CN212690662U - Safety type liquid-gas spring device applied to ship lift - Google Patents
Safety type liquid-gas spring device applied to ship lift Download PDFInfo
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- CN212690662U CN212690662U CN202020523215.2U CN202020523215U CN212690662U CN 212690662 U CN212690662 U CN 212690662U CN 202020523215 U CN202020523215 U CN 202020523215U CN 212690662 U CN212690662 U CN 212690662U
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Abstract
A safety type hydraulic-pneumatic spring device applied to a ship lift comprises a support, a measuring shaft, a lower flange, a guide shaft sleeve, a self-lubricating bearing, a hydraulic-pneumatic spring oil cylinder, a pull rod, an upper flange, a self-lubricating sliding sleeve, an air bag type energy accumulator and an oil pipe; the lower end of the bracket is fixedly arranged on a ship-bearing chamber structure, and a hinge shaft in the middle of the hydro-pneumatic spring oil cylinder is supported on the bracket through a self-lubricating bearing; the end part of the upper piston rod is connected with the upper flange through threads, the lower end of a lower piston rod of the hydro-pneumatic spring oil cylinder is assembled with a mounting hole of the lower flange in a clearance fit mode through a guide shaft sleeve, and the lower end of the measuring shaft and a bottom beam of the gear bracket mechanism form a hinged structure; the upper end of the pull rod is sleeved in an inner hole of a self-lubricating shaft sleeve with a flange, the top of the pull rod is positioned by a nut, the lower end of the pull rod is hinged with a bottom beam of the gear bracket mechanism, and the air bag type energy accumulator is communicated with the rodless cavity through an oil pipe; the function of stable transition from the pinion and the rack to the rotary screw and nut column of the safety mechanism in the vertical support of the ship chamber is realized, and the safety is improved.
Description
Technical Field
The invention relates to a hydraulic-pneumatic spring device, in particular to a safe hydraulic-pneumatic spring device which is suitable for realizing the transfer of bidirectional accident load of a ship receiving chamber from a gear rack of a driving mechanism to a safety mechanism through the movement of double piston rods and corresponding displacement-load mechanical characteristics when a gear rack climbing type vertical ship lift generates unbalance accidents in the ship receiving chamber.
Background
The vertical ship lift is used as a navigation facility, and is increasingly widely applied to a hydro junction due to the fact that the ship has short dam-crossing time and is suitable for high dam navigation. The gear rack full-balanced type vertical ship lift is applied to a hydraulic junction for large ships to pass through a dam with high safety, such as 3000t gear rack climbing type vertical ship lifts of a three gorges hydraulic junction and 1000t gear rack climbing type vertical ship lifts of a dam hydropower station, the two ship lifts are the first of scales of ship lifts built and built in China at present, and the three gorges ship lift is the largest ship lift in the world at present. The total weight of the design of the ship chamber of the full-balanced vertical ship lift is equal to the total weight of the suspension counterweight, so that the ship bearing chamber is driven to run only by overcoming the loads such as wrong water load, frictional resistance of a pulley bearing, stiff resistance of a steel wire rope, inertia force and the like caused by the depth of water of the ship bearing chamber. The fully-balanced gear tooth body climbing type ship lift is characterized in that the ship receiving chamber adopts a driving mode of meshing an open gear and a rack in the lifting operation, wherein the open gear is arranged on the ship receiving chamber, and the rack is arranged in the operating height of a tower column; meanwhile, a safety mechanism is arranged for providing support for the ship receiving chamber when the ship receiving chamber is unbalanced, so that the ship lift has high safety. The safety mechanism is connected with the driving mechanism through a mechanical shaft transmission system, so that the linear speed of the open gear of the driving mechanism is the same as the lifting speed of the rotating screw of the safety mechanism; however, the open gear of the driving mechanism of the prior art rack and pinion full-balanced vertical ship lift often suffers from the problem that when the ship receiving chamber is unbalanced, the open gear often bears large accident load, so that the gear is damaged.
Disclosure of Invention
The invention aims to solve the problem that an open gear of a driving mechanism of a rack-and-pinion fully-balanced vertical ship lift in the prior art is always subjected to larger accident load when a ship receiving chamber is subjected to unbalance accident, so that the gear is damaged.
The technical scheme adopted by the invention is as follows: a safety type hydraulic-pneumatic spring device applied to a ship lift comprises a support, a measuring shaft, a lower flange, a guide shaft sleeve, a self-lubricating bearing, a hydraulic-pneumatic spring oil cylinder, a pull rod, an upper flange, a self-lubricating sliding sleeve, an air bag type energy accumulator and an oil pipe;
the lower end of the support is fixedly arranged on a ship-carrying chamber structure, the gas spring oil cylinder adopts a double-piston rod type, and a hinge shaft in the middle of the liquid gas spring oil cylinder is supported on the support through a self-lubricating bearing; the end part of an upper piston rod of the hydraulic-pneumatic spring oil cylinder is connected with an upper flange through threads, the lower end of a lower piston rod of the hydraulic-pneumatic spring oil cylinder is assembled with a mounting hole of a lower flange in clearance fit through a guide shaft sleeve, a measuring shaft is fixedly mounted at the lower end of the lower flange, and the lower end of the measuring shaft and a bottom beam of a gear bracket mechanism form a hinged structure; the upper flange and the lower flange are connected through a pull rod, a self-lubricating sliding sleeve with a flange is mounted on an upper flange pull rod mounting hole of the upper flange, the upper end of the pull rod is sleeved in an inner hole of the self-lubricating sliding sleeve with the flange, the top of the pull rod is positioned by a nut, and the lower end of the pull rod is fixed on the lower flange through the nut; the measuring shaft at the bottom is hinged with a bottom beam of a gear bracket mechanism, so that a force transmission system is formed together with a pinion bracket, and unbalanced load of a ship receiving chamber under the lifting working condition of the ship lift is transmitted to a tower column; the air bag type energy accumulator is communicated with a rodless cavity of the hydraulic-pneumatic spring oil cylinder through an oil pipe;
the hydraulic-pneumatic spring oil cylinder is communicated with an air bag type energy accumulator of an external hydraulic pump station, and the pretightening force of the hydraulic-pneumatic spring is determined by the oil pressure of the air bag type energy accumulator and can be adjusted as required; the hydro-pneumatic spring composed of the oil cylinder and the air bag type energy accumulator has the displacement load characteristic of a pre-compressed nonlinear spring: when the gear load is smaller than the pre-tightening load determined by the oil pressure of the air bag type energy accumulator, the pistons at the two ends of the hydro-pneumatic spring oil cylinder are propped against the two ends of the hydro-pneumatic spring oil cylinder body by the oil pressure, and the pistons at the two ends of the hydro-pneumatic spring oil cylinder keep the initial positions, so that the normal bearing and operation of the meshing of the gear and the rack of the driving mechanism are maintained; when the gear load exceeds the pre-tightening load, the oil pressure of the rodless cavity of the double-piston rod hydraulic spring oil cylinder exceeds the initial value, the gas of the gas bag type energy accumulator is compressed to reduce the volume of the gas, and the oil liquid in the rodless cavity enters the gas bag type energy accumulator to enable the pressurized piston of the hydraulic spring oil cylinder to generate axial displacement; the up-and-down movement of a connecting hinge point of the lower part of the measuring shaft and a bottom beam of the pinion bracket and the rotation of the hydro-pneumatic spring oil cylinder around a connecting hinge with a ship bearing chamber are generated, so that the motion of the pinion bracket is initiated, the gap between a rotating screw rod of the safety mechanism and a screw pair of a nut column is reduced until the gap between the screw pair of the safety mechanism disappears, and finally, the geometric contact condition that the safety mechanism bears the unbalanced load of the ship bearing chamber is formed; when the ship receiving chamber of the gear rack climbing ship lift has unbalance accidents, the hinge joint of the measuring shaft (2) positioned at the bottom of the hydro-pneumatic spring and the bottom beam of the pinion bracket moves up and down through the axial movement of the upper piston rod and the lower piston rod of the hydro-pneumatic spring oil cylinder, so that the ship chamber is vertically supported and stably passes through the rotating screw rod and the nut column of the safety mechanism from the pinion and the rack.
Furthermore, the bottom measuring shaft is hinged with the bottom beam of the gear bracket mechanism through a self-aligning rolling bearing assembled in a shaft hole of the lower flange and a hinge hole at the end part of the bottom beam, and is axially positioned through a shaft end baffle and a connecting screw which are installed at the end part of the bottom beam.
Furthermore, the support comprises a bottom plate, a vertical plate and a reinforcing triangular plate, the bottom plate is connected with the ship reception chamber structure through a bottom plate bolt, the vertical plate is vertically arranged on the upper end face of the bottom plate, and two side edges of the reinforcing triangular plate playing a reinforcing role are fixedly arranged on the bottom plate and the vertical plate respectively.
The load transfer method of the safety type hydro-pneumatic spring device applied to the ship lift comprises the following steps:
the method comprises the following steps: setting the stroke of the hydro-pneumatic spring oil cylinder, wherein the stroke of the hydro-pneumatic spring oil cylinder is an important parameter of a hydro-pneumatic spring device, and the stroke of the oil cylinder must ensure that the hydro-pneumatic spring oil cylinder still keeps a certain margin stroke after the thread clearance of the safety mechanism disappears so as to avoid the accident that the safety mechanism cannot provide support because the thread clearance of the safety mechanism does not disappear and the stroke of the oil cylinder is used up; therefore, the thread clearance should consider the larger value as much as possible, namely the larger clearance value when the upper and lower thread clearances are unequal and lean to one side, and simultaneously consider the displacement difference value of the ship receiving chamber structure where the safety mechanism and the driving mechanism are located when the ship receiving chamber has unbalance accidents; the stroke of the hydro-pneumatic spring oil cylinder is calculated according to the following formula:
fs＝2(2dsb+df+dm-5mm)
in the formula, fs is the stroke of the hydro-pneumatic spring oil cylinder; dsbThe theoretical thread clearance (namely the thread clearance value when the upper thread pair clearance and the lower thread pair clearance are equal) of the safety mechanism; dfThe difference value of the displacement of the ship reception chamber structure where the safety mechanism and the driving mechanism are located when the ship reception chamber has unbalance accidents; dmThe margin of the stroke of the oil cylinder is used; in the above formula 2dsb5mm represents the maximum thread clearance on one side due to unbalance of the upper and lower thread pairs for various reasons;
step two: setting initial pressure p after air inflation of air bag type energy accumulator0And an initial volume V0；
Step three: in the actual operation of the ship lift, when the butt joint process of the ship lift receiving chamber and the upper and lower lock heads is finished and the centralized control master station sends a 'ship chamber lifting operation' instruction, an external hydraulic system is started to inject pressure oil into the air bag type energy accumulator to enable the initial pressure of the air bag type energy accumulator to be p0So that the pinion bracket of the driving mechanism forms a supporting structure of the ship reception chamber during the lifting process;
when the hydro-pneumatic spring device bears the vertical downward load transmitted by the bottom beam of the pinion carrier at the measuring shaft part, the load is transmitted to the upper piston rod through the lower flange, the threaded pull rod and the upper flange plate to form the pressure of the upper piston on the rodless cavity of the hydro-pneumatic spring oil cylinder; when the downward load is smaller than the initial oil pressure of oil in the rodless cavity of the hydro-pneumatic spring oil cylinder set by the air bag type energy accumulator to the upper piston rod, the upper piston rod is kept still; when the downward load is greater than the initial set value of the oil in the rodless cavity of the hydro-pneumatic spring oil cylinder, the generated oil in the rodless cavity compresses the air of the air bag type energy accumulator, so that the upper piston rod moves downwards, the volume of the rodless cavity of the hydro-pneumatic spring oil cylinder is reduced, the gas of the air bag type energy accumulator is further compressed, and the pressure of the rodless cavity of the hydro-pneumatic spring oil cylinder is increased; meanwhile, the lower flange also moves downwards under the action of downward external load, and the guide shaft sleeve connected with the bottom end of the lower piston rod through threads slides relative to the inner hole of the lower flange, so that the lower piston rod is not influenced by the external load and keeps static relative to the hydro-pneumatic spring oil cylinder body; the lower flange and the downward movement of the lower flange in the measuring axial direction can cause the corresponding movement of the pinion carrier mechanism, so that a ship receiving chamber generates downward displacement, and the lower thread clearance of a rotating screw rod and a nut column of the safety mechanism is reduced;
when the hydro-pneumatic spring device bears the vertical upward load transmitted by the bottom beam of the pinion carrier at the measuring shaft position, the load is transmitted to the lower piston rod through the guide shaft sleeve to form the pressure of the lower piston on the rodless cavity of the hydro-pneumatic spring oil cylinder; when the upward load is smaller than the initial oil pressure of oil in the rodless cavity of the hydro-pneumatic spring oil cylinder set by the air bag type energy accumulator to the lower piston rod, the lower piston rod is kept still; when the upward load is greater than the initial set value of oil in the rodless cavity of the hydro-pneumatic spring oil cylinder, the generated oil in the hydro-pneumatic spring oil cylinder compresses the air of the air bag type energy accumulator, so that the lower piston rod moves upwards, the volume of the rodless cavity of the hydro-pneumatic spring oil cylinder is reduced, the gas in the air bag type energy accumulator is further compressed, and the pressure of the rodless cavity of the hydro-pneumatic spring oil cylinder is increased; the lower flange moves upwards under the action of an upward external load; the pull rod connected with the lower flange through the threads moves upwards; because the upper end of the pull rod is sleeved in an inner hole of the self-lubricating shaft sleeve with the flange in a hollow mode, the pull rod cannot generate acting force on the upper flange when moving upwards, and the upper flange and an upper piston rod of the upper flange keep static relative to the hydro-pneumatic spring oil cylinder body; the lower flange and the movement thereof in the measuring axial direction can cause the corresponding movement of the pinion carrier, so that the ship receiving chamber structure generates upward displacement, and the upper thread clearance of the rotating screw rod and the nut column of the safety mechanism is reduced;
step four: after the ship lift finishes and finishes the current lifting operation, after a ship chamber docking command is sent out at a centralized control master station, after the ship lift is confirmed to dock and lock to form support for a ship chamber, the pressure of the hydraulic-pneumatic spring energy accumulator is released to a value close to zero, the pressure value is determined according to the weight of the gear shaft, so that the pinion bracket of the driving mechanism only supports the weight of the open pinion to keep the open pinion in the mechanism configuration without the capacity of bearing external load, the ship chamber is locked by the docking and locking mechanism, and the open pinion of the driving mechanism is in an unloading state, so that the open pinion is prevented from being subjected to external load in the process of docking the ship chamber with the upper and lower lock heads, and the loaded sliding of the pinion in the width direction caused by the relative horizontal movement of the ship chamber and the tower column is avoided.
Further, the initial pressure P0Setting the shutdown load of the ship lift driving mechanism:
initial volume V0Determined as follows:
in the formula:
Fdssetting load for the driving mechanism overload shutdown pinion;
p0initial pressure after the air bag type energy accumulator is inflated; p1 initial start of liquid-gas spring(ii) the air bag accumulator pressure at a moment;
V1the volume of the air bag type energy accumulator at the moment; p2 is the pressure of the gas-bag accumulator at the end of the gas-liquid spring action, V2The volume of the air bag type energy accumulator at the moment;
Dithe inner diameter of the hydro-pneumatic spring oil cylinder;
lambda is the lever ratio of the pinion carrier mechanism,
l1 and L2 are respectively the distance from the bottom hinged support of the pinion bracket to the supporting hinged support of the hydro-pneumatic spring oil cylinder and the distance from the bottom hinged support to the pinion;
Fspgear load at the initial moment of deformation of the hydro-pneumatic spring, FlimIs gear limit load;
vw is the effective volume of the airbag accumulator,
the invention has the advantages and characteristics that:
the hydraulic-pneumatic spring composed of the oil cylinder and the energy accumulator has the displacement-load mechanical characteristic of a bidirectional precompression nonlinear spring, so that when a ship receiving chamber of the rack-and-pinion climbing ship lift has an unbalance accident, the bottom of the mechanism and a connecting hinge shaft of a pinion bracket are displaced up and down through the axial movement of double piston rods of the hydraulic-pneumatic spring oil cylinder, the function of stable transition from a pinion and a rack to a rotary screw rod and a nut column of the safety mechanism for vertical support of the ship chamber is realized, and the safety is improved;
drawings
FIG. 1 is a cross-sectional view of a hydro-pneumatic spring mechanism according to a preferred embodiment of the present invention;
FIG. 2 is a side view structural diagram of FIG. 1;
FIG. 3 is a schematic structural view of a dual-piston rod hydro-pneumatic spring cylinder according to a preferred embodiment of the present invention;
FIG. 4 is a partial block diagram of the connection of the lower flange, the lower piston rod and the self-lubricating sliding sleeve in accordance with the preferred embodiment of the present invention;
FIG. 5 is a view of the connection structure of the upper flange, the self-lubricating sleeve and the pull rod according to the preferred embodiment of the present invention;
FIG. 6 is a schematic view of the principle of operation of the hydro-pneumatic spring in accordance with the preferred embodiment of the present invention;
FIG. 7 is a schematic view of the connection of the pinion carrier to the fluid in accordance with the preferred embodiment of the present invention.
The reference numbers in the figures denote: the device comprises a support 1, a bottom plate 1-1, a vertical plate 1-2, a reinforcing triangle plate 1-3, a measuring shaft 2-3, a lower flange 3-4, a guide shaft sleeve 4-5, a self-lubricating bearing 6-a liquid-gas spring oil cylinder, an upper piston rod 6-1, a lower piston rod 6-2, a hinged shaft 6-3, a rodless cavity 6-4, a pull rod 7-8, an upper flange 8, a self-lubricating sliding sleeve 9, an air bag type energy accumulator 10-11, an oil pipe 12, a self-aligning rolling bearing 13, a hydraulic oil pipe 15, a bolt 16, a pinion bracket bottom beam 16, a pinion bracket 17 and a ship-bearing box 18. 19-open pinion, 20-rack.
Detailed Description
The invention is further illustrated with reference to the accompanying drawings:
referring to fig. 1 to 4, a safety hydro-pneumatic spring device applied to a ship lift is installed at the tail of a pinion carrier mechanism, and includes a bracket 1, a measuring shaft 2 (the measuring shaft has a force transmission function and is provided with a detection device inside, the shape of the measuring shaft is the same as that of a common shaft), a lower flange 3, a guide shaft sleeve 4, a self-lubricating bearing 5, a hydro-pneumatic spring cylinder 6, a pull rod 7, an upper flange 8, a self-lubricating sliding sleeve 9, parts of a bearing thereof and other parts, an accumulator hydraulic pipeline, a valve and other parts; the hydraulic-pneumatic spring oil cylinder 6 adopts a double-piston rod type, a hinge shaft in the middle of the hydraulic-pneumatic spring oil cylinder 6 is supported on a support 1 through a self-lubricating bearing 5, the bottom of the support 1 is connected with a cabin structure 18 through a bolt 15, the support 1 comprises a bottom plate 1-1, a vertical plate 1-2 and a reinforcing triangular plate 1-3, the bottom plate 1-1 is connected with the cabin structure 18 through the bottom plate bolt 15, the vertical plate 1-2 is vertically arranged on the upper end surface of the bottom plate 1-1, and two side edges of the reinforcing triangular plate 1-3 playing a reinforcing role are respectively and fixedly arranged on the bottom plate 1-1 and the vertical plate 1-2;
the end part of a piston rod at the upper part of the hydro-pneumatic spring oil cylinder 6 is connected with an upper flange 8 through threads, and a piston rod at the lower part of the oil cylinder is assembled with a mounting hole of a lower flange 3 in clearance fit through a guide shaft sleeve 4; the upper flange and the lower flange are connected through a pull rod 7, a self-lubricating shaft sleeve with a flange is installed in an upper flange pull rod installation hole, the upper end of the pull rod 7 is sleeved in an inner hole of the self-lubricating shaft sleeve with the flange in a hollow mode, the top of the pull rod is located through a nut, and the lower end of the pull rod 7 is fixed to the lower flange 3 through the upper nut and the lower nut. The bottom measuring shaft 2 is assembled in a self-aligning rolling bearing 12 in a shaft hole of the lower flange 3 and a hinge hole at the end part of the bottom beam, and is axially fixed through a shaft end baffle and a connecting screw which are arranged at the end part of the bottom beam.
Referring to fig. 5 and 6, the hydro-pneumatic spring cylinder 6 is communicated with the air bag type energy accumulator 10 of the external hydraulic pump station, and the pretightening force of the hydro-pneumatic spring is determined by the oil pressure of the air bag type energy accumulator and can be adjusted as required. The hydro-pneumatic spring composed of the oil cylinder and the air bag type energy accumulator has the displacement load characteristic of a pre-compressed nonlinear spring: when the gear load is less than the pre-tightening load determined by the oil pressure of the air bag type energy accumulator, the pistons at two ends of the hydraulic-pneumatic spring oil cylinder 6 are pressed against two ends of the cylinder body of the hydraulic-pneumatic spring oil cylinder 6 by the oil pressure, the hydraulic-pneumatic spring keeps the initial position, when the gear load exceeds the pre-tightening load, the oil pressure of the rodless cavity 6-4 of the double-piston rod hydraulic-pneumatic spring oil cylinder exceeds the initial value, the gas of the air bag type energy accumulator air bag is compressed to reduce the gas volume, and the oil liquid in the oil cylinder enters the air bag type energy accumulator to enable the pressed piston of the hydraulic-pneumatic spring oil cylinder to generate.
