CN107816460A - Load-transducing formula drive system - Google Patents
Load-transducing formula drive system Download PDFInfo
- Publication number
- CN107816460A CN107816460A CN201710816518.6A CN201710816518A CN107816460A CN 107816460 A CN107816460 A CN 107816460A CN 201710816518 A CN201710816518 A CN 201710816518A CN 107816460 A CN107816460 A CN 107816460A
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- Prior art keywords
- pressure
- customer
- control
- return pipeline
- valve
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Classifications
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- 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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
-
- 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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- 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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
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- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/46—Control of flow in the return line, i.e. meter-out control
Abstract
The present invention relates to load-transducing formula drive system, it has pump and at least one by the double acting customer of pump supply pressure medium, especially cylinder with differential effect, in order to control each customer to set control direction valve and set pressure medium storage device, the connection of return pipeline of the pressure medium storage device with leading to container from corresponding control direction valve controls by means respectively of feedback valve.Control direction valve is provided with the first return pipeline and is provided with the second return pipeline, first return pipeline is connected in the first control position of control direction valve with the second customer side of customer, second return pipeline is connected in the second control position of control direction valve with the first customer side of customer, first feedback valve is set in the first return pipeline and the second feedback valve is set in the second return pipeline, first feedback valve controls the connection of the first return pipeline and pressure medium storage device or container, second feedback valve controls the connection of the second return pipeline and pressure medium storage device or container.
Description
Technical field
The present invention relates to a kind of load-transducing formula drive system, it has pump and at least one by the pump supply pressure medium
Double acting customer, especially cylinder with differential effect, wherein, in order to control each customer, a control direction valve is set and set
One pressure medium storage device, the connection point of return duct of the pressure storage device with leading to container from each control direction valve
Do not controlled by means of feedback valve.
Background technology
The fluid power system for being configured to load-transducing formula drive system uses in mobile operation machinery.Passed in load
In sense formula drive system, pump can be utilized to provide the different loads pressure of different customers.Control at the same time multiple with difference
During the customer of load pressure, pump is adjusted on the highest load pressure of controlled customer.With smaller load pressure
On customer, becoming a mandarin, side sets a pressure compensator respectively, and the pressure compensator drops to the system pressure provided by pump
For in the pressure needed for corresponding customer.Here, there is restriction loss on the lateral pressure compensator that becomes a mandarin of customer.
In order to reduce the restriction loss that customer becomes a mandarin on lateral pressure compensator, driven in the load-transducing formula of the above-mentioned type
It is well known that, pressure medium storage device is set, and the pressure storage device from each control direction valve with leading to container in system
Return duct connection by means respectively of feedback valve control.Disclosed by the A1 of DE 10 2,013 101 107 such
Load-transducing formula drive system with pressure medium storage device and feedback valve, the feedback valve store the pressure medium
Device return pipeline connection corresponding to control direction valve.
The drainage side of the corresponding customer of pressure reloaded composition of pressure medium storage device can be used using feedback valve
Return pipeline and produce counter-pressure in the return pipeline of the composition drainage side of customer.Thus, in the side that becomes a mandarin of customer
Pressure equally with the pressure rise of pressure medium storage device, so as to which the customer is run with elevated stress level.Thus,
Reduce and be arranged on the pressure compensator in the side that becomes a mandarin when can manipulate multiple customers with different loads pressure at the same time
Restriction loss and the pressure compensator that is arranged in the side that becomes a mandarin on restriction loss be situated between at least partially through pressure is loaded
Matter storage device and reclaimed.
Disclosed in by the A1 of DE 10 2,013 101 107 in load-transducing formula drive system, the control direction of customer
Valve has single return pipeline and single feedback valve respectively, and return pipeline and pressure medium can be controlled using the feedback valve
The connection of storage device or container.Feedback valve is respectively by the present load pressure and pressure medium storage device of the customer attached troops to a unit
Pressure and a spring assembly towards drainage position direction load and born by the highest of all customers of drive system
Pressure is carried to load towards the direction of holder " loaded " position, in the drainage position, the return pipeline attached troops to a unit is connected with container,
In the holder " loaded " position, the return pipeline attached troops to a unit is connected with pressure medium storage device.Thus, on feedback valve,
Pressure sum and the highest of controlled customer in the present load pressure and pressure medium storage device of the customer attached troops to a unit are born
Pressure is carried to compare.If pass through pressure drop (the highest load of all customers of pressure compensator when manipulating a customer
The difference of pressure and the present load pressure of customer attached troops to a unit) be more than the pressure in pressure medium storage device, then feedback valve quilt
Holder " loaded " position is loaded into, in the holder " loaded " position, return pipeline and the pressure medium storage device of customer
Connect and so as to which the return pipeline of the composition customer drainage side of the customer is pre-loaded to pressure medium storage device
On stress level.In the holder " loaded " position of the feedback valve, from the pressure medium of customer outflow in return pipeline
No longer it is transported in container, but is transported in pressure medium storage device.It is stored in pressure medium storage device
Pressure medium can be used for answering customer or for driving the pump in drive system.
