CN113565837B - Quick erection equipment - Google Patents

Quick erection equipment Download PDF

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Publication number
CN113565837B
CN113565837B CN202010359012.9A CN202010359012A CN113565837B CN 113565837 B CN113565837 B CN 113565837B CN 202010359012 A CN202010359012 A CN 202010359012A CN 113565837 B CN113565837 B CN 113565837B
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China
Prior art keywords
oil
erection
way valve
hydraulic
arm
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CN202010359012.9A
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Chinese (zh)
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CN113565837A (en
Inventor
张春峰
曾红丰
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Beijing Machinery Equipment Research Institute
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Beijing Machinery Equipment Research Institute
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Priority to CN202010359012.9A priority Critical patent/CN113565837B/en
Publication of CN113565837A publication Critical patent/CN113565837A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/06—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes with jibs mounted for jibbing or luffing movements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/62—Constructional features or details
    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06C—LADDERS
    • E06C7/00—Component parts, supporting parts, or accessories
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03H—PRODUCING A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03H99/00—Subject matter not provided for in other groups of this subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F41—WEAPONS
    • F41F—APPARATUS FOR LAUNCHING PROJECTILES OR MISSILES FROM BARRELS, e.g. CANNONS; LAUNCHERS FOR ROCKETS OR TORPEDOES; HARPOON GUNS
    • F41F1/00—Launching apparatus for projecting projectiles or missiles from barrels, e.g. cannons; Harpoon guns

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The specification provides a quick erection device, which comprises a base part, a erection arm, a hydraulic system and a recoil power device; the base part is hinged with the first end of the erection arm through a first hinge shaft; the hydraulic system comprises a hydraulic control mechanism and a hydraulic cylinder; the recoil power device is arranged on the vertical arm; when the recoil power device works to generate jet flow, the vertical arm rotates around the first hinge shaft in the first direction, and the hydraulic cylinder stretches; and the hydraulic control mechanism injects oil into the first oil cavity of the hydraulic cylinder in the extending process of the hydraulic cylinder so as to ensure that the first oil cavity is always in a state of completely filling the oil. The power provided by the recoil power device can enable the erection arm to be matched with the hydraulic system to realize erection of the erection arm, so that the erection speed of the erection arm is ensured; the oil pressure in the hydraulic system can be kept at a relatively small value, so that the problem that the probability of occurrence of oil leakage faults of the hydraulic system is increased due to overlarge oil pressure in the prior art is avoided.

Description

Quick erection equipment
Technical Field
The application relates to the technical field of hydraulic pressure, in particular to quick erection equipment.
Background
To meet the need for rapid deployment, hydraulic cylinders in hydraulic systems in erection (lifting) equipment such as fire-fighting ladders, missile launchers, etc. should be capable of rapid extension.
At present, in order to realize the rapid extension of a hydraulic cylinder, a high-pressure oil supply branch is arranged in a hydraulic system of the existing rapid erection system; a high-pressure energy storage oil tank is arranged in the oil supply branch; when the hydraulic cylinder needs to be made to work fast to realize the fast erection function, the oil supply branch is communicated with the oil inlet cavity of the hydraulic cylinder, and hydraulic oil flows into the oil inlet cavity from the high-pressure energy storage oil tank in a large flow way under the high-pressure effect.
Because the pressure of the high-pressure conventional tank is greater than that of the conventional hydraulic cylinder, the piping and the respective sealing portions of the aforementioned hydraulic system are required to withstand greater pressures, and the possibility of occurrence of a leakage failure is correspondingly increased.
Disclosure of Invention
The present description provides a quick erection device that enables a erection arm in the quick erection device to be quickly raised while the hydraulic system pressure is maintained relatively small.
The specification provides a quick erection device, which comprises a base part, a erection arm, a hydraulic system and a recoil power device;
the base part is hinged with the first end of the erection arm through a first hinge shaft;
the hydraulic system comprises a hydraulic control mechanism and a hydraulic cylinder;
the recoil power device is arranged on the vertical arm;
when the recoil power device works to generate jet flow, the erection arm rotates around the first hinge shaft in a first direction, and the hydraulic cylinder stretches; in the extending process of the hydraulic cylinder, the hydraulic control mechanism injects oil into the first oil cavity of the hydraulic cylinder, so that the first oil cavity is always in a state of completely filling the oil.
