Control cabin overturning hydraulic system

Abstract

The utility model discloses a turnover hydraulic system of a control cabin. The turnover hydraulic system comprises a turnover oil cylinder of the control cabin, an oil pump, an oil tank, a three-position four-way reversing valve, a one-way valve, an overflow valve, a balance valve, a rod cavity damping connector and a rodless cavity damping connector. According to the utility model, the pressure stabilizing regulator is additionally arranged on the turnover hydraulic system of the control cabin, so that the problems of violent pressure fluctuation of the system and violent vibration of the control cabin caused by violent change of load of a rodless cavity of a turnover oil cylinder of the control cabin at the moment of starting and stopping falling of the control cabin are solved; an optimization scheme of combining a pressure sensor, an electric proportional reversing valve and an electric proportional reversing valve is given, the problem of violent vibration of a control cabin caused by pressure fluctuation is solved, a falling speed adjusting function is added, the flow rate is flexibly adjusted according to different weights and different loads of drivers, and a controller is used for controlling the control cabin according to an external input signal. The falling speed of the control cabin is adjusted, and the operation experience of a driver is improved.

Description

Technical Field

[0001] The utility model relates to the field of hydraulic machinery, in particular to a hydraulic system for turning over a control room. Background Art

[0002] There are two main types of control rooms used in cranes. One is a fixed control room, which is fixed on the crane turntable. The driver observes the status of the crane arm and the load through the glass in front and above the control room. This type of control room is mostly used on small tonnage cranes. Figure 2-3 The reversible control room shown in the figure has a control room reversing cylinder installed under the control room. When the boom is not greatly changed or the extension length is not long, the operator does not need to look up to observe the state of the boom and the load, and the control room does not need to be turned over and remains at the same level. Figure 2 In the position shown, the control room is parallel to the ground. When the boom has a large luffing angle or is extended to a long length, the driver needs to look up for a long time to observe the state of the boom and the load. At this time, the operator needs to extend the control room flip cylinder to drive the control room to flip. After the control room is flipped to an appropriate angle, stop flipping and keep it at the desired angle. Figure 3 Position shown.

[0003] like Figure 4The figure shows a relatively representative hydraulic principle diagram of the control room tilt hydraulic system, and serial number 1 is the control room tilt oil cylinder. When the three-position four-way reversing valve is located in the left position of the figure, the pressure oil enters the balance valve through the V1 port, passes through the balance valve, and enters the rod chamber of the control room tilt oil cylinder through the rod chamber damping joint, the control room tilt oil cylinder retracts, and the hydraulic oil in the rodless chamber of the control room tilt oil cylinder flows into the extension port of the balance valve through the rodless chamber damping joint, then enters the three-position four-way reversing valve through the V2 port, and finally enters the oil tank through the check valve; when the three-position four-way reversing valve is located in the right position of the figure, the pressure oil enters the balance valve through the V2 port, passes through the balance valve, and enters the rodless chamber of the control room tilt oil cylinder through the rodless chamber damping joint, the control room tilt oil cylinder extends, and the hydraulic oil in the rod chamber of the control room tilt oil cylinder flows into the retraction port of the balance valve through the rod chamber damping joint, then enters the three-position four-way reversing valve through the V1 port, and finally enters the oil tank through the check valve. Although this solution can achieve the functional requirement of flipping the control room, the three-position four-way reversing valve used in this hydraulic system is a switch-type solenoid valve. After it is switched to the left position, there will be a large pressure shock and fluctuation when the oil enters the rod chamber of the control room flip cylinder, resulting in obvious vibration of the control room at the start of the downward flip, seriously affecting the driver's operating experience; in addition, when the three-position four-way reversing valve is switched from the left position to the middle position, the oil is instantly locked in the circuit between the rod chamber of the control room flip cylinder and the three-position four-way reversing valve, which will instantly generate a large pressure fluctuation, resulting in more violent vibration of the control room when the control room stops at a certain angle when it is flipped downward, which also seriously affects the driver's operating experience.

