CN110431317A - Oil hydraulic system - Google Patents
Oil hydraulic system Download PDFInfo
- Publication number
- CN110431317A CN110431317A CN201880020464.5A CN201880020464A CN110431317A CN 110431317 A CN110431317 A CN 110431317A CN 201880020464 A CN201880020464 A CN 201880020464A CN 110431317 A CN110431317 A CN 110431317A
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- China
- Prior art keywords
- flow path
- electromagnetic proportional
- proportional valve
- valve
- secondary pressure
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Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
Abstract
Oil hydraulic system has: connecting and pass through the electromagnetic proportional valve that a pressure pipe road is connect with auxiliary pump with adjuster by secondary pressure pipe road；Diverge from a pressure pipe road and be connected to storage tank, be provided with a pair of of flow controller it is urgent when pipeline；Secondary pressure pipe road is segmented into first flow path and second flow path, and pipeline segmentation is the form setting of upstream flow path and downstream flow path when will be urgent between a pair of of flow controller, switches to the switching valve of operating position from neutral position when the secondary pressure of electromagnetic proportional valve is more than setting value；And according to the operation signal exported from operating device, to the control device of electromagnetic proportional valve conveying instruction current in the form of the secondary pressure between the minimum value and maximum value bigger than setting value is exported by electromagnetic proportional valve.
Description
Technical field
The present invention relates to the oil hydraulic systems of electrical positive control (Positive Control) mode.
Background technique
All the time, the oil hydraulic system of electrical positive control mode is used in building machinery, industrial machinery etc..For example, specially
Oil hydraulic system 100 as shown in Figure 9 is disclosed in sharp document 1.
In the oil hydraulic system 100, the tilt angle of the pump 110 of variable capacity type is adjusted by adjuster 120.Adjuster 120 wraps
Flow control piston 121 and horsepower control piston 122 are included, is pressed with the control for acting on flow control piston 121 and is increased or make
Pump discharge pressure for horsepower control piston 122 reduces and increases the tilt angle (discharge flow) of pump 110.In addition, adjuster 120
Be formed as flow control piston 121 preferentially to play with the lesser side that is limited to discharge flow in horsepower control piston 122
The structure of function.
Adjuster 120 is connect by secondary pressure pipe road 130 with electromagnetic proportional valve 140.Electromagnetic proportional valve 140 is omited with figure
Operating device, that is, guide operating valve operating quantity is bigger and to press to adjuster 120 using higher secondary pressure as above-mentioned control defeated
Out.
The switching valve 150 of pilot-operated type is provided on secondary pressure pipe road 130.In the normal situation of electromagnetic proportional valve 140, cut
It changes valve 150 and is located at operating position (right positions of Fig. 9) using the secondary pressure of electromagnetic proportional valve 140, make electromagnetic proportional valve 140
Secondary pressure act on flow control piston 121.On the other hand, function is not played normally due tos failure etc. in electromagnetic proportional valve 140
Can, in the case that secondary buckling is zero, switching valve 150 switches to neutral position (leftward position of Fig. 9), makes from pilot operated
The first pilot of valve output acts on flow control piston 121.Even if electromagnetic proportional valve 140 does not work orderly as a result, also can
According to the operating quantity of guide operating valve come the discharge flow of increasing pump 110.
But since when electromagnetic proportional valve 140 does not work orderly, switching valve 150 is primary by electromagnetic proportional valve 140
Pressure acts on horsepower control piston 122, so power shifting (powershift) is Chong Die with horsepower control.Therefore, horsepower controls
Than more strongly being operated when 140 normal operation of electromagnetic proportional valve, so that the discharge flow of the pump 110 relative to each discharge pressure is upper
Limit is lower.
Existing technical literature:
Patent document:
Patent document 1: No. 4041789 bulletins of Japanese Patent No..
Summary of the invention
Problems to be solved by the invention:
But in structure shown in Fig. 9, relatively long pipeline is needed (such as to build the position for being disposed substantially away from pump 110
For in driver's cabin in machinery) guide operating valve (operating device) and the connection of switching valve 150, and adjuster 120 needs flow control
Two compression chambers of piston 121 and horsepower control piston 122 processed, structure are more complex.
Therefore, electromagnetism of the secondary pressure as control pressure even is being exported to adjuster it is an object of that present invention to provide a kind of
Proportioning valve does not work orderly and in the case that its secondary buckling is zero, can also be ensured to a certain extent with easy structure
The oil hydraulic system of the discharge flow of pump.
The means solved the problems, such as:
In order to solve foregoing problems, oil hydraulic system of the invention is characterized in that having: output and the operating quantity for operation portion
The operating device of corresponding operation signal；The main pump of variable capacity type；Adjuster, the adjuster include flow control piston,
And as the control pressure for acting on the flow control piston increases and increases the tilt angle of the main pump；Auxiliary pump；Solenoid-operated proportional
Valve, the electromagnetic proportional valve connect with the adjuster by secondary pressure pipe road and passes through a pressure pipe road and the auxiliary pump connects
It connects, presses to the tune for higher secondary pressure as the control as the operation signal exported from the operating device is bigger
Save device output；Diverge from a pressure pipe road and be connected to storage tank and be provided with a pair of of flow controller it is urgent when pipeline；With by institute
It states secondary pressure pipe road and is segmented into the first flow path of the electromagnetic proportional valve side and the second flow path of the adjuster side, and described
Pipeline segmentation is the switching valve of the form setting of upstream flow path and downstream flow path when will be described urgent between a pair of of flow controller, described
Switching valve blocks the first flow path in the case where neutral position and makes the upstream flow path and the downstream flow path and described
Second flow path connection, when the secondary pressure of the electromagnetic proportional valve is more than setting value, being shifted to using the secondary crush-cutting makes described the
One flow path is connected to the second flow path and blocks the operating position of the upstream flow path and the downstream flow path；And control dress
It sets, the control device is according to the operation signal exported from the operating device, so that described in electromagnetic proportional valve output ratio
The form of secondary pressure between setting value big minimum value and maximum value conveys instruction current to the electromagnetic proportional valve.
According to above structure, in the normal situation of electromagnetic proportional valve, switching valve is located at operating position, thus solenoid-operated proportional
The secondary pressure of valve acts on the flow control piston of adjuster by secondary pressure pipe road.Therefore, it can be controlled using electromagnetic proportional valve
The tilt angle (discharge flow) of pump.On the other hand, electromagnetic proportional valve do not work orderly and its it is secondary pressure be zero the case where
Under, switching valve is switched to neutral position, and pipeline is flowed from auxiliary pump to storage tank when working oil passes through urgent.Pipeline when urgent as a result,
On a pair of of flow controller between intermediate pressure the flow control piston of adjuster is acted on by the second flow path on secondary pressure pipe road.
As a result it can ensure the discharge flow pumped to a certain extent.Moreover, via switching valve it is urgent when pipeline it is shorter, and adjust
Device controls piston without previous such horsepower, as long as there is the compression chamber of flow control piston, so can be with easy
Structure obtains said effect.
Above-mentioned oil hydraulic system be also possible to be also equipped with drive the main pump and the auxiliary pump by the control device control
The engine of system；The control device is determining the electricity according to the monitoring of the instruction current conveyed to the electromagnetic proportional valve
When magnetic proportioning valve does not work orderly, near the rotational speed regulation of the engine to the maximum revolving speed of motor torque.Root
The pump running torque relative to pump discharge pressure according to the structure, when can to a certain extent not work orderly electromagnetic proportional valve
Maximum value be set to it is higher.So as to increase the intermediate pressure between a pair of of flow controller to a certain extent, it is ensured that solenoid-operated proportional
The discharge flow of pump when valve does not work orderly is more.
