WO1999014505A1 - Hydraulic system - