CN1353794A - Pump control method and pump control device - Google Patents
Pump control method and pump control device Download PDFInfo
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- CN1353794A CN1353794A CN 00808268 CN00808268A CN1353794A CN 1353794 A CN1353794 A CN 1353794A CN 00808268 CN00808268 CN 00808268 CN 00808268 A CN00808268 A CN 00808268A CN 1353794 A CN1353794 A CN 1353794A
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- pump
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- delivery pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1204—Position of a rotating inclined plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1205—Position of a non-rotating inclined plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/06—Motor parameters of internal combustion engines
- F04B2203/0605—Rotational speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/05—Pressure after the pump outlet
Abstract
A variable displacement main pump (11) driven by an engine (13) is provided with a capacity control means (35) for variably controlling a discharge flow rate. According to an engine revolution speed detected by an engine revolution speed detector (44) and a pump discharge pressure from the main pump (11) detected by a pump discharge pressure detector (42), a power shift pressure output from a solenoid proportional reducing valve (46) is controlled by a signal output from a controller (45). The power shift pressure is led to a regulator control valve (39) of the capacity control means (35), and a tilt angle of the swash plate (36) of the main pump (11) is controlled by a regulator (37) to thereby shift-control pump discharge pressure - discharge flow rate characteristics to optimal levels. Whereby, a pump control device is provided that can reduce changes in engine revolution speed when a load pressure is rapidly changed.
Description
Technical field
The present invention relates to control the method for controlling pump and the pump-unit of variable displacement pump.
Background technique
Shown in Japanese kokai publication hei 10-220359 patent gazette, control gear as the variable displacement pump of building machineries such as oil pressure excavator, often receive the output signal of the engine speed detector that engine speed is detected, in advance engine speed is set segmentation and absorb torque continuously and at the pump that constant engine point intersects, increase and decrease corresponding computing pump with engine speed and absorb torque, send instruction according to this operation result to the regulator control valve, making pump absorb torque is that specified value comes the regulator of variable displacement pump is adjusted.
Like this, managed the detection of engine rotating speed in the past and come the computing pump to absorb torque, the regulator of variable displacement pump was adjusted, thereby exist engine speed change with respect to the bigger this problem of induced pressure sudden change.
The present invention is just at such problem, and its purpose is to provide a kind of method for controlling pump and apparatus for controlling pump that engine speed change is reduced with respect to the induced pressure sudden change.
Summary of the invention
Method for controlling pump of the present invention, the detection of engine rotating speed, detection comprises the pump delivery pressure of variable displacement pump that POF is carried out the volume controlled means of variable control by engine-driving, hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure imports the volume controlled means, and the pump delivery pressure-output flow characteristic speed Control of variable displacement pump is good for amount.So pump delivery pressure that can be by detecting variable displacement pump reduces the variation of engine speed with respect to the induced pressure sudden change as the control signal that the volume controlled means are controlled, realizes that stable pump controls.
Method for controlling pump of the present invention, the detection of engine rotating speed, detection comprises the pump delivery pressure of variable displacement pump that POF is carried out the volume controlled means of variable control by engine-driving, neutral condition and micromanipulator state according to the control valve that the working fluid of variable displacement pump supply load is controlled, with the negative sense pilot pressure guiding volume controlled means that taken place, come the control pump output flow for minimum, the pump delivery pressure is imported the volume controlled means, the pump horse power of motor being supplied with variable displacement pump is controlled to be maintenance necessarily, hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure imports the volume controlled means, and the pump delivery pressure-output flow characteristic speed Control of variable displacement pump is good for amount.So, can be according to the neutral condition and the micromanipulator state of control valve, come the control pump output flow for minimum the negative sense pilot pressure guiding volume controlled means that taken place, in case and the negative sense pilot pressure reduces, just the pump delivery pressure can be imported the volume controlled means, the pump horse power of motor being supplied with variable displacement pump is controlled to be maintenance necessarily, in addition, can import the volume controlled means by hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure, pump delivery pressure-output flow characteristic speed Control is good for amount, reduce the variation of engine speed, the volume controlled means of variable displacement pump are controlled to be the optimum state thereby can adapt to various situations with respect to induced pressure sudden change.