Disclosed in by the A1 of DE 10 2,013 101 107 in load-transducing formula drive system, the control direction of customer
Valve has single return pipeline and single feedback valve respectively, and return pipeline and pressure medium can be controlled using the feedback valve
The connection of storage device or container, can not there will be different work two customer sides in this load-transducing formula drive system
The cylinder with differential effect in plug face is used as customer.This cylinder with differential effect is used as pressure converter, so that on the feedback valve of the customer, pressure
Pressure in medium reservoir (highest load pressures of all customers and is attached troops to a unit with the pressure drop via pressure compensator
The difference of the present load pressure of customer) ratio less suitable for use in the cylinder with differential effect two directions of motion.
In addition, it can not be fully utilized in load-transducing formula drive system disclosed in by the A1 of DE 10 2,013 101 107
Or drain the reduction potentiality for the restriction loss being arranged on the pressure compensator for the side that becomes a mandarin.If in DE 10 2,013 101 107
Feedback valve is loaded into holder " loaded " position on a customer in A1 and pressure medium is by the return from the customer
For Pipeline transport to pressure medium storage device, then the pressure in pressure medium storage device, which acts on, forms customer drainage side
The pressure that return pipeline and customer become a mandarin in side correspondingly raises, such as with identical in the case of synchronized cylinder or double-rod cylinder
Value rise.This can be caused as a result, notifying the present load pressure to customer feedback valve equally to raise.Thus, should
Feedback valve is loaded into drainage position very much early in the case of the present load pressure increased for the customer attached troops to a unit,
In the drainage position, the return pipeline of customer is connected with container and so as to which the connection towards pressure medium storage device is cut
It is disconnected, because the present load pressure that the A1 of DE 10 2,013 101 107 feedback valve cannot distinguish between the customer attached troops to a unit is to pass through
What the pressure that the load acted on the customer still passes through cut-in pressure medium reservoir was realized.
The content of the invention
The task of the present invention is to provide a kind of load-transducing formula drive system for starting the type herein, and it is in structure
Simply and in the case that structure consumption is low reduction is also provided in the case that customer is configured to cylinder with differential effect or single-rod cylinder
The possibility of restriction loss on pressure compensator.
According to the present invention, the task solves in the following manner, i.e. control direction valve be provided with the first return pipeline and
Provided with the second return pipeline, first return pipeline disappears in the first control position of control direction valve with the second of customer
Consume the connection of device side, first customer side of second return pipeline in the second control position of control direction valve with customer
Connection, wherein, the first feedback valve is set in first return pipeline and sets second in second return pipeline
Feedback valve, first feedback valve control the company of first return pipeline and the pressure medium storage device or the container
Connect, second feedback valve controls the connection of second return pipeline and the pressure medium storage device or the container.
There is the return pipeline (setting a feedback valve of oneself respectively in the return pipeline) of oneself using for each customer side
Control direction valve can be realized with simple structure and low structure consumption：In the customer of cylinder with differential effect is configured to (its
Two customer sides have different piston areas) in two directions of motion of cylinder with differential effect reduce pressure compensator on throttling damage
Lose, its method is to be connected respective return pipeline with pressure medium storage device by corresponding feedback valve.Utilize these lists
The feedback valve of two direction of motion only, for cylinder with differential effect (is namely individually used for each direction of motion of cylinder with differential effect
Feedback valve), the restriction loss on pressure compensator can be reduced in two directions of motion of cylinder with differential effect in a straightforward manner.
This, the chain of command by corresponding pressure-loaded on respective feedback valve can adapt in a straightforward manner piston area and from
And the area ratio of the cylinder with differential effect is adapted to, so as to be reduced for two directions of motion of the cylinder with differential effect on pressure compensator
Restriction loss.
According to the advantageous embodiment of the present invention, two feedback valves of a customer are respectively by the customer
Load pressure and pressure in the pressure medium storage device and a spring assembly add towards the direction of a drainage position
Carry and loaded by the highest load pressure of the customer of the drive system towards the direction of a holder " loaded " position, described
In drainage position, the return pipeline attached troops to a unit is connected with container, in the holder " loaded " position, the return pipeline and pressure attached troops to a unit
Power media storage device connects.Here, by being added by the present load pressure of customer and the highest load pressure of drive system
The corresponding adaptation of the chain of command of load in a straightforward manner can adapt to the two feedback valves the area of the piston area of cylinder with differential effect
Ratio, so as to for the restriction loss on two directions of motion reduction pressure compensator of the cylinder with differential effect.
According to one of the present invention favourable further scheme, the feedback valve in the return pipeline attached troops to a unit respectively by depositing
It is that the pressure of feedback valve upstream loads towards the direction of holder " loaded " position.Thus, feedback valve is additionally by attaching troops to a unit
The pressure being present in return pipeline between control direction valve and feedback valve loads towards the direction of holder " loaded " position.Thus
It is accomplished that, the present load pressure and drainage side that the side that becomes a mandarin is respectively present on corresponding feedback valve are present in return pipeline
In pressure and so as to exist two customer sides from customer pressure.It hereby is obtained that, is no longer only to disappear
Consume the present load pressure of device and so as to which the pressure on customer side determines when to switch feedback valve, but customer
Actual load pressure determine when switch feedback valve.Even if when the stress level in the drainage side of customer side is due to pressure
When media reservoir is connected on return pipeline and improved, the signal will not also be mistaken.Thus, by by the pressure in return pipeline
Power is additionally connected on corresponding feedback valve, and the pressure compensator for the side that becomes a mandarin can be arranged on small additional consuming full utilization
On restriction loss reduction potentiality.
According to the advantageous embodiment of the present invention, the first feedback valve has towards the direction of holder " loaded " position
The control pressure face of effect, the control pressure face by means of a control piper and first return pipeline control direction valve with
Connected between first feedback valve；Second feedback valve has the control pressure face acted on towards the direction of holder " loaded " position, should
Control pressure face is connected by means of a control piper and second return pipeline between control direction valve and the second feedback valve.
Thus, using this additional control pressure face and control piper, the two feedback valves can in a straightforward manner additionally by
The pressure of feedback valve upstream is in corresponding return pipeline and so as to be entered by the pressure-loaded in customer drainage side
Row control.
According to one of present invention replacement and equally advantageous further scheme, the feedback valve is towards a drainage position
The direction put is respectively only by the load pressure of the customer and spring assembly loading and disappearing by the drive system
The highest load pressure for consuming device loads towards the direction of a holder " loaded " position, wherein, in the drainage position, attach troops to a unit
Return pipeline is connected with container, and in the holder " loaded " position, return pipeline and the pressure medium storage device attached troops to a unit connect
Connect.Thus, this feedback valve forms regulating valve, and it does not consider the pressure in pressure medium storage device.Thus, this feedback valve
The pressure of pressure medium storage device is not compared with the pressure drop of the pressure compensator by customer, but regulation passes through
The maximum pressure drop of pressure compensator, wherein, the feedback valve ensures：Given in advance by spring preloading device on pressure compensator
Maximum pressure drop going out, being carried out by pressure compensator is not exceeded.Thus it can also be fully utilized and be arranged on the side that becomes a mandarin
The reduction potentiality of restriction loss on pressure compensator.
According to one of the present invention favourable further scheme, cause pressure using this feedback valve for being configured to regulating valve
Medium reservoir, which can include at least two, has the horizontal pressure medium reservoir of different pressures, and these feedback valves pair
There is a holder " loaded " position in each pressure medium reservoir.Always maximally blocked by the feedback valve for being configured to regulating valve
The return pipeline of customer is cut or intercepts, so as to which multiple pressure medium reservoirs horizontal with different pressures are connected to
Return pipeline, because by being configured to the feedback valve of regulating valve always by the return pipeline and the pressure with next lower pressure level
Power media holder connects.
Brief description of the drawings
The additional advantages and details of the present invention are elaborated by means of the embodiment shown in schematic diagram.Herein：
Fig. 1：The line map of the first embodiment of the present invention is shown；
Fig. 2：The line map of the second embodiment of the present invention is shown；
Fig. 3：The line map of the third embodiment of the present invention is shown.
Embodiment
The drive system 1 load-transducing regulation, according to the present invention of mobile operation machinery is shown respectively in accompanying drawing 1 to 3
Line map.In accompanying drawing 1 to 3, identical component is provided with identical reference.
The drive system 1 includes the adjustable pump of feed flow, and the pump is in an illustrated embodiment with open loop type circulation loop
Run and be connected with a container 3 in input side and be transported in outlet side in a transfer pipeline 4, multiple customers are connected to institute
State transfer pipeline.In an illustrated embodiment, a double acting customer 5 is only shown, the double acting customer is configured to difference
Dynamic cylinder.
In order to control the customer 5, a control direction valve 6 to be throttled in centre position is set.The customer 5 has
First customer side 5a and the second customer side 5b.In an illustrated embodiment, the first customer side 5a is configured to piston side simultaneously
And second customer side 5b be configured to the piston rod side of the cylinder with differential effect.The first customer side 5a is by means of one first connection
Pipeline 7a is connected to the control direction valve 6.The second customer side 5b is connected to institute by means of one second connecting line 7b
State control direction valve 6.Returned in addition, the control direction valve 6 is connected to the transfer pipeline 4 of the pump 2 and is connected to one first
Return pipe road 8a and one second return pipeline 8b, first return pipeline and the second return pipeline are connected with the container 3 respectively.
