CN1450272A - Cylinder driving system and energy regenerating method thereof - Google Patents
Cylinder driving system and energy regenerating method thereof Download PDFInfo
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- CN1450272A CN1450272A CN 03110324 CN03110324A CN1450272A CN 1450272 A CN1450272 A CN 1450272A CN 03110324 CN03110324 CN 03110324 CN 03110324 A CN03110324 A CN 03110324A CN 1450272 A CN1450272 A CN 1450272A
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Abstract
The present invention provided a cylinder drive system and a method for regenerating its energy. The cylinder drive system has the following three intaking and discharging ports, a first port (B) to supply or discharge oil in the bottom chamber of the hydraulic cylinder (3), a second port (H) to discharge or supply the oil in the head chamber, and a third port (T) to discharge or supply the oil in a tank (5). The cylinder drive system is provided with a hydraulic pump (1) in which the intaking amount and the discharging amount of the first port (B) is the sum of each discharging amount and the intaking amount of the second port (H) and the third port (T), and a drive source (2) to drive the hydraulic pump (1). The control of the discharging amount, the intaking amount, and the discharging direction of the hydraulic pump (1) is executed by controlling the number of rotation and the rotation direction of the drive source (2) or by controlling a tilt angle by making the hydraulic pump (1) as a double tilting type. In this invention, a number of hydraulic equipment for absorbing the difference of a flow rate between a head chamber and a bottom chamber of a hydraulic cylinder and the amount of energy loss can be reduced.
Description
Technical field
The present invention relates to a kind of cylinder driving system and energy regenerating method thereof.
Background technique
In the past, one of mode of controlling for the flow that is used in the oil hydraulic cylinder on building machinery, working truck and the industrial machine more, the rotating speed that the control oil hydraulic pump is arranged that is widely known by the people and the mode of sense of rotation, and the two converter-types (clino-axis type, ramp type etc.) of control (refer to bilateral discharge formula, bidirectional dischargable) tilt angle of oil hydraulic pump (discharge capacity, mode displacement).
As the conventional art of the mode of controlling above-mentioned oil hydraulic pump rotating speed and sense of rotation, for example, have the technology of record in international publication WO01/88381 number, Figure 13 has represented the major component with the driving circuit diagram of putting down in writing in the communique.As shown in figure 13, two oil hydraulic pumps 41,42 are driven by motor 2, and side's delivery outlet of the 1st oil hydraulic pump 41 is connected via pipeline 50 on the chamber, top of oil hydraulic cylinder 3, and the opposing party's delivery outlet is connected via pipeline 51 in the bottom compartment of oil hydraulic cylinder 3.In addition, side's delivery outlet of the 2nd oil hydraulic pump 42 is connected on the pipeline 51, and the opposing party's delivery outlet is connected on the accumulator 43 via switch valve 44 and pipeline 53.Pipeline 50 detects valve 46a via the 1st safety valve 45a and the 1st and is connected on the accumulator 43 by pipeline 52.In addition, similarly pipeline 51 detects valve 46b via the 2nd safety valve 45b and the 2nd and is connected on the accumulator 43 by pipeline 52.
According to above-mentioned formation, with oil hydraulic cylinder 3 indentations the time, when by motor 2 with oil hydraulic pump 41,42 when the indentation direction is rotated, the pressure oil of bottom compartment is via pipeline 51, wherein a part of flow is inhaled in the 1st oil hydraulic pump 41, and discharge from this oil hydraulic pump 41, and flow into the top via pipeline 50 indoor.In addition, other unnecessary pressure oil are inhaled in the 2nd oil hydraulic pump 42, from this oil hydraulic pump 42, discharge and via switch valve 44 and pipeline 53 by pressure accumulation in accumulator 43.On the other hand, with oil hydraulic cylinder 3 elongation the time, when by motor 2 with oil hydraulic pump 41,42 when prolonging direction rotates, the 1st oil hydraulic pump 41 will push up the pressure oil of chamber via pipeline 50 suctions, will press oilyly to be discharged in the bottom compartment via pipeline 51 again.At this moment, the pressure oil of bottom compartment's underfed part, and is flowed into via pipeline 51 from accumulator 43, suck, discharge via pipeline 53 and switch valve 44 by the 2nd oil hydraulic pump 42.Though need be partially absorbing because of the difference of the influx of the bottom compartment of oil hydraulic cylinder 3 and each constant pressure oil that difference produced of the compression area of chamber, top and discharge, but according to above-mentioned formation, can be with the part of bottom compartment and the difference of the flow of chamber, top, with 43 absorptions of two oil hydraulic pumps 41,42 and accumulator.
In addition, as the conventional art of the mode of controlling two converter-type oil hydraulic pump tilt angles, be real cylinder body driving that put down in writing, as shown in figure 14 the loop in the clear 60-122579 communique of opening.As shown in figure 14, two mouths of two type oil hydraulic pumps 64 that vert are connected in the bottom compartment and chamber, top of oil hydraulic cylinder 61 with valve 71 via control.The bar of oil hydraulic cylinder 61 is connected on the slide plate of press machine 6.In addition, come the switching of the discharge direction of control transformation oil hydraulic pump 64 by the regulator 66 of supplying with pilot oil from primer pump 65.Fuel tank 73 is connected control with on the valve 71 by pipeline.In addition, between the bottom compartment of oil hydraulic cylinder 61 (slide plate descend a side) and fuel tank 73, be provided with liquid-filling valve 72, when in press machine 6 work, from oil hydraulic pump 64 send oil mass not follow the time, provide oil by this fuel tank 73 via liquid-filling valve 72.
Yet, the problem below in above-mentioned conventional art, existing.
In the cylinder driving system of in above-mentioned international publication WO01/88381 number, putting down in writing, flow difference for the chamber, top and the bottom compartment of absorption liquid cylinder pressure 3, two oil hydraulic pumps 44,42 and accumulator 43 must be set, thereby need the long pipe distribution operation time, also will increase fabricating cost in addition.
In addition, drive on the loop at the real cylinder body of putting down in writing in the clear 60-122579 communique of opening, has in the not content of write up with communique, promptly, when slide plate rises, the oil of discharging from the bottom compartment of oil hydraulic cylinder 61, its part (than the unnecessary oil mass of top chamber one side capacity) is got back in the fuel tank 73 with valve 71 from control.Therefore, oil control is bigger with the energy loss on the valve 71 pressing, and is difficult to reach the effective operation that is undertaken by oil hydraulic cylinder.
