CN114135537B - Oil cylinder assembly and high-altitude operation machine - Google Patents
Oil cylinder assembly and high-altitude operation machine Download PDFInfo
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- CN114135537B CN114135537B CN202111196390.0A CN202111196390A CN114135537B CN 114135537 B CN114135537 B CN 114135537B CN 202111196390 A CN202111196390 A CN 202111196390A CN 114135537 B CN114135537 B CN 114135537B
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- 230000007246 mechanism Effects 0.000 claims abstract description 50
- 238000005086 pumping Methods 0.000 claims description 12
- 230000004323 axial length Effects 0.000 claims description 11
- 230000002093 peripheral effect Effects 0.000 claims description 11
- 238000007906 compression Methods 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 10
- 230000006835 compression Effects 0.000 claims description 9
- 230000001133 acceleration Effects 0.000 claims description 6
- 238000004891 communication Methods 0.000 claims description 6
- 238000003780 insertion Methods 0.000 claims description 5
- 230000037431 insertion Effects 0.000 claims description 5
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 238000003825 pressing Methods 0.000 claims description 3
- 230000002265 prevention Effects 0.000 claims description 2
- 239000003921 oil Substances 0.000 claims 48
- 239000010720 hydraulic oil Substances 0.000 claims 1
- 238000001514 detection method Methods 0.000 abstract description 3
- 230000009471 action Effects 0.000 description 19
- 230000036316 preload Effects 0.000 description 5
- 239000000463 material Substances 0.000 description 4
- 238000011160 research Methods 0.000 description 4
- 230000006978 adaptation Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000036632 reaction speed Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Classifications
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- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
-
- 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
- B66C23/72—Counterweights or supports for balancing lifting couples
- B66C23/78—Supports, e.g. outriggers, for mobile cranes
- B66C23/80—Supports, e.g. outriggers, for mobile cranes hydraulically actuated
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F17/00—Safety devices, e.g. for limiting or indicating lifting force
- B66F17/006—Safety devices, e.g. for limiting or indicating lifting force for working platforms
-
- 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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
-
- 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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/007—Overload
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Structural Engineering (AREA)
- Actuator (AREA)
- Forklifts And Lifting Vehicles (AREA)
Abstract
The invention discloses an oil cylinder assembly and an overhead working machine, wherein the oil cylinder assembly comprises a main oil cylinder provided with a main oil cylinder barrel (1) and a main oil cylinder piston rod (2), an oil cylinder sleeve and a safety pin device, the oil cylinder sleeve is sleeved outside the main oil cylinder and comprises an outer sleeve (3) and an inner sleeve (4) which are telescopic and nested, the outer sleeve is fixedly connected with the main oil cylinder barrel, the inner sleeve is fixedly connected with the main oil cylinder piston rod and synchronously stretches, and a brake pin hole is penetrated and arranged on the circumferential wall of the oil cylinder sleeve; the shear pin device comprises a shear pin (5) and a shear pin driving mechanism (6) for driving the shear pin to be inserted into or separated from the brake pin hole. The hydraulic system is combined with a special mechanical structure in the overhead working machine, so that the vertical leg soft leg protection function of the equipment is realized, the equipment not only has the function realized by a leg soft leg detection scheme, but also has more substantial and reliable anti-tipping protection capability and realizes the control interlocking of getting on and off in a simpler mode.
Description
Technical Field
The invention belongs to the field of engineering machinery, and particularly relates to an overhead working machine and an oil cylinder assembly.
Background
The basic operation requirement of the high-altitude operation machine is to keep the vehicle body horizontal and execute all operation actions on the premise; the stable posture is maintained during operation, and the arm support mechanism and the supporting leg mechanism which are closely related to the maintenance of the operation posture and the operation safety are required to have enough self-locking or self-protecting functions. Therefore, the ability of the self-protecting device of the leg mechanism in relation to maintaining the vehicle body level has an extremely important role in securing work safety for the working aloft machine.
In the aspect of self-protection research of the support leg mechanism, a part of research is to detect whether the support leg oil cylinder stretches out or retracts back to a proper position through a travel switch arranged on the support leg so as to judge whether the support leg is correctly supported (namely, soft leg judgment), and after the support leg supporting state is checked by an electric control system, the action of the arm support is correspondingly limited according to the actual safety condition reached by the support leg. Some researches are also conducted by arranging a mechanical locking device for a get-on and get-off control valve group to realize the interlocking of get-on and get-off actions, so that an electric control system automatically cuts off the control of a get-off landing leg when an operator gets on a car (for example, a boom is lifted), and the risk of tilting the car body caused by misoperation of the landing leg by ground irrelevant personnel is prevented.
The researches have common defects, such as the problem that the soft leg of the supporting leg can only be passively detected, the protection measures for the soft leg are insufficient, more electromagnetic valves are required to be arranged in the existing hydraulic type on-off interlocking scheme, complicated machinery and control devices are required to be arranged in mechanical interlocking, and the operation is inconvenient and the cost is relatively high.
Disclosure of Invention
The invention aims to provide an oil cylinder assembly and an overhead working machine, which have stronger oil cylinder soft leg protection function and have more substantial and reliable anti-tipping protection capability.
To achieve the above object, according to a first aspect of the present invention, there is provided a cylinder assembly comprising:
the main oil cylinder comprises a main oil cylinder barrel and a main oil cylinder piston rod;
the cylinder sleeve is sleeved outside the main cylinder and comprises an outer sleeve and an inner sleeve which are telescopically nested, the outer sleeve is fixedly connected with the cylinder barrel of the main cylinder, the inner sleeve is fixedly connected with the piston rod of the main cylinder and synchronously telescopic, and brake pin holes are formed in the circumferential walls of the outer sleeve and the inner sleeve in a penetrating manner; and
the safety pin device comprises a safety pin and a safety pin driving mechanism, wherein the safety pin driving mechanism is used for driving the safety pin to be inserted into or separated from the brake pin hole.