Optionally, the hydraulic cylinder is hinged with the erection arm through a second hinge shaft; the recoil power device is provided on a side remote from the first hinge shaft with respect to the second hinge shaft.
Optionally, the direction of the jet of the recoil power device is perpendicular to the extending direction of the erection arm.
Optionally, the recoil power device is a gas power device, a blade pushing device or a high-pressure thrust reverser.
Optionally, the hydraulic control mechanism comprises a hydraulic pump, an energy storage oil tank, a first two-way valve and a second two-way valve;
one port of the first two-way valve is communicated with an oil outlet of the hydraulic pump, and the other port of the first two-way valve is communicated with the first oil cavity;
one port of the second two-way valve is communicated with the energy storage oil tank, and the other port of the second two-way valve is communicated with the first oil cavity.
Optionally, the first two-way valve is a proportional valve; the hydraulic control mechanism further comprises a proportional overflow valve; and an oil inlet of the proportional overflow valve is communicated with an oil outlet of the hydraulic pump.
Optionally, the hydraulic cylinder is a multi-stage hydraulic cylinder; and a cylinder barrel of the hydraulic cylinder is hinged with the erection arm through a second hinge shaft.
Optionally, the hydraulic cylinder is a double-acting hydraulic cylinder; the hydraulic cylinder further comprises a second oil cavity;
the hydraulic control mechanism further comprises a third two-way valve; the third two-way valve is a proportional valve; and one port of the third two-way valve is communicated with the second oil cavity.
Optionally, the hydraulic control mechanism further comprises a three-position four-way valve; the oil supply port of the three-position four-way valve is communicated with the oil outlet of the hydraulic pump; one oil outlet of the three-position four-way valve is communicated with one port of the first two-way valve, and the other oil outlet of the three-position four-way valve is communicated with one port of the third two-way valve.
Optionally, the hydraulic control mechanism further comprises a fourth two-way valve; the fourth two-way valve is arranged between the hydraulic pump and the energy storage oil tank.
In the quick erection equipment provided by the specification, the recoil power device provides power to enable the erection arm to be matched with the hydraulic system to realize erection of the erection arm, so that the erection speed of the erection arm is ensured; in one case, during operation of the recoil power device, the hydraulic system is only used for providing sufficient oil to the first oil chamber so that the first oil chamber is in a state of being completely filled with oil; in this case, the oil pressure in the hydraulic system can be kept at a relatively small value, so that the problem that the oil pressure of the hydraulic system is large in order to realize quick lifting of the vertical arm in the prior art is avoided, and the problem that the occurrence probability of oil leakage faults of the hydraulic system is increased because the oil pressure is too large is avoided.
In the application, the technical schemes can be mutually combined to realize more preferable combination schemes. Additional features and advantages of the application will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the application. The objectives and other advantages of the application may be realized and attained by the structure particularly pointed out in the written description and drawings.
Drawings
The drawings are only for purposes of illustrating particular embodiments and are not to be construed as limiting the application, like reference numerals being used to refer to like parts throughout the several views.
FIG. 1 is a schematic illustration of a quick erection device provided by an embodiment;
wherein: the hydraulic system comprises a base part 11, a lifting arm 12, a hydraulic system 13, a hydraulic cylinder 131, a first oil cavity 131A, a cylinder barrel 131B, a cylinder sleeve 131C, a second oil cavity 131D, a hydraulic pump 132, a 133-energy storage oil tank 134, a first two-way valve 135, a second two-way valve 136, a proportional overflow valve 137, a third two-way valve 138, a three-position four-way valve 139, a fourth two-way valve 140, a conventional oil tank 141, a one-way valve 14, a recoil power device 15, a first hinge shaft 16, a second hinge shaft 17 and a third hinge shaft.
Detailed Description
The following detailed description of preferred embodiments of the application is made in connection with the accompanying drawings, which form a part hereof, and together with the description of the embodiments of the application, are used to explain the principles of the application and are not intended to limit the scope of the application.
The embodiment of the specification provides quick erection equipment, which is used for realizing quick erection of equipment by utilizing the cooperation of other power sources and a hydraulic system.
FIG. 1 is a schematic diagram of a quick erection device provided by an embodiment. As shown in fig. 1, the quick erection device in this embodiment includes a base portion 11, an erection arm 12, a hydraulic system 13, and a recoil power device 14.