The present invention is conceived to the problems referred to above point, and its purpose is to provide a kind of cylinder driving system and energy regenerating method thereof, can be reduced to the chamber, top of absorption liquid cylinder pressure and the hydraulic machine quantity of bottom compartment's flow difference, and can reduce energy loss.
Summary of the invention
In order to achieve the above object, the present invention's 1 cylinder driving system, it is characterized in that, have: oil hydraulic cylinder, supply with oil or discharge oily the 1st mouthful with bottom compartment from above-mentioned bottom compartment to this oil hydraulic cylinder, with discharge oil from the chamber, top of oil hydraulic cylinder or supply with the 2nd mouthful of oil to chamber, above-mentioned top, with 3 suction exhaust ports of the 3rd mouthful supplying with oil from fuel tank discharge oil or to above-mentioned fuel tank, and with the 1st mouthful intake the sum of discharge capacity separately as the 2nd mouthful and the 3rd mouthful, or with the 1st mouthful discharge capacity as the oil hydraulic pump of the sum of intake separately of the 2nd mouthful and the 3rd mouthful with drive the driving source of oil hydraulic pump.
1 invention according to the present invention, when oil hydraulic cylinder is stretched out, to push up the oil of chamber from the 2nd mouthful of suction, be discharged in the bottom compartment from the 1st mouthful again, and, utilize the 3rd mouthful of part from fuel tank, to suck the difference in flow of bottom compartment and chamber, top, in addition, when making the oil hydraulic cylinder withdrawal, from the 1st mouthful of suction, it is indoor to be discharged to the top from the 2nd mouthful again with the oil of bottom compartment, and unnecessary oil is turned back in the fuel tank from the 3rd mouthful, like this, can drive oil hydraulic cylinder by the loop circuit after using 1 oil hydraulic pump to absorb the part of bottom compartment and the difference in flow of chamber, top.Its result has used two oil hydraulic pumps and accumulator in the conventional art of record in the world in open WO01/88381 number, but can only use 1 oil hydraulic pump in the present invention, thereby loop structure is oversimplified.In addition, open in the conventional art of putting down in writing in the clear 60-122579 communique real, bigger in control with the energy loss on the valve (switching valve), but in the present invention owing to do not need switching valve, so with regard to the energy loss that on switching valve, forms, and, owing to be to utilize that the pressure oil in any one party comes drive motor in the 1st mouthful and the 2nd mouthful, so can reduce the loss on oil hydraulic pump.
The formation of the present invention's 2 inventions, be in the present invention's 1 invention, to the discharge capacity of above-mentioned oil hydraulic pump, intake and discharge the control of direction, be according to the rotating speed of above-mentioned driving source and the control of sense of rotation, or the type pumps that will two vert are controlled as above-mentioned oil hydraulic pump and according to this tilt angle of control.
2 invention according to the present invention, owing to be discharge capacity, intake above-mentioned oil hydraulic pump and the control of discharging direction, according to the rotating speed of driving source and the control of direction are carried out, so, with the mode of tilt angles such as control swash plate and inclined shaft mutually specific energy loop structure is oversimplified.In addition, under the situation that two converter-types are implemented according to the control tilt angle during as above-mentioned oil hydraulic pump, can control and discharge the responsiveness that direction is switched, like this, on the purposes that frequent travel direction switches, be effectively, and, driving source can be turned round with the certain orientation rotation.
The energy regenerating method of the present invention's 3 cylinder driving system, it is characterized in that, the use motor is controlled to have to the bottom compartment of oil hydraulic cylinder and is supplied with oil or discharge oily the 1st mouthful from above-mentioned bottom compartment, with discharge oil from the chamber, top of oil hydraulic cylinder or supply with the 2nd mouthful of oil to chamber, above-mentioned top, supply with 3 suction exhaust ports of the 3rd mouthful of oil with discharge oil from fuel tank or to above-mentioned fuel tank, and with the separately discharge capacity sum of the 1st mouthful intake as the 2nd mouthful and the 3rd mouthful, or with the 1st mouthful discharge capacity rotating speed and sense of rotation as the oil hydraulic pump of the sum of intake separately of the 2nd mouthful and the 3rd mouthful, and, the regenerated energy when reclaiming the oil hydraulic pump regenerative braking by motor.
3 invention according to the present invention utilizes 1 oil hydraulic pump just can constitute the loop circuit of Driven by Hydraulic Cylinder system, and, because the regenerated energy just can reclaim the oil hydraulic cylinder regenerative braking by motor the time, so can improve energy efficiency.
Description of drawings
Fig. 1 is the fundamental circuit of cylinder driving system of the present invention.
Fig. 2 is the sectional perspective sectional view of embodiment 1 plunger pump major component.
Fig. 3 is the 1st a cylinder body configuration example of plunger pump.
Fig. 4 is the 2nd a cylinder body configuration example of plunger pump.
Fig. 5 is the loop block diagram that applies the present invention to the embodiment of hydraulic bucket.
Fig. 6 is the sectional view of embodiment 2 oil hydraulic pump.
Fig. 7 is the sectional perspective sectional view of same oil hydraulic pump major component.
Fig. 8 is the cylinder unit explanatory drawing of same oil hydraulic pump.
Fig. 9 is the sectional view of major component of embodiment 3 cylinder unit.
Figure 10 is the valve plate plan view of embodiment 4 oil hydraulic pump.
Figure 11 is the valve plate plan view of embodiment 5 oil hydraulic pump.
Figure 12 is the A-A sectional view among Figure 11.
Figure 13 is the major component that the cylinder body of the 1st conventional art drives circuit diagram.
Figure 14 is that the cylinder body of the 2nd conventional art drives circuit diagram.