Apparatus for controlling pump of the present invention comprises: the volume controlled means of the output flow of engine-driven variable displacement pump being carried out variable control; The engine speed detection means that engine speed is detected; The pump delivery pressure detection means that the pump delivery pressure of variable displacement pump is detected; And hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure imports the volume controlled means, and the pump delivery pressure-output flow characteristic speed Control of variable displacement pump is the good hydraulic speed-changing control device of amount.So, detect the pump delivery pressure of variable displacement pump by pump delivery pressure detection means, and the control signal that conduct is controlled the volume controlled means is obtained by the hydraulic speed-changing control device, thereby can reduce the variation of engine speed with respect to the induced pressure sudden change, realize stable pump control, simultaneously only for the pump delivery pressure is obtained the change of this purposes as control signal, be that system does not have the good apparatus for controlling pump of realization under the situation of bigger change yet so can almost not have change in existing hardware.
Apparatus for controlling pump of the present invention comprises: the volume controlled means of the output flow of engine-driven variable displacement pump being carried out variable control; The engine speed detection means that engine speed is detected; The pump delivery pressure detection means that the pump delivery pressure of variable displacement pump is detected; Hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure imports the volume controlled means, and the pump delivery pressure-output flow characteristic speed Control of variable displacement pump is the good hydraulic speed-changing control device of amount; The pump delivery pressure is imported the volume controlled means, and the pump horse power of motor being supplied with variable displacement pump is controlled to be the fixed horsepower control device that keeps certain; And,, come the control pump output flow to be minimum negative sense control device with the negative sense pilot pressure guiding volume controlled means that taken place according to the neutral condition and the micromanipulator state of the control valve that the working fluid of variable displacement pump supply load is controlled.So, can be by neutral condition and the micromanipulator state of negative sense control device according to control valve, with the negative sense pilot pressure guiding volume controlled means that taken place, come the control pump output flow for minimum, in case and the negative sense pilot pressure reduces, just can lean on fixed horsepower control device that the pump delivery pressure is imported the volume controlled means, the pump horse power of motor being supplied with variable displacement pump is controlled to be maintenance necessarily, in addition, can lean on the hydraulic speed-changing control device, by hydraulic speed-changing pressure importing volume controlled means that will be corresponding with engine speed and pump delivery pressure, pump delivery pressure-output flow characteristic speed Control is good for amount, reduce the variation of engine speed, the volume controlled means of variable displacement pump are controlled to be the optimum state thereby can adapt to various situations with respect to induced pressure sudden change.
And the volume controlled means comprise: the swash plate that POF is carried out variable adjustment; And the hydraulic actuating type mechanical governor that the swash plate tilt angle is controlled, mechanical governor comprises: be subjected to making the swash plate tilt angle increase the elastic force of direction and the piston that moves; And be pressed in by the fluid relative and make the swash plate tilt angle reduce the pilot-operated type regulator control valve of control piston on the direction with elastic force.So, can be by importing pilot-operated type regulator control valve from the signal pressure of negative sense control device, fixed horsepower control device, hydraulic speed-changing control device, lean on this regulator control valve that the piston of mechanical governor is carried out high-precision Stroke Control, thereby can in statu quo use ready-made mechanical governor, under the situation that changes existing hardware hardly, realize good apparatus for controlling pump.
In addition, the hydraulic speed-changing control device comprises: the controller that the hydraulic speed-changing pressure corresponding with engine speed and pump delivery pressure is carried out computing; And the solenoid-operated proportional operating valve of the pilot pressure of the regulator control valve of input capacity control device being controlled according to the electrical signal of controller output.So, by with proportional action solenoid valve controlled adjuster control valve as desired of the corresponding action of electrical signal that comes self-controller, even if existing machinery formula regulator can be an ideal characterisitics with pump delivery pressure-output flow Characteristics Control also.