As shown in fig. 1, the base portion 11 is represented by a frame in a conventional mechanical drawing. The base portion 11 may be a fixed base or may be a movable base such as a vehicle chassis, and the embodiment is not particularly limited.
In practical use, the base portion 11 is often a base portion 11 that can be moved, such as a vehicle chassis. Before the quick erection equipment works, another hydraulic device can be adopted to prop up the base part 11, so that the stability and the safety of the subsequent operation process are ensured.
The erection arm 12 is an erected arm 12 member in the quick erection device, and the erection arm 12 is hinged with the base portion 11 through a first hinge shaft 15. Depending on the field of use of the quick erection device, the actual product form of the erection arm 12 correspondingly varies. In practical application, in the case that the quick erection device is a missile launcher, the erection arm 12 may be a missile launcher; in the case where the quick erection device is a crane or rescue aerial ladder, the erection arm 12 may be a boom.
The hydraulic system 13 includes a hydraulic cylinder 131 and a hydraulic control mechanism (the hydraulic control mechanism is an integral body of the hydraulic system other than the hydraulic cylinder 131). As shown in fig. 1, the hydraulic cylinder 131 has one end hinged to the erection arm 12 via the second hinge shaft 16 and the other end hinged to the base portion 11 via the third hinge shaft 17. As is known from the prior art and the application requirements, the second hinge axis 16 and the third hinge axis 17 are both parallel to the first hinge axis 15. The hydraulic control mechanism is used for controlling the expansion and contraction of the hydraulic cylinder 131, and then controlling the erection or the return of the erection arm 12.
The recoil power device 14 is provided on the erection arm 12. The nozzle of the recoil device is arranged towards the ground. The recoil power device 14, when operated, generates a jet.
From the force interactions, it is known that the jet acts on the recoil power device 14 with a certain opposing force when the jet of the recoil power device 14 is being ejected. When the velocity of the jet reaches a certain value, the opposing force acting on the reflex spraying apparatus can overcome the gravity of the lifting arm 12, so that the lifting arm 12 forms a turning moment (or turning momentum) turning around the first hinge shaft 15; under the action of the turning moment, the erection arm 12 can be turned around the first hinge shaft 15 to be erected.
During the operation of the recoil power device 14 to raise the raising arm 12, the cylinder tube 131B (or the cylinder rod) of the hydraulic cylinder 131 is extended out of the cylinder tube 131B by the pulling action of the raising arm 12, so that the first oil chamber 131A of the hydraulic cylinder 131 is increased in volume. When the volume of the first oil cavity 131A increases, the hydraulic control mechanism injects oil into the first oil cavity 131A, so that the first oil cavity 131A is always in a state of completely filling oil, and the phenomenon of emptying in the first oil cavity 131A is avoided.
In this embodiment, the recoil power device 14 is operated to form a turning moment that turns the erection arm 12 about the first hinge shaft 15 at least during the erection of the erection arm 12 to the set state.
As can be seen from the foregoing description, the quick erection device provided in the embodiments of the present disclosure, the power provided by the recoil power device 14 can enable the erection arm 12 to cooperate with the hydraulic system 13 to achieve the erection of the erection arm 12, so as to ensure the erection speed of the erection arm 12.
In one operating condition, only the recoil jet device 14 is used to drive the upstand arm 12 in rotation during the initial stage of upstand of the upstand arm 12. During operation of the recoil power device 14, the hydraulic cylinder is in a passively stretched state, not in an actively stretched state due to the pressure formed by the injection of the oil. At this time, the hydraulic system 13 only needs to supply sufficient oil to the first oil chamber 131A, so that the first oil chamber 131A is in a state of being completely filled with oil, and thus the oil pressure in the entire hydraulic system 13 can be maintained at a relatively small value. Thus, the problem that the oil pressure of the hydraulic system 13 is large in order to realize the rapid lifting of the vertical arm 12 in the prior art can be avoided, and the problem that the occurrence probability of oil leakage faults of the hydraulic system 13 is increased because the oil pressure is too large is avoided.