According to the structural types of the pull rod and the head of the piston rod, when the hydro-pneumatic spring device bears the vertical downward load transmitted by the bottom beam 16 of the pinion carrier at the measuring shaft position, the load is transmitted to the upper piston rod 6-1 through the lower flange 3, the threaded pull rod 7 and the upper flange plate, and the pressure of the upper piston on a rodless cavity of the hydro-pneumatic spring oil cylinder is formed. When the load is smaller than the initial oil pressure of oil in the rodless cavity 6-4 of the hydro-pneumatic spring oil cylinder set by the air bag type energy accumulator to the upper piston rod, the upper piston rod 6-1 is kept still; when the load is greater than the initial set value of the oil in the rodless cavity 6-4 of the hydro-pneumatic spring oil cylinder, the generated oil in the rodless cavity 6-4 compresses the air of the air bag type energy accumulator 10, so that the upper piston rod moves downwards, the volume of the rodless cavity 6-4 of the hydro-pneumatic spring oil cylinder is reduced, the gas of the air bag type energy accumulator 10 is further compressed, and the pressure of the rodless cavity of the hydro-pneumatic spring oil cylinder is increased; meanwhile, the lower flange 3 also moves downwards under the action of a downward external load, and at the moment, the guide shaft sleeve 4 which is in threaded connection with the bottom end of the lower piston rod slides relative to the inner hole of the lower flange, so that the lower piston rod 6-2 is not subjected to the action of the external load and is kept static relative to the cylinder body of the hydro-pneumatic spring cylinder 6. The downward movement of the lower flange 3 and its measuring shaft 2 can cause a corresponding movement of the pinion carrier 16 mechanism, thereby producing a downward displacement of the ship reception compartment, resulting in a reduction of the lower thread clearance of the rotary screw and nut stud of the safety mechanism.
When the hydro-pneumatic spring device bears the vertical upward load transmitted by the bottom beam of the pinion carrier 16 at the position of the measuring shaft 2, the load is transmitted to the lower piston rod through the guide shaft sleeve 4, and the pressure of the lower piston on the rodless cavity 6-4 of the hydro-pneumatic spring oil cylinder is formed. When the load is less than the initial oil pressure of the oil in the rodless cavity 6-4 of the hydro-pneumatic spring oil cylinder set by the air bag type energy accumulator 10 to the lower piston rod, the lower piston rod is kept still; when the load is greater than the initial set value of oil in the rodless cavity 6-4 of the hydro-pneumatic spring oil cylinder, the generated oil in the oil rod cavity 15 compresses the air of the air bag type energy accumulator, so that the lower piston rod 6-2 moves upwards, the volume of the rodless cavity 6-4 of the hydro-pneumatic spring oil cylinder is reduced, the gas in the air bag type energy accumulator 10 is further compressed, and the pressure of the rodless cavity 6-4 of the hydro-pneumatic spring oil cylinder is increased. The lower flange moves upward under the action of an upward external load. At the same time, the pull rod of the lower flange threaded connection also moves upwards along with the lower flange threaded connection. Because the upper end of the pull rod is sleeved in an inner hole of the self-lubricating shaft sleeve 9 with the flange, the pull rod 7 does not generate acting force on the upper flange 8 when moving upwards, and the upper flange 8 and the upper piston rod 6-1 thereof keep static relative to the cylinder body of the hydro-pneumatic spring cylinder. An upward movement of the lower flange 3 and its measuring shaft 2 may cause a corresponding movement of the pinion carrier 17, thereby causing an upward displacement of the ship reception compartment structure 18, resulting in a reduction of the upper thread clearance of the safety gear rotating screw and nut stud.
(2) Calculation of basic parameters and mechanical properties of hydro-pneumatic spring oil cylinder
1) Determination of hydro-pneumatic spring cylinder stroke
The stroke of the hydro-pneumatic spring oil cylinder is an important parameter of the hydro-pneumatic spring device, and the stroke of the oil cylinder must ensure that the hydro-pneumatic spring oil cylinder still keeps a certain margin stroke after the thread clearance of the safety mechanism disappears so as to avoid the accident that the thread clearance of the safety mechanism does not disappear and the stroke of the oil cylinder is used up to cause the safety mechanism to be incapable of providing support. Therefore, the thread clearance should consider the larger value as possible, namely the larger clearance value when the upper and lower thread clearances are unequal and are deviated to one side, and the displacement difference value when the ship receiving chamber structure where the safety mechanism and the driving mechanism are located generates unbalance accident should be considered. For a large and medium gear rack climbing ship lift, the stroke of a hydro-pneumatic spring oil cylinder can be calculated according to the following formula:
fs＝2(2dsb+df+dm-5mm) (1)
in the formula (f)sThe stroke of the hydro-pneumatic spring oil cylinder is adopted; dsbThe theoretical thread clearance (namely the thread clearance value when the upper thread pair clearance and the lower thread pair clearance are equal) of the safety mechanism; dfThe difference value of the displacement of the ship reception chamber structure where the safety mechanism and the driving mechanism are located when the ship reception chamber has unbalance accidents; dmThe margin of the stroke of the oil cylinder. In the above formula 2dsb5mm represents the maximum thread clearance on one side due to unbalance of the upper and lower thread pairs for various reasons.
2) Total volume calculation for airbag accumulators
The pressure p and the volume V of the gas in the gas bag accumulator satisfy the Boyle's law
pVn＝C (2)
Wherein n is an index and C is a constant. For isothermal thermodynamic processes, n is 1; for adiabatic thermodynamic processes, n is 1.4. The ship reception chamber unbalance accident in the lifting operation of the ship lift is generally caused by ship reception chamber water leakage, and the field tests of the three gorges ship lift and the ship lift towards the family dam show that the action of the liquid-gas spring caused by the ship reception chamber water leakage accident is relatively slow, so that the design of the liquid-gas spring gas-bag type energy accumulator can be considered according to the isothermal process. Thus, the basic equation for a hydro-pneumatic spring-bladder accumulator design is
p0V0＝p1V1＝p2V2＝C (3)
In the formula p0Initial pressure after inflation of the airbag accumulator, V0The initial volume is the total volume of the air bag type energy accumulator; p is a radical of1Accumulator pressure, V, at the initial moment of the beginning of the action of the hydro-pneumatic spring1The volume of the air bag type energy accumulator at the moment; p is a radical of2Pressure of air-bag accumulator at the end of the action of liquid-gas spring, V2Is the airbag type accumulator volume at the moment.