Among the figure: 1,1B, 1A, 1K, 1R-oil hydraulic pump, 2,2B, 2A, 2K, 2R-motor, 3,3B, 3A, 3K-oil hydraulic cylinder, 4,4B, 4A, 4K, 4R-transducer, 5-fuel tank, 6-motor, 7-generator, 7a-rectifier, 8-storage battery, 11,35-cylinder unit, 12,34-plunger, 13,37,37c-valve plate, 14-swash plate (swash plate), 15B, 15H, 15T-slotted hole, 16-arrow, 20-controller, 22a, 22b-safety valve, 23a, 23b-detection valve, 24a, 24b-switch valve, 25a, 25b-pipeline, 29-VDC circuit, 30-inclined shaft pump, 32-live axle, 33-plectane, 36-cylinder body running shaft, 37a, 37b-plate, 37B, 37H, 37T-slotted hole, 38,38a, 38b-cylinder bore, 39-sleeve pipe, a-bottom compartment's compression area and the ratio that pushes up the chamber compression area, B, H, T-mouth, Po-lateral port, Pi-inboard mouth.
Embodiment
Below, with reference to accompanying drawing embodiments of the invention are described,
At first, the fundamental circuit to cylinder driving system of the present invention describes with reference to Fig. 1.In Fig. 1, have 3 suctions, exhaust port B, H, T by electric motor driven two-way discharge type oil hydraulic pump 1, respectively mouth B is connected in the bottom compartment of oil hydraulic cylinder 3, a mouthful H is connected on the chamber, top of oil hydraulic cylinder 3, a mouthful T is connected on the fuel tank 5.Here, 3 mouth B, H of oil hydraulic pump 1, the flow of T are made as QB, QH, QT respectively, in addition the compression area Sb of bottom compartment of oil hydraulic cylinder 3 is made as α with the ratio (Sb/Sh) that pushes up chamber compression area Sh, like this, the discharge relation of mouthful B, H, T satisfies two following formula.
QB＝QH+QT (1)
QB/QH＝Sb/Sh＝α (2)
Have 3 mouth B, H of this relation, the oil hydraulic pump 1 of T, for example can be made of plunger pump, Fig. 2 is the sectional perspective sectional view of major component structure of this plunger pump of expression embodiment 1.
(embodiment 1)
In Fig. 2, on the cylinder unit 11 of drum, be formed with the regulation number parallel (n 's) cylinder body with axial direction, plunger 12 is housed respectively in this cylinder body.On this cylinder unit 11 and with the end face of plunger 12 opposite sides on be formed with the lateral port Po and the inboard mouthful Pi of the regulation number that is communicated with each plunger 12, this end face and valve plate 13 connect.On valve plate 13, with the axle center is the center, be formed with the circular-arc slotted hole 15B of conduct mouthful B in a side, along the circumferential direction be formed with side by side at the circular-arc slotted hole 15H of the conduct mouth H in the outside and the circular-arc slotted hole 15T of the conduct mouth T of side within it at opposite side, and above-mentioned respectively slotted hole 15B is connected with a lateral port Po and an inboard mouthful Pi, slotted hole 15H is connected with lateral port Po, and slotted hole 15T is connected with an inboard mouthful Pi.In addition, at each plunger 12, dock with the swash plate (swashplate) 14 that is fixed on the not shown pump case with the tilt angle θ (swivel angle) (hereinafter referred to as the swash plate angle) that stipulates sliding freely.Cylinder unit 11 is installed on the not shown axle, this axle and cylinder unit 11 rotatable being supported on freely on the above-mentioned pump case.
Below, with reference to Fig. 2 the action of the oil hydraulic pump 1 of above-mentioned plunger pump type is described.When the axle of oil hydraulic pump 1 rotated, cylinder unit 11 was rotated, and the plungers 12 that are contained in the cylinder unit 11 are followed the swash plate 14 that tilts with above-mentioned swash plate angle θ and carried out back and forth movement, the pumping action that sucks, discharges with performance repeatedly.At this moment, when cylinder unit 11 when the direction of illustrated arrow 16 is rotated, the plunger 12 that links to each other with the slotted hole 15B (mouthful B) of valve plate 13 enters induction stroke, and the plunger 12 that links to each other with slotted hole 15H (mouthful H), 15T (mouthful T) enters discharge stroke.When cylinder unit 11 being rotated continuously by motor 2, will suck oil from mouth B continuously, discharge the oil of (following detailed description) shunting to scale from mouth H and mouthful T.When cylinder unit 11 continuously when rotating with above-mentioned opposite direction, will suck oil to scale from a mouth H and a mouthful T continuously, and discharge the oil at its interflow from mouth B.
At this, when all the cylinder body numbers plunger pump are made as n, be communicated with mouth H (promptly, Po is corresponding with lateral port) the cylinder body number is made as nH, (that is, corresponding with inboard mouthful of Pi) the cylinder body number that is communicated with mouth T is made as nT, be communicated with mouth B (promptly, corresponding with lateral port Po and inboard mouthful Pi) when the cylinder body number is made as nB, then
n＝nH+nT＝nB。(3)
In addition, as preceding above-mentioned, when the ratio (Sb/Sh) when being made as α of the compression area Sb of bottom compartment of oil hydraulic cylinder 3 with top chamber compression area Sh, according to (3) formula,
α=n/nH=1+nT/nH is so obtain
nT/nH＝α-1 (4)
That is, than α, need to be provided with the cylinder body that is communicated with mouthful H and count nH and reach the cylinder body that is communicated with mouth T and count nT according to the above-mentioned compression area of oil hydraulic cylinder 3.
Below, exemplify several formation examples and describe.As the 1st example, at above-mentioned compression area than α=2 o'clock, i.e. (more on the general oil hydraulic cylinder) when " bottom compartment's compression area Sb=2 * chamber, top compression area Sh ", be nT/nH=1 owing to becoming from (4) formula, so cylinder body is counted nH and cylinder body and is counted nT and equate to be provided with, for example, when all cylinder bodies being counted n be made as 10, just can constitute the plunger pump of arrangement as shown in Figure 3.In addition, as the 2nd example, at above-mentioned compression area than α=3/2 o'clock, promptly, when " the compression area Sb=of bottom compartment (3/2) * top chamber compression area Sh ", be nT/nH=1/2 owing to becoming from (4) formula, so, for example be made as 9, just can constitute the plunger pump of arrangement as shown in Figure 4 when all cylinder bodies are counted n.In addition, the H of Fig. 3, Fig. 4 has represented that the cylinder body that is communicated with mouth H, T represented the cylinder body that is communicated with mouth T.
Below, to by the above-mentioned action that constitutes, describe with reference to Fig. 1 and Fig. 2.
