CN111807227A - Intelligent distribution method for power of engine of port mobile crane - Google Patents

Intelligent distribution method for power of engine of port mobile crane Download PDF

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CN111807227A
CN111807227A CN202010667361.7A CN202010667361A CN111807227A CN 111807227 A CN111807227 A CN 111807227A CN 202010667361 A CN202010667361 A CN 202010667361A CN 111807227 A CN111807227 A CN 111807227A
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CN111807227B (en
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金建
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Nantong Rainbow Heavy Machineries Co Ltd
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Nantong Rainbow Heavy Machineries Co Ltd
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B66C13/20—Control systems or devices for non-electric drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/087—Control strategy, e.g. with block diagram

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  • Mechanical Engineering (AREA)
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Abstract

The invention discloses an intelligent distribution method for the power of a port mobile crane engine, which calculates the lifting request speed v according to the lifting action request value of a handlehCurrent request value C of hydraulic pump of slewing mechanismsAnd the current request value C of the hydraulic pump of the luffing mechanismb(ii) a Calculating the lifting request power PhCalculating the requested power P of the amplituderbAnd requested power P of slewingrs(ii) a Calculating an additional power demand P in excess of engine demandex(ii) a Calculating the maximum allowable power P of a single mechanismmhl、Pmbl、Pmsl(ii) a Calculating the maximum lifting working speed v according to the maximum allowable power requirementmhMaximum operating current C of revolutionmsAmplitude variation maximum working current CmbAnd finally given. The invention greatly reduces the model selection of the engine of the port mobile overhead crane, can fully play the maximum operation efficiency of a single mechanism or two mechanisms under the working condition that three mechanisms are not required to be linked, and ensures that the three mechanisms can play the efficiency in the maximum proportion under the working condition that three mechanisms are required to be linked.

Description

Intelligent distribution method for power of engine of port mobile crane
Technical Field
The invention relates to an intelligent power distribution method, in particular to an intelligent power distribution method for a port mobile crane engine, and belongs to port equipment.
Background
The port moves the advantage that overhead crane compares in rail mounted loop wheel machine: the mobility is strong, the trafficability characteristic is high, and the transition is convenient. Most of the harbor mobile overhead crane projects are driven by an engine, and the power systems of the harbor mobile overhead crane are mainly the engine, a transfer case and a generator. Considering the comprehensive factors of all aspects, a certain gap exists between the actual maximum output power of the engine and the maximum use power of the whole engine. In certain special cases, the engine may be rapidly slowed down to cause a voltage drop or engine shutdown because of an inability to meet the plant instantaneous power request. The power requirement of the whole engine determines the power selection of the engine, but simultaneously, the maximum instantaneous power of the engine cannot meet the requirements of the weight control, the space control and the cost control of the equipment, so that the engine is blocked or stalled.
Disclosure of Invention
The invention aims to provide an intelligent distribution method for the power of the engine of the port mobile crane, which can give full play to the maximum operating efficiency of each mechanism.
In order to solve the technical problems, the technical scheme adopted by the invention is as follows:
an intelligent distribution method for the power of an engine of a port mobile crane is characterized by comprising the following steps:
the method comprises the following steps: reading engine real-time torque percentage TactPercent idle torque TidleAcceleration and deceleration time t for liftingh；
Step two: read handle lifting action request value JrAmplitude variation request value JbRequested value J of turning operations；
Step three: calculating the lifting request speed v according to the lifting action request value of the handlehCurrent request value C of hydraulic pump of slewing mechanismsAnd the current request value C of the hydraulic pump of the luffing mechanismb；
Step four: calculating the lifting request power PhCalculating the flow q according to the direct proportion relation between the flow and the current of the rotation and amplitude variation request current, recording the pressure P of the rotation pump head, and calculating the amplitude variation request power PrbAnd requested power P of slewingrs；
Step five: by raising the requested power PhRequested power P of variable amplituderbRequested power of revolution PrsAnd the current power P usedactSum of the sum and total power P of the enginetCalculating a ratio s of the total power of the engine, if the ratio s is less than 1, the maximum power of the engine is not exceeded, and directly giving a request value; if the ratio s is equal to or greater than 1 and the maximum engine power has been exceeded, an additional power demand P is calculated that exceeds the engine demandex；
Step six: according to the speed proportional relation of the three mechanisms, the extra power requirement of the corresponding proportion is proportionally subtracted, and when a single mechanism acts, the limit power allowed by lifting is PmhThe limit power allowed by amplitude variation is PmbAnd the limit power allowed by the revolution is PmsCalculating the maximum allowable power P of a single mechanismmhl、Pmbl、Pmsl；
Step seven: calculating the maximum lifting working speed v according to the maximum allowable power requirementmhMaximum operating current C of revolutionmsAmplitude variation maximum working current CmbAnd finally given.