Brief Description Of Drawings
Fig. 1 is the oil hydraulic circuit figure of expression apparatus for controlling pump one example of the present invention, Fig. 2 is the block diagram of this apparatus for controlling pump internal controller function of expression, Fig. 3 is the performance plot of the engine speed-shaft horsepower characteristic of low speed controlling torque operational part in this controller of expression, Fig. 4 allows the block diagram of torque operational part function for main pump in this controller of expression, Fig. 5 is the block diagram of main pump control device function in this controller of expression, Fig. 6 is the pump delivery pressure-Flow characteristics figure of this main pump control device of explanation internal torque-Di 1 flex point pressure conversion usefulness, and Fig. 7 is the performance plot of expression pump delivery pressure-POF characteristic.
The best mode that carries out an invention
An example of the present invention is described with reference to the accompanying drawings.
Fig. 1 represents the oil hydraulic circuit of excavator.Oil pressure excavator (not shown) is loading the main pump 11 of supplying with a pair of variable displacement pump of working oil as walking to the left and right with oil pressure motor, rotation with each oil hydraulic cylinder of oil pressure motor and anterior work mechanism respectively on the upper rotating body on the lower running body, supply with the control pump 12 of control, the fuel tank 14 that drives the motor 13 of these main pumps 11 and control pump 12 and deposit the oil hydraulic circuit working oil with pilot pressure.
This oil pressure excavator also comprise to about walking with the oil pressure motor, rotate the oil hydraulic circuit of controlling with the action of oil pressure motor and anterior each oil hydraulic cylinder of work mechanism.
This oil hydraulic circuit comprises: walking oil pressure motor, rotation the working oil travel direction control of oil pressure motor and anterior each oil hydraulic cylinder of work mechanism and the control valve 15 of flow control about a pair of main pump 11 is supplied with, the control oil pressure of supplying with by control pump 12 carries out remote-operated control valve (following this control valve is called " remote-controlled valve 16 ") to this control valve 15, and they are carried out the oil pressure path that pipe arrangement connects.
Aforementioned remote-controlled valve 16 only illustrates local, but has a reduction valve 32, use the operating handle manually-operable by the operator in the oil pressure excavator operating room, supply with the pressure chamber of control valve 15 each valve rod end by the oily control of reducing pressure of oil pressure control that control pump 12 is supplied with via pilot pressure path 31.And, also be provided with the relief valve 34 that pilot pressure is remained setting pressure with filter element 33 on the pilot pressure path 31.
Aforementioned a pair of main pump 11 comprises the volume controlled means 35 of POF being carried out variable control, and these volume controlled means 35 comprise respectively according to tilt angle control pump discharging volume coming POF is carried out the swash plate 36 of variable adjustment and the hydraulic actuating type mechanical governor 37 of control swash plate 36 tilt angles.
Above-mentioned mechanical governor 37 comprises respectively: the tilt angle that is subjected to making swash plate 36 increases the elastic force of direction and the piston 38 that moves; And lean on the hydrodynamic pressure (oil pressure) relative making swash plate 36 tilt angles reduce the pilot-operated type regulator control valve 39 of this piston 38 of control on the direction with elastic force.These regulator control valve 39 one are assembled in the regulator body of built-in piston 38.
One end of each piston 38 is acting on the pump delivery pressure of each main pump 11 respectively, and the other end of each piston 38 is also acting on the pilot pressure that 39 pairs of pump delivery pressures of each regulator control valve are controlled respectively with elastic force.The swash plate position detector (not shown) that tilt angle (swash plate position) is detected is being set respectively on each swash plate 36.
On the output channel from two main pumps 11, make and take out reciprocable valve 41 that high pressure side pump delivery pressure uses, be connected with pump delivery pressure detector 42 as the pump delivery pressure detection means that this pump delivery pressure is detected between the centre.
As importing the volume controlled means 35 of main pump 11 with aforementioned engine speed detector 44 and corresponding hydraulic speed-changing pressure P s such as pump delivery pressure detector 42 detected engine speed and pump delivery pressure, and be best hydraulic speed-changing control device with the pump delivery pressure-output flow characteristic speed Control of main pump 11, be provided with the controller 45 that the hydraulic speed-changing pressure P s corresponding with engine speed and pump delivery pressure carried out computing, and as being the solenoid-operated proportional reduction valve 46 of the proportional action solenoid valve controlled of hydraulic speed-changing pressure P s to the pilot pressure that is input to regulator control valve 39 according to the electrical signal of this controller 45 outputs.