In some embodiments, the brake pin hole comprises an outer sleeve barrel wall pin hole and a plurality of inner sleeve barrel wall pin holes which are sequentially arranged at intervals along the axial direction of the inner sleeve, and the tail end of the safety pin passes through the outer sleeve barrel wall pin hole to be abutted against the barrel peripheral wall of the inner sleeve or inserted into the inner sleeve barrel wall pin hole;
the safety pin is provided with an end guide inclined plane, and when the inner sleeve extends out, the hole wall of the pin hole of the wall of the inner sleeve abuts against the end guide inclined plane to push the safety pin outwards.
In some embodiments, the shear pin drive mechanism is a hydraulic ram and includes a piston rod assembly connected to the shear pin and a preload spring assembly disposed in the rodless chamber for resiliently urging the piston rod assembly.
In some embodiments, the axial length L of each of the inner sleeve barrel wall pin holes is the same, the inner sleeve is retracted by a retraction time t of the axial length L 1 The method meets the following conditions: t is t 1 ＝(2L/g) 1/2 G is the free falling acceleration; the sum of the mass of the piston rod assembly and the shear pin is m, the expansion resistance is f, the spring stiffness of the pre-compression spring assembly is k, the pre-compression amount of the spring is x, and the shear pin is inserted into the pin hole of the cylinder wall of the inner sleeve for a time T beyond the wall thickness T of the cylinder peripheral wall of the inner sleeve 2 The method meets the following conditions: t is t 2 ＝[2mT/(kx-f)] 1/2 The method comprises the steps of carrying out a first treatment on the surface of the Wherein t is 2 ＜t 1 。
In some embodiments, the rod cavity of the shear pin drive mechanism is in communication with the rod cavity of the master cylinder.
In some embodiments, the pin hole axial spacing between pin holes of any adjacent inner sleeve wall is H, and the sum of the pin hole axial spacing H and the axial length L is not greater than an equipment rollover prevention safe operating value.
In some embodiments, the shear pin comprises:
the pin shaft driving end is connected with the safety pin driving mechanism;
the bolt end is used for being inserted into the brake pin hole; and
and the pin shaft hinge point is positioned between the safety pin driving end and the pin end of the safety pin and is used for hingedly mounting the safety pin on the cylinder peripheral wall of the outer sleeve.
In some embodiments, the cylinder end of the shear pin drive mechanism is mounted on the cylinder peripheral wall of the outer sleeve and the piston rod end is pivotally connected to the pin drive end.
According to another aspect of the present invention there is also provided an overhead working machine, at least part of the vertical leg ram of which is a ram assembly according to the present invention as described above.
In some embodiments, the hydraulic system of the aerial work machine comprises:
a main pump for pumping system pressure oil to the hydraulic system through a pumping oil path;
the arm support control system comprises an arm support control valve;
the landing leg control system comprises a landing leg control valve; and
and the oil supply reversing valve is arranged in the pumping oil way and is used for alternatively switching and supplying the pumped system pressure oil to the arm support control valve or the landing leg control valve.
In some embodiments, the oil supply reversing valve is provided with a main oil return port, a main oil inlet connected with the main pump, a support oil supply port connected with the support control valve, and the oil supply reversing valve is an electromagnetic reversing valve and comprises a first electromagnet for controlling switching to a first switching position and a second electromagnet for controlling switching to a second switching position, the main oil inlet is communicated with the support oil supply port and the support oil supply port is communicated with the main oil return port, and the main oil inlet is communicated with the support oil supply port and the support oil supply port is communicated with the main oil return port.
In some embodiments, the oil supply reversing valve further includes an intermediate cutoff position that causes the main oil inlet to communicate with the main oil return port and the leg oil supply port and the boom oil supply port to both cutoff.
In some embodiments, the electronic control system of the aerial work machine is configured to cause the coil of the first electromagnet to remain de-energized when the coil of the second electromagnet is energized.
In some embodiments, the landing leg control valve comprises a motion direction reversing valve, an oil inlet of the motion direction reversing valve is connected with the landing leg oil supply port of the oil supply reversing valve, a first working port of the motion direction reversing valve is connected with a landing leg oil cylinder rodless cavity oil way, a second working port of the motion direction reversing valve is connected with a landing leg oil cylinder rodless cavity oil way, the respective rodless cavities of a vertical landing leg oil cylinder and a horizontal landing leg oil cylinder of the overhead working machine are connected with the landing leg oil cylinder rodless cavity oil way, and the respective rodless cavities of the vertical landing leg oil cylinder and the horizontal landing leg oil cylinder are connected with the landing leg oil cylinder rodless cavity oil way.
In some embodiments, the overhead working machine comprises a plurality of groups of support leg oil cylinders, each group of support leg oil cylinders comprises a vertical support leg oil cylinder and a horizontal support leg oil cylinder, a plurality of oil cylinder switching valves which are arranged in a one-to-one correspondence with the plurality of groups of support leg oil cylinders are arranged in a support leg oil cylinder rodless cavity oil circuit, and the oil cylinder switching valves are used for communicating rodless cavities of the vertical support leg oil cylinders or the horizontal support leg oil cylinders in the corresponding groups of support leg oil cylinders with the support leg oil cylinder rodless cavity oil circuit.
In some embodiments, in each group of the leg cylinders, the rodless cavity of the horizontal leg cylinder is connected with the corresponding working oil port of the cylinder switching valve through a horizontal leg cylinder rodless cavity oil path, and the horizontal leg cylinder rodless cavity oil path is connected with an oil return oil path through a low-pressure overflow valve.
In some embodiments, the horizontal leg cylinder is provided with a hydraulic lock.
In some embodiments, the shear pin driving mechanism is a hydraulic cylinder and a rod cavity is in oil communication with the leg cylinder rod cavity oil passage, and the rod cavity of the shear pin driving mechanism is connected with an oil return oil passage through a throttle valve.