Being also possible to the setting value is the first setting value；It is corresponding with the operation signal exported from the operating device
The maximum value of the secondary pressure of the electromagnetic proportional valve is following in the second setting pressure lower than the discharge pressure of the auxiliary pump；It is described to cut
Valve is changed when the secondary pressure of the electromagnetic proportional valve is more than second setting value, blocks the first flow path and makes the upstream
Flow path is connected to the downstream flow path and the second flow path.According to this structure, it is not played normally in electromagnetic proportional valve even
In the case that function and its secondary pressure are equal to primary pressure, it can also ensure the discharge flow pumped to a certain extent.
Invention effect:
According to the present invention, even to adjuster export it is secondary pressure as control press electromagnetic proportional valve do not work orderly
And in the case that its secondary pressure is zero, the discharge flow pumped can be also ensured to a certain extent with easy structure.
Detailed description of the invention
Fig. 1 is the schematic structural diagram of the oil hydraulic system of first embodiment according to the present invention；
Fig. 2 is the operating quantity and the figure of the relationship of the instruction current to electromagnetic proportional valve shown for the operation portion of operating device
Table；
Fig. 3 is the chart for showing the relationship of the secondary pressure to the instruction current and electromagnetic proportional valve of electromagnetic proportional valve；
Fig. 4 is the chart shown to the control pressure and the relationship of the discharge flow of main pump of adjuster；
5A and 5B in Fig. 5 relate to the chart of the main pump in variation, and the 5A in Fig. 5 shows discharge flow restraining line
Chart, the 5B in Fig. 5 are the charts for showing the relationship of pump discharge pressure and pump running torque；
Fig. 6 is the chart for showing the relationship of revolving speed and motor torque of engine；
Fig. 7 is the schematic structural diagram of the oil hydraulic system of the second implementation form according to the present invention；
Fig. 8 is the chart for showing the relationship of the secondary pressure to the instruction current and electromagnetic proportional valve of electromagnetic proportional valve；
Fig. 9 is the schematic structural diagram of previous oil hydraulic system.
Specific embodiment
(first embodiment)
Fig. 1 is the oil hydraulic system 1A for showing first embodiment according to the present invention.Oil hydraulic system 1A is for example loaded into oil pressure digging
Building machinery, building machinery, agricultural machinery or industrial machinery as pick machine, oil pressure crane.
Specifically, oil hydraulic system 1A includes oil pressure actuator 24 and supplies work to oil pressure actuator 24 via control valve 3
Make the main pump 22 of oil.In legend, the combination (set) of oil pressure actuator 24 and control valve 3 is one, but oil pressure actuator 24 and control
The combination of valve 3 processed also can be set multiple.
Main pump 22 is driven by engine 21.Engine 21 also drives auxiliary pump 23.
Main pump 22 is the pump of the modifiable variable capacity type of tilt angle.In this implementation form, main pump 22 is inclined rotor pump.But it is main
Pump 22 or inclined shaft pump.The tilt angle of main pump 22 is adjusted by adjuster 5.
Main pump 22 is connect by feeding pipe 11 with control valve 3.The discharge pressure of main pump 22 is maintained at by relief valve 12
Below vent pressure.
In this implementation form, oil pressure actuator 24 is double action cylinder, and control valve 3 is executed by a pair of to row pipeline 31 and oil pressure
Device 24 connects.It may also be oil pressure actuator 24 is single-acting cylinder, control valve 3 is executed by one to row pipeline 31 and oil pressure
Device 24 connects.Or oil pressure actuator 24 may be hydraulic motor.
Control valve 3 is switched to first position from neutral position and (makes oil pressure actuator 24 to one because operating device 4 is by operation
The position of direction work) or the second position (position for making oil pressure actuator 24 work to opposite direction).In this implementation form, control
Valve 3 is oil pressure pilot-operated type, has a pair of of pilot port.But control valve 3 may be electromagnetic pilot-operated.
Operating device 4 has operation portion 41, output and the operating quantity corresponding operation signal for operation portion 41.That is, from
The operation signal that operating device 4 exports becomes larger as operating quantity becomes larger.Operation portion 41 is, for example, operating stick, but may be foot
Pedal etc..
In this implementation form, operating device 4 is the guide operating valve for exporting first pilot as operation signal.Therefore, it grasps
Make device 4 to connect by a pair of of pilot line 42 with the pilot port of control valve 3.Moreover, with the elder generation exported from operating device 4
Pilot (operation signal) becomes larger, and control valve 3 increases the opening area that the access of working oil is supplied to oil pressure actuator 24.But it operates
Device 4 is also possible to the electrical control bar for exporting electric signal as operation signal.In this case, each elder generation of control valve 3
The secondary pressure side mouth for leading port and electromagnetic proportional valve connects.
Above-mentioned adjuster 5 includes flow control piston 56, as Pc liter is pressed in the control for acting on flow control piston 56
Tilt angle that is high and increasing main pump 22.Adjuster 5 is connect by secondary pressure pipe road 62 with the secondary pressure side mouth of electromagnetic proportional valve 61,
Pressure side mouth of electromagnetic proportional valve 61 is connect by a pressure pipe road 65 with auxiliary pump 23.The discharge pressure of auxiliary pump 23 passes through pressure release
Valve 13 maintains pressure release setting pressure.
Adjuster 5 more specifically, the servo piston 51 that is changed including the tilt angle to main pump 22 and for driving
The regulating valve 53 of servo piston 51.The first compression chamber 5a and the importing of the discharge pressure for importing main pump 22 are formed in adjuster 5
Control the second compression chamber 5b of pressure.Servo piston 51 has first end and the second end than first end major diameter.First end
Portion exposes to the first compression chamber 5a, and the second end exposes to the second compression chamber 5b.
Regulating valve 53 is used to that the control pressure for importing the second compression chamber 5b to be adjusted.Specifically, regulating valve 53 includes
In the direction (flow increases direction, in Fig. 1 to the left) for reducing control pressure and the direction for increasing control pressure, (flow reduces direction, Fig. 1
In to the right) mobile spool 54 and accommodate the sleeve 55 of spool 54.Spool 54 by the above-mentioned pressing of flow control piston 56 and to
Flow increases direction movement, reduces direction to flow due to configuring in the applied force of the spring 57 of 56 opposite side of flow control piston
It is mobile.
Servo piston 51 by can in the axial movement of the servo piston 51 in the form of link with the inclined plate 22a of main pump 22.Set
Cylinder 55 by can in the axial movement of servo piston 51 in the form of linked by feedback rod 52 and servo piston 51.It is formed on sleeve 55
There are pump port, storage tank port and output port (output port is connected to the second compression chamber 5b), according to sleeve 55 and spool 54
Relative position, output port is from pump port and storage tank port both sides blocking or output port and pumps port and storage tank port one
Connection.Moreover, spool 54 by flow control piston 56 to flow increase direction or flow reduce direction it is mobile when, with from servo
The form of power (pressure × servo piston compression area) equilibrium of the double side acting of piston 51 determines the phase of spool 54 with sleeve 55
To position, control pressure is adjusted.
In addition, being formed with the operating room 5c for making control pressure Pc act on flow control piston 56 in adjuster 5.That is, flow
Control piston 56 keeps spool 54 mobile to flow increase direction as control pressure Pc is increased.Prolong from above-mentioned electromagnetic proportional valve 61
The secondary pressure pipe road 62 stretched is connected to operating room 5c.
Electromagnetic proportional valve 61 is to show the instruction current and the electromagnetism conveyed to the electromagnetic proportional valve 61 as shown in Figure 3
The secondary pressure that proportioning valve 61 exports is positively related direct proportion type.Electromagnetic proportional valve 61 is controlled by control device 9.
Also, control device 9 also controls engine 21.Specifically, control device 9 is the revolving speed of engine 21 to be maintained at
Engine control system output order of the form of specified value to engine 21.
For example, there is control device 9 memories and CPU, the programs for being stored in ROM such as ROM, RAM to be executed by CPU.Control
Device 9 processed can be single equipment, also be segmented into multiple equipment (such as apparatus for controlling pump and engine control system).
