CN2058178U - Static-hydraulic driving and eontrol system for fork lift truck - Google Patents

Static-hydraulic driving and eontrol system for fork lift truck Download PDF

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Publication number
CN2058178U
CN2058178U CN 89206774 CN89206774U CN2058178U CN 2058178 U CN2058178 U CN 2058178U CN 89206774 CN89206774 CN 89206774 CN 89206774 U CN89206774 U CN 89206774U CN 2058178 U CN2058178 U CN 2058178U
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CN
China
Prior art keywords
valve
gear shift
piston
vehicle
shift pedal
Prior art date
Application number
CN 89206774
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Chinese (zh)
Inventor
彭昌宗
Original Assignee
彭昌宗
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Priority to CN 89206774 priority Critical patent/CN2058178U/en
Publication of CN2058178U publication Critical patent/CN2058178U/en

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Abstract

The utility model relates to a static-hydraulic driving and control system for fork truck, which adopts a direct current electric machinery, and a variable hydraulic pump, realizing the control of static-hyraulic driving system for fork trucks through manipulating a shift gears footplate and a linkage mechanism thereof and matching with a power limiter, an inching valve, and a control direction-changing valve group, and radically avoids the condition of electric machinery burning and accumulator spoiling for improper manipulations which cause a plurality of electric machinery and working conditions manipulate simultaneously and the output power is exceeded large. The impact phenomenon of vehicles starting off and stopping is also eliminated. The utility model has the advantages of simple structure, easy manufacture, safety and high efficiency, and novelty, and which can be broadly used for various unloading vehicles, in particular to fork trucks and anti-exploding fork trucks.

Description

The present invention relates to a kind of handling vehicle hydrostatic drive control system, particularly a kind of fork truck hydrostatic drive control system.

Existing handling vehicle, no matter be mechanical drive or hydrostatic drive, it does not all have fine motion control and Power Limitation function for moving control system, so can not control maloperation effectively, avoids some unnecessary loss.Often controllable capacity pump being on the position of peak output discharge capacity as the handling vehicle of common employing controllable capacity pump operating personal when the up-hill journey, making the power machine overwork, is that the meeting of combustion engine is flame-out as supplying power; Electrical motor can cause motor to damage and storage battery heavy-current discharge and the situation of reduction of service life greatly in this way; Occur on lifting simultaneously or the bevelled loading and unloading vehicle as above-mentioned situation, the accident of car crash also can occur.And generally adopt the loading and unloading vehicle of permanent power and variable pump, delivery rate is little when its load is big, load hour delivery rate is big, with its wish when the walking operating mode flow exported also little require inconsistent.Under the situation that the traveling gear of the machine driven system of general fork truck is advancing, stopping, falling back in the process of loading and unloading operation, the vehicle body ballistic motion can occur simultaneously, increase safety hazard.When running into sometimes operating personal and will promote operating mode and walking operating mode for saving time and carry out simultaneously; because the walking of existing handling vehicle, to hoist or tilt be separately-driven by several DC machine respectively; the big electric current that several motors start simultaneously is superimposed; can cause the discharge of storage battery overload; storage battery can be damaged at short notice, also usually accidents such as goods falls can be occurred.And the mechanical drive traveling gear of existing storage battery forktruck, generally with resistance or thyristor speed control, the former exists power supply in ohmically loss, wastes energy, and there is the shortcoming of the high maintenance difficult of price in the latter.

Purpose of the present invention, be that a kind of improved fork truck hydrostatic drive control system will be provided, it can carry out fine motion control to the handling vehicle, can carry out Power Limitation again, basically many deficiencies of existing handling vehicle hydrostatic drive have been remedied, be a kind of novel structure, simple and practical loading and unloading vehicle, particularly fork truck hydrostatic drive control system.

Fig. 1 is the fluid control schematic diagram.

Fig. 2 is a tread plate control setup front elevation.

Fig. 3 is that Fig. 2 I-I is to view.

Fig. 4 is that Fig. 2 II-II is to part sectional view.

Fig. 5 is that Fig. 2 A is to view.

Fig. 6 is Fig. 2 radian revision board enlarged view.

Fig. 7 is a load limiter.

Fig. 8 is the micrometering valve device.

Fig. 9 is the principle features figure of power limitation device.

Figure 10 is the structural representation of differential type load limiter.

Figure 11 is for using two a kind of load limiter structural representations that spring is exerted pressure to piston.