In the oil cylinder assembly and the overhead working machine, the oil cylinder sleeve and the safety pin device are additionally arranged outside the main oil cylinder, and when the soft leg of the piston rod of the main oil cylinder is retracted, the safety pin device can be timely inserted into the brake pin hole of the oil cylinder sleeve, so that the piston rod of the main oil cylinder is prevented from being retracted continuously, and the protection function of the soft leg of the oil cylinder is realized. The hydraulic system of the high-altitude operation machine adopts a mechanical and hydraulic combination mode of an oil supply reversing valve and an oil cylinder assembly, so that the equipment has more substantial and more reliable anti-tipping protection capability.
Additional features and advantages of the invention will be set forth in the detailed description which follows.
Drawings
The accompanying drawings are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate the invention and together with the description serve to explain, without limitation, the invention. In the drawings:
FIG. 1 is a schematic view of a cylinder assembly according to one embodiment of the present invention, wherein a shear pin is in a state of not being fully inserted into a brake pin hole;
FIG. 2 is an enlarged view of a portion of the dashed circle in FIG. 1;
FIG. 3 is a schematic view of the shear pin device used in FIG. 1;
FIG. 4 illustrates the shear pin of the cylinder assembly of FIG. 1 in a fully inserted condition into the brake pin bore;
FIG. 5 is a schematic view of a cylinder assembly according to another embodiment of the present invention;
FIG. 6 is a schematic diagram of a hydraulic system of an aerial work machine according to an embodiment of the present invention;
fig. 7 shows the internal structure of the leg control valve in fig. 6 in a partially enlarged manner.
Description of the reference numerals
100. Main pump 200 landing leg control valve
300. Oil supply reversing valve of arm support control valve 400
500. Vertical leg cylinder 600 horizontal leg cylinder
700. Telescopic cylinder of luffing cylinder 800
900. Rotary table rotary motor
201. Oil cylinder switching valve of action direction reversing valve 202
203. Hydraulic lock 204 low pressure overflow valve
205. Throttle valve
1. Master cylinder barrel 2 master cylinder piston rod
3. Outer sleeve 4 inner sleeve
5. Safety pin 6 safety pin driving mechanism
7. Outer sleeve barrel wall pin hole 8 inner sleeve barrel wall pin hole
51. End guiding inclined plane of pin hinge point 52
53. Bolt end 61 piston rod assembly
62. Pre-compression spring assembly
P0 main oil inlet T0 main oil return port
C1 Oil supply port of support leg oil supply port C2 arm support oil supply port
a first electromagnet b second electromagnet
D1 A first working oil port D2 and a second working oil port
P1 pumping oil way T1 oil return oil way
Rodless cavity oil way of L1 supporting leg oil cylinder and rod cavity oil way of L2 supporting leg oil cylinder
Rodless cavity oil way of L11 vertical leg oil cylinder and rodless cavity oil way of L12 horizontal leg oil cylinder
Detailed Description
Specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for purposes of illustration and explanation only and are not intended to limit the present invention.
The cylinder assembly and the working aloft machine according to the present invention will be described below with reference to the accompanying drawings.
In the overhead working machine, the phenomenon of soft legs of the supporting legs can be generated under the condition that the oil cylinder or the oil cylinder valve is leaked, the prior art can only passively detect whether the vertical supporting legs are soft, the operation range of the arm support is limited and larger when the supporting legs are soft, even the operation can not be performed, and the safety and the use efficiency of the equipment are greatly influenced. In particular, once the vertical leg is soft during operation, the prior art has difficulty in preventing the vertical leg from retracting by an effective means, and in this case, the vehicle cannot be prevented from overturning, and the life safety of operators or operators and the safety of the vehicle cannot be effectively protected.
In view of the above, the present invention provides a novel cylinder assembly. As shown in fig. 1 to 4, in one embodiment, the cylinder assembly includes:
the main oil cylinder comprises a main oil cylinder barrel 1 and a main oil cylinder piston rod 2;
the cylinder sleeve is sleeved outside the main cylinder and comprises an outer sleeve 3 and an inner sleeve 4 which are telescopically nested, the outer sleeve 3 is fixedly connected with the main cylinder barrel 1, the inner sleeve 4 is fixedly connected with the main cylinder piston rod 2 and synchronously telescopic, and brake pin holes are formed in the circumferential walls of the outer sleeve 3 and the inner sleeve 4 in a penetrating manner; and
the safety pin device comprises a safety pin 5 and a safety pin driving mechanism 6, wherein the safety pin driving mechanism 6 is used for driving the safety pin 5 to be inserted into or separated from a brake pin hole.
Therefore, in the oil cylinder assembly, the inner sleeve and the outer sleeve which are respectively synchronous with the piston rod and the cylinder barrel of the main oil cylinder are additionally arranged, and the safety pin device is additionally arranged so as to timely lock the relative axial sliding between the inner sleeve and the outer sleeve, thereby correspondingly locking the extension or retraction of the main oil cylinder. Therefore, once the main oil cylinder is soft in legs, the inner sleeve and the outer sleeve can be locked through the safety pin device to achieve the purpose of locking the main oil cylinder, so that the leg oil cylinder is effectively prevented from retracting.
The master cylinder may be any type of cylinder, but is particularly suitable for use as a vertical leg cylinder for a leg system. In this way, the safety pin device can be driven to perform locking action by passively detecting whether the leg is soft or not so as to lock the master cylinder. It should be noted that, when the hydraulic cylinder assembly is used as the leg system, the shear pin driving mechanism 6 is generally hydraulically driven, pneumatically driven or electrically controlled, and the shear pin driving mechanism 6 in the following embodiments is a hydraulic cylinder, which is more convenient for integrated hydraulic control, but is not limited thereto. In the embodiment shown in fig. 1, the master cylinder rod 2, the outer sleeve 3 and the inner sleeve 4 are arranged coaxially, the outer sleeve 3 is connected to the master cylinder 1 by means of a transverse pin at the axial end, and the inner sleeve 4 is integrally fixedly connected to the master cylinder rod 2 at the extension end. Likewise, the connection manner, arrangement manner, etc. of the inner and outer sleeves and the master cylinder are not limited thereto.