Further, the third step is specifically
According to the request value J of the handle lifting actionrCalculating the speed of the lifting request according to the formula (1)
vh，
Figure BDA0002580974390000021
Wherein v ishFor requesting speed of lifting, JmaxMaximum value of the handle, JrRequesting value of lifting action for handle, vmaxThe maximum speed value corresponding to the maximum value of the handle;
calculating the current request value C of the hydraulic pump of the slewing mechanism according to the formula (2)sAnd the current request value C of the hydraulic pump of the luffing mechanismb；
Figure BDA0002580974390000031
Where C is the current request value, JmaxMaximum value of the handle, JrRequesting value for lifting handle, CmaxIs the maximum value of the current, CminIs the current minimum; cmaxAnd CminAre known parameter values.
Further, the fourth step is specifically
Calculating acceleration time t to a lifting request by formula (3)r；
Figure BDA0002580974390000032
Wherein, JmaxMaximum value of the handle, JrRequesting a value for the lifting action of the handle, thAccelerating and decelerating time for lifting;
calculating the acceleration a of the hoisting mechanism by the formula (4)h；
υh＝ah*tr(4)
Calculating the force F required by the load lifting of the lifting mechanism by the formula (5)h；
Fh-mg＝m*ah(5)
Wherein m is the current hoisting weight of the hoisting mechanism, and g is the gravity acceleration;
calculating the lifting request power P by the formula (6)h；
Figure BDA0002580974390000033
Wherein v ishIs the speed of the load, ηhThe transmission efficiency of a mechanical system of a hoisting mechanism is improved;
obtaining a formula (8) through the deformation of the formula (7);
Figure BDA0002580974390000041
Figure BDA0002580974390000042
wherein, P0For delivery of power from hydraulic pumps, p0For delivery of pressure, q, from a hydraulic pump0Is the flow rate of the hydraulic pump,
η0the system transmission efficiency; prefTo request power, CrefTo request control of current, CmaxIs the maximum value of the current, CminIs the minimum value of current, q is the rated displacement of a single circle of the pump, n is the rotating speed of the pump, p is the pressure of the pump, and eta is the mechanical system transmission efficiency of the mechanism;
calculating the request power P of amplitude variation through a formula (8)r_bAnd requested power P of slewingr_s。
Further, the fifth step is specifically that
Calculating the current consumed power P of the engine through a formula (9)idle；
Pidle＝Pt*Tidle(9)
Wherein, PtIs the total power of the engine, TidleIs the idle torque percentage;
by raising the requested power PhRequested power P of variable amplituderbRequested power of revolution PrsAnd the current power P usedactSum of the sum and total power P of the enginetCalculating a ratio s to the total power of the engine;
Figure BDA0002580974390000043
wherein, PrhIs a power P of a lifting requesth；
If the ratio s is less than 1, the maximum power of the engine is not exceeded, and a request value is directly given;
if the ratio s is greater than or equal to 1, the maximum engine power has been exceeded, at which point an additional power demand P is calculated that exceeds the engine demandex；
Pex＝Prh+Prb+Prs+Pidle-Pt(11)。
Further, the sixth step is specifically that
Calculating the percentage S of the currently used power of a certain mechanism to the maximum used power through the formula (12)0；
Figure BDA0002580974390000051
Wherein, PactThe current power value, P, of the mechanismmaxPower limit values are used for this mechanism;
according to the speed proportional relation of the three mechanisms, the extra power requirement of the corresponding proportion is proportionally subtracted, and when a single mechanism acts, the limit power allowed by lifting is PmhThe limit power allowed by amplitude variation is PmbAnd the limit power allowed by the revolution is PmsCalculating the maximum allowable power P of a single mechanismmhl、Pmbl、Pmsl；
Figure BDA0002580974390000052
Wherein, PmhFor a single mechanism currently allowing maximum power, PrhPower requested for a single authority, ShFor lifting ratio, SbIn order to vary the amplitude ratio, SsTo a revolution ratio, PexIs the requested power that exceeds the total power of the engine.