Figure 12 replaces a kind of inching valve scheme drawing simple in structure of throttling channel with cutoff port.

Introduce the structure of apparatus of the present invention in detail below in conjunction with accompanying drawing.

Apparatus of the present invention are mainly by volume adjustable hydraulic pump 4, by the control cock group that change-over valve 16,17,18 is formed, and inching valve 19, load limiter 8, gear shift pedal 11 formations such as grade.They are connected as shown in Figure 1 with other parts.Volume adjustable hydraulic pump 4 is to be driven by the DC machine 3 that battery feed 1, appliance controller 2 are controlled.Its function mainly is to provide pressure oil by oil circuit c to control cock group 16,17,18 change-over valves, and the size of its output is to regulate by the angle that changes swash plate.And the angle of swash plate is by the distance control of the valve rod travel S of the servovalve 6 of servo-cylinder 5.Change-over valve 16 in the control cock group mainly is the lifting of control vehicle jack cylinder 23, with jack cylinder 23 bonded assemblys are decline governor valves 24, auxiliary security valve 25.Change-over valve 17 is control vehicle door frame anteversion and retroversion oil cylinders 22, and change-over valve 18 advancing and retreats by oil circuit b, a control forklift-walking HM Hydraulic Motor 21, and 20 for slipping sloping governor valve and buffering Fill valve group, and 15 is the safety valve of working connection.19 is the micrometering valve when walking HM Hydraulic Motor 21, and it is connected with the control cock group by oil circuit b, a.Gear shift pedal 11 is by pivot pin 27 and the fixing feet 26 chains strand that is fixed on the vehicle body frame plate 12, as shown in Figure 2.Its bottom end plate 28 is shelved on the top of spacing regulating control 9, switch 10, constitutes an on-off system jointly.Switch 10 is connected with appliance controller 2, with control motor starting with stop.The static balancing position of gear shift pedal is fixing by the screw levelling back on spacing regulating control 9 tops, and spacing regulating control 9 mainly is that the gear shift pedal lower back panel is played position-limiting action.The other end of gear shift pedal is formed an operating system of servo-cylinder 6 being carried out variable speed control by link gear and the push rod 14 that passes sleeve.Load limiter 8 is installed in the relevant position of the beneath vehicle body frame plate 12 in gear shift pedal middle part, its outstanding circular shaft partly ejects when the vehicle horsepower output surpasses certain limit, withstand gear shift pedal, the operator can not down be stepped on gear shift pedal again, thereby reach the purpose of total system being carried out Power Limitation.

The gear shift pedal front-end structure sees Fig. 3 for details with being connected of other parts.Some tread plates 29 are equipped with on gear shift pedal 11 surfaces, and its both sides have symmetrical flanging 31,32, and its front end and U type support 30 weld togethers are convenient to flexible connection with other parts with additional strengthening Qiang Du And.U type support 30 width are slightly littler than gear shift pedal, and there is symmetrical flap 33,34 both sides, and they are by little axle 39,40 and shake link rod 37,38 movable bindings.Shake link rod 37,38 other ends and bar 35 link joints, bar 35 offers a cross-section hole 36 in the centre, push rod 14 threaded upper ends 41, the interstitial hole 36 Shang And that are enclosed within bar 35 tighten fixing with nut 42,43, the middle part of push rod 14 is enclosed within appearance to have in the interstitial hole 47 of sleeve 13 of screw thread, but the easy on and off activity.Sleeve 13 is fixed on the vehicle body frame plate 12 by nut 45,48 and packing ring 46.Spring 44 1 ends withstand nut 43, one ends and contact with packing ring 46, and such structure makes power that makes progress of generation of spring 44, makes the upper end of push rod 14 withstand gear shift pedal 11 by its link gear, makes it remain on balance position.The bottom of push rod 14 then simultaneously by setting nut 7 or link mechanism, is connected with the servo valve rod of servovalve 6.When gear shift pedal 11 was in static balance position, the swash plate angle of volume adjustable hydraulic pump 4 was in zero position.This moment, volume adjustable hydraulic pump was output as zero state.And when when operation, gear shift pedal 11 was stepped on down, its down the legpower amount pass to the servovalve of servo-cylinder 5 by push rod 14, levelling swash plate angle makes the output increase of volume adjustable hydraulic pump reach the purpose that the vehicle horsepower output is controlled.

