CN100586831C - Frequency-changing hydraulic elevator system - Google Patents
Frequency-changing hydraulic elevator system Download PDFInfo
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- CN100586831C CN100586831C CN200710094095A CN200710094095A CN100586831C CN 100586831 C CN100586831 C CN 100586831C CN 200710094095 A CN200710094095 A CN 200710094095A CN 200710094095 A CN200710094095 A CN 200710094095A CN 100586831 C CN100586831 C CN 100586831C
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Abstract
The invention discloses a frequency conversion hydraulic elevator system, consisting of a leakage measurement system, a leakage estimating system and a pressure adjusting system; wherein, the leakagemeasurement system consists of a first pressure transmitter, an oil temperature sensor, a motor side encoder and an elevator car side encoder; the practical leakage quantity of the hydraulic system isdirectly measured during the running process of the elevator; furthermore, corresponding leakage quantity is memorized according to the conditions of oil temperature and load during the measurement process; the leakage estimating system consists of a second pressure transmitter and an oil temperature sensor; leakage quantity parameters under the corresponding conditions of oil temperature and load memorized by the leakage measurement system are extracted, the leakage quantity of the hydraulic system is estimated and the leakage is compensated before the elevator is started; the pressure adjusting system consists of the first pressure transmitter and the second pressure transmitter; during the starting process of the elevator, the rotation speed of the hydraulic pump is adjusted graduallyso as to lead the oil pressure at the outlet of the hydraulic pump and the oil pressure in the oil cylinder to achieve balance. The frequency conversion hydraulic elevator system can reduce the speedimpact and pressure impact during the starting process of the frequency conversion hydraulic elevator and leads to stable and quick starting process.
Description
Technical field
The present invention relates to a kind of hydraulic elevator system, this is a kind of by variable voltage variable frequency speed governing drive motor, before elevator starts, make the rate of discharge of Hydraulic Pump just in time can compensate the leakage of hydraulic efficiency pressure system, and Hydraulic Pump outlet oil pressure and load oil pressure balance, thereby the frequency-changing hydraulic elevator system of realization lift car smooth starting.
Background technology
Motor speed control system is applied in the hydraulic elevator system, can improve its efficient to a great extent, is considered to a kind of energy-saving hydraulic elevator device.Thereby a kind of constant flow rate Hydraulic Pump provides pressure oil to move up and down car by an electromagnetic valve to oil cylinder, above-mentioned electromagnetic valve is usually as unidirectional stop valve operation, in case the descending generation safety misadventure of elevator, but when electromagnetic valve is subjected to electric magnetization, but reverse-conducting makes elevator descending.Because the deadweight of car, the pressure oil in oil cylinder and the pipeline thereof is under certain oil pressure constantly.When said pump during by an Induction Motor-Driven, speed control system is regulated rotating speed of motor by the variable voltage variable frequency technology in the scope of broad, move up and down car thereby change hydraulic pressure delivery side of pump oil mass.
Yet in common hydraulic efficiency pressure system, the leakage of oil is that inevitably therefore, the actual speed of rotating speed of motor and car is nonsynchronous; A Hydraulic Pump is promptly arranged at low-speed running, but the scope that car does not start.When elevator turns round according to start command signal, produced the problem of Vibration on Start-up and human discomfort.
In order to overcome this problem, method the earliest is to export oil in advance according to corresponding spillage, or in other words, a low speed is started motor but the bias model signal and that do not start car to drive the model signals of car superimposed, leakage is compensated just, the car smooth starting.
According to this kind method, in order to reduce bias model signal that Vibration on Start-up obtains is to serve as with reference to determining with the spillage under certain load and the uniform temperature, and the oil leakage quantity under the real-world operation state is the calculating that the leakage of oil amount of the temperature of load, fuel tank according to car and each Hydraulic Pump, valve is done.But the leakage of oil amount of Hydraulic Pump changes with the difference in the Hydraulic Pump manufacturing, and along with the time changes gradually, the leakage compensation of oily gentle load is difficult to draw a precise analytic model.Therefore, calculating the leakage of oil amount exactly is difficult to reduce Vibration on Start-up; Because the bias model signal is definite by calculating indirectly, thereby the effect of reduction Vibration on Start-up is restricted.Another kind method provides the means that start compensation, the oil pressure of hydraulic pressure delivery side of pump oil pressure and oil cylinder one side is complementary (differential pressure is a predetermined value), restarts elevator.Start compensating device poor based on the output oil pressure of the oil pressure of oil cylinder and Hydraulic Pump, that is to say that a bias model of the inlet outlet pressure differential of boiler check valve compensates.Above-mentioned pressure reduction is the value that records according to actual, is not subjected to the influence of fluctuations of each Hydraulic Pump leakage of oil amount.As long as it is any to the feeling Vibration on Start-up of human body that car does not produce, pressure reduction can be set at a negative code, also can be set at zero.Chinese invention patent specification sheets CN1024338C (Granted publication day: on April 2nd, 1994) disclose said method.