[0004] The utility model is a control room turning hydraulic system developed to solve the above problems, which can eliminate the pressure shock caused by the switching valve switching moment, so that the control room will not produce obvious vibration at the moment of starting or stopping. Utility Model Content

[0005] The technical problem to be solved by the utility model is to provide a control room flip hydraulic system in view of the deficiencies of the above-mentioned prior art. On the control room flip hydraulic system, a voltage stabilizer regulator is added in the middle of the hydraulic circuit from the extension port of the balance valve to the control room flip cylinder to solve the problem that at the moment of starting and stopping the control room descent, due to the drastic change of the rodless chamber load of the control room flip cylinder, the system experiences drastic pressure fluctuations and the control room experiences drastic vibrations.

[0006] In order to solve the above technical problems, the technical solution adopted by the utility model is:

[0007] A control room tilting hydraulic system comprises a control room tilting oil cylinder, an oil pump, an oil tank, a three-position four-way reversing valve, a one-way valve, a relief valve, a balancing valve, a rod cavity damping joint and a rodless cavity damping joint, and the control room tilting oil cylinder, the oil pump, the oil tank, the three-position four-way reversing valve, the one-way valve, the relief valve, the balancing valve, the rod cavity damping joint and the rodless cavity damping joint are connected and assembled through an oil pipeline;

[0008] The interior of the control room tilting oil cylinder is divided into a rod chamber and a rodless chamber by the output shaft and the piston, and the rod chamber of the control room tilting oil cylinder and the outer wall of the control room tilting oil cylinder are respectively provided with a rod chamber damping joint and a rodless chamber damping joint;

[0009] The oil pump provides the hydraulic system with a power oil source for controlling the extension and retraction of the cylinder, and the oil tank is used to recover the hydraulic oil in the hydraulic system;

[0010] The three-position four-way reversing valve is used to control the flow direction of the hydraulic oil, so that the control room can turn the oil cylinder to perform the extension / retraction action conversion;

[0011] The three-position four-way reversing valve has a left-position Ya port, a middle-position port and a right-position Yb port, and the balancing valve has a V1 port and a V2 port. When the left-position Ya port is connected to the hydraulic system, the hydraulic oil enters the balancing valve through the V1 port, and after passing through the balancing valve, enters the rod chamber of the control room tilting cylinder from the rod chamber damping joint, the output shaft of the control room tilting cylinder retracts, and the hydraulic oil in the rodless chamber of the control room tilting cylinder flows into the extension port of the balancing valve through the rodless chamber damping joint, and then enters the three-position four-way reversing valve through the V2 port, and finally enters the oil tank through the one-way valve; when the right-position Yb port is connected to the hydraulic system, the hydraulic oil enters the balancing valve through the V2 port, and after passing through the balancing valve, enters the rodless chamber of the control room tilting cylinder through the rodless chamber damping joint, the output shaft of the control room tilting cylinder extends, and the hydraulic oil in the rod chamber of the control room tilting cylinder flows into the retraction port of the balancing valve through the rod chamber damping joint, and then enters the three-position four-way reversing valve through the V1 port, and finally enters the oil tank through the one-way valve;

[0012] A voltage regulator is arranged between the extension port of the balance valve and the rod chamber of the tilting cylinder in the control room and the circuit of the three-position four-way reversing valve to eliminate the severe pressure fluctuation and impact in the hydraulic system.

[0013] Preferably, the voltage regulator includes a pressure sensor, a controller and an electric proportional reversing valve, the sensing end of the pressure sensor is connected to the oil pipeline, the electric proportional reversing valve is connected in series to the oil pipeline, and the electric proportional reversing valve is electrically connected to the controller, an acceleration key and a deceleration key are electrically connected to the connection end of the controller, and the acceleration key and the deceleration key are electrically connected to the control end of the electric proportional reversing valve, which are used to adjust the control current of the electric proportional reversing valve so that the throttle opening of the electric proportional reversing valve can be adjusted.