As shown in fig. 1, in the embodiment of the present specification, the recoil power device 14 is provided on a side remote from the first hinge shaft 15 with respect to the second hinge shaft 16. Preferably, the recoil power device 14 may be positioned in the top region of the lift arm 12 as far as possible from the hydraulic cylinder 131 to reduce the impact of the jet generated by its operation on the hydraulic system. In other embodiments, the recoil power device 14 can be positioned elsewhere on the riser arm 12,
in the present embodiment, the ejection direction of the recoil power device 14 is preferably set perpendicular to the extending direction of the rising arm 12. It is conceivable that in this case, the recoil power device 14 allows the arm of force when the erection arm 12 is rotated to maintain a stable value; under the same recoil momentum, the turning moment acting to turn the vertical arm 12 is greater.
In other embodiments, the direction of injection of the recoil upstand device may be adaptively changed depending on the upstand condition of the upstand arm 12 to achieve superior upstand control of the upstand arm 12.
For example, in one other embodiment, the direction of injection of the recoil upstand arm 12 may be adaptively changed to push the upstand arm 12 up quickly during the period that the upstand arm 12 is just erected, and to change the direction of injection to reduce the upstand speed of the upstand arm 12 when the upstand arm 12 will reach the set upstand condition, avoiding the upstand arm 12 from transitioning from the resistive load to the overrunning load.
In this embodiment, the recoil power device 14 is a gas power device, that is, it adopts a gas injection mode to form a jet.
In practical applications, the gas power device may be a small turbojet engine, a small rocket engine, or the like. In other embodiments, the recoil power device 14 may also be a blade pushing device, i.e. it may use blade rotation to drive the jet of air to create the power for rotating the lifting arm 12 about the first hinge axis 15. In other embodiments, the recoil power device 14 may also employ a high pressure thrust reverser formed from high pressure gas.
In this embodiment, in order to rapidly increase the volume of the first oil chamber 131A in cooperation with the aforementioned recoil power device 14, the hydraulic control mechanism should provide an oil supply speed that matches the rate of change of the volume of the first oil chamber 131A.
To achieve matching of the oil supply speed and the volume change of the first oil chamber 131A, in the present embodiment, the hydraulic control mechanism is provided with a hydraulic pump 132, an accumulator tank 133, a first two-way valve 134, and a second two-way valve 135.
One port of the first two-way valve 134 communicates with the oil outlet of the hydraulic pump 132, and the other port communicates with the port of the first oil chamber 131A; one port of the second two-way valve 135 communicates with the accumulator tank 133, and the other port also communicates with the port of the first oil chamber 131A.
The accumulator tank 133 stores high-pressure oil. In the case where the second two-way valve 135 is opened and the external pressure is smaller than the internal pressure of the accumulator tank 133, the hydraulic oil of the accumulator tank 133 flows outward. In practical applications, the energy storage oil tank 133 may implement the foregoing functions by providing a control air bag.
In this embodiment, when the recoil power device 14 works to drive the vertical arm 12 to be erected, the hydraulic control mechanism can supply oil to the first oil chamber 131A in two ways at the same time: (1) Opening the first two-way valve 134, pumping oil from the conventional oil tank 140 to the first oil chamber 131A using the hydraulic pump 132; (2) The second two-way valve 135 is opened, and the oil is made to flow toward the first oil chamber 131A by the internal pressure of the accumulator tank 133.
It is contemplated that with the two modes described above, a smaller maximum unit pumping capacity of the hydraulic pump 132 may be employed; a higher power hydraulic pump 132 is not required. Of course, in other embodiments, the accumulator tank 133 and the first two-way valve 134 may not be provided if the hydraulic pump 132 is capable of ensuring that the amount of pumped oil is satisfactory.
In this embodiment, the first two-way valve 134 is a proportional valve to adapt to the rate of change of the volume of the first hydraulic chamber. In practice, the oil supply amount of the hydraulic pump 132 to the first oil chamber 131A may be adjusted by adjusting the first two-way valve 134.
Preferably, the first two-way valve 134 may be a proportional directional valve, which has a function of adjusting a flow rate, and also has a function of realizing unidirectional control by adjusting, so that the hydraulic oil is prevented from flowing reversely into the hydraulic pump 132 during the process of injecting the hydraulic oil into the first oil chamber 131A.
In the case where the first two-way valve 134 is a proportional valve, the hydraulic control mechanism further includes a proportional relief valve 136. The oil inlet of the proportional relief valve 136 communicates with the oil outlet of the hydraulic pump 132. When the hydraulic control mechanism works, the hydraulic pump 132 of the hydraulic control system can maintain a certain working power, and the pumping liquid amount is ensured to be constant. While the first two-way valve 134 reduces the amount of oil passing therethrough, if the outlet pressure of the hydraulic pump 132 is too high, the proportional relief valve 136 opens to allow excess oil to flow back to the conventional oil tank 140.