Chinese invention patent specification sheets CN1105074C (Granted publication day: on April 9th, 2003) disclose another kind of pressure compensated method, this method relies on an oil cylinder control cock to regulate, when the car low cruise, adjusting is finished (with the leakage of compensation hydraulic efficiency pressure system) by valve cell, when the car high-speed cruising, the speed setting of car is finished by the adjusting to motor.
Chinese invention patent specification sheets CN1228229C (Granted publication day: on November 23rd, 2005) disclose a kind of control method of pressure closed loop, this method is measured the oil pressure of hydraulic pressure delivery side of pump oil pressure and oil cylinder respectively by two pressure transformers, feedback forms a pressure circle system, the spillage of direct compensation hydraulic efficiency pressure system is impacted with the startup that prevents elevator.In the exit of Hydraulic Pump one energy storage is arranged in addition,, make pressure control more stable, start more steady to improve the math modeling of pressure circle system.
In the hydraulic elevator system technical scheme of all disclosed employing bunchers, the problem that exists is common, promptly because the oil leakage in the system, make that the actual speed of rotating speed of motor and elevator is nonsynchronous, this asynchrony phenomenon shows and is the vibration of elevator and impact in the start-up course.The purpose of these inventions all is for this impact being reduced to minimum degree.Present two aspects of this collimeter, one is velocity shock, Hydraulic Pump is the full remuneration leakage flow in advance; Another is a compression shock, and promptly must make the hydraulic valve two ends reach equilibrium of pressure could the rate of load application curve.Two conditions of the fine compensation of hydraulic system leakage and the equilibrium of pressure of valve must satisfy simultaneously, otherwise the elevator startup must have greater impact.Velocity shock when the method that compensates oil leakage quantity indirectly by bias model has only been considered to start, the not compression shock of taking into account system, and leakage compensation can not be applicable to the situation of variations such as load, oil temperature, Hydraulic Pump Mismachining tolerance.Adopt pressure regulating method to start compensation higher precision can be provided, but pressure control is a dynamic process, the rotating speed of Hydraulic Pump constantly changes in this process, when reaching equilibrium of pressure point, the flow of Hydraulic Pump output might not the full remuneration spillage, causes velocity shock, in addition during converter plant work, the signal of pressure transformer is interfered easily, therefore only uses pressure controlled reliability not high.
Summary of the invention
The technical problem to be solved in the present invention provides a kind of frequency-changing hydraulic elevator system, reduces velocity shock and compression shock simultaneously when it can make frequency-changing hydraulic elevator start, and starts steady, quick.
For solving the problems of the technologies described above, frequency-changing hydraulic elevator system of the present invention comprises motor side coder, cage side coder;
Hydraulic Pump is by electromagnetic valve and Hydraulic Pump bonded assembly oil cylinder; Be used for first pressure transformer that the detective liquid press pump exports oil pressure, be used to detect second pressure transformer of oil cylinder oil pressure; Hydraulic Pump, oil cylinder are connected with fuel tank by valve respectively;
The oil temperature sensor that is used for detective liquid pressing system hydraulic fluid temperature;
Wherein: described first pressure transformer, oil temperature sensor, motor side coder and cage side coder are formed the leakage measuring instrumentation system, in running process of elevator, directly measure the actual spillage of hydraulic efficiency pressure system, and the oil when measuring is warm, loading condition is preserved corresponding spillage;
Described second pressure transformer, oil temperature sensor are formed the leakage estimating system, and the corresponding oily temperature that the described leakage measuring instrumentation of extraction system preserves before elevator starts, the spillage parameter under the loading condition are estimated the hydraulic system leakage amount, before starting leakage are compensated; When elevator moves for the first time,, calculate the acquisition spillage by bias model according to the oil temperature of oil temperature sensor measurement and the oil cylinder oil pressure of second pressure transmitter measurement;
Described first and second pressure transformer decomposition pressure control system, in the elevator start-up course, progressively the rotating speed of regulator solution press pump makes the oil pressure of hydraulic pressure delivery side of pump oil pressure and oil cylinder reach balance; The flow that Hydraulic Pump (4) is exported just in time can compensate the leakage of hydraulic efficiency pressure system.