[0014] Preferably, when the solenoid valve Yb is energized, the electric proportional reversing valve is energized to be unidirectional, and the hydraulic oil flows from the extension port of the balance valve into the rodless chamber of the tilting cylinder in the control room.

[0015] Preferably, when the solenoid valve Ya is energized, the electric proportional reversing valve can be energized to work, the diameter of the throttling hole of the electric proportional reversing valve is set to 0.5mm, and the flow area of ​​the electric proportional reversing valve is positively correlated with the load pressure of the rodless chamber of the flip cylinder.

[0016] Preferably, the voltage regulator is configured as a one-way throttle valve, the one-way throttle valve is connected in series to the oil pipeline, and the diameter of the throttle hole of the one-way throttle valve is configured to be 0.3 mm-0.7 mm.

[0017] Preferably, the pressure stabilizing regulator is configured as a back pressure valve, the back pressure valve is connected in series to the oil pipeline, and the pressure of the back pressure valve is set to 20-30 bar.

[0018] A crane using a cab tilting hydraulic system.

[0019] The utility model has the following beneficial effects:

[0020] By adding a voltage stabilizer to the hydraulic system of the cab flipping, the problem of severe pressure fluctuations in the system and severe vibrations in the cab caused by the drastic changes in the load in the rodless chamber of the cab flipping cylinder at the moment of starting and stopping the cab's descent is solved. An optimized solution combining a pressure sensor, an electric proportional reversing valve and an electric proportional reversing valve is given, which not only solves the problem of severe vibrations of the cab caused by pressure fluctuations, but also adds a falling speed adjustment function, which can flexibly adjust the flow rate according to the different weights of the driver and the size of the load. The controller is used to adjust the falling speed of the cab according to external input signals, thereby improving the driver's operating experience. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 A hydraulic principle diagram of a control room flip hydraulic system provided by the utility model;

[0022] Figure 2 This is a schematic diagram of the control room of the utility model in an unturned state;

[0023] Figure 3 This is a schematic diagram of the turning state of the control room of the utility model;

[0024] Figure 4 It is a hydraulic principle diagram of a hydraulic system for turning over a control room in the prior art;

[0025] Figure 5 A hydraulic principle diagram is given for the first embodiment of a control room flip hydraulic system provided by the utility model.

[0026] Among them are:

[0027] 1-Operation room tilting cylinder; 2-Oil pump; 3-Oil tank; 4-Three-position four-way reversing valve; 5-Check valve; 6-Overflow valve; 7-Balance valve; 8-Rod cavity damping joint; 9-Rodless cavity damping joint; 10-Pressure sensor; 11-Controller; 12-Electric proportional reversing valve. DETAILED DESCRIPTION

[0028] The present invention will be further described in detail below in conjunction with the accompanying drawings and specific preferred embodiments.

[0029] In the description of the present invention, it should be understood that the terms "left side", "right side", "upper part", "lower part", etc. indicate the orientation or position relationship based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present invention and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. "First", "second", etc. do not indicate the importance of the components, and therefore cannot be understood as a limitation on the present invention. The specific dimensions used in this embodiment are only for illustrating the technical solution, and do not limit the scope of protection of the present invention.

[0030] like Figure 1-5 As shown, a control room tilting hydraulic system comprises a control room tilting oil cylinder 1, an oil pump 2, an oil tank 3, a three-position four-way reversing valve 4, a one-way valve 5, a relief valve 6, a balancing valve 7, a rod chamber damping joint 8 and a rodless chamber damping joint 9, and the control room tilting oil cylinder 1, the oil pump 2, the oil tank 3, the three-position four-way reversing valve 4, the one-way valve 5, the relief valve 6, the balancing valve 7, the rod chamber damping joint 8 and the rodless chamber damping joint 9 are connected and assembled through an oil pipeline;

[0031] The interior of the control room tilting oil cylinder 1 is divided into a rod chamber and a rodless chamber by the output shaft and the piston, and the rod chamber of the control room tilting oil cylinder 1 and the outer wall of the control room tilting oil cylinder 1 are respectively provided with a rod chamber damping joint 8 and a rodless chamber damping joint 9;