1 port of this solenoid-operated proportional reduction valve 46 is connected with 31,2 ports of aforementioned pilot pressure path and then is communicated with respectively via the pilot pressure introduction part 48 of 2 regulator control valves 39 in hydraulic speed-changing pressure port 47 and the volume controlled means 35.
This solenoid-operated proportional reduction valve 46 keeps certain pilot pressure to carry out proportional control according to controller 45 to the electrical signal of solenoid 49 to being controlled to be by aforementioned relief valve 34, to import the pilot pressure introduction part 48 of regulator control valve 39, by relative this regulator control valve 39 is carried out displacement control with spring 50, come the piston 38 of various mechanical governors 37 is carried out high-precision Stroke Control, drive swash plate 36 and be in desirable tilt angle.
And import the regulator control valve 39 of volume controlled means 35 and the pump horse power that motor 13 is supplied with main pump 11 is controlled to be the fixed horsepower control device that keeps certain as the pump delivery pressure with main pump 11, the path 52 that the output channel of 2 main pumps 11 is drawn through valve 51 is communicated with respectively with another pilot pressure introduction part 53 of 2 regulator control valves 39.
In addition, as according to neutral condition and the micromanipulator state of main pump 11 being supplied with the control valve of controlling as the working oil of the various oil pressure activated devices of load 15, come the control pump output flow to be minimum negative sense control device the negative sense pilot pressure guiding volume controlled means 35 that taken place, when each valve rod 21～30 of control valve 15 is in neutral condition and micromanipulator state, be discharging type paths 54 in the middle of to be communicated with fuel tank 14 via each valve rod 21～30 2 groups, also be respectively arranged with throttle orifice 57 at boundary part with relief valve 56, be communicated with respectively with other another pilot pressure introduction part 58 of 2 regulator control valves 39 from the negative sense control access 58 that upstream one side of these throttle orifices 57 is drawn with the fuel tank path 55 that is communicated with fuel tank 14.Each negative sense control access 58 is respectively arranged with the pressure detector 60 that the negative sense pilot pressure is detected usefulness, and these pressure detectors 60 are connected with aforementioned controller 45 respectively.
Like this, aforementioned mechanical governor 37 just in statu quo uses existing parts, to import pilot-operated type regulator control valve 39 from the signal pressure of negative sense control device, fixed horsepower control device, hydraulic speed-changing control device, make piston 38 action of mechanical governor 37 control the tilt angle of swash plate 36 by this regulator control valve 39, come the control pump discharge capacity according to the tilt angle of swash plate 36.
And, various detectors (sensor) are except aforementioned pump delivery pressure detector 42, engine speed detector 44, aforementioned swash plate position detector etc., induced pressure detector that manipulated variable detector that the joystick manipulation amount is detected also is set as required, detects to the flow detector controlled from the POF of main pump 11, to oil pressure activated device induced pressure etc., the output of these detectors is as control information signal input controller 45.
The following describes the content of this controller 45.
As shown in Figure 2, pump control system roughly comprises oil hydraulic circuit control device 61, engine speed control device 62 and main pump control device 63 these 3 modules.
Aforementioned oil hydraulic circuit control device 61 according to the oil temperature signal TEMP of working oil, to the anterior work mechanism of whether operating the oil pressure excavator and rotation with the cantilever operating stem detect usefulness from the testing signal SWim of meter switch and to whether operate walking with control stick detect usefulness from the testing signal SWtr that drives switch, the desired flow Q that requires of computing oil hydraulic circuit.
Aforementioned engine speed control device 62 comprises state of a control determination section 64, low speed controlling torque operational part 65, prevents that engine cut-off torque operational part 66 and main pump from allowing torque operational part 67, according to pulling out motor set rotary speed Nac, engine speed detector 44 detected engine speed N that code-disc sets by dynamic mode PM, mode of operation WM and acceleration and selecting high pressure sides and by pump delivery pressure detector 42 detected pump delivery pressure Pp etc., decision main pump 11 available level of torque are that main pump allows torque Tmpallow by reciprocable valve 41.
