CN105484222A - Active anti-overturning mechanical synchronizing system for anti-overturning hydraulic power type ship lift and arrangement method of active anti-overturning mechanical synchronizing system - Google Patents

Abstract

The invention provides an arrangement method of an active anti-overturning mechanical synchronizing system for an anti-overturning hydraulic power type ship lift. The rigidity and strength of synchronizing shafts of the active anti-overturning mechanical synchronizing system are set and gaps and manufacturing errors of the active anti-overturning mechanical synchronizing system are controlled, so that the active anti-overturning mechanical synchronizing system simultaneously has the ship lift chamber anti-overturning function and the uneven ship lift chamber load evenly-transmission function; when a ship lift chamber bears the uneven load and inclines, the anti-overturning force moment can be actively generated for the ship lift chamber through tiny deformation of the active anti-overturning mechanical synchronizing system, and the purposes that the inclination of the ship lift chamber is controlled and the torque of the synchronizing shafts is reduced are achieved; and when the inclination of the ship lift chamber or the torque of the synchronizing system reaches a designed value, rotation of a coiling block is locked through a brake of the active anti-overturning mechanical synchronizing system, the overall safety of the ship lift chamber is guaranteed, and safe and reliable operation of the hydraulic power type ship lift can be guaranteed.

Description

Overturning or slip resistance analysis Waterpower type ship elevator active overturning or slip resistance analysis mechanical synchronization system and method to set up thereof

Technical field

The present invention relates to the method to set up of a kind of overturning or slip resistance analysis Waterpower type ship elevator active overturning or slip resistance analysis mechanical synchronization system and this system, belong to navigation building field.

Background technology

Waterpower type ship elevator is a kind of novel ship lift, it arranges multiple the separation with lock chamber and the vertical shaft filling, discharge water be communicated with each other respectively, in each vertical shaft, floating drum is set, multiple balance weight---i.e. floating drum, each floating drum is connected (namely on ship reception chamber, forming multiple suspension centre) by corresponding steel cable, reel, pulley with the multiple position of ship reception chamber, when in vertical shaft during water-filling floating drum rise, ship reception chamber decline, otherwise ship reception chamber rises, thus completes hydro powered formula and rise ship or fall ship.The each suspension centre of Waterpower type ship elevator ship reception chamber has hydro powered, the hydro powered source of all suspension centres is all by a Valve controlling, there will not be the situation that certain suspension centre hydro powered lost efficacy, even if lost efficacy in indivedual hydro powered source, because whole hydraulic hoisting system drive source is more, the unbalanced load needing mechanical synchronization axle to overcome neither be very large, therefore, can be connected by synchronizing shaft between each reel, the design of initiatively overturning or slip resistance analysis mechanical synchronization system can be enormously simplify like this.

Waterpower type ship elevator synchronizing shaft is directly connected with reel, and the gap between its synchronizing shaft torsional deflection and synchronizing shaft is directly delivered to ship reception chamber by reel, and the gap between synchronizing shaft or torsional deflection size directly affect the tilt quantity size of ship reception chamber; The heeling moment that ship reception chamber is subject to and unbalanced load are directly delivered to synchronizing shaft by reel, and under identical ship reception chamber Inclined Load, the motor-driven traditional ship lift of torque ratio of Waterpower type ship elevator synchronizing shaft is large.Therefore, the requirement of ship lift to aspects such as synchronizing shaft rigidity, intensity and gaps of hydro powered has higher requirement than motor-driven traditional ship lift.

Because the mechanical elevating system of Waterpower type ship elevator and traditional ship lift differ greatly, and it is very great on the impact improving the overall resistance to capsizing of Waterpower type ship elevator ship reception chamber, the security of operation of its safe and reliable direct relation ship lift, so ship lift initiatively overturning or slip resistance analysis mechanical synchronization system and method to set up, ship booster supporting compartment active overturning or slip resistance analysis mechanical synchronization system and the method to set up particularly with resistance to capsizing are particularly important.

Summary of the invention

The present invention is by the further investigation to Waterpower type ship elevator active overturning or slip resistance analysis mechanical synchronization system loading characteristic, in conjunction with Waterpower type ship elevator general principle, for Waterpower type ship elevator ship reception chamber band water tilt problem, propose the method to set up of a kind of Waterpower type ship elevator with resistance to capsizing initiatively overturning or slip resistance analysis mechanical synchronization system and this active overturning or slip resistance analysis mechanical synchronization system.To solve Waterpower type ship elevator ship reception chamber band water, the problem of operation normally can not be elevated.

The present invention is completed by following technical proposal: a kind of overturning or slip resistance analysis Waterpower type ship elevator is overturning or slip resistance analysis mechanical synchronization system initiatively, comprise the many steel cables be connected with multiple positions of ship reception chamber both sides, the other end of many steel cables walks around the corresponding reel being arranged on top respectively and the pulley arranged on floating drum is in the shaft fixed on the top of vertical shaft, is connected between multiple reel by synchronizing shaft and shaft coupling.

Described multiple reel and shaft coupling and synchronizing shaft are arranged to two rows accordingly with the steel cable of ship reception chamber both sides, two row between by umbrella tooth to and shaft coupling be connected with synchronous cross axle, form rectangle frame to connect, and each reel is equipped with conventional brake, so that when ship reception chamber is subject to occurring tilting under unbalanced load effect, micro-deformation by the synchronizing shaft in active overturning or slip resistance analysis mechanical synchronization system produces initiatively resistance to tipping moment, to control ship reception chamber tilt quantity, reduce synchronizing shaft moment of torsion, and when ship railway carriage or compartment tilt quantity or Synchronous Transmission moment of torsion reach design load, corresponding reel is locked by brake, ensure ship lift general safety.

Described overturning or slip resistance analysis Waterpower type ship elevator comprises the ship reception chamber be arranged in lock chamber, the stable equilibrium hydraulic driving system be connected with ship reception chamber, initiatively overturning or slip resistance analysis mechanical synchronization system and self feed back systems stabilisation, wherein:

Described stable equilibrium hydraulic driving system comprises the water delivery supervisor of vertical shaft, setting floating drum in the shaft, band delivery valve, the many points of branching pipes be connected are responsible in lower end and water delivery, many point branching pipes are made up of the straight tube on the straight tube of bottom, the corner pipe at middle part and/or bifurcated pipe and top, and the straight tube water side on top is placed in corresponding silo bottom, and straight tube water side is provided with energy dissipater, be connected by water level balance gallery between each vertical shaft; And be provided with the first resistance equalization member in a point branching pipe corner, be provided with the second resistance equalization member at bifurcated pipe place, be provided with hoop artificial aeration mechanism, valve before water delivery supervisor delivery valve valve after, be provided with voltage stabilizing vibration damping box; Be set to the cone of 120 ° bottom described floating drum, and the gap ratio between vertical shaft and floating drum remains between 0.095 ~ 0.061, the stability exported with the hydrodynamic characterisitic change and hydrodynamic force that improve stable equilibrium hydraulic driving system;

Described self feed back systems stabilisation comprises the guide rail be symmetricly set on lock chamber sidewall, be symmetricly set on ship reception chamber both sides corresponding upper and lower parts, the multiple guide wheels matched with the guide rail on lock chamber sidewall, each guide wheel is all fixed on ship reception chamber by supporting mechanism;

Each guide wheel of described self feed back systems stabilisation is fixed on ship reception chamber by supporting mechanism, described supporting mechanism comprises the base be connected with ship reception chamber, be hinged on the support on base, be fixed on the flexible piece between support and base, be arranged on the spacing block piece outside flexible piece, be arranged on the guide wheel rolled on support and along guide rail;

By above-mentioned active overturning or slip resistance analysis mechanical synchronization system, stable equilibrium hydraulic driving system, ship reception chamber self feed back systems stabilisation associating acting in conjunction, solve Waterpower type ship elevator ship reception chamber and carry water, normally cannot be elevated the problem of operation, improve the overall resistance to capsizing of Waterpower type ship elevator, ensure Waterpower type ship elevator safety, stable, reliability service.