Control device 9 is electrically connected with the pressure sensor 91 being separately positioned on above-mentioned a pair of of pilot line 42.But
A part of signal wire is only drawn in Fig. 1 in order to simplify attached drawing.
Pressure sensor 91 detects the first pilot exported from operating device 4.Moreover, control device 9 as shown in Fig. 2, with
The guide's buckling exported from operating device 4 is big and increases the instruction current conveyed to electromagnetic proportional valve 61.That is, electromagnetic proportional valve 61
With the first pilot (operation signal) exported from operating device 4 it is bigger and using higher secondary pressure as above-mentioned control press Pc to
Adjuster 5 exports.As a result, as the operating quantity of the operation portion 41 for operating device 4 becomes larger, the discharge flow of main pump 22 increases
Add.
More specifically, control device 9 makes as shown in Fig. 2, according to the first pilot exported from operating device 4 to electromagnetism ratio
The instruction current that example valve 61 conveys changes between slightly above zero minimum value I1 and maximum value I2.Therefore, electromagnetic proportional valve 61
Secondary pressure also as shown in figure 3, greater than zero minimum value P1 and maximum value P2 between change.That is, 61 basis of electromagnetic proportional valve
The operation signal exported from operating device 4, exports the secondary pressure between minimum value P1 and maximum value P2.
In this implementation form, as shown in figure 4, at least master when the secondary pressure exported from electromagnetic proportional valve 61 is minimum value P1
The discharge flow of pump 22 is minimum, at least when secondary pressure export from electromagnetic proportional valve 61 is maximum value P2 main pump 2 discharge
Flow is maximum.But the discharge flow of main pump 22 is maintained the smallest range, and necessity and control press Pc from zero to minimum value P1's
Range is consistent, can also be narrower than the range.Similarly, the discharge flow of main pump 22 is maintained maximum range necessity and control
It presses the range that Pc is maximum value P2 or more consistent, the range can also be narrower than.
A pressure pipe road 65 fork of the pipeline 71 between electromagnetic proportional valve 61 and auxiliary pump 23, pipeline when this is urgent when urgent
71 are connected to storage tank.A pair of of flow controller 74,75 is provided on pipeline 71 when urgent.
Secondary pressure pipe road 62 between electromagnetic proportional valve 61 and adjuster 5 and it is urgent when pipeline 71 on be provided with switching valve
8A.Switching valve 8A is set as secondary pressure pipe road 62 being segmented into 5 side of first flow path 64 and adjuster of 61 side of electromagnetic proportional valve
Second flow path 63, and will be urgent between a pair of of flow controller 74,75 when pipeline 71 be segmented into upstream flow path 72 and downstream flow path 73.
Switching valve 8A is the secondary pressure according to electromagnetic proportional valve 61 come the pilot-operated type of work.Switching valve 8A is in neutral position
When blocking the first flow path 64 on secondary pressure pipe road 62 in (leftward position of Fig. 1), and making urgent the upstream flow path 72 of pipeline 71 with
The second flow path 63 on flow path 73 and secondary pressure pipe road 62 is connected to downstream.
Switching valve 8A is changed to working position using the secondary crush-cutting when the secondary pressure of electromagnetic proportional valve 61 is more than setting value α
Set (right positions of Fig. 1).On operating position, switching valve 8A makes the first flow path 64 and its second flow path 63 on secondary pressure pipe road 62
The upstream flow path 72 and downstream flow path 73 of pipeline 71 when being connected to, and blocking urgent.
Setting value α is as shown in figure 3, be set as than electromagnetic proportional valve 61 corresponding with the first pilot exported from operating device 4
Secondary pressure minimum value P1 it is small.That is, switching valve 8A is located at operating position when electromagnetic proportional valve 61 is normal.
As described above, in the oil hydraulic system 1A of this implementation form, when electromagnetic proportional valve 61 is normal, switching valve 8A is located at work
Make position, so that the secondary pressure of electromagnetic proportional valve 61 acts on the flow control piston 56 of adjuster 5 by secondary pressure pipe road 62.