The control direction valve 6 for being configured to direction valve has a neutral position 6c, in the neutral position, the pump
2 transfer pipeline 4, described return pipeline 8a, 8b and described customer pipeline 7a, 7b are ended.In the control direction valve 6
In one first control position 6a, the transfer pipeline 4 is connected with the first customer pipeline 7a and second customer
Pipeline 7b is connected with the first return pipeline 8a.In the described first control position 6a, the second return pipeline 8b is cut
Only.In one second control position 6b of the control direction valve 6, the transfer pipeline 4 and the second customer pipeline 7b
Connect and the first customer pipeline 7a is connected with the second return pipeline 8b.In the described second control position 6b,
The first return pipeline 8a is ended.The control direction valve 6 has measuring diaphragm 10a in the described first control position 6a
And it is provided with a pressure compensator being arranged in measuring diaphragm 10a downstreams, not being shown specifically.The control direction valve 6 exists
It is described second control position 6b in have measuring diaphragm 10b and provided with one be arranged in measuring diaphragm 10b downstreams, it is not detailed
The pressure compensator shown.
Towards described first control position 6a direction to control described in control direction valve 6 when, the customer 5 in institute
State the load pressure that the downstream of pressure compensator is present on the first customer side 5a and be informed to one and be connected to the load sense
The load-sensing of formula drive system 1 is answered to notify the load pressure signal pipeline 20a of pipeline 21 and further conducted.Accordingly
Ground, towards described second control position 6b direction to control described in control direction valve 6b when, the customer 5 in the pressure
The load pressure that the downstream of force compensating device is present on the second customer side 5b is informed to one and load-sensing notice pipeline 21
The load pressure signal pipeline 2ba of connection and further conducted.
In the measuring diaphragm 10a arranged downstreams in the flow path from the customer pipeline of transfer pipeline 4 to the first 7a
Pressure compensator there is flow passing position and rest position.Towards the direction of flow passing position, pressure compensator is surveyed by being present in
The discharge pressure loading in orifice 10a downstreams.Towards the direction of rest position, pressure compensator is born by the highest of controlled customer
Carry pressure-loaded.In the measuring diaphragm 10b arranged downstreams in the flow path from the customer pipeline of transfer pipeline 4 to the second 7b
In pressure compensator there is flow passing position and rest position.Towards the direction of flow passing position, pressure compensator is by being present in
The discharge pressure loading in measuring diaphragm 10b downstreams.Towards the direction of rest position, pressure compensator by controlled customer highest
Load pressure loads.
When manipulating multiple customers, the highest that controlled customer be present in load pressure notifies pipeline 21 loads pressure
Power, to control the conveying capacity for the pump 1 for being configured to adjust pump in the embodiment shown.In order to control conveying capacity, the pump 1 has one
Adjusting means 25, such as an axial poiston pump that can be controlled by means of being configured to the conveying throttle regulator 26 of flow of requirement regulating valve
The adjustable pitch of slope.The conveying throttle regulator 26 is present in load pressure notice pipeline 21 by controlled customer
Highest load pressure controls.
The drive system 1 is provided with pressure medium storage device 30, the pressure medium storage device with from control direction
The connection that valve 6 leads to return pipeline 8a, 8b of a container is controlled by means of feedback valve 31a, 31b.
According to the present invention, first feedback valve 31a is set in the first return pipeline 8a of the control direction valve 6, this
One feedback valve controls the first return pipeline 8a and the pressure medium storage device 30 or the container 3 connection, and
The second feedback valve 31b is set in the second return pipeline 8b, second feedback valve control the second return pipeline 8b with
The connection of the pressure medium storage device 30 or the container 3.
In Fig. 1 and 2 embodiment, feedback valve 31a, 31b are configured to stop valve, and it has respectively is configured to flow passing position
Drainage position 31c and be configured to the holder " loaded " position 31d of rest position, in the drainage position, the return attached troops to a unit
Pipeline 8a, 8b are opened and so as to being connected with the container 3, in the holder " loaded " position, the return pipeline 8a that attaches troops to a unit,
8b is connected with the pressure medium storage device 30.The pressure medium storage device 30 is by means of one first connecting line 35a
The first return pipeline 8a is connected between the control direction valve 6 and the first feedback valve 31a and by means of one second
Connecting line 35b is connected to the second return pipeline 8b between the control direction valve 6 and the second feedback valve 31b.Institute
State the check-valves 36a for setting in the first connecting line 35a and being opened towards the direction of pressure medium storage device 30.Correspondingly,
The check-valves 36b opened towards the direction of pressure medium storage device 30 is set in the second connecting line 35b.