The support of the supporting mechanism in described self feed back systems stabilisation is two pieces of set squares be oppositely arranged, the right angle of this set square is fixed on the projection inside base by hinge, between horizontal outer end and base, flexible piece is set, be specially spring, guide wheel is fixed between two pieces of set squares by wheel shaft by upper end, right angle, so that in the process that guide wheel rolls along guide rail, when running into irregular guide rail, by flexible piece, support is swung around hinge and jolting of alleviating that guide rail out-of-flatness brings, connecting simultaneously by guide rail and guide wheel, overturning or slip resistance analysis moment of torsion is provided automatically, to carry out active correction to ship reception chamber, prevent ship reception chamber from tilting.

The guide rail of described self feed back systems stabilisation arranges two respectively along lock chamber both sides inwall, totally four, the left and right sides wall of each root guide rail and two supporting mechanisms on ship reception chamber top, two supporting mechanisms of bottom, totally four supporting mechanisms are matched, when ship reception chamber be subject to unbalanced load and cause ship reception chamber occur tilt after, by connecting of guide rail and guide wheel, overturning or slip resistance analysis moment of torsion is provided automatically, to carry out active correction to ship reception chamber, prevent ship reception chamber from tilting, and carry out spacing to the inclination produced, prevent ship reception chamber tilt quantity from continuing to increase, make Waterpower type ship elevator stability and safety reliability service.

The left and right sides wall of the guide rail of described self feed back systems stabilisation arranges level board or L-square accordingly, two supporting mechanisms of the side plate of this level board or L-square and two supporting mechanisms on ship reception chamber top, bottom, totally four supporting mechanisms are matched, to improve the planeness of guide rail.

Described stable equilibrium hydraulic driving system:

Energy dissipater comprises the vertical rod that compartment of terrain is arranged at silo bottom and along straight tube water side port periphery, be arranged on the horizontal plate washer of vertical rod upper end, can only enter in vertical shaft in the space downwards again between vertical rod to the water of upper punch under horizontal baffle effect, thus reduce water outlet water velocity, eliminate water energy, slow down water flow impact pressure, improve floating drum bottom water flow condition, avoid current directly to impact bottom floating drum and cause floating drum to rock;

First resistance equalization member is right-angle elbow pipe, and tube head to downward-extension and closed is set below right-angle elbow pipe right angle, equal to ensure the flow of each point of branching pipe in narrow vertical space, farthest ensure that each point of branching pipe enters vertical shaft flow consistent, meet and wait resistance that requirement is set;

Second resistance equalization member is up big and down small solid or hollow cone, the upper end of this cone is fixed on the horizontal tube wall of bifurcated pipe, lower end extends downward in the VERTICAL TUBE of bifurcated pipe, equal to ensure the flow of each point of branching pipe in narrow vertical space, farthest ensure that each point of branching pipe enters vertical shaft flow consistent, meet and wait resistance that requirement is set;

Hoop artificial aeration mechanism comprises: be fixed on the ventilation endless tube that water delivery supervisor is outside, the inside wall of ventilation endless tube is provided with the first through hole, first through hole be arranged on the second through hole that water delivery is responsible on wall and be communicated with, the lateral wall of ventilation endless tube is provided with third through-hole, third through-hole is connected with air supply pipe, air supply pipe is connected with source of the gas, pressure air is sent in ventilation endless tube through air supply pipe, again through first, second through hole is sent in water delivery supervisor, namely in water, gas is joined, to solve stable equilibrium hydraulic driving system because of the water-delivery valve cavitation under the non-constant effect of high water head and vibration problem, reduce pressure fluctuation, the relative cavitation number of valve is made to be reduced to 0.5 by 1.0, make the large aperture opening time of valve in advance, emptying effectiveness improves more than 60%, the first through hole on described ventilation endless tube, third through-hole interval arrange multiple, and each third through-hole is all in charge of by corresponding air feed and is connected with air supply header, air supply header is connected with source of the gas, and to be in charge of a point multichannel by air feed, multiple spot is responsible for even air feed to ventilation endless tube, water delivery,

Voltage stabilizing vibration damping box comprises the casing of band cavity, and casing side is provided with water inlet, opposite side is provided with delivery port, water inlet establishes three, to be responsible for water delivery respectively by the delivery valve of correspondence and to be connected, wherein being positioned at middle delivery valve is main valve, the delivery valve of both sides is auxiliary valve, and before the valve of a main valve and two auxiliary valves, water delivery supervisor is provided with hoop artificial aeration mechanism, so that by the less and anti-cavitation ability of water delivery flow preferably auxiliary valve control ship reception chamber low cruise (during docking), the speed of service that ship reception chamber is normally elevated the stage is improved again by the main valve that water delivery flow is larger, the impact that the unsteady flow eliminating the generation of waterpower stable equilibrium system brings ship reception chamber speed of service stability.

Active overturning or slip resistance analysis mechanical synchronization system provided by the invention designs by following method:

Initiatively overturning or slip resistance analysis mechanical synchronization system possesses ship reception chamber overturning or slip resistance analysis simultaneously and transmits the uneven load dual-use function of balanced ship reception chamber, this system initiatively produces resistance to tipping moment by the micro-deformation of synchronizing shaft to ship reception chamber, and when ship reception chamber tilt quantity or synchro system moment of torsion reach design load, by being arranged on the safety device locking reel on reel, ensure ship lift general safety; Described safety device is brake;

If two row's reels initiatively in overturning or slip resistance analysis mechanical synchronization system and shaft coupling and synchronizing shaft, and umbrella tooth to, shaft coupling and synchronous cross axle full symmetric, the abundant leveling of ship reception chamber, each reel, wire rope stressed with rub identical, ignore ship reception chamber and wire rope stiffness effect, then initiatively overturning or slip resistance analysis mechanical synchronization system stiffness, intensity are arranged by following method, are specially:

One, rigidity method to set up

Described ship reception chamber acts on initiatively overturning or slip resistance analysis mechanical synchronization system maximum inclination load Δ P after tilting is calculated as follows:

$\mathrm{\Δ}P=\frac{(\mathrm{\Δ}h+{\mathrm{\Δh}}_0)L_c{B}_c\mathrm{\ρ}g}{24}+\frac{M_b+M_p}{2L_c}---\left(1\right)$

In formula:

Δ h is the ship reception chamber tilt quantity that synchronizing shaft causes by the gap sum between uneven load generation distortion and synchronizing shaft, and unit is m;

Δ h ₀for the ship reception chamber tilt quantity that the ship reception chamber lifting operation processing such as reel, steel cable alignment error causes, unit is m;

L _cfor ship reception chamber length, unit is m;

B _cfor ship reception chamber width, unit is m;

ρ is density, and unit is kg/m ³;

G is acceleration of gravity, and unit is m/s ^-2;

M _bfor the overturning moment that ship reception chamber water level fluctuation causes, unit is kNm;

M _pfor the overturning moment that ship reception chamber eccentric load causes, unit is kNm;

After synchronizing shaft causes ship reception chamber run-off the straight amount Δ h by the uneven load gap sum produced between distortion and synchronizing shaft, the anchorage Δ F that initiatively overturning or slip resistance analysis mechanical synchronization system acts on ship reception chamber by reel again calculates according to following formula:

$\mathrm{\Δ}F=\frac{\mathrm{\Δ}h-{\mathrm{\θ}}_{2}R+4M_{f}R\underset{i=1}{\overset{n}{\Σ}}\frac{L_i}{{\mathrm{GI}}_{pi}}}{R^2\underset{i=1}{\overset{n}{\Σ}}\frac{L_i}{{\mathrm{GI}}_{pi}}}---\left(2\right)$

In formula: Δ F is the anchorage acting on ship reception chamber, unit is kN;

Δ h is the ship reception chamber tilt quantity that synchronizing shaft causes by uneven load generation distortion and synchronizing shaft gap sum, and unit is m;

θ ₂for the total backlash between synchronizing shaft, unit is radian;

R is reel radius, and unit is m;

M _ffor the moment of torsion that single reel frictional force produces, unit is kNm;

G is the coefficient of rigidity, and unit is kPa;

L _ibe i-th synchronizing shaft length, unit is m;

I _pibe i-th synchronizing shaft second polar moment of area, wherein:

$I_p=\frac{{\mathrm{\πD}}^4}{32}(1-a^4)$

In formula: D--synchronizing shaft external diameter;

The hollow synchronizing shaft of a--, inner/outer diameter; It is 0 that solid synchronizing shaft is equivalent to internal diameter, i.e. a=0;

Therefore, do not considering, under synchronizing shaft strength failure condition, to learn:

(1) Δ F> Δ P, synchronizing shaft by uneven load produce distortion and synchronizing shaft gap sum cause ship reception chamber inclination Δ h time, the anchorage Δ F acting on ship reception chamber by reel is greater than when acting on the maximum inclination load Δ P of initiatively overturning or slip resistance analysis mechanical synchronization system after ship reception chamber tilts, and ship reception chamber tilt quantity Δ h will reduce;

(2) Δ F< Δ P, ship reception chamber tilt quantity Δ h continue to increase, and synchronizing shaft needs larger torsional deflection occurs, and produces larger resistance, such guarantee ship reception chamber balance;

(3) Δ F=Δ P, ship reception chamber tilt quantity Δ h equal it when acting on the maximum inclination load Δ P of initiatively overturning or slip resistance analysis mechanical synchronization system, and ship reception chamber is stablized, then remember

$\mathrm{\&beta;}=\frac{L_c{B}_c\mathrm{\&rho;}g}{24},\mathrm{\&delta;}=R\underset{i=1}{\overset{n}{\&Sigma;}}\frac{L_i}{{\mathrm{GI}}_{pi}}$

Condition when stablizing according to ship reception chamber and Δ F=Δ P, should meet the following conditions when ship reception chamber is stablized:

$\mathrm{\&Delta;}h=\frac{{\mathrm{\&theta;}}_{2}R}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}+\frac{{\mathrm{\&Delta;h}}_0\mathrm{\&beta;}\mathrm{\&delta;}R}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}+\frac{\mathrm{\&delta;}R(M_b+M_p)}{2L_c(1-\mathrm{\&beta;}\mathrm{\&delta;}R)}-\frac{4{\mathrm{\&delta;M}}_f}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}---\left(3\right)$

Due to Δ h>=0, definition is overturning or slip resistance analysis mechanical synchronization entire system rigidity initiatively the necessary condition that formula (4) is set up is: 1> β δ R, and namely initiatively overturning or slip resistance analysis mechanical synchronization system can maintain the stable necessary condition of ship reception chamber and is:

$K>\frac{L_c{B}_c{\mathrm{\&rho;gR}}^2}{24}---\left(4\right)$

In ship reception chamber lifting running, ship reception chamber allows the maximum inclination occurred to be Δ h _max, then initiatively overturning or slip resistance analysis mechanical synchronization system stiffness also should meet:

γ ₁(θ ₂R+Δh ₀)+γ ₂(M _b+M _p)-γ ₃M _f≤Δh _max(5)

In formula:

(1) γ ₁(θ ₂r+ Δ h ₀) tilt quantity that produces for foozle, the i.e. initiatively ship reception chamber tilt quantity that causes such as overturning or slip resistance analysis mechanical synchronization system lash, steel cable cabling error, definition: for foozle inclination factor, definition γ ₁for the coefficient relevant with synchronizing shaft rigidity to ship reception chamber yardstick, in conjunction with formula (5) known γ ₁∈ [1 ,+∞), according to coefficient gamma ₁define known γ ₁for being more than or equal to the numerical value of 1; Synchronizing shaft rigidity is larger, γ ₁be worth less, but can not 1 be less than; The γ when synchronizing shaft rigidity is infinitely great ₁=1, the ship reception chamber maximum inclination that now foozle causes is θ ₂r+ Δ h ₀; Therefore γ ₁can play amplification to the ship reception chamber tilt quantity that foozle produces, the rigidity of synchronizing shaft is less, and the ship reception chamber tilt quantity amplification produced foozle is larger; The rigidity of synchronizing shaft is larger, and the ship railway carriage or compartment tilt quantity amplification produced foozle is less;

(2) γ ₂(M _b+ M _p) the ship reception chamber tilt quantity Δ H that causes for overturning moment ₂, i.e. the tilt quantity that occurs under the overturning moment effects such as water level fluctuation, ship reception chamber eccentric load of ship reception chamber, definition for fluctuation tilt quantity coefficient, when rigidity is infinitely great, γ ₂→ 0, now water level fluctuation overturning moment produces tilt quantity to ship reception chamber to be affected less;

(3)-γ ₃m _ffor the ship reception chamber tilt quantity opposing amount that system friction produces, definition for frictional force tilt quantity opposing coefficient, system is larger, more favourable to reduction ship reception chamber tilt quantity;

Therefore, initiatively overturning or slip resistance analysis mechanical synchronization system will possess resistance to capsizing, and its synchronizing shaft rigidity should meet formula (4) and formula (5) simultaneously;

Two, intensity method to set up

Synchronizing shaft peak torque T in ship reception chamber running _nbe expressed as:

In formula, for overturning moment coefficient,

M _qfor ship reception chamber overturning moment, unit is kNm;

for foozle coefficient;

θ ₂r+ Δ h ₀for active overturning or slip resistance analysis mechanical synchronization system foozle;

embody the ship reception chamber overturning moment M that ship reception chamber water level fluctuation, ship reception chamber eccentric load etc. produce _qon the impact of synchronizing shaft moment of torsion;

embody after ship reception chamber adds water, initiatively overturning or slip resistance analysis mechanical synchronization system foozle θ ₂r+ Δ h ₀on the impact of synchronizing shaft moment of torsion;

to embody in ship reception chamber water body to the impact of synchronizing shaft moment of torsion load;

reflect the resistant function of system friction to synchronizing shaft moment of torsion;

M _kreflect the synchronizing shaft internal torque change because alignment error etc. produces when synchronizing shaft rotates;

M _gwhen reflecting the initial leveling of ship reception chamber, the initial torque that adjacent reel, steel cable unbalance stress produce synchronizing shaft;

When anhydrous ship reception chamber lifting runs, these two impacts can be ignored, and when therefore anhydrous ship reception chamber lifting runs, synchronizing shaft moment of torsion can be expressed as:

Three, gap and foozle controlled condition

For active overturning or slip resistance analysis mechanical synchronization system lash θ ₂r, foozle tilt quantity Δ h ₀, should control by following condition:

$({\mathrm{\&theta;}}_{2}R+{\mathrm{\&Delta;h}}_0)\&le;\frac{{\mathrm{\&Delta;h}}_{max}+{\mathrm{\&gamma;}}_3{M}_f-{\mathrm{\&gamma;}}_2(M_b+M_p)}{{\mathrm{\&gamma;}}_1}---\left(6\right)$

In formula: Δ h _maxfor ship reception chamber allows the maximum inclination of generation, unit is m;

M _maxfor the peak torque that active overturning or slip resistance analysis mechanical synchronization system allows, unit is kNm; All the other symbolic significances are the same; Other setting of described active overturning or slip resistance analysis mechanical synchronization system is carried out routinely.

The present invention has following advantages and effect: by active overturning or slip resistance analysis mechanical synchronization system synchronization axle rigidity, intensity is arranged and gap, foozle controls, when ship reception chamber is subject to occurring tilting under unbalanced load effect, micro-deformation by active overturning or slip resistance analysis mechanical synchronization system initiatively produces resistance to tipping moment to ship reception chamber, reach the object controlling ship reception chamber tilt quantity and reduce synchronizing shaft moment of torsion, and when ship railway carriage or compartment tilt quantity or synchro system moment of torsion reach design load, by the brake locking spool turns of active overturning or slip resistance analysis mechanical synchronization system, ensure ship lift general safety, be conducive to guaranteeing Waterpower type ship elevator safety, reliability service.