Therefore, the tilt angle (discharge flow) of the control pump of electromagnetic proportional valve 61 can be utilized.On the other hand, the abnormal hair of electromagnetic proportional valve 61
Wave function and its secondary pressure when being zero, switching valve 8A switches to neutral position, working oil from auxiliary pump 23 by it is urgent when pipeline 71
Flow to storage tank.The intermediate pressure Pm between a pair of of flow controller 74,75 when urgent as a result, on pipeline 71 passes through secondary pressure pipe road 62
Second flow path 63 acts on the flow control piston 56 of adjuster 5.As a result (Qm in Fig. 4) it can ensure main pump to a certain extent
22 discharge flow.Moreover, via switching valve 8A it is urgent when pipeline 71 it is shorter, and adjuster 5 is without previous such
Horsepower control piston, as long as there is the operating room 5c of flow control piston 56, so can be obtained with easy structure above-mentioned
Effect.Adjuster 5 can as a result, be less than previous, and cost can be reduced than in the past.
< variation >
Just whether control device 9 can determine electromagnetic proportional valve 61 according to the monitoring of the instruction current conveyed to electromagnetic proportional valve 61
Often function.Here, electromagnetic proportional valve 61 refers to the case where not working orderly, 61 faults itself of electromagnetic proportional valve is (disconnected
Line) the case where, extend to electromagnetic proportional valve 61 electric wiring broken string the case where, control device 9 or electromagnetic proportional valve 61 company
It connects device and is in contact the case where bad (non-energized) etc..Control device 9 can be played being determined as that electromagnetic proportional valve 61 is not normal
The revolving speed of engine 21 is not changed when function yet.But control device 9 can also normally not play function determining electromagnetic proportional valve 61
Can when as shown in fig. 6, by (such as ± the 20% of Na near the rotational speed regulation of engine 21 to the maximum revolving speed Na of motor torque
In the range of).In addition, this variation can also be applied to aftermentioned second implementation form.
According to the mechanical type for loading oil hydraulic system 1A, it is arranged sometimes for selecting from multiple values by control device
9 are maintained at the selection switch of the revolving speed of certain engine 21.Therefore, when electromagnetic proportional valve 61 does not work orderly, start
The revolving speed of machine 21 may be near rated speed Nr, it is also possible to be rather low revolving speed Nb.
As shown in the 5A in Fig. 5, in main pump 22, it is set with to make the pump running torque of main pump 22 be no more than motor torque
Discharge flow restraining line.It is shown in solid in the 5A of discharge flow restraining line such as Fig. 5, the highest in motor torque maximum, if hair
Motivation torque is lower, then as shown in single dotted broken line in the 5A of Fig. 5, discharge flow restraining line is also lower corresponding to which.To In
In the case where the revolving speed for not changing engine 21 when electromagnetic proportional valve 61 does not work orderly, for two point in the 5A of such as Fig. 5
Make fixed discharge flow consistent with the minimum value of discharge flow restraining line of condition when most tight like that shown in scribing line, it is necessary to as schemed
The pump running torque maximum value relative to pump discharge pressure is set to like that shown in double dot dash line in 5 5B at a fairly low.
In this regard, if as this variation in this way, turn of the engine 21 when electromagnetic proportional valve 61 is not worked orderly
Speed is adjusted near the maximum revolving speed Na of motor torque, then can as Fig. 5 5B in shown in dotted line, to a certain extent by electromagnetism
The pump running torque maximum value relative to pump discharge pressure when proportioning valve 61 does not work orderly is set to higher.So as to one
Determine to increase the intermediate pressure Pm between a pair of of flow controller 74,75 in degree, and as shown in dotted line in the 5A of Fig. 5, it is ensured that solenoid-operated proportional
The discharge flow of pump when valve 61 does not work orderly is more.
(the second implementation form)
Fig. 5 shows the oil hydraulic system 1B of the second implementation form according to the present invention.In addition, implementing in this implementation form to first
The constituent element of homomorphosis is marked with the same symbol, omits repeated explanation.