The aforementioned state of a control attitude determination section 64 of determining is connected with each operational part 65～67, has following function: engine speed is carried out in the control procedure, according to the various signals that quicken to pull out inputs such as code-disc, engine speed sensor, decide all will making in this way to prevent that the engine cut-off function from working or make engine speed remain near the rated speed this low speed control state of a control such as work.
Aforementioned low speed controlling torque operational part 65 as shown in Figure 3, rated speed-rated horsepower is arranged on the discontinuity point of engine output characteristics by the regional and uncontrollable hysteresis region of the speed governing of speed regulator control boundary, so set low speed amount Nus in order to ensure stable running, in order only to lack the engine speed of this low speed amount Nus as rotating speed of target than rated speed, be in arithmograph 3 hysteresis regions rotating speed of target only to be moved the low speed controlling torque that low speed amount Nus uses to left, will speed up and pull out setting rotating speed that code-disc sets and engine speed detector 44 detected engine speed as input signal.
Basically, in order to realize the low speed control of this motor 13, regulator 37 to main pump 11 is controlled, and coming according to the load torque that engine output torque absorbs with the form of (pump delivery pressure) * (POF) main pump 11 is that pump absorbs torque and controls.
The aforementioned torque operational part 66 that prevents engine cut-off, by engine speed detector 44 detected engine speed computings in order to prevent preventing the engine cut-off torque because of what load caused that motor stops.
Then, aforementioned main pump allow torque operational part 67 according to the low speed controlling torque of quickening to pull out acceleration torque that code-disc sets, 65 outputs of low speed controlling torque operational part and prevent 66 outputs of engine cut-off operational part prevent the engine cut-off torque, decide a pair of main pump 11 available main pumps to allow torque Tmpallow.
This main pump allows torque operational part 67 as shown in Figure 4, by by adder 71 on the required standard torque Tt of the main pump 11 of rated speed to aforementioned prevent that the computing of engine cut-off torque operational part from drawing prevent that engine cut-off torque Tas from carrying out addition process and coming the static torque Ts of computing, come computing dynamic torque Td by on this static state torque Ts, acceleration torque Tac being carried out addition process by adder 72, come the computing main pump to allow torque Tmpallow by carry out addition process by the adder 73 low speed controlling torque Tus that 65 computings draw to aforementioned low speed controlling torque operational part on this dynamic torque Td, allow torque Tmpallow to aforementioned main pump control device 63 these main pumps of output.
This main pump control device 63, press (the pump delivery pressure at the 1st flex point place of the pump delivery pressure-Flow characteristics shown in Fig. 6) that the flow Q (%) that requires of aforementioned oil hydraulic circuit control device 61 outputs as shown in Figure 5 is scaled main pump requirement torque Tmpreg (%) by torque route marker 74 usefulness the 1st flex point, require this main pump requirement torque Tmpreq to engine speed control device 62.
The torque that this main pump requires torque Tmpreq to determine for the load state according to main pump 11 from the requirement of pump one side, main pump allows the torque of torque Tmpallow (%) for being allowed to according to motor 13 1 lateral load situations on the other hand, so it just is that main pump 11 actual used pumps absorb torques that these main pumps require torque Tmpreq and main pump to allow the central low torque of torque Tmpallow.
Then, allow torque Tmpallow and aforementioned main pump to require torque Tmpreq input torque selection approach 75 main pump of aforementioned engine speed control device 62 outputs, select little torque, promptly obtain pump and absorb torque, by route marker 76 this pump is absorbed torque and be scaled the 1st flex point pressure, by route marker 77 the 1st flex point is pressed again and be scaled hydraulic speed-changing pressure P s, and then use input signal (control electric current) Ips in order to export the solenoid 49 required hydraulic speed-changings that hydraulic speed-changing pressure P s is scaled solenoid-operated proportional reduction valve 46 from solenoid-operated proportional reduction valve 46 by route marker 78.