In fig 1 and 2, feedback valve 31a, 31b is respectively by the present load pressure and pressure medium storage device of customer 5
Pressure and spring assembly 40a, a 40b in 30 load towards drainage position 31c direction and by the consumption of drive system 1
The highest load pressure of device loads towards holder " loaded " position 31d direction.
In order to be loaded by the present load pressure of customer 5 towards drainage position 31c direction, first feedback valve
31a has the first control pressure face 41a, and the first control pressure face is by means of a control piper 42a and first customer
Pipeline 7a connections.In order to be loaded with the pressure in pressure medium storage device 30 towards drainage position 31c direction, described first
Feedback valve 31a has the second control pressure face 43a, and the second control pressure face is by means of a control piper 44a and the connection
The downstream connection of pipeline 35a, 35b in described check-valves 36a, 36b.In order to be loaded by the highest of the customer of drive system 1
Pressure loads towards holder " loaded " position 31d direction, and the first feedback valve 31a has the 3rd control pressure face 45a, should
3rd control pressure face is by means of a control piper 46a and the load-sensing formula drive system 1 all customers of guiding
The load pressure notice pipeline 21 of highest load pressure connects.
In order to be loaded by the present load pressure of customer 5 towards drainage position 31c direction, second feedback valve
31b has the first control pressure face 41b, and the first control pressure face is by means of a control piper 42b and second customer
Pipeline 7b connections.In order to be loaded with the pressure in pressure medium storage device 30 towards drainage position 31c direction, described second
Feedback valve 31b has the second control pressure face 43b, and the second control pressure face is by means of a control piper 44b and the connection
The downstream connection of pipeline 35a, 35b in described check-valves 36a, 36b.In order to be loaded by the highest of the customer of drive system 1
Pressure loads towards holder " loaded " position 31d direction, and the second feedback valve 31b has the 3rd control pressure face 45b, should
3rd control pressure face is by means of a control piper 46b and the load-sensing formula drive system 1 all customers of guiding
The load pressure notice pipeline 21 of highest load pressure connects.
In fig. 2, feedback valve 31a, 31b in return pipeline 8a, 8b for attaching troops to a unit respectively additionally by being present in feedback valve
The pressure of 31a, 31b upstream and so as to by the pressure in the drainage side of customer 5 towards holder " loaded " position 31d direction
Loading.
Therefore, the first feedback valve 31a is provided with another control pressure face acted on towards holder " loaded " position 31d direction
47a, another control pressure face is by means of a control piper 48a and the first return pipeline 8a in the control direction valve 6
It is connected between the first feedback valve 31a.Therefore, the second feedback valve 31b is provided with towards holder " loaded " position 31d's
Another control pressure face 47b of direction effect, another control pressure face are returned by means of a control piper 48b and described second
Pipeline 8b is connected between the control direction valve 6 and the second feedback valve 31b.
In addition, in fig. 2, throttling arrangement 49a, 49b, such as orifice plate are set in control piper 46a, 46b.In Fig. 1
This throttling arrangement 49a, 49b can also be set.
In fig 1 and 2, pressure medium storage device 30 includes only one pressure medium reservoir.
In figure 3, pressure medium storage device 30, which includes at least two, has the horizontal pressure medium storage of different pressures
Device 30a, 30b.
Pressure medium reservoir 30a is by means of the connecting line 35a in the control direction valve 6 and the described first feedback
Be connected between valve 31a the first return pipeline 8a and by means of the connecting line 35b the control direction valve 6 with
The second return pipeline 8b is connected between the second feedback valve 31b.Non-return is set in described connecting line 35a, 35b
Valve 36a, 36b.
Pressure medium reservoir 30b is connected to the first feedback valve 31a simultaneously by means of a connecting line 50a in outlet side
And it is connected to the second feedback valve 31b in outlet side by means of a connecting line 50b.Set in the connecting line 50a
The check-valves 51a opened towards pressure medium reservoir 30b direction.Correspondingly, one is set in the connecting line 50b
The check-valves 51b opened towards pressure medium reservoir 30b direction.
In the fig. 3 embodiment, feedback valve 31a, 31b are configured to stop valve, they have respectively is configured to flow passing position
Drainage position 31c, in the drainage position, return pipeline 8a, 8b for attaching troops to a unit are opened and so as to are connected with the container 3,
And the feedback valve has holder " loaded " position 31d, 31e for each pressure medium reservoir 30a, 30b, in the storage
In storage " loaded " position, return pipeline 8a, 8b and the pressure medium reservoir 30a or described pressure medium reservoirs attached troops to a unit
30b connections.