Accompanying drawing explanation

Fig. 1 is ship lift side-looking structure chart;

Fig. 2 is the A-A profile of Fig. 1;

Fig. 3 is the stable equilibrium hydraulic driving system structure chart in Fig. 1;

Fig. 4 is active overturning or slip resistance analysis mechanical synchronization system construction drawing;

Fig. 5 is self feed back systems stabilisation structure chart;

Fig. 6 is the top view of Fig. 5;

Fig. 7 is the C portion enlarged drawing of Fig. 5;

Fig. 8 is the D portion enlarged drawing of Fig. 6;

Fig. 9 is the B portion enlarged drawing in Fig. 3;

Figure 10 is the hoop artificial aeration mechanism structure figure in Fig. 3;

Figure 11 is the E-E view in Figure 10;

Figure 12 is the voltage stabilizing vibration damping box structure chart in Fig. 3;

Figure 13 is ship reception chamber up fore-and-aft tilt amount evolution with distance figure;

Figure 14 is ship reception chamber Trimming Moment, the initiatively anti-square of going all out of overturning or slip resistance analysis mechanical synchronization system, the anti-square evolution with distance figure that goes all out of ship reception chamber self feed back systems stabilisation;

Figure 15 is ship reception chamber Trimming Moment and the anti-square evolution with distance figure that goes all out;

Figure 16 is the comparison diagram that prior art and the present invention affect tilt quantity when ship reception chamber water level fluctuation;

Figure 17 is prior art and the comparison diagram of the present invention when ship reception chamber water level fluctuation to synchronizing shaft torque influence;

Figure 18 is the pressure fluctuation root mean square figure of measuring point after prior art valve under the identical open degree of delivery valve;

Figure 19 is the pressure fluctuation root mean square figure of measuring point after valve of the present invention under the identical open degree of delivery valve;

Figure 20 is the noise intensity figure under the identical open degree of delivery valve of prior art;

Figure 21 is the noise intensity figure under the identical open degree of delivery valve of the present invention;

Figure 22 is water-supply-pipe vibration acceleration comparison diagram before and after aeration.

In figure, 1 is lock chamber, and 11 is ship reception chamber, and 12 is boats and ships, and 14 is the guide rail of lock chamber sidewall;

2 is active overturning or slip resistance analysis mechanical synchronization system, and 21 is steel cable, and 22 is pulley, and 24 is reel, and 25 is synchronizing shaft, and 26 is shaft coupling, and 27 is brake, and 28 is bevel gear pair, and 29 is synchronous cross axle;

3 is stable equilibrium hydraulic driving system, 31 is vertical shaft, 311 is floating drum, 32 is water delivery supervisor, 327 is the second through hole, 321 for dividing the straight tube of branching pipe lower end, 324 for dividing the straight tube of branching pipe upper end, 323 for dividing the corner pipe of branching pipe, 322 for dividing the bifurcated pipe of branching pipe, 325 is energy dissipater, 326 is water level balance gallery, 33 is delivery valve, 34 is hoop artificial aeration mechanism, 341 is ventilation endless tube, 342 is the first through hole, 343 are in charge of for air feed, 344 is third through-hole, 345 is air supply header, 35 is voltage stabilizing vibration damping box, 351 is housing, 352 is water inlet, 36 is the first resistance equalization member, 37 is the second resistance equalization member,

4 is ship reception chamber self feed back systems stabilisation, and 41 is the base of guide wheel mechanism, and 42 is spacing block piece, and 43 is flexible piece, and 44 is support, and 45 is guide wheel, and 46 is that metal water is dull and stereotyped.

Detailed description of the invention

Below in conjunction with drawings and Examples, the present invention is described further.

Overturning or slip resistance analysis Waterpower type ship elevator provided by the invention comprises the ship reception chamber 11 be arranged in lock chamber 1, the stable equilibrium hydraulic driving system 3 be connected with ship reception chamber 11, initiatively overturning or slip resistance analysis mechanical synchronization system 2 and self feed back systems stabilisation 4, wherein:

Described active overturning or slip resistance analysis mechanical synchronization system 2 comprises: the many steel cables 21 be connected with multiple positions of ship reception chamber 11 both sides in lock chamber 1, the other end of many steel cables 21 walks around the top that the corresponding reel 24 being arranged on top and the pulley 22 be arranged in vertical shaft 31 on floating drum 311 are fixed on vertical shaft 31 respectively, as shown in Figure 1, Figure 2, be connected by synchronizing shaft 25 and shaft coupling 26 between multiple reel 24, multiple reel 24 and shaft coupling 26 and synchronizing shaft 25 are arranged to two rows accordingly with the steel cable 21 of ship reception chamber 11 both sides, by umbrella tooth, synchronous cross axle 29 is connected with to 28 and shaft coupling 26 between two rows, form rectangle frame to connect, and each reel 24 is equipped with conventional brake 27, as Fig. 1, Fig. 2, Fig. 4, so that when ship reception chamber 11 is subject to occurring tilting under unbalanced load effect, micro-deformation by the synchronizing shaft 25 in active overturning or slip resistance analysis mechanical synchronization system 2 produces initiatively resistance to tipping moment, to control ship reception chamber 11 tilt quantity, reduce synchronizing shaft 25 moment of torsion, and when ship reception chamber 11 tilt quantity or Synchronous Transmission moment of torsion reach design load, corresponding reel 24 is locked by brake 27, ensure ship lift general safety.

Described stable equilibrium hydraulic driving system 3 comprises vertical shaft 31, be arranged on the floating drum 311 in vertical shaft 31, water delivery supervisor 32 with delivery valve 33, 32 many of being connected point branching pipes are responsible in lower end and water delivery, many point branching pipes are by the straight tube 321 of bottom, the corner pipe 323 at middle part and the straight tube 324 on bifurcated pipe 322 and top are formed, and the straight tube 321 of bottom, the corner pipe 323 at middle part and the straight tube 324 on bifurcated pipe 322 and top are set to, lower two-stage, lower end straight tube 321 and the water delivery of subordinate are responsible for 32 and are connected, upper end straight tube 324 water side of higher level is placed in bottom corresponding vertical shaft 31, and energy dissipater 325 is set in upper end straight tube 324 water side, be communicated with by water level balance gallery 326 between each vertical shaft 31, described stable equilibrium hydraulic driving system 3 also comprises the first resistance equalization member 36 of corner pipe 323 corner being arranged on point branching pipe and the second resistance equalization member 37 at bifurcated pipe 322 place, be separately positioned on water delivery and be responsible for the hoop artificial aeration mechanism 34 before 32 delivery valve 33 valves and the voltage stabilizing vibration damping box 35 after valve, as Fig. 1, Fig. 2, Fig. 3, the cone of 120 ° is set to bottom floating drum 311, and the gap ratio between vertical shaft 31 and floating drum 311 remains between 0.095 ~ 0.061, with the stability that the hydrodynamic characterisitic change and hydrodynamic force that improve stable equilibrium hydraulic driving system export, wherein:

Energy dissipater 325 comprises the vertical rod that compartment of terrain is arranged at silo bottom and along straight tube 324 water side port periphery, be arranged on the horizontal plate washer of vertical rod upper end, to reduce water outlet water velocity by horizontal baffle, eliminate water energy, slow down water flow impact pressure, improve floating drum bottom water flow condition, avoid current directly to impact bottom floating drum and cause floating drum to rock;

First resistance equalization member 36 is right-angle elbow pipe, and tube head to downward-extension and closed is set below right-angle elbow pipe right angle, as Fig. 9, equal to ensure the flow of each point of branching pipe in narrow vertical space, farthest ensure that each point of branching pipe enters vertical shaft flow consistent, meet and wait resistance that requirement is set;

Second resistance equalization member 37 is up big and down small solid or hollow cone, the upper end of this cone is fixed on the horizontal tube wall of bifurcated pipe 322, lower end extends downward in the VERTICAL TUBE of bifurcated pipe 322, as Fig. 9, equal to ensure the flow of each point of branching pipe in narrow vertical space, farthest ensure that each point of branching pipe enters vertical shaft flow consistent, meet and wait resistance that requirement is set;