Further, the seventh step is specifically
Reversely calculating the maximum lifting working speed v according to the formula (6)mh；
Figure BDA0002580974390000053
Calculating the maximum rotary working current C according to the formula (15)msAnd amplitude variation maximum working current Cmb；
Figure BDA0002580974390000054
The hoisting mechanism realizes frequency conversion driving, namely, the speed output of the motor is limited, hydraulic pressure, namely, the current output of the hydraulic pump is limited, and the power output is limited by limiting the current output and the speed output, so that the intelligent power distribution is realized.
Compared with the prior art, the invention has the following advantages and effects:
according to the intelligent distribution method for the engine power of the port mobile crane, the model selection of the engine of the port mobile overhead crane can be greatly reduced through a power distribution technology, the weight of the whole machine is reduced, the manufacturing cost of the product is reduced, and the market competitiveness of the product is increased; under the working condition that three mechanisms are not required to be linked, the single mechanism or the two mechanisms can fully exert the maximum operation efficiency, and the efficiency of the three mechanisms can be exerted in the maximum proportion under the working condition that the three mechanisms are required to be linked.
Drawings
FIG. 1 is a flow chart of the intelligent distribution method of the power of the harbor mobile crane engine.
Fig. 2 is a control transmission schematic diagram of the intelligent distribution method of the power of the harbor mobile crane engine.
Detailed Description
To elaborate on technical solutions adopted by the present invention to achieve predetermined technical objects, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, it is obvious that the described embodiments are only partial embodiments of the present invention, not all embodiments, and technical means or technical features in the embodiments of the present invention may be replaced without creative efforts, and the present invention will be described in detail below with reference to the drawings and in conjunction with the embodiments.
As shown in fig. 1 and fig. 2, the intelligent distribution method for the power of the harbor mobile crane engine of the invention comprises the following steps:
the method comprises the following steps: reading engine real-time torque percentage TactPercent idle torque TidleAcceleration and deceleration time t for liftingh；
Step two: read handle lifting action request value JrAmplitude variation request value JbRequested value J of turning operations；
Step three: calculating the lifting request speed v according to the lifting action request value of the handlehCurrent request value C of hydraulic pump of slewing mechanismsAnd the current request value C of the hydraulic pump of the luffing mechanismb；
According to the request value J of the handle lifting actionrCalculating the speed of the lifting request according to the formula (1)
vh，
Figure BDA0002580974390000071
Wherein v ishFor requesting speed of lifting, JmaxMaximum value of the handle, JrRequesting value of lifting action for handle, vmaxThe maximum speed value corresponding to the maximum value of the handle; j. the design is a squaremaxFor a known parameter, vmaxObtained by table lookup.
Calculating the current request value C of the hydraulic pump of the slewing mechanism according to the formula (2)sAnd the current request value C of the hydraulic pump of the luffing mechanismb；
Figure BDA0002580974390000072
Where C is the current request value, JmaxMaximum value of the handle, JrRequesting value for lifting handle, CmaxIs the maximum value of the current, CminIs the current minimum; cmaxAnd CminAre known parameter values.