Further, after the inner and outer sleeves and the safety pin device are added, in order to realize the active detection of the soft leg adaptation phenomenon and to enable active countermeasures, in the embodiments shown in fig. 1 and 2, a mechanical optimization design is performed on the pin structure. Specifically, the brake pin hole includes an outer sleeve barrel wall pin hole 7 and a plurality of inner sleeve barrel wall pin holes 8 sequentially spaced apart in the axial direction of the inner sleeve 4, so that the shear pin 5 can be inserted into the nearest inner sleeve barrel wall pin hole 8 as soon as the cylinder piston rod 2 is retracted. In order to complete the insertion of the pin holes as soon as possible, see fig. 2, in the unlocked state the safety pin may be pre-placed in a state of not being fully inserted into the brake pin holes, i.e. the end of the safety pin 5 is passed through the outer sleeve wall pin hole 7 and is abutted against the wall of the inner sleeve 4, so that it can be inserted into the inner sleeve wall pin hole 8 as soon as possible when the cylinder piston rod 2 is retracted, as shown in fig. 4.
As shown in fig. 3, the shear pin driving mechanism 6 takes the form of a hydraulic cylinder and includes a piston rod assembly 61 connected to the shear pin 5 and a preload spring assembly 62 provided in the rodless chamber for elastically pushing out the piston rod assembly 61. The safety pin 5 is elastically pre-stressed by the pre-stressed spring assembly 62 so as to be half-inserted into the brake pin hole (i.e. retained in the outer sleeve barrel wall pin hole 7), elastically pressed against the barrel peripheral wall of the inner sleeve 4, and then the camera is fully inserted into the brake pin hole.
The kingpin device does not interfere with the extension of the piston rod of the master cylinder. For this purpose, as shown in fig. 2 to 5, the safety pin 5 is formed with an end guide slope 52, and when the inner sleeve 4 is extended, the hole wall of the inner sleeve wall pin hole 8 presses against the end guide slope 52 to push the safety pin 5 outwards. The cylinder rod 2 in each figure extends downwards, so that the end guide inclined surface 52 of the safety pin 5 is suitably designed as an inclined downward top surface at the end of the pin shaft.
Referring to fig. 1 and 2, a plurality of inner sleeve barrel wall pin holes 8 are sequentially arranged at equal intervals along the axial direction of the inner sleeve 4, wherein the axial length L of each inner sleeve barrel wall pin hole 8 is the same, the pin hole axial distance between any adjacent inner sleeve barrel wall pin holes 8 is H, and the wall thickness of the barrel peripheral wall of the inner sleeve 4 is T. It should be noted that the sum of the pin bore axial spacing H and the axial length L is not greater than the equipment anti-roll safe operating value, i.e., the corresponding allowable leg retraction length. Specifically, the anti-tipping safety allowable value of the equipment, the safety pin, the supporting leg materials and the like can be determined according to the national standard, the industry standard and the like.
Neglecting the friction of the landing leg, considering the retraction of the cylinder piston rod 2 as free-falling body movement (the actual landing leg retraction acceleration is lower than the free-falling body acceleration due to the factors such as friction, fluid resistance and the like), the free-falling body acceleration value g=10m/s 2 According to the displacement calculation formula l=gt 2 /2, the retraction time t of the inner sleeve 4 by the retraction axial length L 1 The method meets the following conditions: t is t 1 ＝(2L/g) 1/2 。
The mass of the piston rod assembly 61 is m and the expansion resistance is F, the spring rate of the pre-compression spring assembly 62 is k and the pre-compression amount of the spring is x, and the elastic pre-compression force f=kx applied by the pre-compression spring assembly 62 to the shear pin 5; piston rod assembly 61 and shear pin5 and the expansion resistance is f (which can be determined by actual measurement), the acceleration of the movement of the piston rod assembly 61 and the shear pin 5 is: a= (F-F)/m= (kx-F)/m; thus, the shear pin 5 is inserted into the inner sleeve barrel wall pin hole 8 over the wall thickness T of the barrel peripheral wall of the inner sleeve 4 for a time T 2 The method meets the following conditions: t is t 2 ＝(2T/a) 1/2 ＝[2mT/(kx-f)] 1/2 。
Therefore, in order to ensure reliable locking of the master cylinder and to take into account the shear pin 5, the strength of the cylinder material, the shear pin 5 needs to extend a certain length into the brake pin bore. The correct insertion of the shear pin 5 into the brake pin hole in time requires two points, namely, the size of the brake pin hole is larger than the cross-sectional size of the shear pin 5, and the setting of various relevant parameters (including spring stiffness k, mass sum m of the piston rod assembly 61 and the shear pin 5, spring precompression x and axial length L of the pin hole) requires ensuring that the aforementioned insertion time of the shear pin is smaller than the retraction time of the inner sleeve 4 by the axial length L, i.e., t 2 ＜t 1 。
When the safety pin driving mechanism 6 and the main oil cylinder are driven by hydraulic pressure, the rod cavity of the safety pin driving mechanism 6 can be communicated with the rod cavity of the main oil cylinder. Thus, when the cylinder piston rod 2 of the master cylinder extends, since the end guide inclined surface 52 is formed on the safety pin 5, the hole wall of the inner sleeve wall pin hole 8 on the inner sleeve 4 extending synchronously with the cylinder piston rod 2 can press the end guide inclined surface 52 to push the safety pin 5 outwards, so that the extension of the cylinder piston rod 2 is not hindered. And when the cylinder piston rod 2 of the main cylinder stretches out, the rod cavity of the main cylinder and the rod cavity of the safety pin driving mechanism 6 can return oil. When high-pressure oil is introduced into the rod cavity of the main oil cylinder and the rod cavity of the safety pin driving mechanism 6, the piston rod assembly 61 of the safety pin driving mechanism 6 is driven to retract and compress the pre-compression spring assembly 62 when the oil cylinder piston rod 2 of the main oil cylinder is driven to retract, the safety pin 5 is driven to retract actively, and the safety pin device does not prevent the oil cylinder piston rod 2 of the main oil cylinder from retracting actively. When the cylinder piston rod 2 of the main cylinder is retracted passively, the rod cavity of the main cylinder and the rod cavity of the safety pin driving mechanism 6 are both low-pressure oil and are connected with an oil return oil way, and the safety pin 5 is not prevented from being pushed out under the action of the elastic force of the pre-pressing spring assembly 62 of the safety pin driving mechanism 6 at the moment so as to lock the cylinder assembly.