In the drainage position 31c, the return pipeline 8a or 8b is connected with the container 3 and leads to connecting line
50a or 50b connection is ended.Pressure medium reservoir 30a can be loaded in the holder " loaded " position 31d, should
Holder " loaded " position 31d is configured to rest position, and in the rest position, all joints are all ended.Pressure medium stores up
Storage 30b can be loaded in the holder " loaded " position 31e, in holder " loaded " position 31e, the recurrent canal
Road 8a or 8b is connected with the connecting line 50a or 50b and the return pipeline 8a or 8b and the container 3 connection are cut
Only.The holder " loaded " position 31e is arranged between the drainage position 31c and the holder " loaded " position 31d.
In figure 3, feedback valve 31a, 31b is only consumed the present load of device 6 towards drainage position 31c direction respectively
Pressure and spring assembly 40a, 40b loading.Towards the direction of holder " loaded " position 31d, 31e, feedback valve 31a, 31b are driven
The highest load pressure loading of the customer of dynamic system 1.Thus, compared with Fig. 1 and Fig. 2, feedback valve 31a, 31b are not present in
Pressure-loaded in pressure medium storage device 30.
In order to be loaded by the present load pressure of customer 5 towards drainage position 31c direction, first feedback valve
31a has control pressure face 41a, and the control pressure face is connected by means of control piper 42a with the first customer pipeline 7a.
In order to be loaded by the highest load pressure of the customer of drive system 1 towards the direction of holder " loaded " position 31d, 31e, institute
Stating the first feedback valve 31a has control pressure face 45a, and the control pressure face is by means of control piper 46a and the load-sensing
The load pressure notice pipeline 21 of the highest load pressure of all customers of guiding of formula drive system 1 connects.
In order to be loaded by the present load pressure of customer 5 towards drainage position 31c direction, second feedback valve
31b has control pressure face 41b, and the control pressure face is connected by means of control piper 42b with the second customer pipeline 7b.
In order to be loaded by the highest load pressure of the customer of drive system 1 towards the direction of holder " loaded " position 31d, 31e, institute
Stating the second feedback valve 31b has control pressure face 45b, and the control pressure face is by means of control piper 46b and the load-sensing
The load pressure notice pipeline 21 of the highest load pressure of all customers of guiding of formula drive system 1 connects.
Other customers not shown further of the drive system 1 can be by means of the control direction valve 6 that accordingly forms
Control and connected by means of Fig. 1 to 3 feedback valve 31a, 31b and pressure medium reservoir 30.
It is single using the two in two return pipelines 8a, 8b of customer 5 in Fig. 1 to 3 drive system 1
Feedback valve 31a, 31b and so that feedback valve 31a, 31b of single, for customer 5 each direction of motion of difference one
Two directions of motion in the case where being configured to the customer of cylinder with differential effect for cylinder with differential effect reduce the side pressure that becomes a mandarin in a simple manner decoupled
Restriction loss on force compensating device, its method be, by corresponding feedback valve 31a or 31b by respective return pipeline 8a or 8b
And so as to which the corresponding drainage side of customer be connected with the pressure medium reservoir 30.Here, by corresponding on feedback valve 31a
Pressure-loaded control pressure face 41a, 43a, 45a and feedback valve 31b by corresponding pressure-loaded control pressure face
41b, 43b, 45b can adapt to piston area in a straightforward manner and so as to adapt to the face ratio of cylinder with differential effect, so as to
The restriction loss to become a mandarin on lateral pressure compensator is reduced for two directions of motion of the cylinder with differential effect.
Using in Fig. 2 by be present in return pipeline 8a, 8b for attaching troops to a unit control direction valve 6 and feedback valve 31a, 31b it
Between pressure additionally load feedback valve 31a, 31b towards the direction of holder " loaded " position 31 and be accomplished that：Feedback valve 31a,
31b not only by customer 5 the side that becomes a mandarin the pressure-loaded being present on control pressure face 41a, 41b, but additionally controlling
The pressure-loaded of the upper drainage side by customer 5 of pressing pressure face 47a, 47b, so that feedback valve 31a, 31b are by customer two
The pressure-loaded of side and so that feedback valve 31a or 31b respectively by the actual loading Stress control of customer 5.Therefore, exist
In Fig. 2 embodiment, be no longer only the pressure in the side that becomes a mandarin of customer 5 and thus the pressure of a customer side come it is true
It is fixed when to switch feedback valve 31a, 31b, but the actual loading pressure of customer 5 determines when to switch feedback valve 31a, 31b.Disappear
The rise of the stress level consumed in the drainage side of device 5 will not also obscure the signal.Thus, by by return pipeline 8a, 8b
Pressure is additionally connected on corresponding feedback valve 31a, 31b, can be arranged on the side that becomes a mandarin with small additional consuming full utilization
The reduction potentiality of restriction loss on pressure compensator.