Step four: calculating the lifting request power PhCalculating the flow q according to the direct proportion relation between the flow and the current of the rotation and amplitude variation request current, recording the pressure P of the rotation pump head, and calculating the amplitude variation request power PrbAnd requested power P of slewingrs；
Calculating acceleration time t to a lifting request by formula (3)r；
Figure BDA0002580974390000073
Wherein, JmaxMaximum value of the handle, JrRequesting a value for the lifting action of the handle, thAccelerating and decelerating time for lifting;
calculating the acceleration a of the hoisting mechanism by the formula (4)h；
υh＝ah*tr(4)
Calculating the force F required by the load lifting of the lifting mechanism by the formula (5)h；
Fh-mg＝m*ah(5)
Wherein m is the current hoisting weight of the hoisting mechanism, and g is the gravity acceleration;
calculating the lifting request power P by the formula (6)h；
Figure BDA0002580974390000081
Wherein v ishIs the speed of the load, ηhThe transmission efficiency of a mechanical system of a hoisting mechanism is improved; obtaining a formula (8) through the deformation of the formula (7);
Figure BDA0002580974390000082
Figure BDA0002580974390000083
wherein, P0For delivery of power from hydraulic pumps, p0For delivery of pressure, q, from a hydraulic pump0Is the flow rate of the hydraulic pump,
η0the system transmission efficiency; prefTo request power, CrefTo request control of current, CmaxIs the maximum value of the current, CminIs the minimum current value, q is the rated displacement of a single pump ring, n is the rotating speed of the pump, p is the pressure of the pump, and eta is the mechanical system transmission efficiency of the mechanism；
Calculating the request power P of amplitude variation through a formula (8)r_bAnd requested power P of slewingr_s。
Step five: by raising the requested power PhRequested power P of variable amplituderbRequested power of revolution PrsAnd the current power P usedactSum of the sum and total power P of the enginetCalculating a ratio s of the total power of the engine, if the ratio s is less than 1, the maximum power of the engine is not exceeded, and directly giving a request value; if the ratio s is equal to or greater than 1 and the maximum engine power has been exceeded, an additional power demand P is calculated that exceeds the engine demandex；
Calculating the current consumed power P of the engine through a formula (9)idle；
Pidle＝Pt*Tidle(9)
Wherein, PtIs the total power of the engine, TidleIs the idle torque percentage; ptIs a known value, TidleObtained by reading.
By raising the requested power PhRequested power P of variable amplituderbRequested power of revolution PrsAnd the current power P usedactSum of the sum and total power P of the enginetCalculating a ratio s to the total power of the engine;
Figure BDA0002580974390000091
wherein, PrhIs a power P of a lifting requesth；
If the ratio s is less than 1, the maximum power of the engine is not exceeded, and a request value is directly given;
if the ratio s is greater than or equal to 1, the maximum engine power has been exceeded, at which point an additional power demand P is calculated that exceeds the engine demandex；
Pex＝Prh+Prb+Prs+Pidle-Pt(11)。
Step six: according to the three mechanisms at this timeThe speed proportional relation of the lifting mechanism is that the additional power requirement of the corresponding proportion is proportionally subtracted, and when a single mechanism acts, the limit power allowed by lifting is PmhThe limit power allowed by amplitude variation is PmbAnd the limit power allowed by the revolution is PmsCalculating the maximum allowable power P of a single mechanismmhl、Pmbl、Pmsl；
Calculating the percentage S of the currently used power of a certain mechanism to the maximum used power through the formula (12)0；
Figure BDA0002580974390000101
Wherein, PactThe current power value, P, of the mechanismmaxPower limit values are used for this mechanism;
according to the speed proportional relation of the three mechanisms, the extra power requirement of the corresponding proportion is proportionally subtracted, and when a single mechanism acts, the limit power allowed by lifting is PmhThe limit power allowed by amplitude variation is PmbAnd the limit power allowed by the revolution is PmsCalculating the maximum allowable power P of a single mechanismmhl、Pmbl、Pmsl；
Figure BDA0002580974390000102
Wherein, PmhFor a single mechanism currently allowing maximum power, PrhPower requested for a single authority, ShFor lifting ratio, SbIn order to vary the amplitude ratio, SsTo a revolution ratio, PexIs the requested power that exceeds the total power of the engine.
Step seven: calculating the maximum lifting working speed v according to the maximum allowable power requirementmhMaximum operating current C of revolutionmsAmplitude variation maximum working current CmbAnd finally given.