Hoop artificial aeration mechanism 34 comprises: be fixed on the ventilation endless tube 341 that 32 outsides are responsible in water delivery, the inside wall of ventilation endless tube 341 is provided with the first through hole 342, first through hole 342 be arranged on the second through hole 327 that water delivery is responsible on 32 walls and be communicated with, the lateral wall of ventilation endless tube 341 is provided with third through-hole 344, third through-hole 344 is connected with air supply pipe, air supply pipe is connected with source of the gas, pressure air is sent in ventilation endless tube 341 through air supply pipe, again through first, second through hole 342, 327 send in water delivery supervisor 32, namely to aeration in water, to solve stable equilibrium hydraulic driving system because of delivery valve 33 cavitation under the non-constant effect of high water head and vibration problem, reduce pressure fluctuation, the relative cavitation number of valve is made to be reduced to 0.5 by 1.0, make the large aperture opening time of valve in advance, emptying effectiveness improves more than 60%, the first through hole 342 on described ventilation endless tube 341, third through-hole 344 interval be symmetrical arranged four, and each third through-hole 344 is all in charge of 343 by corresponding air feed and is connected with air supply header 345, air supply header 345 and source of the gas---namely air compressor is connected, as Figure 10, Figure 11, to be in charge of 343 points of multichannels, multiple spot by air feed to ventilation endless tube 341, water delivery supervisor 32 even aerations,

Voltage stabilizing vibration damping box 35 comprises the casing 351 of band cavity, and casing 351 side is provided with water inlet 352, opposite side is provided with delivery port, water inlet 352 establishes three, delivery valve 33 respectively by correspondence is responsible for 32 with water delivery and is connected, as Fig. 3, Figure 12, wherein being positioned at middle delivery valve is main valve, the delivery valve of both sides is auxiliary valve, and before the valve of a main valve and two auxiliary valves, water delivery supervisor 32 is provided with hoop artificial aeration mechanism 34, so that by the less and anti-cavitation ability of water delivery flow preferably auxiliary valve control ship reception chamber low cruise (during docking), the speed of service that ship reception chamber is normally elevated the stage is improved again by the main valve that water delivery flow is larger, the impact that the unsteady flow eliminating the generation of waterpower stable equilibrium system brings ship reception chamber speed of service stability.

Described self feed back systems stabilisation 4 comprises the guide rail 14 be symmetricly set on lock chamber 1 sidewall, be symmetricly set on ship reception chamber 11 corresponding upper and lower part, the multiple guide wheels matched with the guide rail 14 on lock chamber 1 sidewall, each guide wheel is all fixed on ship reception chamber 11 by supporting mechanism, described guide rail 14 arranges two respectively along lock chamber 1 both sides inwall, totally four, as Fig. 6, and two supporting mechanisms of the left and right sides wall of each root guide rail 14 and two supporting mechanisms on ship reception chamber 11 top, bottom, totally four supporting mechanisms are matched, as Fig. 5, the left and right sides wall of described guide rail 14 arranges metal water flat board 46 accordingly, as Fig. 8, this metal water dull and stereotyped 46 and two supporting mechanisms on ship reception chamber 11 top, two supporting mechanisms of bottom, totally four supporting mechanisms are matched, to improve the planeness of guide rail 14, described supporting mechanism comprises the base 41 be connected with ship reception chamber 11, be hinged on the support 44 on base 41, be fixed on the flexible piece 43 between support 44 and base 41, be arranged on the spacing block piece 42 outside flexible piece 43, be arranged on the guide wheel 45 rolled on support 44 and along guide rail 14, described support 44 is made up of the set square that two pieces are oppositely arranged, the right angle of two pieces of set squares is fixed on the projection inside base 41 by hinge, between outside horizontal outer end and base 41, flexible piece 43 is set, this flexible piece 43 is spring, guide wheel 45 is fixed between two pieces of set squares by wheel shaft by upper end, right angle, as Fig. 7, so that in the process that guide wheel 45 rolls along guide rail 14, when running into irregular guide rail, by flexible piece, support is swung around hinge and jolting of alleviating that guide rail out-of-flatness brings, connecting simultaneously by guide rail and guide wheel, overturning or slip resistance analysis moment of torsion is provided automatically, to carry out active correction to ship reception chamber, prevent ship reception chamber from tilting.

Active overturning or slip resistance analysis mechanical synchronization system provided by the invention designs by following method:

Initiatively overturning or slip resistance analysis mechanical synchronization system possesses ship reception chamber overturning or slip resistance analysis simultaneously and transmits the uneven load dual-use function of balanced ship reception chamber, this system initiatively produces resistance to tipping moment by the micro-deformation of synchronizing shaft to ship reception chamber, and when ship reception chamber tilt quantity or synchro system moment of torsion reach design load, by being arranged on the brake locking reel on reel, ensure ship lift general safety;

If two row's reels initiatively in overturning or slip resistance analysis mechanical synchronization system and shaft coupling and synchronizing shaft, and umbrella tooth to, shaft coupling and synchronous cross axle full symmetric, the abundant leveling of ship reception chamber, each reel, wire rope stressed with rub identical, ignore ship reception chamber and wire rope stiffness effect, then initiatively overturning or slip resistance analysis mechanical synchronization system stiffness, intensity are arranged by following method, are specially:

One, rigidity method to set up

Described ship reception chamber acts on initiatively overturning or slip resistance analysis mechanical synchronization system maximum inclination load Δ P after tilting is calculated as follows:

$\mathrm{\&Delta;}P=\frac{(\mathrm{\&Delta;}h+{\mathrm{\&Delta;h}}_0)L_c{B}_c\mathrm{\&rho;}g}{24}+\frac{M_b+M_p}{2L_c}---\left(1\right)$

In formula:

Δ h is the ship reception chamber tilt quantity that synchronizing shaft causes by the gap sum between uneven load generation distortion and synchronizing shaft, and unit is m;

Δ h ₀for the ship reception chamber tilt quantity that the ship reception chamber lifting operation processing such as reel, steel cable alignment error causes, unit is m;

L _cfor ship reception chamber length, unit is m;

B _cfor ship reception chamber width, unit is m;

ρ is density, and unit is kg/m ³;

G is acceleration of gravity, and unit is m/s ^-2;

M _bfor the overturning moment that ship reception chamber water level fluctuation causes, unit is kNm;

M _pfor the overturning moment that ship reception chamber eccentric load causes, unit is kNm;

After synchronizing shaft causes ship reception chamber run-off the straight amount Δ h by the uneven load gap sum produced between distortion and synchronizing shaft, the anchorage Δ F that initiatively overturning or slip resistance analysis mechanical synchronization system acts on ship reception chamber by reel again calculates according to following formula:

$\mathrm{\&Delta;}F=\frac{\mathrm{\&Delta;}h-{\mathrm{\&theta;}}_{2}R+4M_{f}R\underset{i=1}{\overset{n}{\&Sigma;}}\frac{L_i}{{\mathrm{GI}}_{pi}}}{R^2\underset{i=1}{\overset{n}{\&Sigma;}}\frac{L_i}{{\mathrm{GI}}_{pi}}}---\left(2\right)$

In formula: Δ F is the anchorage acting on ship reception chamber, unit is kN;

Δ h is the ship reception chamber tilt quantity that synchronizing shaft causes by uneven load generation distortion and synchronizing shaft gap sum, and unit is m;

θ ₂for the total backlash between synchronizing shaft, unit is radian;

R is reel radius, and unit is m;

M _ffor the moment of torsion that single reel frictional force produces, unit is kNm;

G is the coefficient of rigidity, and unit is kPa;

L _ibe i-th synchronizing shaft length, unit is m;

I _pibe i-th synchronizing shaft second polar moment of area, wherein:

$I_p=\frac{{\mathrm{\&pi;D}}^4}{32}(1-a^4)$

In formula: D--synchronizing shaft external diameter;

The hollow synchronizing shaft of a--, inner/outer diameter; It is 0 that solid synchronizing shaft is equivalent to internal diameter, i.e. a=0;

Therefore, do not considering, under synchronizing shaft strength failure condition, to learn:

(1) Δ F> Δ P, synchronizing shaft by uneven load produce distortion and synchronizing shaft gap sum cause ship reception chamber inclination Δ h time, the anchorage Δ F acting on ship reception chamber by reel is greater than when acting on the maximum inclination load Δ P of initiatively overturning or slip resistance analysis mechanical synchronization system after ship reception chamber tilts, and ship reception chamber tilt quantity Δ h will reduce;

(2) Δ F< Δ P, ship reception chamber tilt quantity Δ h continue to increase, and synchronizing shaft needs larger torsional deflection occurs, and produces larger resistance, such guarantee ship reception chamber balance;