At first, when make oil pump 1 when the direction of arrow shown in Figure 2 16 is rotated by motor 2, oil from mouth B inhalant liquid cylinder pressure 3 bottom compartments, and with its part, discharge and supply with top chamber than the pressure oil of the flow of α from mouth H corresponding to above-mentioned compression area, in addition flow is discharged in the fuel tank 5 from mouth T.In addition, when oil pump 1 when rotating with arrow 16 opposite directions shown in Figure 2, from the oil of the chamber, top of mouth H inhalant liquid cylinder pressure 3, and suck oil in the fuel tank 5 from mouth T, behind the oil interflow of two mouths, discharging and supply with the bottom compartment than the pressure oil of the corresponding flow of α from mouth B with above-mentioned compression area.
Owing to be formed with above-mentioned structure, thereby can obtain following effect.
For balance by the compression area difference of the chamber, top of oil hydraulic cylinder and bottom compartment and delivery volume that causes and the poor part between the discharge capacity, the ratio of the suction of oil hydraulic pump 1 and exhaust port quantity, sense of rotation according to oil hydraulic pump was made as 1: 2 or 2: 1, so that the total amount separately of its intake and discharge capacity equates, and, owing to use the flow that is connected the mouth in the bottom compartment and be connected the flow-rate ratio of pushing up the mouth on the chamber, the two-way discharge type oil hydraulic pump 1 that equates than α of compression area with bottom compartment and chamber, top, control discharge capacity with the rotating speed of controlling this oil hydraulic pump to oil hydraulic cylinder 3, therefore, utilize an oil hydraulic pump just can on the loop circuit, control, do not need as in the past, for balance to the required other oil hydraulic pump of the flow of the chamber, top of oil hydraulic cylinder and bottom compartment and accumulator etc.Thereby, because loop structure becomes simple and reduced components number,, and can improve reliability so fabricating cost is low.
Between oil hydraulic pump 1 and oil hydraulic cylinder 3, above-mentioned reality is not set opens the cylinder body of putting down in writing in the clear 60-122579 communique that resembles and drive the flow switching valve of circuit controls with valve, thereby just can on this flow switching valve, energy loss not occur yet.In addition, utilize the pressure oil that sucks from the mouth B or mouthful H of oil hydraulic pump 1 that motor 2 is rotated, just can obtain regenerated energy.Therefore can improve and drive loop energy efficiency on the whole.
In addition, owing to be by the rotating speed of control motor 2 and flow and the conversion of discharge direction that sense of rotation is controlled oil hydraulic pump 1, so do not need such regulator of swash plate angle control mode or regulator primer pump, thereby can constitute with simple structure.
In addition, the control of the discharge direction of oil hydraulic pump 1 of the present invention is to carry out with the sense of rotation of switching motor 2, but also be not limited to this point, oil hydraulic pump 1 can certainly be made of two converter-types (ramp type, or clino-axis type), and control the discharge direction by controlling its tilt angle.
Below, with reference to Fig. 5 the embodiment who cylinder driving system of the present invention is applied to the hydraulic shovel of building machinery one example is described.Fig. 5 is the loop block diagram of present embodiment.Corresponding with each working machine of shear leg, cantilever, scraper bowl, have oil hydraulic cylinder 3B, 3A, 3K (below, when not distinguishing especially, only be designated as oil hydraulic cylinder 3), and have the oil hydraulic pump 1B, the 1A that drive oil hydraulic cylinder separately, 1K (below, equally only be designated as oil hydraulic pump 1), and rotation drives motor 2B, 2A, the 2K (below, equally only be designated as motor 2) of this oil hydraulic pump 1B, 1A, 1K.3 mouth B, H, T that oil hydraulic pump 1 and above-mentioned fundamental circuit shown in Figure 1 have same suction, discharge capacity characteristic.The cylinder body corresponding with each working machine of shear leg, cantilever, scraper bowl drives loop CB, CA, CK is a same structure, below, the cylinder body of shear leg is driven loop CB describe.
The mouth H of oil hydraulic pump 1B via the 1st switch valve 24a and pipeline 25a, is connected on the chamber, top of oil hydraulic cylinder 3B, and the mouth B of oil hydraulic pump 1B via the 2nd switch valve 24b and pipeline 25b, is connected in the bottom compartment of oil hydraulic cylinder 3B.The mouth T of oil hydraulic pump 1B is connected on the fuel tank 5.In addition, between pipeline 25a and fuel tank 5, be provided with the 1st safety valve 22a and the 1st and detect valve 23a, between pipeline 25b and fuel tank 5, be provided with the 2nd safety valve 22b and the 2nd and detect valve 23b.The safety valve setting of controller 20 is pressed signal, is imported in the solenoid of the 1st safety valve 22a and the 2nd safety valve 22b.
In addition, in the present embodiment, running shaft is constituted rotation and is driven loop CR by directly (being to pass through speed reducer mostly) driving of motor 2R.And, also can be arranged on the oil hydraulic pump of oil hydraulic motor on the output shaft of motor 2R, and utilize this oil hydraulic motor to come the rotary driving axle by two-way discharge formula.
Each motor 2B, 2A, 2K, 2R for example are made of AC motor such as three phase induction motors, and by transducer 4B, 4A, 4K, 4R when not having special difference (following only remember make transducer 4) control speed separately.The power input terminal of each transducer 4 and is connected the output three-phase alternating voltage of the generator 7 that is driven by motor 6, the VDC circuit 29 that converts VDC to rectifier 7a.And, on VDC circuit 29, connecting the storage battery 8 that constitutes by storage battery and capacitor (battery of capacity charge and discharge greatly).
Each transducer 4, input slave controller 20 be to the speed command of each working machine, and be made as zero this speed command with from the deviate of the rate signal of each motor 2 velocity transducer, comes controlling torque (motor current).In addition, transducer 4, (for example, when shear leg, cantilever are descended control, when perhaps braking is stopped the rotation etc.) gives VDC circuit 29 power delivery of each motor 2 regeneration when opening regenerative braking in speed controlling.With this regenerated energy or charging accumulators 8, or when driving other working machines, consume with motor 2.
Below, the work that the hydraulic shovel working machine that is formed by this structure is driven the loop describes.
The control of the stretching speed of each oil hydraulic cylinder 3 and flexible direction is by using each self-corresponding motor 2 to control the rotating speed of oil hydraulic pump 1 and discharge direction, and this point is identical with the foregoing description.The part of the difference in flow that is caused by the compression area difference of the bottom compartment of oil hydraulic cylinder 3 and chamber, top is recently absorbing according to the intake of the mouth B of oil hydraulic pump 1 and mouthful H, discharge capacity.