The medial side face of gear shift pedal 11 is welded with a square side plate 49, as shown in Figure 5.Below the vehicle body frame plate relevant position of pedal 11 below side plate 49, load limiter 8 and inching valve 19 are housed respectively, as shown in Figure 4.And arranges the aperture 52,54 of two axle center line of centers unanimities on vehicle body frame plate and the side plate, and T template post 53 of fixing dress usefulness is housed in the middle of it, with screw be installed in the vehicle body frame plate below.Liang Ce And row is equipped with load limiter 8 and inching valve 19.Vehicle body frame plate hole 52,54 is passed on piston rod 55, the 64 dome-type tops of load limiter and inching valve respectively, and piston rod 55 and vehicle body frame plate keep flushing, and piston rod 64 then leaves suitable space with the side plate of its top.Flow levelling plate 50 is equipped with in gear shift pedal 11 belows, its center be installed in the vehicle body frame plate on the 54 axial line consistent location of hole.The lower surface of flow levelling plate 50 is circular arc correction curve 51, make on the one hand its move downward with gear shift pedal 11 can kiss when contacting with load limiter piston rod 55 connect and unlikely running over and kill prop up.Be correction on the other hand to volume adjustable hydraulic pump delivery rate error.

The concrete structure of load limiter 8 is seen Fig. 7.It is by housing 62, middle cavity 63, and interior dress piston 58, the piston rod 55 of captive joint on the piston 58, housing inner chamber 63 piston rod surrounding spaces are equipped with spring 56, housing bottom aperture 59, the small plunger 60 and the inner bolt hole 61 of interior dress constitute.Inner bolt hole 61 is connected by auxiliary oil circuit and working connection c.57,64 is the adapter plate of load limiter 8, captives joint with T template post 53 with screw.Small plunger 60 during work is because the effect of the external pressure oil of inner bolt hole makes it withstand on the bottom surface of piston 58.When oil circuit pressure was lower than the deformation force of spring 56, small plunger 60, piston 58 all were in the original place, kept quiescence.When oil circuit pressure increases when making power that small plunger is subjected to greater than the deformation force of spring 56 gradually, small plunger begins to rise, piston 58 is ejected, piston rod 55 is risen, below withstanding gear shift pedal during the circular arc correction curve 51 of flow levelling plate for this reason.When gear shift pedal 11 can not be stepped on down because of piston rod 55 withstands again, when being in stalemate, just reached the limit value of vehicle power peak output this moment.Down step on if strengthen external force again, then cause the oil pressure increasing that pedal is pushed up back, so just reached the purpose of vehicle being carried out Power Limitation because of the output oil mass further increases.

The structure of load limiter 8 also can be changed on the basis of Fig. 7 slightly, becomes as Figure 10, such structure shown in Figure 11.Structure shown in Figure 10 is most identical with Fig. 7, and the small plunger of piston base that different is has made small piston rod into, its diameter d 2With the diameter of big piston bar difference is arranged, and form a differential type load limiter, it carried out with being connected by two oil inlet passages 77 of auxiliary oil circuit d.Figure 11 has showed the another kind of frame mode of load limiter, and different is exerts pressure to piston with two springs 78,79 with Fig. 7 for it, and the spring perch of nut is by the elastic force of screw 80, nut 81 regulating springs 78,79.

The concrete structure of inching valve 19 as shown in Figure 8.It has a valve body 70, and there is cylindrical cavity 71 centre, and piston 65 is housed in the inner chamber, has throttling channel 76 above it.Piston rod 64 is fixed on the center of piston 65.Stretch out from the hole 75 of valve body upper end center its upper end, spring 69 is housed below the piston, and piston 65 is withstood in its upper end, and the lower end contacts with inner chamber 71 bottoms, and its effect makes spring have a power that makes progress to be added in below the piston 65 all the time.Passage 66,68 is connected with oil circuit b, c.The effect of throttling channel 76 is to make HM Hydraulic Motor 21 when starting and stopping, when gear shift pedal 11 has been run into piston rod 64, make piston move down And when beginning to hide passage 66, throttling channel 76 on the piston 65, make between oil circuit a and the oil circuit b and begin throttling, along with piston further hides passage 66, throttling action is strengthened gradually, make HM Hydraulic Motor 21 bear up the process that strengthens gradually that power becomes from original impact conditions, thereby realize level and smooth fine motion, unlikely generation impact phenomenon.The structure of inching valve also can make into as shown in Figure 12, replaces the throttling channel 76 of Fig. 8 with cutoff port 82.