[0032] The oil pump 2 provides a power oil source for the hydraulic system, which is used for the extension and retraction control of the oil cylinder, and the oil tank 3 is used to recover the hydraulic oil in the hydraulic system;

[0033] The three-position four-way reversing valve 4 is used to control the flow direction of the hydraulic oil, so that the turning cylinder in the control room can perform the extension / retraction action conversion;

[0034] The three-position four-way reversing valve 4 has a left-position Ya port, a middle-position port and a right-position Yb port, and the balance valve 7 has a V1 port and a V2 port. When the left-position Ya port is connected to the hydraulic system, the hydraulic oil enters the balance valve 7 through the V1 port, and after passing through the balance valve 7, it enters the rod chamber of the control room tilting cylinder 1 from the rod chamber damping joint 8. The output shaft of the control room tilting cylinder 1 retracts, and the hydraulic oil in the rodless chamber of the control room tilting cylinder 1 flows into the extension port of the balance valve 7 through the rodless chamber damping joint 9, and then enters the three-position four-way reversing valve 4 through the V2 port. The hydraulic oil flows through the reversing valve 4 and finally enters the oil tank 3 through the one-way valve 5; when the right Yb port is connected to the hydraulic system, the hydraulic oil enters the balance valve 7 through the V2 port, and after passing through the balance valve 7, enters the rodless chamber of the control room tilting cylinder 1 through the rodless chamber damping joint 9, and the output shaft of the control room tilting cylinder 1 extends. The hydraulic oil in the rod chamber of the control room tilting cylinder 1 flows through the rod chamber damping joint 8 into the retraction port of the balance valve 7, and then enters the three-position four-way reversing valve 4 through the V1 port, and finally enters the oil tank 3 through the one-way valve 5;

[0035] A voltage regulator is arranged between the extending port of the balance valve 7 and the rod chamber of the tilting cylinder 1 in the control room and the circuit of the three-position four-way reversing valve 4 to eliminate the severe pressure fluctuation and impact in the hydraulic system.

[0036] Embodiment 1

[0037] The voltage regulator includes a pressure sensor 10, a controller 11 and an electric proportional reversing valve 12. The sensing end of the pressure sensor 10 is connected to the oil pipeline. The electric proportional reversing valve 12 is connected in series to the oil pipeline. The electric proportional reversing valve 12 is electrically connected to the controller 11. An acceleration key and a deceleration key are electrically connected to the connection end of the controller 11. The acceleration key and the deceleration key are electrically connected to the control end of the electric proportional reversing valve 12, and are used to adjust the control current of the electric proportional reversing valve 12 so that the throttle opening of the electric proportional reversing valve 12 can be adjusted.

[0038] When the solenoid valve Yb is energized, the electric proportional reversing valve 12 is not energized and is a one-way flow, and the hydraulic oil flows from the extension port of the balance valve 7 into the rodless chamber of the tilting oil cylinder 1 in the control room;

[0039] When the solenoid valve Ya is energized, the electric proportional reversing valve 12 can be energized to work, and the diameter of the throttle hole of the electric proportional reversing valve 12 is set to 0.5mm. The pressure sensor 10 detects the pressure of the rodless chamber of the tilting oil cylinder 1 in the control room, and the controller 11 converts the pressure signal into a control current signal of the electric proportional reversing valve 12, thereby controlling the throttle hole opening of the electric proportional reversing valve 12. The flow area of ​​the electric proportional reversing valve 12 is positively correlated with the load pressure of the rodless chamber of the tilting oil cylinder, that is, the greater the load of the control room, the greater the flow area of ​​the internal throttle hole, and vice versa, thereby achieving the change of the load pressure of the rodless chamber according to the size of the hydraulic oil flow through the electric proportional reversing valve.

[0040] During operation, when the left Ya port is connected to the hydraulic system, the hydraulic oil enters the balance valve 7 through the V1 port, and after passing through the balance valve 7, enters the rod chamber of the control room tilting cylinder 1 from the rod chamber damping joint 8. The output shaft of the control room tilting cylinder 1 retracts, and the hydraulic oil in the rodless chamber of the control room tilting cylinder 1 enters the electric proportional reversing valve 12 through the rodless chamber damping joint 9. At this time, the pressure sensor 10 detects the pressure in the rodless chamber of the control room tilting cylinder 1, and converts the pressure signal into an electrical signal of the electric proportional reversing valve 12 after being processed by the controller 11, thereby controlling the throttle opening of the electric proportional reversing valve 12. Due to factors such as the weight of the driver, the greater the load borne by the control room, the larger the flow area of ​​the internal throttle hole, and the larger the flow through the electric proportional reversing valve 12. After the filtering and throttling effect, the oil cylinder in the control room will not produce obvious pressure shock at the moment of retraction, so as to eliminate the violent vibration at the moment of the control room falling and starting; when the three-position four-way reversing valve 4 is located at the position of switching from the left position Ya port to the middle position port, it means that the control room needs to stay at a certain angle at this time. At this time, the hydraulic circuit between the rodless chamber of the control room turning oil cylinder 1 and the three-position four-way reversing valve 4 is suddenly locked, and under the action of the gravity of the driver and the control room and the oil pressure of the rodless chamber, a violent pressure shock is generated. By using the voltage regulator in this system, the high-pressure hydraulic oil generated at the moment of stopping can eliminate its violent pressure fluctuations and shocks after passing through the electric proportional reversing valve 12 that flexibly adjusts the hydraulic oil flow rate according to the load pressure, and the effect is remarkable;

[0041] In addition, during the descending process of the control cab, if the driver needs to adjust the descending speed of the control cab, the controller 11 can also adjust the control current of the electric proportional reversing valve 12 according to the driver's input signal, such as pressing the acceleration key and the deceleration key, thereby adjusting the descending speed of the control cab, which is beneficial to improving the driver's operating experience.

[0042] Embodiment 2

[0043] The voltage regulator is set as a one-way throttle valve, which is connected in series to the oil pipeline, and the diameter of the throttle hole of the one-way throttle valve is set to 0.3mm-0.7mm. The high-pressure hydraulic oil generated at the moment of stopping can significantly eliminate its violent pressure fluctuations and impacts after entering the throttle port of the one-way throttle valve.

[0044] Embodiment 3

[0045] The pressure regulator is set as a back pressure valve, which is connected in series to the oil pipeline and the pressure of the back pressure valve is set to 20-30bar. The high-pressure hydraulic oil generated at the moment of stopping can significantly eliminate its violent pressure fluctuations and impacts after entering the back pressure valve.

[0046] A crane using a cab flipping hydraulic system greatly improves the operating experience of the driver and can improve work efficiency by using the crane.

[0047] The embodiments of the present invention are described in detail above with reference to the accompanying drawings, but the present invention is not limited to the described embodiments. For those skilled in the art, various changes, modifications, substitutions and variations of these embodiments are made without departing from the principles and spirit of the present invention, and still fall within the scope of protection of the present invention.

Claims

1. A hydraulic system for turning over a control room, characterized in that: The invention comprises a control room tilting oil cylinder (1), an oil pump (2), an oil tank (3), a three-position four-way reversing valve (4), a one-way valve (5), an overflow valve (6), a balancing valve (7), a rod chamber damping joint (8) and a rodless chamber damping joint (9), and the control room tilting oil cylinder (1), the oil pump (2), the oil tank (3), the three-position four-way reversing valve (4), the one-way valve (5), the overflow valve (6), the balancing valve (7), the rod chamber damping joint (8) and the rodless chamber damping joint (9) are connected and assembled through an oil pipeline; The interior of the control room tilting oil cylinder (1) is divided into a rod chamber and a rodless chamber by an output shaft and a piston, and the outer walls of the rod chamber of the control room tilting oil cylinder (1) and the rodless chamber of the control room tilting oil cylinder (1) are respectively provided with a rod chamber damping joint (8) and a rodless chamber damping joint (9); The oil pump (2) provides a power oil source for the hydraulic system and is used for controlling the extension and retraction of the oil cylinder, and the oil tank (3) is used to recover the hydraulic oil in the hydraulic system; The three-position four-way reversing valve (4) is used to control the flow direction of the hydraulic oil, so that the turning cylinder in the control room can perform the extension / retraction action conversion; The three-position four-way reversing valve (4) has a left-position Ya port, a middle-position port and a right-position Yb port, and the balance valve (7) has a V1 port and a V2 port. When the left-position Ya port is connected to the hydraulic system, the hydraulic oil enters the balance valve (7) through the V1 port, and after passing through the balance valve (7), enters the rod chamber of the control room tilting oil cylinder (1) from the rod chamber damping joint (8). The output shaft of the control room tilting oil cylinder (1) retracts, and the hydraulic oil in the rodless chamber of the control room tilting oil cylinder (1) flows into the extension port of the balance valve (7) through the rodless chamber damping joint (9), and then enters the three-position four-way reversing valve through the V2 port. (4), and finally enters the oil tank (3) through the one-way valve (5); when the right position Yb port is connected to the hydraulic system, the hydraulic oil enters the balance valve (7) through the V2 port, passes through the balance valve (7), and then enters the rodless chamber of the control room tilting cylinder (1) through the rodless chamber damping joint (9), the output shaft of the control room tilting cylinder (1) extends, and the hydraulic oil in the rod chamber of the control room tilting cylinder (1) flows into the retraction port of the balance valve (7) through the rod chamber damping joint (8), and then enters the three-position four-way reversing valve (4) through the V1 port, and finally enters the oil tank (3) through the one-way valve (5); A pressure regulator is arranged between the extension port of the balance valve (7) and the rod chamber of the tilting oil cylinder (1) in the control room and the circuit of the three-position four-way reversing valve (4) to eliminate the severe pressure fluctuation and impact in the hydraulic system.

2. A control room tilting hydraulic system according to claim 1, characterized in that: The voltage regulator comprises a pressure sensor (10), a controller (11) and an electric proportional reversing valve (12); the sensing end of the pressure sensor (10) is connected to the oil pipeline; the electric proportional reversing valve (12) is connected in series to the oil pipeline; the electric proportional reversing valve (12) is electrically connected to the controller (11); an acceleration key and a deceleration key are electrically connected to the connection end of the controller (11); the acceleration key and the deceleration key are electrically connected to the control end of the electric proportional reversing valve (12) and are used to adjust the control current of the electric proportional reversing valve (12) so that the throttle opening of the electric proportional reversing valve (12) can be adjusted.

3. A control room tilting hydraulic system according to claim 2, characterized in that: When the electromagnetic valve Yb is energized, the electric proportional reversing valve (12) is de-energized to allow one-way flow, and the hydraulic oil flows from the extension port of the balance valve (7) into the rodless chamber of the tilting oil cylinder (1) in the control room.

4. A control room tilting hydraulic system according to claim 2, characterized in that: When the electromagnetic valve Ya is energized, the electric proportional reversing valve (12) can be energized to work, the diameter of the throttle hole of the electric proportional reversing valve (12) is set to 0.5 mm, and the flow area of ​​the electric proportional reversing valve (12) is positively correlated with the load pressure of the rodless chamber of the tilting oil cylinder.

5. The hydraulic system for turning over a control room according to claim 1, characterized in that: The voltage regulator is configured as a one-way throttle valve, which is connected in series to the oil pipeline, and the diameter of the throttle hole of the one-way throttle valve is configured to be 0.3 mm-0.7 mm.

6. The hydraulic system for turning over a control room according to claim 1, characterized in that: The pressure stabilizing regulator is configured as a back pressure valve, the back pressure valve is connected in series to the oil pipeline, and the pressure of the back pressure valve is set to 20-30 bar.

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