Compared with prior art, have following remarkable result: elevator is in operational process, the spillage of hydraulic efficiency pressure system can directly be measured by the leakage measuring instrumentation system, and oil temperature, loading condition when measuring preserve corresponding spillage, obtains specific hydraulic system spillage parameter accurately; When elevator starts, by leaking estimating system, extract the spillage parameter under current oil temperature, the loading condition by the leakage measuring instrumentation system, before starting leakage is compensated the velocity shock when the minimizing elevator starts; By the effect (promptly passing through the progressively rotating speed of regulator solution press pump of special algorithm) of pressure regulating system, regulator solution press pump outlet oil pressure is the load oil pressure, the compression shock when reducing the elevator startup in start-up course.Can when hydraulic elevator starts, reduce velocity shock and compression shock simultaneously like this, make startup more steady, fast.
Description of drawings
The present invention is further detailed explanation below by accompanying drawing and the specific embodiment:
Fig. 1 is frequency-changing hydraulic elevator system one an embodiment scheme drawing of the present invention;
Fig. 2 is a frequency-changing hydraulic elevator system speed curve diagram shown in Figure 1, wherein, (a) is speed curve diagram in the ascending for elevator process, (b) is the speed curve diagram in the descending process of elevator.
The specific embodiment
Referring to shown in Figure 1, described hydraulic elevator system comprises elevator hoistways 13, be embedded in the oil cylinder 11 at elevator hoistways 13 pit places, inject the pressure oil of oil cylinder 11, piston 14 by the pressure oil support, be fixed on the car 12 of piston 14 upper ends, motor 2, Hydraulic Pump 4, electric life controller 1 that links to each other with motor 2 and motor side coder 3, the electromagnetic valve 10 that links to each other with oil cylinder 11 with Hydraulic Pump 4, first pressure transformer 7 that is used for the outlet oil pressure of detective liquid press pump 4, be used to detect second pressure transformer 8 of the oil pressure of oil cylinder 11, be used to measure the cage side coder 9 of car speed, be used to measure the oil temperature sensor 17 of hydraulic efficiency pressure system oil temperature, and the by pass valve 5 that connects Hydraulic Pump 4 and fuel tank 6, the manual oil drain valve 15 of connection oil cylinder 11 and fuel tank 6.
Fig. 2 (a) and (b) are respectively up, the descending run curves of hydraulic elevator, and at the elevator normal operation period, the flow Q of Hydraulic Pump 4 is divided into 2 parts, and a part enters oil cylinder 11, form the speed Vc of car 12; Another part flow back into fuel tank 6 by the movable parts of Hydraulic Pump 4 and the gap between non-movable parts, and this part is internal leakage Qx.Therefore the speed command of motor 2 is stacks of car speed and internal leakage.
According to Fig. 2, the start-up course that can describe hydraulic elevator is as follows: when apparatus for controlling elevator receives the command signal that needs ascending for elevator, electric life controller 1 sends instruction and allows motor 2 to start.This moment, the oil pressure P1 in Hydraulic Pump 4 exits was little more than the oil pressure P2 at oil cylinder 11 places; If this moment is with regard to the rate of load application curve, because the leakage of hydraulic efficiency pressure system, motor 2 rotating speeds and car 12 speed asynchronous exists a motor 2 to turn round, but the zone that car 12 does not start; When motor 2 reached certain rotating speed, this rotating speed was enough to compensate the leakage of hydraulic efficiency pressure system, and then oil pressure P1 will increase to the check valve spool that can back down electromagnetic valve 10, make car 12 upward movements.But motor 2 has bigger speed and acceleration/accels at this moment, and causing car 12 to have bigger startup acceleration/accel, people to ride in the car 12 when starting will have uncomfortable sensation.If before velocity curve loads, a pre-boot process is arranged, the oil pressure P1 in Hydraulic Pump 4 exits is risen to oil cylinder 11 places oil pressure P2 near, just in time can compensate the leakage of hydraulic efficiency pressure system simultaneously, then the stationary performance that starts of elevator will increase greatly.