In the embodiment of the present description, the recoil power device 14 provides greater power for the erection of the erection arm 12; in practical applications, the final erection angle of the erection arm 12 needs to be precisely controlled, and the recoil power device 14 is not suitable for the requirement of precisely controlling the erection angle, so that the recoil power device 14 is only used in the initial stage of erection of the erection arm 12; after the erection arm 12 reaches a certain state, the recoil power device 14 stops working, and the hydraulic system is used for continuously controlling the erection arm 12 until the erection is up to a set angle. Since the accumulator tank 133 can only provide a small oil pressure and cannot be used to continue to control the hydraulic cylinder 131 to push the boom 12 to extend after a certain time later, it is necessary to disconnect the accumulator tank 133 from the first oil chamber 131A at a proper time point by using the second two-way valve 135 and supply oil to the first oil chamber 131A only using the hydraulic pump 132.
As shown in fig. 1, the hydraulic cylinder 131 in the present embodiment is a multi-stage hydraulic cylinder 131. The cylinder tube 131B of the multistage hydraulic cylinder 131 is hinged to the erection arm 12 through the second hinge shaft 16. According to the operating characteristics of the multi-stage hydraulic cylinder 131, when the first stage sleeve of the multi-stage hydraulic cylinder 131 extends out of the previous stage sleeve (or the cylinder 131B), the corresponding hydraulic reasoning area is correspondingly changed, and when the hydraulic cylinder 131 extends out of the same length, the volume change amount of the first oil chamber 131A is also different.
In this embodiment, the output power of the recoil power device 14 is relatively high, and after a short period of operation, the vertical arm 12 can obtain a relatively high rotational speed. In order to avoid the recoil power device 14 operating such that the hydraulic cylinder 131 produces a large speed change when the cylinder liner 131C fully extends out of the cylinder barrel 131B, and then exceeds the vibration impact threshold of the erection arm 12, the recoil power device 14 is used only when the primary sleeve of the hydraulic cylinder 131 fully extends out of the cylinder barrel 131B.
Specifically, the recoil power device 14 has stopped operating before the primary sleeve of the hydraulic cylinder 131 fully extends out of the cylinder tube 131B. When the primary sleeve of the hydraulic cylinder 131 extends out of the cylinder 131B completely, the collision speed of the primary sleeve and the cylinder 131B makes the vibration impact amount generated by the erection arm 12 smaller than the vibration impact threshold of the erection arm 12.
In the specific application of the embodiment, the recoil power device 14 can stop the operation of the vertical arm 12 after reaching a certain speed; subsequently, the vertical arm 12 continues to rotate about the first hinge shaft 15 under the action of its own kinetic energy. During the continued rotation of the erection arm 12 by its own kinetic energy, the volume change speed of the first oil chamber 131A gradually decreases to the rated flow rate of the hydraulic pump 132.
In the present embodiment, a speed sensor that detects the erection speed and an angle sensor that detects the erection angle of the erection arm 12 may be provided to determine the rate of change in volume of the first oil chamber 131A using the speed sensor and the angle sensor. When the rate of change of the volume of the first oil chamber 131A decreases to the empty unit pumping amount of the hydraulic pump 132, the second two-way valve 135 may be closed, and hydraulic oil may be pumped to the first oil chamber 131A using only the hydraulic pump 132 by adjusting the first two-way valve 134.
In other embodiments, a pressure sensor that detects the pressure of the hydraulic fluid in the second hydraulic chamber may be provided to determine the opening and closing of the first two-way valve 134 and the second two-way valve 135 using the pressure value detected by the pressure sensor, and to control the flow rate of the hydraulic fluid of the first two-way valve 134 and the operation state of the hydraulic pump 132.
In other embodiments, if the output power of the recoil power device 14 can be precisely controlled, the recoil power device 14 can be used when the multi-stage sleeve of the hydraulic cylinder 131 is extended, and the operating states of the first two-way valve 134, the second two-way valve 135, and the hydraulic pump 132 can be adaptively controlled.
In the present embodiment, the hydraulic cylinder 131 is a multi-stage hydraulic cylinder 131. In other embodiments, hydraulic cylinder 131 may be a single stage hydraulic cylinder 131.