In the embodiment of fig. 1 to 4, the shear pin device is arranged transversely, i.e. the shear pin 5 is inserted radially into the sleeve cylinder. In another embodiment shown in fig. 5, a lever type shear pin is used, and the shear pin operation speed can be improved to some extent.
Referring to fig. 5, the shear pin 5 includes:
the pin shaft driving end is connected with the safety pin driving mechanism 6;
a latch end 53 for insertion into a brake pin hole; and
a pin hinge point 51 located between the drive end of the shear pin on the shear pin 5 and the spigot end 53 and used to hinge the shear pin 5 to the barrel peripheral wall of the outer sleeve 3.
The safety pin 5 is a long lever, the end part is a bolt end 53 inserted into the brake pin hole, the end part guiding inclined plane 52 is formed on the bolt end 53, and the middle part of the safety pin 5 can be hinged on the cylinder circumference wall of the outer sleeve 3. Thus, by the lever principle, the smaller driving force of the shear pin driving mechanism 6 can drive the plug end 53 of the shear pin 5 to move, and the moving distance can be enlarged, thereby improving the reaction speed.
In fig. 5, as an example, the cylinder end of the shear pin driving mechanism 6 is mounted on the cylinder peripheral wall of the outer sleeve 3 and the rod end is pivotally connected to the driving end of the pin shaft. Thus, the safety pin device is integrally assembled with the main oil cylinder and the oil cylinder sleeve to form the oil cylinder assembly with more compact structure and discrete parts.
On the basis of the oil cylinder assembly, the invention also discloses an overhead working machine, wherein at least part of the vertical support oil cylinder 500 of the overhead working machine is the oil cylinder assembly. In other words, the oil cylinder assembly with the locking function can be used as a vertical leg oil cylinder, so that the locking action can be timely performed when the soft leg phenomenon occurs, and the safety and the reliability of the aerial working machine are improved.
As shown in fig. 6 and 7, the hydraulic system of the working-altitude machine includes, as an example:
a main pump 100 for pumping system pressure oil to the hydraulic system through a pumping oil path P1;
the arm support control system comprises an arm support control valve 300;
a leg control system including a leg control valve 200; and
the oil supply switching valve 400 is provided in the pumping oil path P1 and is used to switch the supply of the pumped system pressure oil to the boom control valve 300 or the leg control valve 200 alternatively.
To achieve the getting-on and getting-off motion interlock, the hydraulic system of the overhead working truck of the present invention is provided with an oil supply reversing valve 400 in the pumping oil path P1 to switch and guide the system pressure oil to get on or off. Thus, when the operator performs the get-on operation, as in fig. 6, when the luffing cylinder 700, the telescopic cylinder 800 or the turntable rotation motor 900 is controlled to operate, the system pressure oil is led to the boom control system through the oil supply reversing valve 400, so that the pressure oil supply to the landing leg control system of the get-off is automatically cut off, and the risk of the vehicle body tilting and the like caused by misoperation of landing legs by ground irrelevant personnel are prevented. In comparison, in the current hydraulic type on-off interlocking scheme, more electromagnetic valves are required to be arranged, or mechanical interlocking is adopted, so that complicated mechanical and control devices are required to be arranged, and the cost is relatively high and the method is not simple.
In fig. 6 and 7, the oil supply switching valve 400 is a three-position four-way switching valve by way of example, but is not limited thereto. The oil supply reversing valve 400 is provided with a main oil return port T0, a main oil inlet P0 connected with the main pump 100, a support leg oil supply port C1 connected with the support leg control valve 200 and a support arm oil supply port C2 connected with the support arm control valve 300; the oil supply reversing valve 400 is an electromagnetic reversing valve and includes a first electromagnet a for controlling switching to a first switching position where the main oil inlet P0 is communicated with the leg oil supply port C1 and the boom oil supply port C2 is communicated with the main oil return port T0, and a second electromagnet b for controlling switching to a second switching position where the main oil inlet P0 is communicated with the boom oil supply port C2 and the leg oil supply port C1 is communicated with the main oil return port T0.
In this way, the electrical control system of the aerial work machine may be arranged to cause the coils of the first electromagnet a to remain de-energized when the coils of the second electromagnet b are energized. That is, when the support leg is normally opened and correctly supported, and the electric control system receives a signal that the support leg travel switch transmits and works normally, if the arm support is operated, the electric control system makes the coil of the second electromagnet b of the oil supply reversing valve 400 be powered on, the main pump 100 outputs oil to the arm support control valve 300 of the getting-on vehicle, and the oil inlet path and the oil return path T1 of the support leg control valve 200 are communicated. When the arm support is in a working position, the electric control system only allows the coil of the second electromagnet b to be electrified, and in the working state of the arm support, the coil of the first electromagnet a cannot be electrified at any time, so that the phenomenon that the landing leg of a vehicle gets off to malfunction and overturn is prevented.
When the electric control system judges that the arm support is at the storage position, the landing leg is allowed to act, and at the moment, if the landing leg is operated, the electric control system enables the first electromagnet a of the oil supply reversing valve 400 to be powered on, the main pump 100 outputs oil to the landing leg control system, an oil inlet oil way of the arm support control valve 300 is communicated with an oil return oil way, the arm support control valve 300 does not input oil, and the phenomenon that the amplitude of the arm support acts beyond the limit under the condition that the landing leg is opened and supported correctly is prevented from tipping is avoided.
In particular, the oil supply reversing valve 400 further includes an intermediate cutoff position that allows the main oil inlet P0 to communicate with the main oil return port T0 and cuts off both the leg oil supply port C1 and the boom oil supply port C2, as shown in fig. 7. In the oil supply reversing valve 40 with the M-shaped unloading function, when the equipment is in standby, a hydraulic system is unloaded through the middle stop position of the oil supply reversing valve 400, and system pressure oil output by the main pump 100 flows back to an oil tank through the pumping oil path P1 and the oil supply reversing valve 400.