Therefore to make two conditions of elevator smooth starting be, fine compensation internal leakage and Hydraulic Pump 4 exit oil pressure and oil cylinder 11 oil pressure balances, these two conditions are indispensable.Yet the spillage of oil is not only the relevant parameter of oily gentle load (oil pressure), and each Hydraulic Pump has different spillages.(wherein P is a Hydraulic Pump outlet oil pressure to the spillage bias model available functions f of hydraulic efficiency pressure system for P, T) expression, and T is the oil temperature.The spillage of this function representation hydraulic efficiency pressure system is relevant with the pressure-flow characteristic of viscosity-temperature characteristics, the pump of oil, the viscosity-temperature characteristics difference of the hydraulic oil of the different trades mark or producer, the pressure-flow characteristic of different Hydraulic Pumps is also different, and the formula that embodies of function is difficult to describe.In addition, this function is also relevant with the processing quality of fit of Hydraulic Pump; Simultaneously relevant with the abrasion loss of Hydraulic Pump, be time dependent therefore.As seen Gu Ding compensation can not be satisfied system requirements.In the system of practical application, it also is almost can't realize that the theory of spillage is calculated.Even compensate the influence of hydraulic efficiency pressure system oil pressure, oil temperature by matched curve, but,, then need the on-the-spot adjustment data of commissioning staff owing to the working accuracy of Hydraulic Pump and worn-down reason cause leaking over time for the elevator of batch manufacturing, work capacity is very big, also can't accomplish fine compensation.
The present invention can directly measure the speed Vc of car 12 by cage side coder 9.According to the relation between the rotating speed Vm of the speed Vc of car 12 and motor 2, can calculate the spillage of hydraulic efficiency pressure system.
When up: v
x(P, T)=Kf (P, T)=Cv
m-v
c(1)
When descending: v
x(P, T)=Kf (P, T)=v
c-Cv
m(2)
Wherein: Vm is a motor speed, and Vc is a car speed, and two speed can be measured the hydraulic efficiency pressure system speed ratio that C calculates for the theoretical discharge capacity according to Hydraulic Pump with motor side coder 3 and cage side coder 9 respectively.P is the pump discharge oil pressure, and T is the oil temperature.Because oily temperature is slowly to change, can accurately measure by oil temperature sensor 17, Hydraulic Pump outlet oil pressure is measured by first pressure transformer 7.And concerning the process that travels at the uniform speed of any hydraulic elevator, its load (hydraulic efficiency pressure system oil pressure) remains unchanged, and oil temperature (oil viscosity) is constant substantially.Therefore can both self-measuring during the elevator each run go out the spillage under relevant temperature and the loading condition.
Yet, find in the actual calculation that the hydraulic efficiency pressure system speed ratio C that calculates according to the theoretical discharge capacity of Hydraulic Pump is inaccurate, and finally causes the calculating of spillage to have than mistake.Order:
C′＝C+C
e (3)
In the formula: C ' is for calculating used hydraulic efficiency pressure system speed ratio, and Ce is the error of C ' and actual speed ratio C, the spillage v ' that then calculates
x:
When up: v '
Xup(P, T)=C ' v
m-v
Car=(C+C
e) v
m-v
Car=v
x+ C
eV
m(4)
When descending: v '
Xdn(P, T)=v
Car-C ' v
m=v
Car-(C+C
e) v
m=v
x-C
eV
m(5)
Therefore, the spillage of actual measurement has the error of a Ce*Vm, investigate above two formulas, the spillage error of discovery uplink and downlink is the is-symbol relation just in time, if with the once descending and once up spillage addition under same oil pressure and the oily temperature condition, just offset this error, thereby calculated the spillage of hydraulic efficiency pressure system exactly.
All above measurements are all finished in running process of elevator automatically, do not need manual intervention, and measure and calculate according to The actual running results, go in the hydraulic elevator system of any specification, even in some occasion such as hydraulic efficiency pressure system speed ratio inaccuracy, still can accurately calculate the spillage of hydraulic efficiency pressure system.Behind the each run, spillage result and the oily gentle oil pressure condition thereof measured are preserved simultaneously, form the spillage data sheet.
Final data is preserved and is carried out as follows, and the oil temperature is divided into M zone from 15 ℃～65 ℃ (these are the effective working oil temperature of hydraulic elevator).For example, divide a zone every 5 ℃, be divided into and be totally 11 zones; Load is divided into N zone, for example from zero load, 25% load, semi-load, 75% load, be fully loaded with and be divided into 5 zones; And divide up district, two zones of descender; Amount to M * N * 2 data point, these data points all are kept among the EEPROM.After each elevator operation, according to the oily temperature and the load of this time operation of measuring, the hydraulic system leakage amount v ' that calculates of software the most at last
xBe saved in the corresponding data point.And when oily gentle load is not on the data point of setting, be 35% load as the charge capacity of actual measurement, then it is converted by approach based on linear interpolation on 25% the POL.