In the fig. 3 embodiment, feedback valve 31a, 31b form regulating valve, it is not considered in pressure medium storage device 30
Pressure.Therefore, feedback valve 31a, 31b be not by the pressure of pressure medium storage device 30 and the pressure compensation by customer 5
The pressure drop that device is carried out compares, but the maximum pressure drop that regulation is carried out by pressure compensator when manipulating customer 5.
In figure 3, if customer 5 moves towards a direction of motion, each feedback valve being arranged in the drainage side of customer 5
31a or 31b ensure：On the pressure compensator being arranged in the corresponding side that becomes a mandarin of customer 5, given in advance by spring preloading device
The maximum pressure drop gone out can not be exceeded by pressure compensator.Thereby, it is possible to be fully utilized be arranged on the side that becomes a mandarin pressure benefit
Repay the reduction potentiality of the restriction loss on device.Equally, it is feedback valve 31a, 31b of regulating valve using Fig. 3 construction, can also makes
Pressure medium storage device 30 is obtained with least two with different pressures horizontal pressure medium reservoir 30a, 30b.Disappearing
Consume in the operation of device 5, always maximally intercept or intercept the return of customer 5 by feedback valve 31a, 31b for being configured to regulating valve
Pipeline 8a or 8b and by means of feedback valve 31a, 31b always by return pipeline 8a or 8b with next lower or secondary low-pressure
Horizontal pressure medium reservoir 30a, 30b connection, is situated between so as to be transported to the pressure with next lower or secondary lower pressure level
In matter holder 30a, 30b.
It can improve energy in load-sensing formula drive system 1 using feedback valve 31a, 31b in Fig. 1 to 3 of the present invention
Effect, because (these losses pass through load different on customer for the loss as caused by system when manipulating multiple customers at the same time
Pressure produce) can partly in pressure medium storage device 30 be captured and and can to the drive system provide be stored in
Pressure medium in pressure medium storage device 30.
Using two in Fig. 1 to 3, two return pipelines 8a, 8b single feedback valve 31a, 31b (wherein for
One direction of motion of customer 5 sets feedback valve a 31a or 31b respectively), the customer for being configured to cylinder with differential effect can be reduced
The above-mentioned loss caused by system in 5 two directions of motion.
In addition, the pressure compensator for being arranged on the side that becomes a mandarin can be fully utilized using feedback valve 31a, 31b in Fig. 2 and 3
On restriction loss reduction potentiality.
In addition, Fig. 3 feedback valve 31a, 31b allow using multiple pressure medium reservoirs horizontal with different pressures
30a、30b。
Claims (6)
1. a kind of load-transducing formula drive system (1), it has a pump (2) and at least one by the pump (2) supply pressure Jie
The double acting customer (5) of matter, especially cylinder with differential effect, wherein, in order to control each customer (5) to set a control direction valve
(6) and a pressure medium storage device (30) is set, the pressure medium storage device is with one from corresponding control direction valve (6)
Towards the return pipeline (8a of a container (3)；Connection 8b) is by means respectively of a feedback valve (31a；31b) control, its feature exists
In the control direction valve (6) is provided with the first return pipeline (8a) and is provided with the second return pipeline (8b), and described first returns
Second customer side (5b) of the pipeline in the first control position (6a) of the control direction valve (6) with the customer (5)
Connection, second return pipeline the control direction valve (6) second control position (6b) in the customer (5)
First customer side (5a) connects, wherein, the first feedback valve (31a) is set in first return pipeline (8a) and in institute
State and the second feedback valve (31b) is set in the second return pipeline (8b), first feedback valve controls first return pipeline
(8a) and the pressure medium storage device (30) or the container (3) connection, the second feedback valve control described second
The connection of return pipeline (8b) and the pressure medium storage device (30) or the container (3).
2. load-transducing formula drive system (1) as claimed in claim 1, it is characterised in that the feedback valve (31a；31b) divide
Not by the pressure and a spring assembly in the load pressure and the pressure medium storage device (30) of the customer (5)
(40a, 40b) is loaded towards the direction of a drainage position (31c) and born by the highest of the customer (5) of the drive system (1)
Pressure is carried to load towards the direction of a holder " loaded " position (31d), in the drainage position, the return pipeline (8a that attaches troops to a unit；
8b) it is connected with container (3), in the holder " loaded " position, the return pipeline (8a that attaches troops to a unit；8b) filled with pressure medium storage
Put (30) connection.
3. load-transducing formula drive system (1) as claimed in claim 1 or 2, it is characterised in that the feedback valve (31a；
31b) respectively by the return pipeline (8a to attach troops to a unit；It is present in feedback valve (31a in 8b)；31b) pressure of upstream is towards holder
The direction loading of " loaded " position (31d).