The oil supply reversing valve 400 may be present alone or may be integrated into the leg control valve 200. The overhead working machine typically includes multiple sets of leg cylinders, such as the 4 sets shown in fig. 6, each set including a vertical leg cylinder 500 and a horizontal leg cylinder 600.
The leg control valve 200 includes an action direction switching valve 201 for controlling the extension or retraction of the respective leg cylinders. In fig. 6 and 7, an oil inlet of the motion direction reversing valve 201 is connected to a leg oil supply port C1 of the oil supply reversing valve 400, a first working port D1 of the motion direction reversing valve 201 is connected to a leg cylinder rod-less cavity oil path L1, a second working port D2 of the motion direction reversing valve 201 is connected to a leg cylinder rod-less cavity oil path L2, rod-less cavities of the vertical leg cylinder 500 and the horizontal leg cylinder 600 of the overhead working machine are both connected to a leg cylinder rod-less cavity oil path L1, and rod cavities of the vertical leg cylinder 500 and the horizontal leg cylinder 600 are both connected to a leg cylinder rod-less cavity oil path L2.
Further, a plurality of cylinder switching valves 202 are arranged in the rodless cavity oil way L1 of the supporting leg cylinders in a one-to-one correspondence with the plurality of groups of supporting leg cylinders, and the cylinder switching valves 202 are used for communicating rodless cavities of the vertical supporting leg cylinders 500 or the horizontal supporting leg cylinders 600 in the corresponding groups of supporting leg cylinders with the rodless cavity oil way L1 of the supporting leg cylinders. In other words, the cylinder switching valve 202 is used to selectively connect the leg cylinder rodless cavity oil path L1 to the rod cavity of the vertical leg cylinder 500 or the rod cavity of the horizontal leg cylinder 600, that is, the leg cylinder rodless cavity oil path L1 is alternatively guided to the rodless cavity of the vertical leg cylinder 500 through the vertical leg cylinder rodless cavity oil path L11 or to the rodless cavity of the horizontal leg cylinder 600 through the horizontal leg cylinder rodless cavity oil path L12 by the cylinder switching valve 202.
The vertical leg ram 500 shown in fig. 6 employs a ram assembly with a shear pin arrangement. When the shear pin device is hydraulically driven, as shown in fig. 6, the rod chamber of the shear pin driving mechanism 6 is communicated with the rod chamber oil path L2 of the leg cylinder, and the rod chamber of the shear pin driving mechanism 6 is connected to the oil return oil path T1 through the throttle valve 205. The rodless cavity of the shear pin drive mechanism 6 also returns oil directly.
The following takes the vertical leg cylinder 500 shown in fig. 6 as an example, and the other vertical leg cylinders operate in a similar manner. When the vertical leg oil cylinder 500 needs to be controlled to extend, the action direction reversing valve 201 in the leg control valve 200 is switched to guide system pressure oil to the rodless cavity oil path L1 of the leg oil cylinder provided with the oil cylinder switching valve 202, then the vertical leg oil cylinder 500 is selected through the oil cylinder switching valve 202, and the pressure oil is guided to the rodless cavity of the vertical leg oil cylinder 500 through the rodless cavity oil path L11 of the vertical leg oil cylinder to push out a piston rod, so that the extending of the vertical leg oil cylinder 500 is realized. At this time, the system pressure oil enters the rodless cavity of the vertical leg cylinder 500 through the oil supply reversing valve 400, the action direction reversing valve 201, the cylinder switching valve 202 and the hydraulic lock 203, the vertical leg cylinder 500 extends, and the oil in the rod cavity of the vertical leg cylinder 500 flows to the oil return oil path T1 through the leg cylinder rod cavity oil path L2 and the action direction reversing valve 201.
At this time, referring to fig. 1 and 2, the inner sleeve 4 in the vertical leg cylinder 500 moves downward along the end guide slope 52 of the shear pin 5, the shear pin 5 moves leftward, and the piston rod assembly 61 of the shear pin driving mechanism 6 compresses the preload spring assembly 62 under the pushing of the shear pin 5. Meanwhile, the oil in the rod cavity of the vertical support leg oil cylinder 500 returns, part of the oil enters the rod cavity of the safety pin driving mechanism 6 under the back pressure action of the return oil path T1, a small amount of the oil flows back to the oil tank through the throttle valve 205, and most of the oil flows back to the oil tank through the rod cavity oil path L2 of the support leg oil cylinder and the action direction reversing valve 201. The oil in the rodless cavity of the safety pin driving mechanism 6 flows back to the oil tank through the oil return pipe.
When the upper arm support of the high-altitude operation machine is in a working state, the vertical support leg extends out, at the moment, the electronic control system locks the lower operation, the oil supply reversing valve 400 can only be switched between the middle stop position and the a position, the hydraulic system does not supply oil to the support leg control system, and the vertical support leg oil cylinder 500 is kept pressure and locked under the locking action of the hydraulic lock 203, and can not extend out or retract.
If the hydraulic lock 203 or the vertical leg cylinder 11 has unexpected faults such as internal leakage, rupture and the like, the leg cannot be kept supported, and the vertical leg retracts under the dead weight of the equipment. At this time, the safety pin driving mechanism 6 pushes the piston rod assembly 61 and drives the safety pin 5 to be inserted into the pin hole 8 of the inner sleeve wall on the inner sleeve 4 of the vertical support leg under the action of the spring force of the pre-pressing spring assembly 62 in the safety pin driving mechanism, so as to prevent the continuous retraction action of the inner sleeve 4, realize the protection of the soft leg of the oil cylinder of the vertical support leg and prevent the equipment from tipping.