When the oil pressure in the pipeline 25a rises to the setting pressure of the 1st safety valve 22a when above, the 1st safety valve 22a opens, and pipeline 25a is communicated with fuel tank 5 to prevent producing abnormal pressure in pipeline 25.In addition, similarly, when the oil pressure in the pipeline 25b rises to the setting pressure of the 2nd safety valve 22b when above, the 2nd safety valve is opened, and pipeline 25b is communicated with fuel tank 5 to prevent producing abnormal pressure in pipeline 25b.Therefore, when digging operation, even unusual in the bottom compartment of oil hydraulic cylinder 3, more than the indoor generation setting pressure in top, but owing to can be controlled at below the setting pressure, so can protect hydraulic machine.
In addition, when in the bottom compartment of hydraulic cylinder 3 or when pushing up indoor generation abnormal pressure, in the chamber, top of its opposition side or bottom compartment, can produce negative pressure (or vacuum).At this moment, the 1st detects valve 23a is communicated with chamber, top and fuel tank 5, or the 2nd detect valve 23b and be communicated with bottom compartment and fuel tank, so that oily inflow produced in the chamber, top or bottom compartment of negative pressure (or vacuum), to prevent negative pressure (or vacuum).Oil hydraulic cylinder 3 is stably worked.
In addition, when the rotation of oil hydraulic pump 1 stops, because the deadweight of working machine (shear leg, cantilever, scraper bowl) and on the flexible direction of oil hydraulic cylinder 3, promptly the situation of the external force of being subjected to arranged on the direction that working machine descends.At this moment, the oil in the bottom compartment of oil hydraulic cylinder 3, or push up indoor oil can be via moving in the chamber, top of shifting to an opposite side in the oil hydraulic pump 1 or the bottom compartment.Therefore, by disconnecting the decline that the 1st switch valve 24a and the 2nd switch valve 24b just can prevent that the deadweight because of above-mentioned working machine from bringing.
Can obtain following effect according to present embodiment.
The flow-rate ratio of two mouth B, H of oil hydraulic pump 1 (i.e. the ratio of a side intake and the opposing party's discharge capacity) according to the compression area of the bottom compartment of oil hydraulic cylinder 3 separately and chamber, top than constituting, these two mouth B, H are connected in the bottom compartment, chamber, top of oil hydraulic cylinder 3, make to suck or discharge this intake to be connected with fuel tank with another mouthful T of the part of the difference of discharge capacity.And discharge capacity and discharge direction by motor 2 these oil hydraulic pumps 1 of control just can drive oil hydraulic cylinder 3 on the loop circuit.Therefore, use the pressure oil that sucks from the mouth B or mouthful H of oil hydraulic pump 1 to make motor 2 rotations, and can obtain regenerated energy.In addition, in the speed controlling of carrying out working machine, promptly carry out discharge capacity when control of oil hydraulic pump 1, for example, and at shear leg, when cantilever descends or rotation brake when stopping etc., the regenerative braking that can implement by motor 2.Its result charges the energy of this regeneration in storage battery, or consumes when driving other working machines, and like this, the energy of can applying in a flexible way has effectively reduced energy loss again, and can improve energy efficiency.
In addition, for the cavitation effect that prevents to cause, also can use supply pump in the loop circuit, to replenish that part of oil of missing in each hydraulic machine in addition because of the low on fuel in the above-mentioned loop circuit.
In addition, in the above-described embodiments, the example that the motor by each is carried out speed controlling is illustrated, but not only like this, also can use torque control etc. to carry out.
(embodiment 2)
Below, with reference to Fig. 6～Fig. 8 embodiment 2 is described.Fig. 6 is the sectional view of embodiment 2 oil hydraulic pump, and Fig. 7 is the tool portion perspective, cut-away view of same oil hydraulic pump major component, and Fig. 8 is the cylinder body block diagram of same oil hydraulic pump.
In Fig. 6, inclined shaft pump 30, rotatably support has live axle 32 in shell 31, and an end of this live axle 32 is provided with plectane.With the face of the above-mentioned plectane 33 of live axle 32 opposite sides on, and be connected cylinder body running shaft 36 between the shell 31, the axle center of this cylinder body running shaft 36 is with respect to the axle center of above-mentioned live axle 32, only tilt angle θ is obliquely installed in accordance with regulations.In the one distolateral center of rotation portion that is connected 33 of above-mentioned plectanes of cylinder body running shaft 36, another distolateral rotatable being supported on freely on the shell 31.In addition, cylinder unit 35 with the state that is positioned sense of rotation by intercalation on the periphery of cylinder body running shaft 36.As shown in Figure 8, on this cylinder unit 35, around above-mentioned cylinder body running shaft 36, slightly uniformly-spaced and with cylinder body running shaft 36 to be formed with the cylinder bore 38 of specified quantity, insertion plunger 34 each cylinder bore 38 in abreast.The front end of plunger 34 slidably is connected on the face of cylinder body running shaft 36 1 sides of above-mentioned plectane 36 freely.According to above structure, utilize the rotation of the plectane 33 that drives by means of live axle 32 rotations, making cylinder unit 35 by cylinder body running shaft 36 is that rotate at the center with cylinder body running shaft 36, thereby makes plunger 34 carry out back and forth movement in the cylinder bore 38 of cylinder unit 35.In addition, be fixed on the valve plate 37 on the shell 31, slidably contact freely on the bottom surface of cylinder unit 35.
Each cylinder bore 38 that on cylinder unit 35, forms, corresponding with mouth H and mouthful T (with reference to Fig. 1) respectively as shown in Figure 8, be the formation same in this example with the housing structure shown in Figure 3 of the foregoing description 1.In addition, as Fig. 6, shown in Figure 7, on the bottom of each cylinder bore 38 corresponding, be formed with the lateral port Po and the inboard mouthful Pi that are communicated with this cylinder bore 38 and cylinder unit 35 bottom surfaces respectively with mouth H and mouth T difference.In addition, on valve plate 37, with the axle center is the center, is formed with the circular-arc slotted hole 37B as mouthful B on a side, along the circumferential direction is being formed with circular-arc slotted hole 37H as mouth H on the outside of opposite side side by side, is being formed with circular-arc slotted hole 37T as mouthful T on the side within it.And above-mentioned slotted hole 37B is connected with a lateral port Po and an inboard mouthful Pi, and above-mentioned slotted hole 37H is connected with lateral port Po respectively, and above-mentioned slotted hole 37T is connected with an inboard mouthful Pi.