As described above, in the present embodiment, the cylinder tube 131B of the multistage hydraulic cylinder 131 is hinged to the erection arm 12 through the second hinge shaft 16. This is so arranged as to ensure that the primary cylinder 131B (i.e., the cylinder 131B having the largest diameter) of the multistage hydraulic cylinder 131 is first extended. Of course, in other embodiments, if the thinnest cylinder liner 131C (or cylinder rod) of the multi-stage hydraulic cylinder 131 has sufficient support strength, the thinnest cylinder liner 131C (or cylinder rod) of the multi-stage hydraulic cylinder 131 may be hinged to the erection arm 12 through the second hinge shaft 16.
As shown in fig. 1, the hydraulic cylinder 131 in the present embodiment is a double-acting cylinder. The hydraulic control mechanism further includes a third two-way valve 137. The third two-way valve 137 is also a proportional valve, and one port of the third two-way valve 137 is communicated with the second oil chamber 131D; during the erection of the erection arm 12, the third two-way valve 137 is opened, and the hydraulic oil in the second oil chamber 131D in the double-acting cylinder flows back to the conventional oil tank 140 through the third two-way valve 137.
In practical application, in order to avoid the transformation of the lifting arm 12 from the impedance load to the overrunning load, before the lifting arm 12 reaches the everting point, the third two-way valve 137 may be controlled to change the outflow rate of the oil in the second oil chamber 131D, so as to make the second oil chamber 131D form a certain back pressure, so as to slow down the moving speed of the lifting arm 12, and then, the precise control of the lifting angle of the lifting arm 12 is realized by precisely controlling the reflux amount of the oil.
In this embodiment, the hydraulic control mechanism further includes a three-position four-way valve 138. The oil supply port of the three-position four-way valve 138 is communicated with the oil outlet of the hydraulic pump 132, one oil outlet of the three-position four-way valve 138 is communicated with one port of the first two-way valve 134, and the other oil outlet is communicated with one port of the third two-way valve 137; the return port of the three-position four-way valve 138 communicates with a conventional oil tank 140.
In this embodiment, the three-position four-way valve 138 is an O-valve. During the raising of the lift arm 12, the three-position four-way valve 138 is in a state such that the oil outlet of the hydraulic pump 132 communicates with one port of the first two-way valve 134 such that one port of the third two-way valve 137 communicates with the conventional oil tank 140; and during the return of the lift arm 12, the three-position four-way valve 138 is in another state such that the upstream port of the hydraulic pump 132 communicates with one port of the third two-way valve 137 such that one port of the second two-way valve 135 communicates with the conventional tank 140.
Of course, according to practical applications, the three-position four-way valve 138 in the present embodiment may be any other type of three-position four-way valve 138, and the present embodiment is not limited thereto.
With continued reference to fig. 1, in this embodiment, the hydraulic control mechanism further includes a fourth two-way valve 139. A fourth two-way valve 139 is provided between the hydraulic pump 132 and the accumulator tank 133. Before the erection operation of the erection arm 12 is performed, the fourth two-way valve 139 is opened, and the hydraulic pump 132 works to pump oil into the energy storage oil tank 133, so that oil energy storage is realized.
In addition to the foregoing structure, the hydraulic control mechanism of the present embodiment further includes a check valve 141 positioned as shown in fig. 1.
The present application is not limited to the above-mentioned embodiments, and any changes or substitutions that can be easily understood by those skilled in the art within the technical scope of the present application are intended to be included in the scope of the present application.