(4) And (5) formula (D)iIs the inner diameter of the hydro-pneumatic spring oil cylinder, and lambda is the lever ratio of the pinion bracket mechanism:
l1 and L2 are the pinion carrier base to hydraulic spring cylinder fulcrum and base to pinion distances, respectively, as shown in fig. 6.
FspGear load at the initial moment of deformation of the hydro-pneumatic spring, FlimFor gear limit load, the effective volume of the air bag type energy accumulator is the volume of hydraulic oil discharged by the full-stroke movement of the piston of the hydro-pneumatic spring oil cylinder:
according to the formulas (3) and (6), the total volume of the air bag type energy accumulator is obtained
It should be noted that, because the isothermal process is an ideal thermodynamic process, the system temperature inevitably changes during the action of the liquid-gas spring, and particularly when the load of the pinion gear is rapidly increased due to the blockage of the ship reception chamber during the lifting process, the large amount of water leakage of the ship reception chamber and the like, the actual thermodynamic process of the airbag type energy accumulator has a certain deviation from the isothermal process, and the total volume of the airbag type energy accumulator is slightly smaller by calculation according to the isothermal process, so the total volume of the airbag type energy accumulator calculated according to the formula (7) should be regarded as the minimum value, and when the design value of the total volume of the airbag type energy accumulator is determined, a proper margin should be considered.
3) Spring rate function and mechanical characteristic function of hydro-pneumatic spring
In the action process of the liquid-gas spring, the volume corresponding to the displacement x of the piston rod of the liquid-gas spring is
V(x)＝V1-Sx (8)
In the above formula, S ═ π Di 2And 4, the area of a rodless cavity of the hydraulic-pneumatic spring oil cylinder.
Boyle's law according to isothermal processes
pV(x)＝C (9)
Differentiating the two sides of the formula (8) to obtain
dpV(x)+pdV(x)＝0 (10)
Substituting the formulas (8) and (9) into the formula (10)
C is equal to p1V1And Fsp ═ Sp1Substituting/lambda into formula (11) to obtain
The axial load of the hydro-pneumatic spring oil cylinder in the action process is
F(x)＝p(x)S (13)
Substituting the formula (13) into the formula (12) to obtain the liquid-gas spring with the elastic coefficient function of
As can be seen from (14), the liquid-gas spring has a coefficient of elasticity function that is a positive, non-linear function of displacement.
The mechanical characteristic curve of the hydro-pneumatic spring can be obtained by integrating (14). Write (14) to
Integration of two sides of equation (15)
The mechanical characteristic curve of the liquid-gas spring is accurately expressed as
Let F0＝Fsp/λ，x0＝V1(S), (17) can be written as
For the convenience of dynamic analysis and control of the ship lift system, the formula (18) can also be written into the form of polynomial series
Due to x/x0<<1, the number of stages is convergent, so n may be omitted>3 term of
It is apparent that the hydro-pneumatic spring has an initial load of F0Precompression amount of x0The precompressed nonlinear spring of (1). It should be noted that the expressions (18) and (20) correspond to the case where f (x) and x are both positive numbers, i.e., correspond to the case of the first quadrant of the x-f (x) coordinate plane. The mechanical characteristic curves corresponding to equations (18) and (20) are antisymmetric with respect to the origin of the x-f (x) coordinate because the hydro-pneumatic spring can bear bidirectional load.
The load transfer implementation process comprises the following steps:
1. a gear carrier mechanism is arranged according to the figures 1-5 and is connected with a pinion carrier mechanism according to the figure 7. The hydro-pneumatic spring mechanism and the air bag type energy accumulator are configured according to the figure 6, and the hydro-pneumatic spring oil cylinder is determined according to the formula (1).
2. Setting initial pressure p of air bag type accumulator0And an initial volume V0Wherein the initial pressure is set according to the shutdown load of the ship lift driving mechanism:
in the formula, FdsA load is set for the drive mechanism to overload the stop pinion. The initial volume is determined as in equation (7).
3. In the actual operation of the ship lift, when the butt joint process of the ship lift receiving chamber and the upper and lower lock heads is finished and the centralized control station sends a 'ship chamber lifting operation' instruction, the hydraulic system injects pressure oil into the air bag type energy accumulator 10 to ensure that the initial pressure is p0So that the pinion carrier 17 of the drive mechanism forms a supporting structure for the ship receiving chamber during lifting and carries out the liquid and gas according to the principles of the claims and the summary of the inventionSpring load transfer and transfer to the safety mechanism.
4. After the ship lift finishes and finishes the current lifting operation, after a command of 'ship chamber docking' is sent out at a centralized control master station, after the ship lift is confirmed to be docked and locked to support a ship chamber, the pressure of the air bag type energy accumulator 10 is released to a value close to zero, the pressure value is determined according to the weight of the gear shaft, so that the driving mechanism pinion bracket only supports the weight of the open pinion 19 to keep the mechanism configuration without the capacity of bearing external load, the ship chamber is locked by the docking locking mechanism, the driving mechanism open pinion 19 is in an unloading state, the open pinion 19 is prevented from being under the external load during the docking process of the ship chamber and the upper and lower lock heads, and the pinion slides along the width direction due to the relative horizontal movement of the ship chamber and the tower column.