It is employed as the switching valve 8A of two valves in first embodiment, but is employed as three-position valve in this embodiment
Switching valve 8B.Other structures in second implementation form are identical as first embodiment.
Switching valve 8B is in the same manner as the switching valve 8A of first embodiment, in neutral position (leftward position of Fig. 7) and work
Make to switch between position (central location of Fig. 7).That is, switching valve 8B is more than setting value α (phase in the secondary pressure of electromagnetic proportional valve 61
When in the first setting value of the invention) when, operating position is switched to from neutral position.
In addition, the secondary pressure of electromagnetic proportional valve 61 is more than that setting value β (is equivalent to of the invention second in this implementation form
Setting value) when, switching valve 8B switches to limit positions (right positions of Fig. 7).As shown in figure 8, setting value β is to fill with from operation
The maximum value P2 or more of the secondary pressure of the corresponding electromagnetic proportional valve 61 of first pilot (operation signal) of 4 outputs is set, and is lower than auxiliary pump
23 discharge pressure.
In limit positions, switching valve 8B blocks the first flow path 64 on secondary pressure pipe road 62 in the same manner as neutral position and makes tight
The upstream flow path 72 of pipeline 71 is connected to the second flow path 63 of flow path 73 downstream and secondary pressure pipe road 62 when anxious.
Also effect same as first embodiment can be obtained in this implementation form.In addition, in this implementation form, in electromagnetism
Proportioning valve 61 does not work orderly and in the case that its secondary pressure is equal to primary pressure, switching valve 8B also switches to performance and neutral
The limit positions of position said function, so can ensure the discharge flow of main pump 22 to a certain extent.
(other implementation forms)
The present invention is not limited to above-mentioned implementation forms, can carry out various deformations without departing from the scope of the subject in the invention.
For example, a pair of of flow controller 74,75 can also be built in switching valve (8A or 8B).Also, switching valve (8A or 8B) and electricity
Magnetic proportioning valve 61 can also be built in adjuster 5.
Symbol description:
1A, 1B oil hydraulic system；
21 engines；
22 main pumps；
23 auxiliary pumps；
4 operating devices；
41 operation portions；
5 adjusters；
56 flow control pistons；
61 electromagnetic proportional valves；
62 2 pressure pipe roads；
63 second flow paths；
64 first flow path；
65 pressure pipe roads；
71 it is urgent when pipeline；
72 upstream flow paths；
73 downstream flow paths；
74,75 flow controller；
8A, 8B switching valve；
9 control devices.
Claims (3)
1. a kind of oil hydraulic system, which is characterized in that have:
The operating device of output and the operating quantity corresponding operation signal for operation portion；
The main pump of variable capacity type；
Adjuster, the adjuster include flow control piston, and press and rise with the control for acting on the flow control piston
Tilt angle that is high and increasing the main pump；
Auxiliary pump；
Electromagnetic proportional valve, the electromagnetic proportional valve connect by secondary pressure pipe road with the adjuster and pass through a pressure pipe road with
Auxiliary pump connection, with the operation signal exported from the operating device it is bigger and using higher secondary pressure as the control
Press to the adjuster output；
Diverge from a pressure pipe road and be connected to storage tank and be provided with a pair of of flow controller it is urgent when pipeline；
The secondary pressure pipe road to be segmented into the first flow path of the electromagnetic proportional valve side and the second of the adjuster side
Road, and will be described urgent between the pair of flow controller when pipeline segmentation be upstream flow path and downstream flow path form setting
Switching valve, the switching valve block the first flow path in the case where neutral position and make the upstream flow path and the downstream
Flow path and second flow path connection are changed when the secondary pressure of the electromagnetic proportional valve is more than setting value using the secondary crush-cutting
To being connected to the first flow path with the second flow path and block the operating position of the upstream flow path and the downstream flow path；
And
Control device, the control device is according to the operation signal exported from the operating device, so that the electromagnetic proportional valve
The form for exporting the secondary pressure between the minimum value and maximum value bigger than the setting value is conveyed to the electromagnetic proportional valve to be instructed
Electric current.
