lower than 5 Bar, the pressure of the brake pressure detection switch is greater than 100 Bar, and the electromagnetic valve (S6) in the pilot integrated block is electrified, the two-position two-way electromagnetic valve is electrified to change direction, the MA1 port of the anti-swing tail plug-in valve is communicated with the MB1 port, and the pressure of the working oil ports A1 and B1 of the rotary hydraulic motor is rapidly balanced during braking.

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