So as shown in Figure 2, in a single day this hydraulic speed-changing imports the solenoid 49 of solenoid-operated proportional reduction valve 46 with input signal Ips, just export the hydraulic speed-changing pressure P s of the regulator control pressure signal that draws as computing from solenoid-operated proportional reduction valve 46, by this hydraulic speed-changing pressure P s controlled adjuster control valve 39, control the tilt angle of the swash plate 36 of main pump 11.
Like this, engine speed was detected in the past and carried out pump control, but this controlling method can in statu quo be used with the mechanical governor 37 of the same in the past two sections springs of usefulness and come control pump to require horsepower by going back testing pump delivery pressure Pp (or actuator load pressure) and being added on the control device.
Specifically, with respect to increasing delivery pressure detector 42, controlling based on the pump swash plate that has two sections springs now of oil pressure shoveling pump control usefulness and use the regulator drive portion, can and control hydraulic speed-changing pressure P s by testing pump delivery pressure Pp and make the P-Q feature of mechanical governor 37 become Ideal Characteristics, can reduce the error between target control torque and actual torque.
In other words, as shown in Figure 7, in fixed horsepower control device, controlled adjuster 37 makes the relation (is " pump P-Q characteristic " to call this pass in the following text) of pump delivery pressure Pp and POF Q change on the pump horse power curve in specific deciding, on the other hand, in the hydraulic speed-changing control device, by the rotating speed deviation of controller 45 according to engine target rotating speed and actual engine speed, the pump that computing must be revised absorbs torque, control hydraulic speed-changing pressure P s by exporting corresponding hydraulic speed-changing with electrical signal Ips control solenoid-operated proportional reduction valve 46, by making pump P-Q characteristic move to other curve from the specific pump horse power curve of deciding, proofread and correct the flex point of the used spring 50 of mechanical governor 37, revise above-mentioned rotating speed deviation, among Fig. 7, when pump horse power was increased, the pump horse power curve of deciding to the upper right moved.
The effect of the example shown in the above-mentioned control content explanatory drawing 1 of following foundation.
When whole valve rods 21～30 of control valve 15 are neutral condition and micromanipulator state, the negative sense pilot pressure that will take place at throttle orifice 57 upstream sides of middle discharging type path 54 by the negative sense control device, the pilot pressure introduction part 59 of 58 guiding regulator control valves 39 through the negative sense control access makes POF become minimum by regulator 37 control swash plates 36.
Have again, when the displacement negative sense pilot pressure owing to valve cash 21～30 reduces, just import the pump delivery pressure Pp of the pilot pressure introduction part 53 of regulator control valves 39 according to the path 52 of the fixed horsepower of process control device, controlled adjuster control valve 39, the tilt angle of controlling swash plates 36 by regulator 37 make motor 13 supply with the pump horse power (or pump absorption torque) of main pumps 11 for certain.That is, among Fig. 7,, make POF Q decide the pump horse power curvilinear motion along one by the inclination angle of regulating 37 control swash plates 36 along with the variation of pump delivery pressure Pp.
Hydraulic speed-changing pressure P s by detected engine speed N of controller 45 computings and pump delivery pressure Pp correspondence, control the solenoid-operated proportional reduction valve 46 of hydraulic speed-changing means according to the control signal of this operation result, to be the pilot pressure introduction part 48 that hydraulic speed-changing pressure P s imports regulator control valve 39 by the pilot pressure of these solenoid-operated proportional reduction valve 46 decompression controls, by regulator 37 control swash plates, it is best that speed Control pump delivery pressure-output flow characteristic becomes, and promptly decides the pump horse power curve from one among Fig. 7 and shift to another and decide the pump horse power curve.
As mentioned above, for carrying out fixed horsepower control by the detection of engine rotational speed N as feedback control in the past, this control gear also detects the pump delivery pressure Pp from main pump 11, because accomplished to be taken into the control information signal of control capacity means 35, so, with respect to the induced pressure sudden change, can reduce the rotation speed change of motor 13.
Have, do not use the control gear of high price, system does not do big change, still uses existing hardware, just detected pump delivery pressure Pp is taken into as control signal, so neither increase cost, can realize good control gear again.