When the gear load is smaller than the spring deformation initial load determined by the oil pressure of the air bag type energy accumulator, the two pistons are propped against the two ends of the oil cylinder by the oil pressure of the rodless cavity of the oil cylinder between the two pistons, and the hydro-pneumatic spring keeps the initial position, so that the normal bearing and operation of the meshing of the gear and the rack of the driving mechanism are maintained; when the gear load exceeds the initial load of the spring deformation, an overload signal of the driving mechanism is sent out through the measuring shaft of the structure, and the driving system is stopped; meanwhile, the volume of the oil cylinder from a rod cavity is reduced by the oil pressure between two pistons formed by the overload load of the oil cylinder, the gas volume of the air bag type energy accumulator is compressed by the pressure of the hydraulic oil, the pressed piston at one end is displaced, and the up-and-down movement of the connecting hinge point of the lower part of the mechanism and the pinion bracket and the rotation of the liquid-gas spring oil cylinder around the connecting hinge with the ship bearing chamber are generated, so that the movement of the pinion bracket mechanism is initiated, the gap between the rotary screw rod of the safety mechanism and the thread pair of the nut column is reduced until the gap between the thread pair of the safety mechanism disappears, and finally the geometric contact condition that the safety mechanism bears the unbalanced load of the ship.
The safe type liquid-gas spring device is used as a component of a supporting system of the open gear on the ship reception chamber under the normal lifting operation working condition of the ship lift and participates in the load transmission of the unbalanced load of the ship reception chamber to the tower column structure; under the working condition of ship reception chamber unbalance accident, the load and displacement of the double-piston oil cylinder show the mechanical characteristics of a spring through the compression of energy accumulator air generated by the overload of the hydro-pneumatic spring device and the movement of piston rods at two ends of the double-piston oil cylinder generated by the compression; the mechanism of the device is arranged, so that the respective unidirectional axial movement of two pistons of the double-piston oil cylinder causes the up-and-down movement of a hinge shaft connected with a bottom beam of a pinion bracket on a lower flange of the device, and the clearance of the safety mechanism disappears slowly. The mechanism design of the hydro-pneumatic spring device enables each piston rod of the double-piston rod hydro-pneumatic spring oil cylinder to bear only one-way axial load, and the movement of the piston rod of each hydro-pneumatic spring oil cylinder when the driving mechanism is overloaded causes the upward or downward movement of the connecting hinge point of the device and the bottom beam of the pinion bracket along the axis of the hydro-pneumatic spring oil cylinder and the rotation of the hydro-pneumatic spring oil cylinder around the hinge shaft, so that a thread contact pair formed by the disappearance of thread gaps corresponds to the direction of unbalanced load of a ship bearing compartment.
The respective unidirectional axial movement of two pistons of the double-piston oil cylinder leads to the up-and-down movement of a hinged shaft connected with a bottom beam of a pinion carrier on a lower flange plate of the device, so that the clearance of the safety mechanism disappears slowly, each piston rod of the double-piston rod hydraulic spring oil cylinder only bears unidirectional axial load, and the movement of the piston rod of each hydraulic spring oil cylinder when the driving mechanism is overloaded leads to the upward or downward movement of a hinged point connected with the bottom beam of the pinion carrier of the device along the axis of the hydraulic spring oil cylinder and the rotation of the hydraulic spring oil cylinder around the hinged shaft, so that a thread contact pair formed by the disappearance of the thread clearance corresponds to the direction of unbalanced load of a ship bearing compartment, and safe and stable load transfer is realized.
Under normal working conditions, loads such as unbalanced force, friction force, inertia force and the like of the ship reception chamber of the gear-rack full-balance vertical ship lift are transmitted to the tower column through the hydraulic gas spring, the gear bracket and the pinion of the driving mechanism through the racks, power is provided for the open gear by the motor, the reducer and the universal coupling, and the load of the driving mechanism is overcome to drive the ship reception chamber to lift and run. The open gear is supported on the ship bearing chamber side wing structure platform through a gear bracket and a hydro-pneumatic spring device and is horizontally and transversely positioned relative to the rack through a gear bracket mechanism. The horizontal relative displacement and angular displacement of the tower and the ship reception chamber are accommodated by the gear bracket. The bottom of the hydro-pneumatic spring oil cylinder mechanism is hinged with a gear bracket bottom beam through a measuring shaft and a bearing. Under the normal lifting working condition of the ship reception chamber, the hydro-pneumatic spring oil cylinder is used as one of force transmission components for transmitting unbalanced force of the ship reception chamber to the tower column, and the integral rotation is not caused by the fact that the gear bracket mechanism adapts to the relative displacement of the tower column and the ship reception chamber, and the axial displacement of a piston caused by axial load is not caused. When the ship reception chamber is overloaded due to unbalance of water leakage and other reasons, the hydro-pneumatic spring device causes the movement of the gear bracket mechanism through the compression of gas in the air bag type energy accumulator and the axial movement of the double-acting oil cylinder piston, so that the thread clearance at one side of the rotary screw rod and the nut column of the safety mechanism is stably and slowly disappeared, and a necessary condition is provided for the safety mechanism to bear the ship reception chamber unbalance accident load. After the clearance between the rotary screw rod of the safety mechanism and the screw teeth of the nut column disappears and the rotary screw rod and the screw teeth of the nut column are contacted with each other, the newly increased unbalanced force generated by the unbalanced accident of the ship receiving chamber is transmitted to the nut column and the tower column structure through the thread pair of the safety mechanism, and the load of the open gear of the driving mechanism is not increased any more, so that the driving mechanism is free from bearing larger accident load.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "parallel", "vertical", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred devices or elements must have specific orientations, be constructed in specific orientations, and be operated, and thus, should not be construed as limiting the present invention.