(3) Δ F=Δ P, ship reception chamber tilt quantity Δ h equal it when acting on the maximum inclination load Δ P of initiatively overturning or slip resistance analysis mechanical synchronization system, and ship reception chamber is stablized, then remember

$\mathrm{\&beta;}=\frac{L_c{B}_c\mathrm{\&rho;}g}{24},\mathrm{\&delta;}=R\underset{i=1}{\overset{n}{\&Sigma;}}\frac{L_i}{{\mathrm{GI}}_{pi}}$

Condition when stablizing according to ship reception chamber and Δ F=Δ P, should meet the following conditions when ship reception chamber is stablized:

$\mathrm{\&Delta;}h=\frac{{\mathrm{\&theta;}}_{2}R}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}+\frac{{\mathrm{\&Delta;h}}_0\mathrm{\&beta;}\mathrm{\&delta;}R}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}+\frac{\mathrm{\&delta;}R(M_b+M_p)}{2L_c(1-\mathrm{\&beta;}\mathrm{\&delta;}R)}-\frac{4{\mathrm{\&delta;M}}_f}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}---\left(3\right)$

Due to Δ h>=0, definition is overturning or slip resistance analysis mechanical synchronization entire system rigidity initiatively the necessary condition that formula (4) is set up is: 1> β δ R, and namely initiatively overturning or slip resistance analysis mechanical synchronization system can maintain the stable necessary condition of ship reception chamber and is:

$K>\frac{L_c{B}_c{\mathrm{\&rho;gR}}^2}{24}---\left(4\right)$

In ship reception chamber lifting running, ship reception chamber allows the maximum inclination occurred to be Δ h _max, then initiatively overturning or slip resistance analysis mechanical synchronization system stiffness also should meet:

γ ₁(θ ₂R+Δh ₀)+γ ₂(M _b+M _p)-γ ₃M _f≤Δh _max(5)

In formula:

(1) γ ₁(θ ₂r+ Δ h ₀) tilt quantity that produces for foozle, the i.e. initiatively ship reception chamber tilt quantity that causes such as overturning or slip resistance analysis mechanical synchronization system lash, steel cable cabling error, definition: for foozle inclination factor, definition γ ₁for the coefficient relevant with synchronizing shaft rigidity to ship reception chamber yardstick, in conjunction with formula (5) known γ ₁∈ [1 ,+∞), according to coefficient gamma ₁define known γ ₁for being more than or equal to the numerical value of 1; Synchronizing shaft rigidity is larger, γ ₁be worth less, but can not 1 be less than; The γ when synchronizing shaft rigidity is infinitely great ₁=1, the ship reception chamber maximum inclination that now foozle causes is θ ₂r+ Δ h ₀; Therefore γ ₁can play amplification to the ship reception chamber tilt quantity that foozle produces, the rigidity of synchronizing shaft is less, and the ship reception chamber tilt quantity amplification produced foozle is larger; The rigidity of synchronizing shaft is larger, and the ship railway carriage or compartment tilt quantity amplification produced foozle is less;

(2) γ ₂(M _b+ M _p) the ship reception chamber tilt quantity Δ H that causes for overturning moment ₂, i.e. the tilt quantity that occurs under the overturning moment effects such as water level fluctuation, ship reception chamber eccentric load of ship reception chamber, definition for fluctuation tilt quantity coefficient, when rigidity is infinitely great, γ ₂→ 0, now water level fluctuation overturning moment produces tilt quantity to ship reception chamber to be affected less;

(3)-γ ₃m _ffor the ship reception chamber tilt quantity opposing amount that system friction produces, definition for frictional force tilt quantity opposing coefficient, system is larger, more favourable to reduction ship reception chamber tilt quantity;

Therefore, initiatively overturning or slip resistance analysis mechanical synchronization system will possess resistance to capsizing, and its synchronizing shaft rigidity should meet formula (4) and formula (5) simultaneously;

Two, intensity method to set up

Synchronizing shaft peak torque T in ship reception chamber running _nbe expressed as:

In formula, for overturning moment coefficient,

M _qfor ship reception chamber overturning moment, unit is kNm;

for foozle coefficient;

θ ₂r+ Δ h ₀for active overturning or slip resistance analysis mechanical synchronization system foozle;

embody the ship reception chamber overturning moment M that ship reception chamber water level fluctuation, ship reception chamber eccentric load etc. produce _qon the impact of synchronizing shaft moment of torsion;

embody after ship reception chamber adds water, initiatively overturning or slip resistance analysis mechanical synchronization system foozle θ ₂r+ Δ h ₀on the impact of synchronizing shaft moment of torsion;

to embody in ship reception chamber water body to the impact of synchronizing shaft moment of torsion load;

reflect the resistant function of system friction to synchronizing shaft moment of torsion;

M _kreflect the synchronizing shaft internal torque change because alignment error etc. produces when synchronizing shaft rotates;

M _gwhen reflecting the initial leveling of ship reception chamber, the initial torque that adjacent reel, steel cable unbalance stress produce synchronizing shaft;

When anhydrous ship reception chamber lifting runs, these two impacts can be ignored, and when therefore anhydrous ship reception chamber lifting runs, synchronizing shaft moment of torsion can be expressed as:

Three, gap and foozle controlled condition

For active overturning or slip resistance analysis mechanical synchronization system lash θ ₂r, foozle tilt quantity Δ h ₀, should control by following condition:

$({\mathrm{\&theta;}}_{2}R+{\mathrm{\&Delta;h}}_0)\&le;\frac{{\mathrm{\&Delta;h}}_{max}+{\mathrm{\&gamma;}}_3{M}_f-{\mathrm{\&gamma;}}_2(M_b+M_p)}{{\mathrm{\&gamma;}}_1}---\left(6\right)$

In formula: Δ h _maxfor ship reception chamber allows the maximum inclination of generation, unit is m;

M _maxfor the peak torque that active overturning or slip resistance analysis mechanical synchronization system allows, unit is kNm; All the other symbolic significances are the same; Other setting of described active overturning or slip resistance analysis mechanical synchronization system is carried out routinely.

Compared with prior art learnt by above-mentioned setting: ship booster supporting compartment tilt quantity of the present invention much smaller than prior art, when water level fluctuation heeling moment is 20 × 10 ³during kNm, there is 15.6cm and tilt in prior art actual measurement ship reception chamber, and only there is the inclination of 3.0cm in the present invention, see Figure 16, and after the present invention arranges and has the active overturning or slip resistance analysis mechanical synchronization system of resistance to capsizing, the peak torque produced by ship reception chamber water level fluctuation also can significantly reduce, water level fluctuation overturning moment 20 × 10 ³during kNm, the synchronizing shaft peak torque of prior art is 554kNm, and the present invention is only 338.6kNm, sees Figure 17.

In the ship reception chamber dynamic operation test of 1:10, can ensure that Waterpower type ship elevator is one and restrains stable system by the active overturning or slip resistance analysis mechanical synchronization system of overturning or slip resistance analysis function of the present invention, ship reception chamber tilt quantity and ship reception chamber water level fluctuation can not increase disperses, ship reception chamber has water to be elevated in running, ship reception chamber fore-and-aft tilt amount only increases 3.5cm, the peak torque change amplitude of synchronizing shaft is 192.6kNm, and in whole service process, ship reception chamber unstable phenomenon does not occur.

The voltage stabilizing vibration damping box of the present invention by arranging after the hoop artificial aeration mechanism that arranges before delivery valve valve and valve, solve cavitation and the vibration problem of delivery valve, reduce pressure fluctuation, make the large aperture opening time of delivery valve in advance, improve emptying effectiveness, avoid Hydrodynamic cavitation to the destruction of delivery valve and hydraulic pipeline.Show through observed result: before valve, after hoop artificial aeration mechanism and valve, the two kinds of measures of voltage stabilizing vibration damping box are combined, and effectively can suppress cavitation, the cavitation corrosion of delivery valve, reduce vibration acceleration, improve emptying effectiveness, that is:

A) voltage stabilizing vibration damping box compared with prior art, and under identical aperture delivery valve acting head generally improves the condition of 5m, maximum stream flow is by 14.3m ³/ s increases to 21.0m ³/ s; Water transmission way foreshortens to 15.4min by 3213min; Meanwhile, voltage stabilizing vibration damping box substantially improves the disadvantageous flow condition of prior art, and under identical opening ways, pressure fluctuation root mean square maximum value drops to 0.09m water column (see Figure 19) by 2.7m water column (see Figure 18); The relative cavitation number of delivery valve improves 30 ~ 40%, and anti-cavitation effect is given prominence to; In addition, voltage stabilizing vibration damping box each measuring point vibration peak acceleration root-mean-square value on average declines 36%, and its natural frequency is high, more than 1kHz, can not resonate with flow fluctuation load, and structure design, installation meet Anti-vibration Design requirement.

B) after adopting hoop artificial aeration mechanism and voltage stabilizing vibration damping box conbined usage, pressure fluctuation is reduced further, generally decline about 20%; After hoop artificial aeration mechanism aeration, delivery valve airborne-noise level on average reduces 5dB, and in the scope not having reverberation sound, current noise is steady, does not have abnormal voice; Cavitation pulse signal (see Figure 21) almost do not detected, Figure 20 is prior art, and its noise intensity is large; Cavitation noise sound pressure level decline 20 ~ 30dB, aeration ensure that non-cavitating running status, water-supply-pipe vibration acceleration on average reduces 80% ~ 90%, see Figure 22, show that aeration effectiveness in vibration suppression is remarkable, 60% gas can be discharged, 40% gas enters vertical shaft 31, do not form air bag, do not affect the stationarity of vertical shaft 31 water surface, after aeration, vertical shaft 31 water level fluctuation amplitude is less than ± 0.05m;

C), after hoop artificial aeration mechanism and these the two kinds of measures of voltage stabilizing vibration damping box are combined, substantially increase the corresponding aperture acting head of water delivery main valve, reduce water transmission way, the opening ways after reasonably optimizing, can ensure that water transmission way is within 15min.

Known by Waterpower type ship elevator prototype measurement of the present invention, after adopting waterpower stable equilibrium system of the present invention to be optimized transformation, flowing exceed 20m ³within/s, water transmission way 15min under condition, shaft surface maximum fluctuation is only ± 5cm, and adjacent water level of drilled shaft difference is less than 3cm, and valve running non-cavitating phenomenon, vibration acceleration reduces greatly.

By the setting to self feed back systems stabilisation, on the basis of ship reception chamber horizontal stable, band Waterborne running, descending overall process is run, wherein ship reception chamber up fore-and-aft tilt amount evolution with distance as shown in figure 13, ship reception chamber indulges overturning moment and resistance to tipping moment evolution with distance as Figure 14, shown in 15, can find out, ship reception chamber trim is covered and is shown as stable wave process, fluctuating range is less, each inclination all can recover afterwards, in up process, maximum trim covers about 50mm, maximum guide wheel pressure is less than 20t, ship reception chamber self feed back systems stabilisation indulges overturning moment with active overturning or slip resistance analysis mechanical synchronization system shared ship reception chamber, the two resistance to tipping moment sum and vertical overturning moment substantially identical, ship reception chamber is in stable convergence state all the time, solve under along journey, ship reception chamber self feed back systems stabilisation situation is not set, the problem that ship reception chamber knockdown also expands gradually more than 300mm, visible, ship reception chamber self feed back systems stabilisation overturning or slip resistance analysis effect along journey is very remarkable, make the unstable divergence characterization generation fundamental shifts of Waterpower type ship elevator mechanical lift systems, become the system of stable convergence.

Shown by above-mentioned embodiment, stable equilibrium hydraulic driving system achieve synchronously, steadily, hydraulics fast and efficiently, for ship lift stable and high effective operation is laid a good foundation; Initiatively overturning or slip resistance analysis mechanical synchronization system reduces tilt quantity and the synchronizing shaft moment of torsion of ship reception chamber, for ship lift safety, even running provide condition; Ship reception chamber self feed back systems stabilisation can the irregularity degree of flexible adaptation guide rail, ensures ship reception chamber level and stable elevation, under the fluctuation among a small circle, and tilt quantity and stressed further reduction.Therefore, above-mentioned multiple system combined work forms a kind of Waterpower type ship elevator with resistance to capsizing jointly, and ensures that Waterpower type ship elevator can stable and high effective operation.

Claims (2)

1. the method to set up of an overturning or slip resistance analysis Waterpower type ship elevator use active overturning or slip resistance analysis mechanical synchronization system, it is characterized in that described active overturning or slip resistance analysis mechanical synchronization system comprises the many steel cables be connected with multiple positions of ship reception chamber both sides, the other end of many steel cables walks around the corresponding reel being arranged on top respectively and the pulley arranged on floating drum is in the shaft fixed on the top of vertical shaft, is connected between multiple reel by synchronizing shaft and shaft coupling;

Described active overturning or slip resistance analysis mechanical synchronization system designs by following method:

Initiatively overturning or slip resistance analysis mechanical synchronization system possesses ship reception chamber overturning or slip resistance analysis simultaneously and transmits the uneven load dual-use function of balanced ship reception chamber, this system initiatively produces resistance to tipping moment by the micro-deformation of synchronizing shaft to ship reception chamber, and when ship reception chamber tilt quantity or synchro system moment of torsion reach design load, by being arranged on the safety device locking reel on reel, ensure ship lift general safety;

If two row's reels initiatively in overturning or slip resistance analysis mechanical synchronization system and shaft coupling and synchronizing shaft, and umbrella tooth to, shaft coupling and synchronous cross axle full symmetric, the abundant leveling of ship reception chamber, each reel, wire rope stressed with rub identical, ignore ship reception chamber and wire rope stiffness effect, then initiatively overturning or slip resistance analysis mechanical synchronization system stiffness, intensity are arranged by following method, are specially:

One, rigidity method to set up

Described ship reception chamber acts on initiatively overturning or slip resistance analysis mechanical synchronization system maximum inclination load Δ P after tilting is calculated as follows:

$\mathrm{\&Delta;}P=\frac{(\mathrm{\&Delta;}h+{\mathrm{\&Delta;h}}_0)L_c{B}_c\mathrm{\&rho;}g}{24}+\frac{M_b+M_p}{2L_c}---\left(1\right)$

In formula:

Δ h is the ship reception chamber tilt quantity that synchronizing shaft causes by the gap sum between uneven load generation distortion and synchronizing shaft, and unit is m;

Δ h ₀for the ship reception chamber tilt quantity that the ship reception chamber lifting operation processing such as reel, steel cable alignment error causes, unit is m;

L _cfor ship reception chamber length, unit is m;

B _cfor ship reception chamber width, unit is m;

ρ is density, and unit is kg/m ³;

G is acceleration of gravity, and unit is m/s ^-2;

M _bfor the overturning moment that ship reception chamber water level fluctuation causes, unit is kNm;

M _pfor the overturning moment that ship reception chamber eccentric load causes, unit is kNm;

After synchronizing shaft causes ship reception chamber run-off the straight amount Δ h by the uneven load gap sum produced between distortion and synchronizing shaft, the anchorage Δ F that initiatively overturning or slip resistance analysis mechanical synchronization system acts on ship reception chamber by reel again calculates according to following formula:

$\mathrm{\&Delta;}F=\frac{\mathrm{\&Delta;}h-{\mathrm{\&theta;}}_{2}R+4M_{f}R\underset{i=1}{\overset{n}{\&Sigma;}}\frac{L_i}{{\mathrm{GI}}_{pi}}}{R^2\underset{i=1}{\overset{n}{\&Sigma;}}\frac{L_i}{{\mathrm{GI}}_{pi}}}---\left(2\right)$

In formula: Δ F is the anchorage acting on ship reception chamber, unit is kN;

Δ h is the ship reception chamber tilt quantity that synchronizing shaft causes by uneven load generation distortion and synchronizing shaft gap sum, and unit is m;

θ ₂for the total backlash between synchronizing shaft, unit is radian;

R is reel radius, and unit is m;

M _ffor the moment of torsion that single reel frictional force produces, unit is kNm;

G is the coefficient of rigidity, and unit is kPa;

L _ibe i-th synchronizing shaft length, unit is m;