Reversely calculating the maximum lifting working speed v according to the formula (6)mh；
Figure BDA0002580974390000103
Calculating the maximum rotary working current C according to the formula (15)msAnd amplitude variation maximum working current Cmb；
Figure BDA0002580974390000104
The hoisting mechanism realizes frequency conversion driving, namely, the speed output of the motor is limited, hydraulic pressure, namely, the current output of the hydraulic pump is limited, and the power output is limited by limiting the current output and the speed output, so that the intelligent power distribution is realized.
According to the intelligent distribution method for the engine power of the port mobile crane, the model selection of the engine of the port mobile overhead crane can be greatly reduced through a power distribution technology, the weight of the whole machine is reduced, the manufacturing cost of the product is reduced, and the market competitiveness of the product is increased; under the working condition that three mechanisms are not required to be linked, the single mechanism or the two mechanisms can fully exert the maximum operation efficiency, and the efficiency of the three mechanisms can be exerted in the maximum proportion under the working condition that the three mechanisms are required to be linked.
Although the present invention has been described with reference to a preferred embodiment, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.

Claims (6)

1. An intelligent distribution method for the power of an engine of a port mobile crane is characterized by comprising the following steps:
the method comprises the following steps: reading engine real timePercentage of Torque TactPercent idle torque TidleAcceleration and deceleration time t for liftingh；
Step two: read handle lifting action request value JrAmplitude variation request value JbRequested value J of turning operations；
Step three: calculating the lifting request speed v according to the lifting action request value of the handlehCurrent request value C of hydraulic pump of slewing mechanismsAnd the current request value C of the hydraulic pump of the luffing mechanismb；
Step four: calculating the lifting request power PhCalculating the flow q according to the direct proportion relation between the flow and the current of the rotation and amplitude variation request current, recording the pressure P of the rotation pump head, and calculating the amplitude variation request power PrbAnd requested power P of slewingrs；
Step five: by raising the requested power PhRequested power P of variable amplituderbRequested power of revolution PrsAnd the current power P usedactSum of the sum and total power P of the enginetCalculating a ratio s of the total power of the engine, if the ratio s is less than 1, the maximum power of the engine is not exceeded, and directly giving a request value; if the ratio s is equal to or greater than 1 and the maximum engine power has been exceeded, an additional power demand P is calculated that exceeds the engine demandex；
Step six: according to the speed proportional relation of the three mechanisms, the extra power requirement of the corresponding proportion is proportionally subtracted, and when a single mechanism acts, the limit power allowed by lifting is PmhThe limit power allowed by amplitude variation is PmbAnd the limit power allowed by the revolution is PmsCalculating the maximum allowable power P of a single mechanismmhl、Pmbl、Pmsl；
Step seven: calculating the maximum lifting working speed v according to the maximum allowable power requirementmhMaximum operating current C of revolutionmsAmplitude variation maximum working current CmbAnd finally given.
2. The intelligent distribution method of the power of the harbor mobile crane engine according to claim 1, characterized in that: the third step is specifically that
According to the request value J of the handle lifting actionrCalculating a lifting request speed v according to the formula (1)h，
Figure FDA0002580974380000021
Wherein v ishFor requesting speed of lifting, JmaxMaximum value of the handle, JrRequesting value of lifting action for handle, vmaxThe maximum speed value corresponding to the maximum value of the handle;
calculating the current request value C of the hydraulic pump of the slewing mechanism according to the formula (2)sAnd the current request value C of the hydraulic pump of the luffing mechanismb；
Figure FDA0002580974380000022
Where C is the current request value, JmaxMaximum value of the handle, JrRequesting value for lifting handle, CmaxIs the maximum value of the current, CminIs the current minimum; cmaxAnd CminAre known parameter values.