Different operating modes when now the said structure device being used by reality are introduced task of the present invention in detail and how to be implemented.

The walking operating mode: change-over valve 18 is placed the operating mode position of advancing, and with foot-operated gear shift pedal 11 down, this moment, lower back panel 28 lifted, and turned on the power switch 10, started power motor 3, drove volume adjustable hydraulic pump 4, the beginning pressure oil output.Along with the following of gear shift pedal 11 stepped on, by link gear servovalve 6 is moved down, promote servo-cylinder 5 pistons and rise, change the distance of the servovalve throw of lever, the swash plate of regulated variable Hydraulic Pump 4 increases the pressure oil mass of controllable capacity pump Hydraulic Pump output, thereby increases horsepower output.Here want the initial oil drain quantity of explanatory variable pump can also be non-vanishing, allow the output of small discharge capacity.Hydraulic oil still can produce difference of pressure from the restriction of inching valve 19 in the traveling gear oil circuit, and makes servovalve 6 actions.Along with the piston boit 64 of the increase inching valve 19 of horsepower output ejects, prop up the side plate 49 of gear shift pedal 11.Down step on inching valve throttling channel 76(or cutoff port 82 again) begun throttling action, make walking HM Hydraulic Motor no surge start, realize that the vehicle fine motion smoothly starts.Under certain pressure, HM Hydraulic Motor can be carried out speed governing under the delivery scope of volume adjustable hydraulic pump 4.As Figure 90 Q 4N 1P 1Shown in the square frame.This moment, the piston boit 55 of load limiter 8 did not eject and inoperative.Pressure P 1Can satisfy the load of vehicle at full load when level walking.Its speed can be at 0~Q 4Regulate arbitrarily in the delivery scope.When vehicle need stop, as long as gear shift pedal 11 is returned to initial condition.This moment is because the throttling action of inching valve 19 can make vehicle realize fine motion, the level and smooth parking.

Its HM Hydraulic Motor tractive force increases with the gradient when vehicle is in the upward slope walking, maloperation takes place as the driver for increasing horsepower output in this moment, gear shift pedal is depressed with all strength, make the piston stroke maximum of servo-cylinder 5, this moment, volume adjustable hydraulic pump 4 was delivery fuel feeding, its horsepower output can substantially exceed rating horsepower , And works its DC machine 3 or combustion engine under overload.This moment load limiter 8 small plunger because of oil pressure increase to promote piston, make piston rod 55 withstand correction curve plate below the step, make speed change tread plate 11 down step on difficulty gradually.When gear shift pedal 11 can not down be stepped on again, illustrate to reach power output to greatest extent, thereby control maloperation effectively, avoid producing thus the damage of storage battery and motor.Or combustion engine is flame-out.

Because the small plunger 60 of load limiter 8, piston 58, there is certain error in piston rod 55 because of being subjected to different friction force, there is error in the position that the resistance of delivery line also can make piston rod 55 rise, can cause the error of controllable capacity pump delivery rate like this, so apparatus of the present invention are equipped with correction curve 51 at flow levelling plate 50 contact piston bars 55 places, revise by contact position, to reduce error.

The lifting operating mode: at first will control change-over valve 16 and align the position that hoists to jack cylinder 23, and step on gear shift pedal, and make volume adjustable hydraulic pump 4 by working connection a, control change-over valve 16 provides pressure oil to jack cylinder 23, and load is promoted.Because jack cylinder design-calculated rated load, nominal load and Power Limitation are mated as shown in Figure 9, so the driver can carry out work according to the situation of load.As run into valuable, breakables, and stable at a slow speed to jack cylinder 16 fuel feeding as long as control gear shift pedal 11, make the lifting of cargo security ground push away buttress.Unloaded in this way the rising then can make jack cylinder 16 fast rise.To accomplish handling goods safely and efficiently.And when goods descends, change-over valve 16 being in lowering position, jack cylinder 23 is realized the decline of safety by decline governor valve 24, auxiliary security valve 25.

The inclination operating mode: control change-over valve 17 is in the position of leaning forward, and the driver steps on gear shift pedal 11, make variable fuel tap 17 forward, hypsokinesis oil cylinder 22 fuel feeding get final product.When goods need lean forward, the driver if according to operational circumstances to the dump ram fuel feeding, can not produce and resemble the situation that has surplus oil liquid from safety valve 15, to overflow the fix-displacement pump, cause waste.When goods is wanted hypsokinesis, be in reclined position as long as will control change-over valve 17, operating mode is equally operated just with leaning forward.