Leaking estimating system works as follows, when elevator moves for the first time, because the leakage measuring instrumentation system does not set up the spillage data sheet, oil cylinder 11 oil pressure that oil is warm and second pressure transformer 8 is measured that spillage is measured according to oil temperature sensor 17, calculate the acquisition spillage by bias model, in case after the elevator operation, the leakage measuring instrumentation system has promptly set up the spillage data under corresponding oil temperature, the oil pressure condition, leak estimating system and search the spillage data sheet, finish the estimation of spillage.For example actual measurement oil temperature, oil pressure are respectively 33 ℃/35% load before the elevator operation, then by searching the spillage data point of 30 ℃/25% load among the EEPROM, 30 ℃/50% load, 35 ℃/50% load, 35 ℃/25% load, and the spillage by approach based on linear interpolation estimation 33 ℃/35% load.
Having estimated the spillage of hydraulic elevator exactly, only is the first step that hydraulic elevator starts, the compression shock when starting in order to reduce, also the outlet oil pressure of Hydraulic Pump 4 must be risen near the oil pressure of oil cylinder 11, make both reach balance by oil pressure, when hydraulic valve 10 is opened, just do not have impact.Measure the oil pressure of Hydraulic Pump 4 outlet oil pressure, second pressure transformer, 8 measurement oil cylinders 11 by first pressure transformer 7, the common pressure regulating system of forming, when elevator started, progressively the rotating speed of regulator solution press pump 4 made the outlet oil pressure of Hydraulic Pump 4 and oil cylinder 11 oil pressure reach balance.
In pressure controlled process, the rotating speed of control motor 2, the oil pressure in Hydraulic Pump 4 exits is progressively risen from zero pressure, when the oil pressure in Hydraulic Pump 4 exits during far below oil cylinder 11 oil pressure, Hydraulic Pump 4 delivery rates of being realized by the rotating speed of motor 2 are not limited to the hydraulic system leakage amount of aforementioned estimation, can regulate the rotating speed of motor 2 according to both difference of pressures, the rotating speed of motor 2 even temporarily can surpass the required rotating speed operation of spillage compensation (because this moment, Hydraulic Pump 4 exit oil pressure were lower than oil cylinder 11 oil pressure, car 12 can not move), at high speed promotes the oil pressure in Hydraulic Pump 4 exits.When Hydraulic Pump 4 exit oil pressure during near oil cylinder 11 oil pressure, the rotating speed of control motor 2, make the hydraulic system leakage amount running of Hydraulic Pump 4, guarantee that the flow of Hydraulic Pump 4 outputs when reaching equilibrium of pressure just in time can be offset leakage, does not have velocity shock and does not have compression shock yet during startup with aforementioned estimation.
Claims (4)
1, a kind of frequency-changing hydraulic elevator system comprises: motor side coder (3), cage side coder (9);
Hydraulic Pump (4) is by electromagnetic valve (10) and Hydraulic Pump (4) bonded assembly oil cylinder (11); Be used for first pressure transformer (7) that detective liquid press pump (4) exports oil pressure, be used to detect second pressure transformer (8) of oil cylinder (11) oil pressure; Hydraulic Pump (4), oil cylinder (11) are connected with fuel tank (6) by valve respectively;
The oil temperature sensor (17) that is used for detective liquid pressing system hydraulic fluid temperature;
It is characterized in that: described first pressure transformer (7), oil temperature sensor (17), motor side coder (3) and cage side coder (9) are formed the leakage measuring instrumentation system, in running process of elevator, directly measure the actual spillage of hydraulic efficiency pressure system, and the oil when measuring is warm, loading condition is preserved corresponding spillage;
Described second pressure transformer (8), oil temperature sensor (17) are formed the leakage estimating system, the corresponding oil temperature that the described leakage measuring instrumentation of extraction system preserves before elevator starts, the spillage parameter under the loading condition, estimation hydraulic system leakage amount compensates leakage before starting; When elevator moves for the first time,, calculate the acquisition spillage by bias model according to the oil temperature of oil temperature sensor measurement and the oil cylinder oil pressure of second pressure transmitter measurement;
Described first and second pressure transformer (7), (8) decomposition pressure control system, in the elevator start-up course, the rotating speed of regulator solution press pump (4) progressively makes the outlet oil pressure and the oil cylinder of Hydraulic Pump (4)
(11) oil pressure reaches balance; The flow that Hydraulic Pump (4) is exported just in time can compensate the leakage of hydraulic efficiency pressure system.