In the present embodiment, the diameter of each cylinder bore 38 corresponding with mouth H and mouthful T is to set according to the compression area Sb of bottom compartment of the oil hydraulic cylinder of driven object and the ratio α of top chamber compression area Sh.Promptly, shown in above-mentioned (3) formula, if " n=nH+nT " (in this example, all cylinder bodies are counted n=10, nH=nT=5), the compression area of each cylinder bore 38 corresponding with mouth H be respectively S1H, S2H ... SnH, the compression area of each cylinder bore 38 corresponding with mouth T be respectively S1T, S2T ... SnT, process the diameter of each cylinder bore 38 so, will satisfy following formula, that is α=[(S1H+S2H+ ... + SnH)+(S1T+S2T+ ... + SnT)]/(S1H+S2H+ ... + SnH)=1+ (S1T+S2T+ ... + SnT)/(S1H+S2H+ ... + SnH).
And the diameter of cylinder bore 38 separately also can be made as identically by each mouthful H, a mouthful T, and only also can being made as, some is a diameter inequality.Example shown in Figure 8 represented in 5 mouth H, and the diameter of the cylinder bore 38a of 2 mouth H is made as diameter less than the cylinder bore 38b of other mouthfuls H and mouthful T.
According to embodiment 2 structure, the effect in embodiment 1, also just can obtain following effect.
In the present embodiment, owing to adjusted the size of cylinder bore 38 diameters, so, just can precision than α set the intake between mouth H, the T of oil hydraulic pump or the ratio of discharge capacity well according to the compression area between the chamber, top, bottom compartment of oil hydraulic cylinder.Thereby the compression area between the bottom compartment, chamber, top of oil hydraulic cylinder just can be easily and the corresponding well different multiple oil hydraulic cylinder of precision than α.In addition, owing to just possess the function of double pump with 1 pump, thus can accomplish miniaturization, and, because application inclined shaft pump of the present invention just can reach speed up, so, can realize reducing cost and improve vehicle boarded property.And, owing to can use each cylinder body with maximum volume efficient, so can more effectively use this oil pump.
(embodiment 3)
Below, embodiment 3 is described with reference to Fig. 9.Fig. 9 is the sectional view of embodiment 3 cylinder body major component.
In the foregoing description 2, in order to adjust the diameter of each cylinder bore 38, aperture itself is processed and adjusts than α according to target, but in the present embodiment, be to have according to adjusting in the sleeve pipe 39 insertion cylinder bore 38 of target than the regulation internal diameter of α by handle.According to the rough adjustment of target than α, as described in above-mentioned embodiment 1, be to count nH according to the cylinder body of adjusting corresponding mouthful H to count nT with the cylinder body of corresponding mouthful of T and carry out, carry out trickle adjustment in the cylinder bore 38 that sleeve pipe 39 insertions of having adjusted internal diameter are stipulated.
Diameter as cylinder bore 38, be have in advance can cover the such maximum diameter of this oil hydraulic pump Applicable scope cylinder unit as universal component, the oil hydraulic pump that possesses this parts is deposited in the warehouse, like this, is being desirable aspect stock control cost and the cost of production.According to this way, owing to just the internal diameter of sleeve pipe 39 having been carried out adjusting and being inserted in the cylinder bore 38 to be suitable for oil hydraulic cylinder, so improved versatility.
According to this structure owing to only need to adjust the internal diameter of sleeve pipe 39, so, can be easily and precision constitute well the compression area that is suitable between oil hydraulic cylinder bottom compartment and chamber, top than α, have an oil hydraulic pump with the double pump same function.In addition, owing to only need casing replacing 39, just can make its bottom compartment be applicable to other different oil hydraulic cylinders than α, so can improve versatility with the compression area that pushes up between the chamber.And, owing to can carry out the stock to the oil hydraulic pump that the cylinder unit with above-mentioned overdimensioned cylinder body aperture has been installed as the generalization parts, so stock control cost, cost of production are all lower.In addition, therefore other effects omit explanation owing to identical with the above embodiments.
(embodiment 4)
Below, embodiment 4 is described.Figure 10 is the plan view of embodiment 4 oil hydraulic pump valve plate.As suitable machine, be the example explanation with identical inclined shaft pump shown in Figure 6 with embodiment 2.And, the structure that has a roughly the same function with Fig. 6～structure shown in Figure 8 is indicated same-sign, and omits its explanation.
In Figure 10, valve plate 37 has two boards 37a, 37b, on a side plate 37a, be formed with as the circular-arc slotted hole 37B of above-mentioned mouthful B with as the circular-arc slotted hole 37T of above-mentioned mouthful of T, on the opposing party's plate 37b, be formed with circular-arc slotted hole 37H as above-mentioned mouthful of H.One side's plate 37a, be provided with the side of slotted hole 37B, have the large-diameter portion with the summary semi-circular shape of cylinder unit 35 roughly the same external diameters, be provided with the side of slotted hole 37T, be provided with the minor diameter of the summary semi-circular shape of summary intermediate outer with slotted hole 37T external diameter and slotted hole 37H external diameter.In addition, the opposing party's plate 37b, have with cylinder unit 35 slightly same outer diameter as periphery circle portion and than the minor diameter external diameter of above-mentioned plate 37a interior week circle portion of macropore internal diameter slightly, and formation semi-annular shape.And, two boards 37a, 37b, mutually along circumferencial direction slidably freely with above-mentioned minor diameter with above-mentioned in week circle portion contact, and, portion is arranged on the circumferencial direction end with part repetition, so that always cover the bottom surface of cylinder unit 35 and oil-proof.In addition, in order to block the gap of thickness direction between two boards 37a, the 37b in this repetition portion, be formed with side wall portion (not shown) on any one party in two boards 37a, 37b.In addition, can predetermined angular with respect to a side plate 37a be rotated, and whirligig (not shown) such as orientable motor be set on the opposing party's the plate 37b.