I _pibe i-th synchronizing shaft second polar moment of area, wherein:

$I_p=\frac{{\mathrm{\&pi;D}}^4}{32}(1-a^4)$

In formula: D--synchronizing shaft external diameter;

The hollow synchronizing shaft of a--, inner/outer diameter; It is 0 that solid synchronizing shaft is equivalent to internal diameter, i.e. a=0;

Therefore, do not considering, under synchronizing shaft strength failure condition, to learn:

(1) Δ F> Δ P, synchronizing shaft by uneven load produce distortion and synchronizing shaft gap sum cause ship reception chamber inclination Δ h time, the anchorage Δ F acting on ship reception chamber by reel is greater than when acting on the maximum inclination load Δ P of initiatively overturning or slip resistance analysis mechanical synchronization system after ship reception chamber tilts, and ship reception chamber tilt quantity Δ h will reduce;

(2) Δ F< Δ P, ship reception chamber tilt quantity Δ h continue to increase, and synchronizing shaft needs larger torsional deflection occurs, and produces larger resistance, such guarantee ship reception chamber balance;

(3) Δ F=Δ P, ship reception chamber tilt quantity Δ h equal it when acting on the maximum inclination load Δ P of initiatively overturning or slip resistance analysis mechanical synchronization system, and ship reception chamber is stablized, then remember

$\begin{array}{cc}\mathrm{\&beta;}=\frac{L_c{B}_c\mathrm{\&rho;}g}{24},& \mathrm{\&delta;}=R\underset{i=1}{\overset{n}{\&Sigma;}}\frac{L_i}{{\mathrm{GI}}_{pi}}\end{array}$

Condition when stablizing according to ship reception chamber and Δ F=Δ P, should meet the following conditions when ship reception chamber is stablized:

$\mathrm{\&Delta;}h=\frac{{\mathrm{\&theta;}}_{2}R}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}+\frac{{\mathrm{\&Delta;h}}_0\mathrm{\&beta;}\mathrm{\&delta;}R}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}+\frac{\mathrm{\&delta;}R(M_b+M_p)}{2L_c(1-\mathrm{\&beta;}\mathrm{\&delta;}R)}-\frac{4{\mathrm{\&delta;M}}_f}{1-\mathrm{\&beta;}\mathrm{\&delta;}R}---\left(3\right)$

Due to Δ h>=0, definition is overturning or slip resistance analysis mechanical synchronization entire system rigidity initiatively the necessary condition that formula (4) is set up is: 1> β δ R, and namely initiatively overturning or slip resistance analysis mechanical synchronization system can maintain the stable necessary condition of ship reception chamber and is:

$K>\frac{L_c{B}_c{\mathrm{\&rho;gR}}^2}{24}---\left(4\right)$

In ship reception chamber lifting running, ship reception chamber allows the maximum inclination occurred to be Δ h _max, then initiatively overturning or slip resistance analysis mechanical synchronization system stiffness also should meet:

γ ₁(θ ₂R+Δh ₀)+γ ₂(M _b+M _p)-γ ₃M _f≤Δh _max(5)

In formula:

(1) γ ₁(θ ₂r+ Δ h ₀) tilt quantity that produces for foozle, the i.e. initiatively ship reception chamber tilt quantity that causes such as overturning or slip resistance analysis mechanical synchronization system lash, steel cable cabling error, definition: for foozle inclination factor, definition γ ₁for the coefficient relevant with synchronizing shaft rigidity to ship reception chamber yardstick, in conjunction with formula (5) known γ ₁∈ [1 ,+∞), according to coefficient gamma ₁define known γ ₁for being more than or equal to the numerical value of 1; Synchronizing shaft rigidity is larger, γ ₁be worth less, but can not 1 be less than; The γ when synchronizing shaft rigidity is infinitely great ₁=1, the ship reception chamber maximum inclination that now foozle causes is θ ₂r+ Δ h ₀; Therefore γ ₁can play amplification to the ship reception chamber tilt quantity that foozle produces, the rigidity of synchronizing shaft is less, and the ship reception chamber tilt quantity amplification produced foozle is larger; The rigidity of synchronizing shaft is larger, and the ship railway carriage or compartment tilt quantity amplification produced foozle is less;

(2) γ ₂(M _b+ M _p) the ship reception chamber tilt quantity Δ H that causes for overturning moment ₂, i.e. the tilt quantity that occurs under the overturning moment effects such as water level fluctuation, ship reception chamber eccentric load of ship reception chamber, definition for fluctuation tilt quantity coefficient, when rigidity is infinitely great, γ ₂→ 0, now water level fluctuation overturning moment produces tilt quantity to ship reception chamber to be affected less;

(3)-γ ₃m _ffor the ship reception chamber tilt quantity opposing amount that system friction produces, definition for frictional force tilt quantity opposing coefficient, system is larger, more favourable to reduction ship reception chamber tilt quantity;

Therefore, initiatively overturning or slip resistance analysis mechanical synchronization system will possess resistance to capsizing, and its synchronizing shaft rigidity should meet formula (4) and formula (5) simultaneously;

Two, intensity method to set up

Synchronizing shaft peak torque T in ship reception chamber running _nbe expressed as:

In formula, for overturning moment coefficient,

M _qfor ship reception chamber overturning moment, unit is kNm;

for foozle coefficient;

θ ₂r+ Δ h ₀for active overturning or slip resistance analysis mechanical synchronization system foozle;

embody the ship reception chamber overturning moment M that ship reception chamber water level fluctuation, ship reception chamber eccentric load etc. produce _qon the impact of synchronizing shaft moment of torsion;

embody after ship reception chamber adds water, initiatively overturning or slip resistance analysis mechanical synchronization system foozle θ ₂r+ Δ h ₀on the impact of synchronizing shaft moment of torsion;

to embody in ship reception chamber water body to the impact of synchronizing shaft moment of torsion load;

reflect the resistant function of system friction to synchronizing shaft moment of torsion;

M _kreflect the synchronizing shaft internal torque change because alignment error etc. produces when synchronizing shaft rotates;

M _gwhen reflecting the initial leveling of ship reception chamber, the initial torque that adjacent reel, steel cable unbalance stress produce synchronizing shaft;

When anhydrous ship reception chamber lifting runs, these two impacts can be ignored, and when therefore anhydrous ship reception chamber lifting runs, synchronizing shaft moment of torsion can be expressed as:

Three, gap and foozle controlled condition

For active overturning or slip resistance analysis mechanical synchronization system lash θ ₂r, foozle tilt quantity Δ h ₀, should control by following condition:

$({\mathrm{\&theta;}}_{2}R+{\mathrm{\&Delta;h}}_0)\&le;\frac{{\mathrm{\&Delta;h}}_{max}+{\mathrm{\&gamma;}}_3{M}_f-{\mathrm{\&gamma;}}_2(M_b+M_p)}{{\mathrm{\&gamma;}}_1}---\left(6\right)$

In formula: Δ h _maxfor ship reception chamber allows the maximum inclination of generation, unit is m;

M _maxfor the peak torque that active overturning or slip resistance analysis mechanical synchronization system allows, unit is kNm; All the other symbolic significances are the same; Other setting of described active overturning or slip resistance analysis mechanical synchronization system is carried out routinely.

2. the method to set up of a kind of overturning or slip resistance analysis Waterpower type ship elevator active overturning or slip resistance analysis mechanical synchronization system according to claim 1, it is characterized in that described multiple reel and shaft coupling and synchronizing shaft are arranged to two rows accordingly with the steel cable of ship reception chamber both sides, two row between by umbrella tooth to and shaft coupling be connected with synchronous cross axle, form rectangle frame to connect, and each reel is equipped with conventional brake, so that when ship reception chamber is subject to occurring tilting under unbalanced load effect, micro-deformation by the synchronizing shaft in active overturning or slip resistance analysis mechanical synchronization system makes ship reception chamber produce initiatively resistance to tipping moment, to control ship reception chamber tilt quantity, reduce synchronizing shaft moment of torsion, and when ship railway carriage or compartment tilt quantity or Synchronous Transmission moment of torsion reach design load, corresponding reel is locked by brake, ensure ship lift general safety.