4. load-transducing formula drive system (1) as claimed in claim 3, it is characterised in that the first feedback valve (31a) has court
The control pressure face (47a) of the direction effect of holder " loaded " position (31d), the control pressure face is by means of a control piper
(48a) is connected with first return pipeline (8a) between control direction valve (6) and the first feedback valve (31a)；Second feedback
Valve (31b) has the control pressure face (47b) acted on towards the direction of holder " loaded " position (31d), and the control pressure face is borrowed
Help a control piper (48b) and second return pipeline (8b) between control direction valve (6) and the second feedback valve (31b)
Connection.
5. load-transducing formula drive system (1) as claimed in claim 1, it is characterised in that the feedback valve (31a；31b) court
The direction of a drainage position (31c) respectively only by the load pressure of the customer (5) and a spring assembly (40a,
40b) loading and by the drive system (1) customer (5) highest load pressure towards a holder " loaded " position (31d；
Direction loading 31e), wherein, in the drainage position (31c), the return pipeline (8a that attaches troops to a unit；8b) it is connected with container (3),
In the holder " loaded " position, the return pipeline (8a that attaches troops to a unit；8b) it is connected with pressure medium storage device (30).
6. load-transducing formula drive system (1) as claimed in claim 5, it is characterised in that the pressure medium storage device
(30) including at least two has the horizontal pressure medium reservoir (30a of different pressures；30b), the feedback valve (31a；31b)
For each pressure medium reservoir (30a；30b) there is holder " loaded " position (31d；31e).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016117206.5A DE102016117206A1 (en) | 2016-09-13 | 2016-09-13 | Load-sensing drive system |
| DE102016117206.5 | 2016-09-13 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107816460A true CN107816460A (en) | 2018-03-20 |
| CN107816460B CN107816460B (en) | 2020-08-07 |
Family
ID=61247147
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710816518.6A Active CN107816460B (en) | 2016-09-13 | 2017-09-12 | Load sensing drive system |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN107816460B (en) |
| DE (1) | DE102016117206A1 (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010248738A (en) * | 2009-04-13 | 2010-11-04 | Hitachi Constr Mach Co Ltd | Control device for working arm, and working machine |
| CN102425580A (en) * | 2011-08-16 | 2012-04-25 | 中联重科股份有限公司 | Braking valve bank, hydraulic system having same and concrete spreader |
| CN102562694A (en) * | 2010-10-19 | 2012-07-11 | 林德材料控股有限责任公司 | Load-sensing regulated hydrostatic drive system |
| CN102785650A (en) * | 2011-05-18 | 2012-11-21 | 林德材料处理有限责任公司 | Hydraulic brake valve device |
| CN102865261A (en) * | 2011-07-06 | 2013-01-09 | 林德材料处理有限责任公司 | Hydrostatic driving system |
| DE102013101107A1 (en) * | 2013-02-05 | 2014-08-07 | Karlsruher Institut für Technologie | Hydraulic multi-user system with energy-efficient hydraulic circuit |
| CN104047932A (en) * | 2013-03-15 | 2014-09-17 | 宝钢工业炉工程技术有限公司 | Potential energy recovery system of lifting equipment and use method under non-stable load condition |
| CN105298958A (en) * | 2015-12-01 | 2016-02-03 | 华北水利水电大学 | Loader working hydraulic system capable of recycling overflow energy |
-
2016
- 2016-09-13 DE DE102016117206.5A patent/DE102016117206A1/en not_active Withdrawn
-
2017
- 2017-09-12 CN CN201710816518.6A patent/CN107816460B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010248738A (en) * | 2009-04-13 | 2010-11-04 | Hitachi Constr Mach Co Ltd | Control device for working arm, and working machine |
| CN102562694A (en) * | 2010-10-19 | 2012-07-11 | 林德材料控股有限责任公司 | Load-sensing regulated hydrostatic drive system |
| CN102785650A (en) * | 2011-05-18 | 2012-11-21 | 林德材料处理有限责任公司 | Hydraulic brake valve device |
| CN102865261A (en) * | 2011-07-06 | 2013-01-09 | 林德材料处理有限责任公司 | Hydrostatic driving system |
| CN102425580A (en) * | 2011-08-16 | 2012-04-25 | 中联重科股份有限公司 | Braking valve bank, hydraulic system having same and concrete spreader |
| DE102013101107A1 (en) * | 2013-02-05 | 2014-08-07 | Karlsruher Institut für Technologie | Hydraulic multi-user system with energy-efficient hydraulic circuit |
| CN104047932A (en) * | 2013-03-15 | 2014-09-17 | 宝钢工业炉工程技术有限公司 | Potential energy recovery system of lifting equipment and use method under non-stable load condition |
| CN105298958A (en) * | 2015-12-01 | 2016-02-03 | 华北水利水电大学 | Loader working hydraulic system capable of recycling overflow energy |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107816460B (en) | 2020-08-07 |
| DE102016117206A1 (en) | 2018-03-15 |
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