2. oil hydraulic system according to claim 1, which is characterized in that
It is also equipped with the engine controlled by the control device for driving the main pump and the auxiliary pump；
The control device is determining the solenoid-operated proportional according to the monitoring of the instruction current conveyed to the electromagnetic proportional valve
When valve does not work orderly, near the rotational speed regulation of the engine to the maximum revolving speed of motor torque.
3. oil hydraulic system according to claim 1 or 2, which is characterized in that
The setting value is the first setting value；
The maximum value of the secondary pressure of the electromagnetic proportional valve corresponding with the operation signal exported from the operating device is than institute
State auxiliary pump discharge pressure it is low the second setting pressure it is following；
The switching valve blocks the first flow path simultaneously when the secondary pressure of the electromagnetic proportional valve is more than second setting value
It is connected to the upstream flow path with the downstream flow path and the second flow path.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2017081847A JP6815267B2 (en) | 2017-04-18 | 2017-04-18 | Hydraulic system |
| JP2017-081847 | 2017-04-18 | ||
| PCT/JP2018/015990 WO2018194091A1 (en) | 2017-04-18 | 2018-04-18 | Hydraulic system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110431317A true CN110431317A (en) | 2019-11-08 |
| CN110431317B CN110431317B (en) | 2020-08-11 |
Family
ID=63855826
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201880020464.5A Active CN110431317B (en) | 2017-04-18 | 2018-04-18 | Oil pressure system |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6815267B2 (en) |
| CN (1) | CN110431317B (en) |
| WO (1) | WO2018194091A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102198503B1 (en) * | 2018-12-19 | 2021-01-05 | 주식회사 모트롤 | Hydraulic pump flow control system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0756267B2 (en) * | 1989-12-27 | 1995-06-14 | 油研工業株式会社 | Variable displacement pump |
| CN1932306A (en) * | 2005-09-15 | 2007-03-21 | 沃尔沃建造设备控股（瑞典）有限公司 | Hydraulic control system |
| CN100441786C (en) * | 2004-03-18 | 2008-12-10 | 神钢建设机械株式会社 | Hydraulic control device for working machine |
| JP2013185401A (en) * | 2012-03-09 | 2013-09-19 | Sumitomo (Shi) Construction Machinery Co Ltd | Control device and control method for construction machine |
| CN104554432A (en) * | 2014-05-29 | 2015-04-29 | 四川大学 | Novel engineering machine steer-by-wire system |
| CN105971951A (en) * | 2015-03-13 | 2016-09-28 | 川崎重工业株式会社 | Oil pressure drive system |
-
2017
- 2017-04-18 JP JP2017081847A patent/JP6815267B2/en active Active
-
2018
- 2018-04-18 WO PCT/JP2018/015990 patent/WO2018194091A1/en active Application Filing
- 2018-04-18 CN CN201880020464.5A patent/CN110431317B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0756267B2 (en) * | 1989-12-27 | 1995-06-14 | 油研工業株式会社 | Variable displacement pump |
| CN100441786C (en) * | 2004-03-18 | 2008-12-10 | 神钢建设机械株式会社 | Hydraulic control device for working machine |
| CN1932306A (en) * | 2005-09-15 | 2007-03-21 | 沃尔沃建造设备控股（瑞典）有限公司 | Hydraulic control system |
| JP2013185401A (en) * | 2012-03-09 | 2013-09-19 | Sumitomo (Shi) Construction Machinery Co Ltd | Control device and control method for construction machine |
| CN104554432A (en) * | 2014-05-29 | 2015-04-29 | 四川大学 | Novel engineering machine steer-by-wire system |
| CN105971951A (en) * | 2015-03-13 | 2016-09-28 | 川崎重工业株式会社 | Oil pressure drive system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110431317B (en) | 2020-08-11 |
| JP2018179199A (en) | 2018-11-15 |
| JP6815267B2 (en) | 2021-01-20 |
| WO2018194091A1 (en) | 2018-10-25 |
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