If the vertical leg cylinder needs to be controlled to retract, the cylinder switching valve 202 in the leg control valve 200 is switched to the b position, the system pressure oil flows into the rod cavity of the safety pin driving mechanism 6 and the rod cavity of the vertical leg cylinder 500 simultaneously through the action direction reversing valve 201 and the rod cavity oil path L2 of the leg cylinder, so that the safety pin driving mechanism 6 and the vertical leg cylinder 500 retract, the rodless cavity oil of the safety pin driving mechanism 6 flows back to the oil tank through the oil return pipe, and the rodless cavity oil of the vertical leg cylinder 500 flows back to the oil tank through the hydraulic lock 203, the cylinder switching valve 202 and the action direction reversing valve 201.
Since the preload spring force of the preload spring assembly 62 in the shear pin drive mechanism 6 is much less than the force required for retraction of the vertical leg cylinder 500, the piston rod assembly 61 of the shear pin drive mechanism 6 will retract prior to retraction of the vertical leg cylinder 500, at which time the shear pin 5 of the leg exits the brake pin hole to unlock prior to the vertical leg retraction action, and the vertical leg is free to retract.
In addition, not only the vertical leg cylinder 500 is provided with the hydraulic lock 203, but also the horizontal leg cylinder 600 is provided with the hydraulic lock 203. The rodless cavity of the horizontal leg cylinder 600 is connected with the working oil port of the corresponding cylinder switching valve 202 through the horizontal leg cylinder rodless cavity oil path L12, and the horizontal leg cylinder rodless cavity oil path L12 is connected with the oil return oil path T1 through the low-pressure overflow valve 204, so that the overload bending low-pressure overflow valve of the horizontal leg cylinder can be prevented, and the common system safety valve is avoided.
Specifically, in actual use, even if the middle position of the leg control valve 200 is O-shaped, there is a commonality of internal leakage hydraulic elements, and it cannot be guaranteed that the horizontal leg cylinder 600 can be kept in the retracted position in the walking or transportation state of the device, in order to prevent the accidental collision caused by the extension of the horizontal leg cylinder 600 from damaging the legs, hydraulic locks 203 are also provided on the horizontal leg cylinders, the rod cavity oil of the four horizontal leg cylinders 600 is locked, and the hydraulic locks 203 are opened only when the leg control valve 200 controls the extension of the horizontal leg cylinder 600.
The working force and the required pressure of the horizontal leg cylinder 600 are small, an elongated cylinder is generally adopted for controlling the weight, but the system pressure is generally higher, if the horizontal leg cylinder rodless cavity oil path L12 connected with the horizontal leg cylinder 600 shares a system safety valve, when unexpected obstruction is encountered in the extending process of the horizontal leg, the horizontal leg cylinder 600 can be overloaded and bent, or the leg structural member is deformed, so that the low-pressure overflow valve 204 is arranged on each path of the horizontal leg cylinder rodless cavity oil path L12 as the safety valve. The hydraulic lock 203 and the low-pressure overflow valve 204 are arranged to prevent the landing leg structural member and the oil cylinder from being accidentally damaged, in particular to invisible damage such as microcracks of the landing leg structural member, which is not easy to be perceived, and finally can greatly influence the safety and anti-tipping function of the landing leg of the equipment.
In the invention, a mechanical and hydraulic combination mode is adopted to realize the soft leg protection function of the vertical support leg of the equipment, so that the equipment not only has the function realized by the existing support leg soft leg detection scheme, but also has more substantial and more reliable anti-tipping protection capability; the hydraulic lock is used for preventing the horizontal support leg from being accidentally stretched out to be damaged, and the overflow valve is used for preventing the support leg structural member from being damaged due to accidental blocking when the horizontal support leg stretches out and preventing the horizontal support leg oil cylinder from being overloaded and bent, so that the possibility of equipment tipping caused by support leg damage is reduced. In addition, the three-position four-way electromagnetic reversing valve is adopted in the hydraulic system, and compared with the mode of adopting a plurality of valves in the prior art, the three-position four-way electromagnetic reversing valve has great advantages in the aspects of economy, working reliability and maintainability, and can realize the control interlocking of getting on and off in a simpler mode.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present invention, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.
In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; may be mechanically connected, may be electrically connected or may be in communication with each other; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present invention, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.
While embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the invention, and that variations, modifications, alternatives and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the invention.
Claims (15)
1. The hydro-cylinder subassembly, its characterized in that, the hydro-cylinder subassembly includes:
the main oil cylinder comprises a main oil cylinder barrel (1) and a main oil cylinder piston rod (2);
the oil cylinder sleeve is sleeved outside the main oil cylinder and comprises an outer sleeve (3) and an inner sleeve (4) which are telescopically nested, the outer sleeve (3) is fixedly connected with the main oil cylinder barrel (1), the inner sleeve (4) is fixedly connected with the main oil cylinder piston rod (2) and synchronously telescopic, and brake pin holes are formed in the circumferential walls of the outer sleeve (3) and the inner sleeve (4) in a penetrating manner; and
the safety pin device comprises a safety pin (5) and a safety pin driving mechanism (6), wherein the safety pin driving mechanism (6) is used for driving the safety pin (5) to be inserted into or separated from the brake pin hole;
the brake pin hole comprises an outer sleeve barrel wall pin hole (7) and a plurality of inner sleeve barrel wall pin holes (8) which are sequentially arranged at intervals along the axial direction of the inner sleeve (4), and the tail end of the safety pin (5) passes through the outer sleeve barrel wall pin hole (7) to be abutted against the barrel peripheral wall of the inner sleeve (4) or to be inserted into the inner sleeve barrel wall pin hole (8); an end guide inclined plane (52) is formed on the safety pin (5), and when the inner sleeve (4) stretches out, the hole wall of the pin hole (8) of the wall of the inner sleeve abuts against the end guide inclined plane (52) to push the safety pin (5) outwards;
the safety pin driving mechanism (6) is a hydraulic oil cylinder and comprises a piston rod assembly (61) connected with the safety pin (5) and a pre-pressing spring assembly (62) arranged in a rodless cavity and used for elastically pushing out the piston rod assembly (61); the axial length L of each pin hole (8) of the inner sleeve wall is the same, and the retraction time of the inner sleeve (4) for retracting the axial length Lt 1 The method meets the following conditions: t is t 1 ＝(2L/g) 1/2 G is the free falling acceleration; the sum of the masses of the piston rod assembly (61) and the safety pin (5) is m, the expansion resistance is f, the spring stiffness of the pre-compression spring assembly (62) is k, the pre-compression spring amount is x, and the safety pin (5) is inserted into the pin hole (8) of the cylinder wall of the inner sleeve (4) beyond the wall thickness T of the cylinder wall of the inner sleeve for a time T 2 The method meets the following conditions: t is t 2 ＝[2mT/(kx-f)] 1/2 The method comprises the steps of carrying out a first treatment on the surface of the Wherein t is 2 ＜t 1 。
2. The cylinder assembly according to claim 1, characterized in that the rod cavity of the shear pin driving mechanism (6) is in communication with the rod cavity of the master cylinder.