3. The intelligent distribution method of the power of the harbor mobile crane engine according to claim 1, characterized in that: the fourth step is specifically that
Calculating acceleration time t to a lifting request by formula (3)r；
Figure FDA0002580974380000023
Wherein, JmaxMaximum value of the handle, JrRequesting a value for the lifting action of the handle, thAccelerating and decelerating time for lifting;
calculating the acceleration a of the hoisting mechanism by the formula (4)h；
vh＝ah*tr(4)
Calculating the force F required by the load lifting of the lifting mechanism by the formula (5)h；
Fh-mg＝m*ah(5)
Wherein m is the current hoisting weight of the hoisting mechanism, and g is the gravity acceleration;
calculating the lifting request power P by the formula (6)h；
Figure FDA0002580974380000031
Wherein v ishIs the speed of the load, ηhThe transmission efficiency of a mechanical system of a hoisting mechanism is improved;
obtaining a formula (8) through the deformation of the formula (7);
Figure FDA0002580974380000032
Figure FDA0002580974380000033
wherein, P0For delivery of power from hydraulic pumps, p0For delivery of pressure, q, from a hydraulic pump0Is the flow rate of the hydraulic pump, eta0The system transmission efficiency; prefTo request power, CrefTo request control of current, CmaxIs the maximum value of the current, CminIs the minimum value of current, q is the rated displacement of a single circle of the pump, n is the rotating speed of the pump, p is the pressure of the pump, and eta is the mechanical system transmission efficiency of the mechanism;
calculating the request power P of amplitude variation through a formula (8)r_bAnd requested power P of slewingr_s。
4. The intelligent distribution method of the power of the harbor mobile crane engine according to claim 1, characterized in that: the fifth step is specifically that
Calculating the current consumed power P of the engine through a formula (9)idle；
Pidle＝Pt*Tidle(9)
Wherein, PtIs the total power of the engine, TidleIs the idle torque percentage;
by raising the requested power PhRequested power P of variable amplituderbRequested power of revolution PrsAnd the current power P usedactSum of the sum and total power P of the enginetCalculating a ratio s to the total power of the engine;
Figure FDA0002580974380000041
wherein, PrhIs a power P of a lifting requesth；
If the ratio s is less than 1, the maximum power of the engine is not exceeded, and a request value is directly given;
if the ratio s is greater than or equal to 1, the maximum engine power has been exceeded, at which point an additional power demand P is calculated that exceeds the engine demandex；
Pex＝Prh+Prb+Prs+Pidle-Pt(11)。
5. The intelligent distribution method of the power of the harbor mobile crane engine according to claim 1, characterized in that: the sixth step is specifically that
Calculating the percentage S of the currently used power of a certain mechanism to the maximum used power through the formula (12)0；
Figure FDA0002580974380000042
Wherein, PactThe current power value, P, of the mechanismmaxPower limit values are used for this mechanism;
according to the speed proportional relation of the three mechanisms, the extra power requirement of the corresponding proportion is proportionally subtracted, and when a single mechanism acts, the limit power allowed by lifting is PmhBecomeThe limit power allowed by the amplitude is PmbAnd the limit power allowed by the revolution is PmsCalculating the maximum allowable power P of a single mechanismmhl、Pmbl、Pmsl；
Figure FDA0002580974380000043
Wherein, PmhFor a single mechanism currently allowing maximum power, PrhPower requested for a single authority, ShFor lifting ratio, SbIn order to vary the amplitude ratio, SsTo a revolution ratio, PexIs the requested power that exceeds the total power of the engine.
6. The intelligent distribution method of the power of the harbor mobile crane engine according to claim 1, characterized in that: the seventh step is specifically that
Reversely calculating the maximum lifting working speed v according to the formula (6)mh；
Figure FDA0002580974380000051
Calculating the maximum rotary working current C according to the formula (15)msAnd amplitude variation maximum working current Cmb；
Figure FDA0002580974380000052
The hoisting mechanism realizes frequency conversion driving, namely, the speed output of the motor is limited, hydraulic pressure, namely, the current output of the hydraulic pump is limited, and the power output is limited by limiting the current output and the speed output, so that the intelligent power distribution is realized.
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Cited By (1)

* Cited by examiner, † Cited by third party
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CN115818448A (en) * 2023-02-23 2023-03-21 三一汽车起重机械有限公司 Method and device for distributing getting-on power of electric crane and electric crane

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