Also have, this controlling method and control gear are not limited only to the control of ramp type pump, also applicable to the control of the clino-axis type pump with similar means etc.Industrial applicibility
This controlling method and control gear are used for reducing engine speed change with respect to the sudden change of variable displacement pump induced pressure, be not only building machinery, by engine-driven variable displacement pump, then also can be applicable to other work mechanism, fixed manufacturing machine etc. in this way.
Claims (6)
1. method for controlling pump is characterized in that:
The detection of engine rotating speed,
Detection comprises the pump delivery pressure of variable displacement pump that POF is carried out the volume controlled means of variable control by engine-driving,
Hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure imports the volume controlled means, and the pump delivery pressure-output flow characteristic speed Control of variable displacement pump is good for amount.
2. method for controlling pump is characterized in that:
The detection of engine rotating speed,
Detection comprises the pump delivery pressure of variable displacement pump that POF is carried out the volume controlled means of variable control by engine-driving,
According to the neutral condition and the micromanipulator state of the control valve that the working fluid of variable displacement pump supply load is controlled, with the negative sense pilot pressure guiding volume controlled means that taken place, come the control pump output flow for minimum,
The pump delivery pressure is imported the volume controlled means, and the pump horse power of motor being supplied with variable displacement pump is controlled to be maintenance necessarily,
Hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure imports the volume controlled means, and the pump delivery pressure-output flow characteristic speed Control of variable displacement pump is good for amount.
3. an apparatus for controlling pump is characterized in that, comprising:
The output flow of engine-driven variable displacement pump is carried out the volume controlled means of variable control;
The engine speed detection means that engine speed is detected;
The pump delivery pressure detection means that the pump delivery pressure of variable displacement pump is detected; And
Hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure imports the volume controlled means, and the pump delivery pressure-output flow characteristic speed Control of variable displacement pump is the good hydraulic speed-changing control device of amount.
4. an apparatus for controlling pump is characterized in that, comprising:
The output flow of engine-driven variable displacement pump is carried out the volume controlled means of variable control;
The engine speed detection means that engine speed is detected;
The pump delivery pressure detection means that the pump delivery pressure of variable displacement pump is detected;
Hydraulic speed-changing pressure that will be corresponding with engine speed and pump delivery pressure imports the volume controlled means, and the pump delivery pressure-output flow characteristic speed Control of variable displacement pump is the good hydraulic speed-changing control device of amount;
The pump delivery pressure is imported the volume controlled means, and the pump horse power of motor being supplied with variable displacement pump is controlled to be the fixed horsepower control device that keeps certain; And
According to the neutral condition and the micromanipulator state of the control valve that the working fluid of variable displacement pump supply load is controlled,, come the control pump output flow to be minimum negative sense control device with the negative sense pilot pressure guiding volume controlled means that taken place.
5. as claim 3 or 4 described apparatus for controlling pump, it is characterized in that,
The volume controlled means comprise:
POF is carried out the swash plate of variable adjustment; And
The hydraulic actuating type mechanical governor that the swash plate tilt angle is controlled,
Mechanical governor comprises:
The piston that is subjected to making the swash plate tilt angle increase the elastic force of direction and moves; And
Be pressed in the pilot-operated type regulator control valve that makes control piston on the swash plate tilt angle minimizing direction by the fluid relative with elastic force.