3. The cylinder assembly according to claim 1, characterized in that the pin hole axial spacing between any adjacent inner sleeve wall pin holes (8) is H, the sum of the pin hole axial spacing H and the axial length L being no greater than an equipment rollover prevention safe operating value.
4. A cylinder assembly according to any one of claims 1 to 3, characterized in that the shear pin (5) comprises:
the pin shaft driving end is connected with the safety pin driving mechanism (6);
a plug pin end (53) for insertion into the brake pin aperture; and
-a pin hinge point (51) located between the drive end of the shear pin (5) and the plug end (53) and adapted to hinge the shear pin (5) to the circumferential wall of the outer sleeve (3).
5. The cylinder assembly according to claim 4, characterized in that the cylinder end of the shear pin driving mechanism (6) is mounted on the cylinder peripheral wall of the outer sleeve (3) and the piston rod end is pivotally connected to the pin driving end.
6. An aerial working machine, characterized in that at least part of the vertical leg ram (500) of the aerial working machine is a ram assembly according to any one of claims 1-5.
7. The aerial work machine of claim 6 wherein the hydraulic system of the aerial work machine comprises:
a main pump (100) for pumping system pressure oil to the hydraulic system through a pumping oil path (P1);
the arm support control system comprises an arm support control valve (300);
a leg control system including a leg control valve (200); and
an oil supply reversing valve (400) provided in the pumping oil path (P1) and configured to alternately switch supply of the pumped system pressure oil to the boom control valve (300) or the leg control valve (200).
8. The aerial working machine according to claim 7, wherein the oil supply reversing valve (400) is provided with a main oil return port (T0), a main oil inlet (P0) connected to the main pump (100), a boom oil supply port (C1) connected to the boom control valve (300), and a boom oil supply port (C2) connected to the boom control valve (300), the oil supply reversing valve (400) being an electromagnetic reversing valve and comprising a first electromagnet (a) for controlling switching to a first switching position in which the main oil inlet (P0) communicates with the boom oil supply port (C1) and the boom oil supply port (C2) communicates with the main oil return port (T0), and a second electromagnet (b) for controlling switching to a second switching position in which the main oil inlet (P0) communicates with the boom oil port (C2) and the boom oil supply port (C1) communicates with the main oil return port (T0).
9. The aerial working machine according to claim 8, wherein the oil supply reversing valve (400) further includes an intermediate cutoff position that causes the main oil inlet (P0) to communicate with the main oil return port (T0) and the leg oil supply port (C1) and the boom oil supply port (C2) to both be cutoff.
10. The aerial work machine of claim 9 wherein the electronic control system of the aerial work machine is configured to cause the coil of the first electromagnet (a) to remain de-energized when the coil of the second electromagnet (b) is energized.
11. The overhead working machine according to any one of claims 8 to 10, wherein the leg control valve (200) comprises a motion direction reversing valve (201), an oil inlet of the motion direction reversing valve (201) is connected with the leg oil supply port (C1) of the oil supply reversing valve (400), a first working port (D1) of the motion direction reversing valve (201) is connected with a leg cylinder rodless cavity oil path (L1), a second working port (D2) of the motion direction reversing valve (201) is connected with a leg cylinder rod cavity oil path (L2), respective rodless cavities of a vertical leg cylinder (500) and a horizontal leg cylinder (600) of the overhead working machine are both connected with the leg cylinder rodless cavity oil path (L1), and respective rod cavities of the vertical leg cylinder (500) and the horizontal leg cylinder (600) are both connected with the leg cylinder rod cavity oil path (L2).
12. The overhead working machine according to claim 11, wherein the overhead working machine comprises a plurality of groups of leg cylinders, each group of the leg cylinders comprises the vertical leg cylinder (500) and the horizontal leg cylinder (600), a plurality of cylinder switching valves (202) which are arranged in a one-to-one correspondence with the plurality of groups of the leg cylinders are arranged in a leg cylinder rodless cavity oil path (L1), and the cylinder switching valves (202) are used for communicating rodless cavities of the vertical leg cylinder (500) or the horizontal leg cylinder (600) in the corresponding group of the leg cylinders with the leg cylinder rodless cavity oil path (L1).
13. The overhead working machine according to claim 12, wherein in each set of the leg cylinders, a rodless chamber of the horizontal leg cylinder (600) is connected to a corresponding working oil port of the cylinder switching valve (202) through a horizontal leg cylinder rodless chamber oil passage (L12), and the horizontal leg cylinder rodless chamber oil passage (L12) is connected to an oil return oil passage (T1) through a low pressure relief valve (204).
14. The aerial working machine according to claim 11, wherein the horizontal leg cylinder (600) is provided with a hydraulic lock (203).
15. The aerial working machine according to claim 11, wherein the shear pin driving mechanism (6) is a hydraulic cylinder and a rod chamber is in communication with the leg cylinder rod chamber oil passage (L2), and the rod chamber of the shear pin driving mechanism (6) is connected to an oil return oil passage (T1) through a throttle valve (205).
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| CN202415033U (en) * | 2011-12-05 | 2012-09-05 | 三一重工股份有限公司 | Locking system for landing leg of engineering machine and engineering machine |
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| CN114135537A (en) | 2022-03-04 |
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