2, frequency-changing hydraulic elevator system as claimed in claim 1 is characterized in that: described leakage measuring instrumentation system is calculated as follows the spillage of hydraulic efficiency pressure system:
Wherein, v '
Xup(P, the spillage of hydraulic efficiency pressure system when T) being ascending for elevator, v '
Xdn(P T) is the spillage of elevator hydraulic efficiency pressure system when descending, and P is a Hydraulic Pump outlet oil pressure, and T be that oil is warm.
3, frequency-changing hydraulic elevator system as claimed in claim 1 is characterized in that: behind the elevator each run, described leakage measuring instrumentation system preserves spillage and the gentle loading condition of cooresponding oil thereof measured simultaneously, forms the spillage data sheet;
Described spillage data sheet is formed as follows: oily temperature is divided into M zone, and load is divided into N zone, and divides up district, two operation areas of descender, amounts to M * N * 2 data point.
4, frequency-changing hydraulic elevator system as claimed in claim 1, it is characterized in that: after the elevator operation, the leakage measuring instrumentation system has set up the spillage data under corresponding oil temperature, the loading condition, leaks estimating system and searches the spillage data sheet, finishes the estimation of spillage.
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| CN200710094095A CN100586831C (en) | 2007-09-25 | 2007-09-25 | Frequency-changing hydraulic elevator system |
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Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102320510A (en) * | 2011-09-08 | 2012-01-18 | 宁波市胜源技术转移有限公司 | Hydraulic elevator |
| CN106144794B (en) * | 2015-04-02 | 2018-09-28 | 西屋电气（香港）有限公司 | A kind of hydraulic elevator control system and control method |
| CN106315356A (en) * | 2016-09-19 | 2017-01-11 | 中都国脉电梯有限公司 | Hydraulic drive ground floor elevator |
| CN109931255B (en) * | 2019-04-02 | 2023-10-20 | 哈工新欧(岳阳)测控装备有限公司 | Plunger pump abrasion evaluation system and method based on leakage test and pump shell temperature test |
| CN110173485B (en) * | 2019-05-23 | 2020-06-05 | 山东临工工程机械有限公司 | Method and device for controlling hammering frequency of breaking hammer |
| CN112392088A (en) * | 2019-08-15 | 2021-02-23 | 山东临工工程机械有限公司 | Breaking hammer control method and device |
| CN110939617A (en) * | 2019-12-12 | 2020-03-31 | 福建工程学院 | Hydraulic actuator position control method without displacement sensor |
| CN113979250B (en) * | 2021-10-29 | 2023-03-24 | 杭州赛翔科技有限公司 | Hydraulic elevator starting and stopping speed regulation control method based on oil temperature |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1054949A (en) * | 1990-03-16 | 1991-10-02 | 株式会社日立制作所 | Hydraulic elevator |
| CN1220644A (en) * | 1997-02-06 | 1999-06-23 | 贝林格液压设备有限公司 | Method and device for controlling hydraulic lift |
| CN1322668A (en) * | 2001-06-14 | 2001-11-21 | 浙江大学 | Energy-storing power economizer for varying frequency driven hydraulic elevator |
| CN2512757Y (en) * | 2001-12-12 | 2002-09-25 | 浙江大学 | Device by using calculating flow feedback to control hydraulic lift |
| CN1413900A (en) * | 2001-10-25 | 2003-04-30 | 上海三菱电梯有限公司 | Hydraulic elevator system of improvement running performance by accumulator |
-
2007
- 2007-09-25 CN CN200710094095A patent/CN100586831C/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1054949A (en) * | 1990-03-16 | 1991-10-02 | 株式会社日立制作所 | Hydraulic elevator |
| CN1220644A (en) * | 1997-02-06 | 1999-06-23 | 贝林格液压设备有限公司 | Method and device for controlling hydraulic lift |
| CN1322668A (en) * | 2001-06-14 | 2001-11-21 | 浙江大学 | Energy-storing power economizer for varying frequency driven hydraulic elevator |
| CN1413900A (en) * | 2001-10-25 | 2003-04-30 | 上海三菱电梯有限公司 | Hydraulic elevator system of improvement running performance by accumulator |
| CN2512757Y (en) * | 2001-12-12 | 2002-09-25 | 浙江大学 | Device by using calculating flow feedback to control hydraulic lift |
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