Compare with the existing hydrostatic control system of various vehicles, apparatus of the present invention only use a DC machine to drive a principal invariant Hydraulic Pump, by handling gear shift pedal and link gear thereof, be equipped with load limiter, inching valve, control change-over valve group and just realized effective control the hydrostatic drive system of handling vehicle.Have characteristics novel in design, simple in structure, superior performance.Owing to set up load limiter, avoided substantially exceeding the situation that rating horsepower burns motor, damages storage battery because of operating the improper horsepower output that makes.Owing to disposed inching valve, make vehicle when starting or pause, eliminated the ballistic motion phenomenon.Safety rate when having improved the handling and loading goods greatly.By control change-over valve group, changed the situation that drove respectively, moves simultaneously by several DC machine in the past, from eliminated the maloperation of multi-state overlap-add operation at all, a large amount of parts had both been saved, the situation of having avoided storage battery to damage again because of the overload discharge, prolong the service life of storage battery greatly, saved the energy simultaneously, accomplished safety, efficient.Because simple in structure, draw materials easily, manufacturing process is simple, cost reduces greatly, adds apparatus of the present invention processing ease, easy to use, can be widely used on all kinds of handling vehicles, and is more suitable to fork truck.Particularly as be applied on the explosion proof forklift, have more safety, advantage efficiently, effect is particularly desirable.

An embodiment is provided below.

Adopt various parts required for the present invention, make three fulcrum hydrostatic transmissions batter fork lift trucks according to preceding method, its main performance and technical parameter are as follows:

Rated load weight 1200Kg

Load base 500mm

Maximum height of lift 3000mm

The fully loaded 13m/min of maximum lifting velocity

Unloaded 24m/min

3 °/6 ° at door frame inclination angle (front/rear)

Minimum turning radius 1410m/m

Road clearance 100mm

12 ° of fully loaded max. climb slope

9 kilometers/hour of fully loaded maximum travelling speeds

12 kilometers/hour of unloaded maximum travelling speeds

Deadweight 2126Kg

Voltage 24V

1300~1500 rev/mins of DC machine, 4 kilowatts of rotating speeds

40 milliliters/commentaries on classics of oil pump shaft orientation plunger variable pump discharge capacity

400 milliliters/commentaries on classics of wheel HM Hydraulic Motor discharge capacity

System's type of belt drive open type

When actual tests, this vehicle launch and shut down level and smooth.In the process of advancing immediately during backward going manoevreability good.Can promote the speed level by the weight of goods and regulate when promoting goods, hoisting speed is fast during underloading, and hoisting speed is slow during heavy duty, has the good performance of travelling, promote.

Claims (9)