Below, the effect of present embodiment is described.When two boards 37a, 37b when circumferencial direction staggers relatively (mouthful H) changes with the relative position of slotted hole 37T (mouthful T) because slotted hole 37H, so suction or the efflux time of the mouth H after staggering can change.Therefore, the cylinder body volumetric efficiency corresponding with mouth H will change, that is, the volume that sucks equivalently or discharge will change.Therefore, by for satisfying target, come inching cylinder body volume than the relative position that α adjusts slotted hole 37H (mouthful H) and slotted hole 37T (mouthful T).
Like this, the effect in obtaining embodiment 2, can also obtain following effect.The relative angle of mouth H, the T of two boards 37a, 37b by adjust constituting valve plate 37 can at random change volumetric efficiency and carry out inching with the ratio α that is fit to oil hydraulic cylinder.Thereby, can make same oil hydraulic pump be applicable to multiple oil hydraulic cylinder, thereby can improve versatility, because oil hydraulic pump can be accomplished generalization, so can reduce stock control cost and cost of production.
(embodiment 5)
Below, embodiment 5 is described with reference to Figure 11, Figure 12.Figure 11 is the plan view of embodiment 5 oil hydraulic pump valve plate, and Figure 12 is an A-A sectional view among Figure 11.As suitable machine, be the example explanation with same inclined shaft pump shown in Figure 6 with embodiment 2.And, the structure with Fig. 6～shown in Figure 8 is had the structure of roughly the same function, indicate same-sign and omit its explanation.
Valve plate 37c, the circumferencial direction opening angle β 1 as the slotted hole 37H of mouth H only likens the circumferencial direction opening angle β 2 little predetermined angulars into the slotted hole 37T of mouth T to.And, with the circumference of the same radius of above-mentioned slotted hole 37H on, be formed with the circular-arc slotted hole 37Ta that is communicated with above-mentioned slotted hole 37T.In addition, clamp cylinder body running shaft 36 and with slotted hole 37H, slotted hole 37Ta and the opposite side of slotted hole 37T, be formed with circular-arc slotted hole 37B as mouthful B.Structure beyond the valve plate 37c is owing to identical with the foregoing description 1～3, so omitted explanation at this.
Below, describe for the effect that produces by constituting of present embodiment.When cylinder unit 35 is rotated, when cylinder bore 38 is communicated with via lateral port Po and with slotted hole 37H, the plunger 34 of this cylinder body 38 as mouthful H with and the performance function, when being communicated with slotted hole 37Ta, the plunger 34 of this cylinder bore 38 is used as mouthful T and is brought into play function.Therefore, be under the situation of oil hydraulic pump discharge stroke one side at slotted hole 37H, slotted hole 37Ta and slotted hole 37T, have the most of oil in the cylinder bore 38 of lateral port Po, via discharging from mouth H behind the slotted hole 37H, its remaining oil is via discharging from mouth T behind slotted hole 37Ta and the slotted hole 37T.In addition, has the oil in the cylinder bore 38 of inboard mouthful of Pi, via discharging from mouth T behind the slotted hole 37T.And, under the situation of induction stroke, become above-mentioned opposite oily inflow direction.Thereby, become the cylinder body capacity of mouthful H by the oil mass of slotted hole 37H, become the cylinder body capacity of mouthful T by the oil mass of slotted hole 37Ta and slotted hole 37T, therefore, according to adjusting among slotted hole 37H, slotted hole 37Ta and the slotted hole 37T any one circumferencial direction opening angle β or opening area at least, just can adjust than α the compression area that push up between the chamber bottom compartment of above-mentioned oil hydraulic cylinder.
Like this, the effect in obtaining embodiment 2, can also obtain following effect.Promptly, to compression area between the bottom compartment of above-mentioned oil hydraulic cylinder and chamber, top than the rough setting of α, be to count nT according to the mouth T that the mouth H that adjustment has a lateral port Po counts nH with cylinder body and has an inboard mouthful of Pi with cylinder body to carry out, in this is adjusted, according to any one circumferencial direction opening angle β and opening area just can carry out difficult inching at least among the slotted hole 37H, the slotted hole 37Ta that adjust valve plate 37c and the slotted hole 37T.Thereby the bottom compartment of above-mentioned oil hydraulic cylinder and the compression area of top between the chamber can be easily than α and the corresponding well different multiple oil hydraulic cylinder of precision, in addition, with above-mentioned same, because can accomplish the miniaturization and the speed up of pump, so, not only can reduce cost but also can improve vehicle boarded property.
In the foregoing description 2～embodiment 5, the example of the oil hydraulic pump that is suitable for as the present invention is that example illustrates with the inclined shaft pump, but is not only limited to this point, also is applicable to the ramp type pump certainly.
As above explanation can obtain following effect according to the present invention.
3 mouths of hydraulic pump have: the 1st mouthful discharge rate (soakage) as the 2nd mouthful with The 3rd mouthful separately soakage (discharge rate) sum, the 1st mouthful discharge rate (soakage) and the The relation of compression area ratio of the bottom compartment of the ratio hydraulic cylinder of 2 mouthfuls soakage (discharge rate) and chamber, top. The 1st mouthful this hydraulic pump is connected in the bottom compartment, and the 2nd mouthful is connected on the chamber, top, the 3rd mouthful Be connected on the fuel tank, and according to the control rotating speed of this hydraulic pump and direction of rotation control discharge rate and Discharge direction, like this, use a hydraulic pump just can consist of the drive system of loop circuit. Thereby energy Simple and low cost consists of with loop structure. In addition, owing to do not need the flow-control transfer valve Just can reduce energy loss, and, utilize hydraulic cylinder the bottom compartment or the top chamber force feed, pass through hydraulic pressure Pump just can make motor rotate, so can obtain regenerated energy.
Claims (3)
1. a cylinder driving system is characterized in that, is provided with:
Oil hydraulic cylinder (3) and
Oil hydraulic pump (1), this oil hydraulic pump, have: supply with oil or discharge oily the 1st mouthful (B) from described bottom compartment to the bottom compartment of this oil hydraulic cylinder (3), with discharge oil from the chamber, top of oil hydraulic cylinder (3) or supply with the 2nd mouthful (H) of oil to chamber, described top, suck exhaust ports with the 3rd mouthful (T) 3 that discharge oil from fuel tank (5) or supply with oil to described fuel tank (5), and with the intake of the 1st mouthful (B) as the sum of discharge capacity separately of the 2nd mouthful (H) and the 3rd mouthful (T) or with the discharge capacity of the 1st mouthful (B) the sum of intake separately as the 2nd mouthful (H) and the 3rd mouthful (T); With
Drive the driving source (2) of oil hydraulic pump (1).