6. apparatus for controlling pump as claimed in claim 5 is characterized in that, the hydraulic speed-changing control device comprises:
The controller that the hydraulic speed-changing pressure corresponding with engine speed and pump delivery pressure is carried out computing; And
The solenoid-operated proportional operating valve of the pilot pressure of the regulator control valve of input capacity control device being controlled according to the electrical signal of controller output.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000098405A JP3697136B2 (en) | 2000-03-31 | 2000-03-31 | Pump control method and pump control apparatus |
| JP98405/2000 | 2000-03-31 | ||
| JP98405/00 | 2000-03-31 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1353794A true CN1353794A (en) | 2002-06-12 |
| CN1178003C CN1178003C (en) | 2004-12-01 |
Family
ID=18612889
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB008082685A Expired - Fee Related CN1178003C (en) | 2000-03-31 | 2000-10-16 | Pump control method and pump control device |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP1207304A4 (en) |
| JP (1) | JP3697136B2 (en) |
| CN (1) | CN1178003C (en) |
| WO (1) | WO2001075309A1 (en) |
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| CN100406649C (en) * | 2005-12-26 | 2008-07-30 | 三一重工股份有限公司 | Control method and apparatus for omnirange stepless speed-adjusting travel drive of milling machine |
| CN100587172C (en) * | 2004-04-08 | 2010-02-03 | 株式会社小松制作所 | Hydraulic drive device for working machine |
| CN101105164B (en) * | 2006-07-12 | 2010-06-02 | 株式会社电装 | Control device used for electric fuel pump and method for controlling the pump |
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| JPH0617670B2 (en) * | 1985-10-28 | 1994-03-09 | 川崎重工業株式会社 | Input control device for hydraulic pump |
| JP2681841B2 (en) * | 1990-08-02 | 1997-11-26 | 油研工業株式会社 | Control device for variable displacement pump |
| JPH10220359A (en) * | 1997-01-31 | 1998-08-18 | Komatsu Ltd | Controller for variable capacity pump |
| JPH11125187A (en) * | 1997-10-22 | 1999-05-11 | Shin Caterpillar Mitsubishi Ltd | Control device of variable displacement hydraulic pump |
-
2000
- 2000-03-31 JP JP2000098405A patent/JP3697136B2/en not_active Expired - Fee Related
- 2000-10-16 CN CNB008082685A patent/CN1178003C/en not_active Expired - Fee Related
- 2000-10-16 EP EP00966500A patent/EP1207304A4/en not_active Withdrawn
- 2000-10-16 WO PCT/JP2000/007152 patent/WO2001075309A1/en active Application Filing
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN100587172C (en) * | 2004-04-08 | 2010-02-03 | 株式会社小松制作所 | Hydraulic drive device for working machine |
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| CN102828942A (en) * | 2011-06-16 | 2012-12-19 | 中联重科股份有限公司 | Constant-power control device and method for variable displacement pump and concrete pumping installation |
| CN102828942B (en) * | 2011-06-16 | 2015-11-18 | 中联重科股份有限公司 | The constant power control device of variable displacement pump, method and the concrete pump set |
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| CN104334879A (en) * | 2012-07-10 | 2015-02-04 | 川崎重工业株式会社 | Tilt angle control device |
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| CN105164428A (en) * | 2013-02-15 | 2015-12-16 | 派克汉尼芬公司 | Variable load sense open center hybrid system |
| CN103925089A (en) * | 2014-04-09 | 2014-07-16 | 三一汽车起重机械有限公司 | Engineering machinery, dynamic energy saving method and dynamic energy saving system |
| CN110088470A (en) * | 2016-11-30 | 2019-08-02 | 影响解决方案有限公司 | For controlling the equipment and the method for controlling prime mover that pressurized fluid conveys in the duct |
| CN107725505A (en) * | 2017-09-25 | 2018-02-23 | 柳工常州机械有限公司 | Hydraulic system with different accessory flow regulating functions |
| CN107630871A (en) * | 2017-11-13 | 2018-01-26 | 柳工常州机械有限公司 | Hydraulic system |
| CN113508207A (en) * | 2019-03-29 | 2021-10-15 | 住友建机株式会社 | Excavator |
| CN114294210A (en) * | 2021-12-23 | 2022-04-08 | 博世力士乐（常州）有限公司 | Multi-gear pump with delay gear switching function |
| CN114576128A (en) * | 2022-02-09 | 2022-06-03 | 中联重科股份有限公司 | Control method, processor and control device for pumping equipment and pumping equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2001280256A (en) | 2001-10-10 |
| JP3697136B2 (en) | 2005-09-21 |
| CN1178003C (en) | 2004-12-01 |
| WO2001075309A1 (en) | 2001-10-11 |
| EP1207304A4 (en) | 2010-10-13 |
| EP1207304A1 (en) | 2002-05-22 |
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