1, a kind of loading and unloading vehicle hydrostatic drive control system, comprise DC machine, volume adjustable hydraulic pump, servo-cylinder, control change-over valve group, inching valve, load limiter, gear shift pedal, it is characterized in that this system be by the link gear of gear shift pedal by its front end below with pass the movable push bar that the is fixed on vehicle body frame plate upper bush realization that is connected with the servovalve of volume adjustable hydraulic pump the volume adjustable hydraulic pump delivery rate controlled; Volume adjustable hydraulic pump is driven by DC machine, is to be connected with the aperture of reversing control valve group, load limiter bottom by working connection C; Change-over valve group mouth is connected by the same respectively walking of oil circuit, lifting, door frame anteversion and retroversion HM Hydraulic Motor, wherein between the oil circuit a, the b that communicate with the walking HM Hydraulic Motor inching valve is housed; The load limiter of this system, inching valve are to be fixed on screw below the vehicle body frame plate of gear shift pedal below by T template shelf structure, and the piston rod of their upper ends passes the aperture of offering on the vehicle body frame plate respectively, is erected at the gear shift pedal below.
2, a kind of hydrostatic drive control system as claimed in claim 1, be characterised in that its gear shift pedal link gear by gear shift pedal, U type support, shake the movable linkage structure that flap, bar, push rod, spring constitute and formed, its front end is to pass the push rod, the spring that are fixed on threaded cannulated sleeve on the vehicle body frame plate by nut by one to be fixed, and realizes flexibly connecting; The rear end is to be connected and fixed with the fixing feet that is installed on the vehicle body frame plate by hinge.
3, a kind of hydrostatic drive control system as claimed in claim 1 or 2 is characterized in that its gear shift pedal, is to be had a side plate and constituted by pedal, the pedal middle part side of surface with some tread plates, and pedal middle part lower surface is equipped with the levelling current plate.
4, a kind of hydrostatic drive control system as claimed in claim 1 or 2, it is characterized in that having the flow correction curve that is circular arc below the flow levelling plate that its gear shift pedal installs, this correction curve is according to the actual error decision of volume adjustable hydraulic pump flow.
5, a kind of hydrostatic drive control system as claimed in claim 1 is characterized in that load limiter is made up of cavity, the aperture of bottom, inner bolt hole, piston, piston boit, spring, small plunger in the middle of the housing, housing.
6, as claim 1 or 5 described a kind of hydrostatic drive control system, it is characterized in that the small plunger in the load limiter also can be mounted in the small piston rod of piston base, its diameter be installed in the poor of diameter of piston in the housing middle cavity, form the differential type load limiter.
7, as claim 1 or 5 described a kind of hydrostatic drive control system, it is characterized in that the spring of its load limiter also can use two springs, its elastic force can be regulated by the screw, the nut that are installed in the housing upper end respectively.
8, a kind of hydrostatic drive control system as claimed in claim 1, the inching valve that it is characterized in that it is to have circular hole, centre by upper end central authorities to have and have two access openings on the valve body, piston, piston rod, spring, valve body of cylindrical cavity and constitute, have throttling channel in the piston body, during installation, two access openings are connected with oil circuit a, b respectively.
9, as claim 1 or 8 described a kind of hydrostatic drive control system, it is characterized in that the throttling channel offered on its inching valve valve body middle cavity inner carrier body, also can be cutoff port.
CN 89206774 1989-04-29 1989-04-29 Static-hydraulic driving and eontrol system for fork lift truck CN2058178U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN 89206774 CN2058178U (en) 1989-04-29 1989-04-29 Static-hydraulic driving and eontrol system for fork lift truck

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN 89206774 CN2058178U (en) 1989-04-29 1989-04-29 Static-hydraulic driving and eontrol system for fork lift truck

Publications (1)

Publication Number Publication Date
CN2058178U true CN2058178U (en) 1990-06-13

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Application Number Title Priority Date Filing Date
CN 89206774 CN2058178U (en) 1989-04-29 1989-04-29 Static-hydraulic driving and eontrol system for fork lift truck

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100439231C (en) * 2004-09-04 2008-12-03 容海因里希股份公司 Device for the emergency lowering of a load-carrying means for a stacker truck
CN102131684A (en) * 2008-08-28 2011-07-20 卡特彼勒公司 Control system and method for braking a hydrostatic drive machine
CN103857616A (en) * 2011-09-27 2014-06-11 力至优三菱叉车株式会社 Forklift
CN105197840A (en) * 2015-04-16 2015-12-30 上海市闸北区物流工程技术研究所 Electric control hydraulic driving system for industrial vehicle
CN106044561A (en) * 2016-08-18 2016-10-26 甘培嘉 Hydraulic lifting apparatus of crane

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100439231C (en) * 2004-09-04 2008-12-03 容海因里希股份公司 Device for the emergency lowering of a load-carrying means for a stacker truck
CN102131684A (en) * 2008-08-28 2011-07-20 卡特彼勒公司 Control system and method for braking a hydrostatic drive machine
CN102131684B (en) * 2008-08-28 2014-03-19 卡特彼勒公司 Control system and method for braking a hydrostatic drive machine
CN103857616A (en) * 2011-09-27 2014-06-11 力至优三菱叉车株式会社 Forklift
CN103857616B (en) * 2011-09-27 2016-01-06 力至优三菱叉车株式会社 Fork truck
US10023451B2 (en) 2011-09-27 2018-07-17 Mitsubishi Nichiyu Forklift Co., Ltd. Forklift
CN105197840A (en) * 2015-04-16 2015-12-30 上海市闸北区物流工程技术研究所 Electric control hydraulic driving system for industrial vehicle
CN105197840B (en) * 2015-04-16 2018-11-20 上海市闸北区物流工程技术研究所 A kind of Electro-hydraulic drive system for industrial vehicle
CN106044561A (en) * 2016-08-18 2016-10-26 甘培嘉 Hydraulic lifting apparatus of crane
CN106044561B (en) * 2016-08-18 2018-05-18 苏昭缄 A kind of hydraulic hoist unit of crane

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