The foregoing shows and describes the general principles and features of the present invention, together with the advantages thereof. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are described in the specification and illustrated only for the purpose of illustrating the structural relationship and principles of the present invention, but that various changes and modifications may be made without departing from the spirit and scope of the invention as defined in the appended claims. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (3)
1. The utility model provides a safe type liquid gas spring device who uses in ship lift which characterized in that: the device comprises a support (1), a measuring shaft (2), a lower flange (3), a guide shaft sleeve (4), a self-lubricating bearing (5), a hydro-pneumatic spring oil cylinder (6), a pull rod (7), an upper flange (8), a self-lubricating sliding sleeve (9), an air bag type energy accumulator (10) and an oil pipe (11);
the lower end of the support (1) is fixedly arranged on a ship-bearing chamber structure (18), the hydraulic-pneumatic spring oil cylinder (6) adopts a double-piston rod type, and a support hinge shaft (6-3) in the middle of the hydraulic-pneumatic spring oil cylinder (6) is supported on the support (1) through a self-lubricating bearing (5); the end part of an upper piston rod (6-1) of the hydraulic-pneumatic spring oil cylinder (6) is connected with an upper flange (8) through threads, the lower end of a lower piston rod (6-2) of the hydraulic-pneumatic spring oil cylinder (6) is assembled with a mounting hole (3-1) of a lower flange (3) through a guide shaft sleeve (4) in a clearance fit manner, a measuring shaft (2) is fixedly mounted at the lower end of the lower flange (3), and the lower end of the measuring shaft and a bottom beam of a gear bracket mechanism form a hinged structure; the upper flange and the lower flange are connected through a pull rod (7), a self-lubricating sliding sleeve (9) with a flange is mounted on an upper flange pull rod mounting hole (81) of the upper flange (8), the upper end of the pull rod (7) is sleeved in an inner hole of the self-lubricating sliding sleeve (9) with the flange, the top of the pull rod is positioned by a nut, and the lower end of the pull rod (7) is fixed on the lower flange (3) through the nut; the measuring shaft at the bottom is hinged with a bottom beam of a gear bracket mechanism, so that a force transmission system is formed together with a pinion bracket, and unbalanced load of a ship receiving chamber under the lifting working condition of the ship lift is transmitted to a tower column; the air bag type energy accumulator (10) is communicated with a rodless cavity (6-4) of the hydraulic-pneumatic spring oil cylinder (6) through an oil pipe (11);
the hydro-pneumatic spring oil cylinder (6) is communicated with an air bag type energy accumulator (10) of an external hydraulic pump station, and the pre-tightening force of the hydro-pneumatic spring is determined by the oil pressure of the energy accumulator and can be adjusted according to the requirement; the hydro-pneumatic spring composed of the hydro-pneumatic spring oil cylinder and the energy accumulator has the displacement load characteristic of a pre-compressed nonlinear spring: when the gear load is smaller than the pre-tightening load determined by the oil pressure of the energy accumulator, pistons at two ends of the hydro-pneumatic spring oil cylinder (6) are propped against two ends of a cylinder body of the hydro-pneumatic spring oil cylinder (6) by the oil pressure, and the pistons at two ends of the hydro-pneumatic spring oil cylinder (6) keep initial positions, so that the normal bearing and operation of the meshing of the gear and the rack of the driving mechanism are maintained; when the gear load exceeds the pre-tightening load, the oil pressure of the rodless cavity (6-4) of the double-piston rod hydro-pneumatic spring oil cylinder exceeds the initial value, and the gas of the gas bag (10-1) of the energy accumulator is compressed to reduce the gas volume,
oil in the (6-4) enters the air bag type energy accumulator (10) to enable a pressed piston of the hydraulic-pneumatic spring oil cylinder (6) to generate axial displacement; the up-and-down movement of a connecting hinge point of the lower part of the measuring shaft (2) and a bottom beam (16) of the pinion bracket and the rotation of the hydro-pneumatic spring oil cylinder (6) around a hinge connected with a ship bearing chamber are generated, so that the motion of the pinion bracket (17) is initiated, the gap between a rotating screw rod of the safety mechanism and a screw thread pair of a nut column is reduced until the gap between the screw thread pair of the safety mechanism disappears, and finally, the geometric contact condition that the safety mechanism bears the unbalanced load of the ship bearing chamber is formed; when the ship receiving chamber of the gear rack climbing ship lift has unbalance accidents, the hinged part of the measuring shaft (2) positioned at the bottom of the hydro-pneumatic spring and the bottom beam (16) of the pinion bracket moves up and down through the axial movement of the upper piston rod (6-1) and the lower piston rod (6-2) of the hydro-pneumatic spring oil cylinder.
2. The safety type hydro-pneumatic spring device applied to the ship lift according to claim 1, wherein: the bottom measuring shaft (2) is hinged with the gear bracket mechanism bottom beam through a self-aligning rolling bearing (12) assembled in a shaft hole of the lower flange (3) and a hinge hole at the end part of the bottom beam.
3. The safety type hydro-pneumatic spring device applied to the ship lift according to claim 1, wherein: the support (1) comprises a bottom plate (1-1), vertical plates (1-2) and reinforcing triangular plates (1-3), the bottom plate (1-1) is connected with a ship reception chamber structure (18) through bottom plate bolts (15), the vertical plates (1-2) are vertically arranged on the upper end face of the bottom plate (1-1), and two side edges of the reinforcing triangular plates (1-3) playing a reinforcing role are fixedly arranged on the bottom plate (1-1) and the vertical plates (1-2) respectively.
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| CN202020523215.2U CN212690662U (en) | 2020-04-10 | 2020-04-10 | Safety type liquid-gas spring device applied to ship lift |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114212736A (en) * | 2021-12-03 | 2022-03-22 | 杭州昱透实业有限公司 | Forklift with automatically adjustable balance wheel load suspension system and use method |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114212736A (en) * | 2021-12-03 | 2022-03-22 | 杭州昱透实业有限公司 | Forklift with automatically adjustable balance wheel load suspension system and use method |
| CN114212736B (en) * | 2021-12-03 | 2024-04-19 | 浙江昱透实业有限公司 | Fork truck with automatically adjustable balance wheel load suspension system and use method |
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