Claims (7)

1. The quick erection equipment is characterized by comprising a base part, an erection arm, a hydraulic system and a recoil power device;
the base part is hinged with the first end of the erection arm through a first hinge shaft;
the hydraulic system comprises a hydraulic control mechanism and a hydraulic cylinder;
the recoil power device is arranged on the vertical arm;
when the recoil power device works to generate jet flow, the erection arm rotates around the first hinge shaft in a first direction, and the hydraulic cylinder stretches; in the extending process of the hydraulic cylinder, the hydraulic control mechanism injects oil into a first oil cavity of the hydraulic cylinder, so that the first oil cavity is always in a state of completely filling the oil; the recoil power device is only used in the initial stage of erecting the erecting arm, and the hydraulic cylinder is in a passive elongation state in the working process of the recoil power device; after the erection arm reaches a set state, stopping working of the recoil power device, and continuously controlling the erection arm by utilizing a hydraulic system until the erection arm is erected to a set angle;
the first oil cavity is a rodless cavity, and a cylinder barrel of the hydraulic cylinder is hinged with the vertical arm through a second hinge shaft; the recoil power device is arranged on one side, away from the first hinge shaft, relative to the second hinge shaft;
the hydraulic control mechanism comprises a hydraulic pump, an energy storage oil tank, a first two-way valve and a second two-way valve; one port of the first two-way valve is communicated with an oil outlet of the hydraulic pump, and the other port of the first two-way valve is communicated with the first oil cavity; one port of the second two-way valve is communicated with the energy storage oil tank, and the other port of the second two-way valve is communicated with the first oil cavity;
and setting a speed sensor for detecting the erection speed of the erection arm and an angle sensor for detecting the erection angle, determining the volume change rate of the first oil cavity by using the speed sensor and the angle sensor, closing the second two-way valve when the volume change rate of the first oil cavity is reduced to the idle unit pumping capacity of the hydraulic pump, and pumping hydraulic oil to the first oil cavity by using the hydraulic pump only by adjusting the first two-way valve.
2. The quick erection device of claim 1, wherein:
the jet flow of the recoil power device is perpendicular to the extending direction of the erection arm.
3. Quick erection device according to any of claims 1-2, characterized in that:
the recoil power device is a gas power device, a blade pushing device or a high-pressure back pushing device.
4. The quick erection device of claim 1, wherein:
the first two-way valve is a proportional valve; the hydraulic control mechanism further comprises a proportional overflow valve; and an oil inlet of the proportional overflow valve is communicated with an oil outlet of the hydraulic pump.
5. The quick erection device of claim 1, wherein:
the hydraulic cylinder is a double-acting hydraulic cylinder; the hydraulic cylinder further comprises a second oil cavity; the second oil cavity is a rod cavity;
the hydraulic control mechanism further comprises a third two-way valve; the third two-way valve is a proportional valve; and one port of the third two-way valve is communicated with the second oil cavity.
6. The quick erection device of claim 5, wherein:
the hydraulic control mechanism also comprises a three-position four-way valve; the oil supply port of the three-position four-way valve is communicated with the oil outlet of the hydraulic pump; one oil outlet of the three-position four-way valve is communicated with one port of the first two-way valve, and the other oil outlet of the three-position four-way valve is communicated with one port of the third two-way valve.
7. The quick erection device of claim 1, wherein:
the hydraulic control mechanism further comprises a fourth two-way valve; the fourth two-way valve is arranged between the hydraulic pump and the energy storage oil tank.
CN202010359012.9A 2020-04-29 2020-04-29 Quick erection equipment Active CN113565837B (en)

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CN102933932A (en) * 2010-02-11 2013-02-13 霍华德·M·钦 Rocket launch system and supporting apparatus
CN106742025A (en) * 2016-12-20 2017-05-31 陈君恒 A kind of large power shaft is to superpower trust engine, the supersonic ejection device using the engine and ejection control method
CN107701529A (en) * 2017-09-15 2018-02-16 湖北航天技术研究院总体设计所 A kind of multi-cylinder has cooperateed with perpendicular hydraulic system
CN110255460A (en) * 2019-07-07 2019-09-20 中科聚信洁能热锻装备研发股份有限公司 A kind of fluid power system and its control method of weight roll-over table
CN110905872A (en) * 2019-11-15 2020-03-24 湖北航天技术研究院总体设计所 Double-cylinder linkage hydraulic circuit based on control over energy accumulator

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GB2531683B (en) * 2016-02-12 2018-03-28 Robonic Ltd Oy Arrangement in catapult

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102933932A (en) * 2010-02-11 2013-02-13 霍华德·M·钦 Rocket launch system and supporting apparatus
CN106742025A (en) * 2016-12-20 2017-05-31 陈君恒 A kind of large power shaft is to superpower trust engine, the supersonic ejection device using the engine and ejection control method
CN107701529A (en) * 2017-09-15 2018-02-16 湖北航天技术研究院总体设计所 A kind of multi-cylinder has cooperateed with perpendicular hydraulic system
CN110255460A (en) * 2019-07-07 2019-09-20 中科聚信洁能热锻装备研发股份有限公司 A kind of fluid power system and its control method of weight roll-over table
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