2. cylinder driving system as claimed in claim 1 is characterized in that:
By to the rotating speed of described driving source (2) and the control of sense of rotation, perhaps carry out discharge capacity, intake to described oil hydraulic pump (1) and the control of discharging direction to control its tilt angle as the described oil hydraulic pump (1) of two converter-types.
3. the energy regenerating method of a cylinder driving system is characterized in that:
Oil hydraulic pump (1), have: supply with oil or discharge oily the 1st mouthful (B) from described bottom compartment to the bottom compartment of oil hydraulic cylinder (3), with discharge oil from the chamber, top of oil hydraulic cylinder (3) or supply with the 2nd mouthful (H) of oil to chamber, described top, suck exhaust ports with the 3rd mouthful (T) 3 that discharge oil from fuel tank (5) or supply with oil to described fuel tank (5), and with the intake of the 1st mouthful (B) as the sum of discharge capacity separately of the 2nd mouthful (H) and the 3rd mouthful (T) or with the discharge capacity of the 1st mouthful (B) the sum of intake separately as the 2nd mouthful (H) and the 3rd mouthful (T); With motor (2) rotating speed and the sense of rotation of described oil hydraulic pump (1) are controlled,
Regenerated energy when reclaiming the regenerative braking of oil hydraulic pump (1) by motor (2).
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002106453 | 2002-04-09 | ||
| JP2002106453 | 2002-04-09 | ||
| JP2003059148 | 2003-03-05 | ||
| JP2003059148A JP2004003612A (en) | 2002-04-09 | 2003-03-05 | Cylinder drive system and method for regenerating its energy |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1450272A true CN1450272A (en) | 2003-10-22 |
| CN1303330C CN1303330C (en) | 2007-03-07 |
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ID=28793553
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031103243A Expired - Fee Related CN1303330C (en) | 2002-04-09 | 2003-04-08 | Cylinder driving system and energy regenerating method thereof |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2004003612A (en) |
| CN (1) | CN1303330C (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1296627C (en) * | 2005-03-15 | 2007-01-24 | 浙江大学 | Double pump-motor hydraulic drive system for a hydraulic motor of engineering machinery |
| CN101865191A (en) * | 2010-04-22 | 2010-10-20 | 浙江新时空水务有限公司 | Liquid excess pressure energy recovery device |
| CN102712123A (en) * | 2009-12-23 | 2012-10-03 | 赫斯基注塑***有限公司 | Injection molding system having a digital displacement pump |
| WO2013127175A1 (en) * | 2012-02-28 | 2013-09-06 | 中联重科股份有限公司 | Hydraulic system, excavator and control method for hydraulic system |
| CN112443369A (en) * | 2019-08-27 | 2021-03-05 | 现代自动车株式会社 | System and method for controlling dual oil pump |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102004061559A1 (en) * | 2004-12-21 | 2006-06-29 | Brueninghaus Hydromatik Gmbh | Hydraulic drive |
| JP2009121649A (en) * | 2007-11-19 | 2009-06-04 | Yanmar Co Ltd | Hydraulic circuit and working machine |
| JP2014105621A (en) * | 2012-11-27 | 2014-06-09 | Yanmar Co Ltd | Hydraulic device |
| JP6323831B2 (en) * | 2014-06-02 | 2018-05-16 | ヤンマー株式会社 | Hydraulic device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60122579U (en) * | 1984-01-28 | 1985-08-19 | 手塚興産株式会社 | hydraulic power mechanism |
| JPH04277180A (en) * | 1991-02-28 | 1992-10-02 | Hitachi Ltd | Fluid pressure elevator |
| ATE141573T1 (en) * | 1992-03-04 | 1996-09-15 | Inventio Ag | METHOD AND DEVICE FOR SAVING ELECTRICAL ENERGY FOR DRIVING A HYDRAULIC ELEVATOR |
| DE4317782C2 (en) * | 1993-05-28 | 1996-01-18 | Jungheinrich Ag | Hydraulic lifting device for battery-powered industrial trucks or the like |
| JP3584999B2 (en) * | 1995-03-06 | 2004-11-04 | 株式会社小松製作所 | ELECTRO-HYDRAULIC HYBRID MOTOR, ITS CONTROL DEVICE, AND ITS CONTROL METHOD |
| JP3862256B2 (en) * | 2000-05-19 | 2006-12-27 | 株式会社小松製作所 | Hybrid machine with hydraulic drive |
| JP3923242B2 (en) * | 2000-07-14 | 2007-05-30 | 株式会社小松製作所 | Actuator control device for hydraulic drive machine |
| US6502393B1 (en) * | 2000-09-08 | 2003-01-07 | Husco International, Inc. | Hydraulic system with cross function regeneration |
-
2003
- 2003-03-05 JP JP2003059148A patent/JP2004003612A/en active Pending
- 2003-04-08 CN CNB031103243A patent/CN1303330C/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1296627C (en) * | 2005-03-15 | 2007-01-24 | 浙江大学 | Double pump-motor hydraulic drive system for a hydraulic motor of engineering machinery |
| CN102712123A (en) * | 2009-12-23 | 2012-10-03 | 赫斯基注塑***有限公司 | Injection molding system having a digital displacement pump |
| CN102712123B (en) * | 2009-12-23 | 2014-10-29 | 赫斯基注塑***有限公司 | Injection molding system having a digital displacement pump |
| CN101865191A (en) * | 2010-04-22 | 2010-10-20 | 浙江新时空水务有限公司 | Liquid excess pressure energy recovery device |
| CN101865191B (en) * | 2010-04-22 | 2013-04-24 | 浙江新时空水务有限公司 | Liquid excess pressure energy recovery device |
| WO2013127175A1 (en) * | 2012-02-28 | 2013-09-06 | 中联重科股份有限公司 | Hydraulic system, excavator and control method for hydraulic system |
| CN112443369A (en) * | 2019-08-27 | 2021-03-05 | 现代自动车株式会社 | System and method for controlling dual oil pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2004003612A (en) | 2004-01-08 |
| CN1303330C (en) | 2007-03-07 |
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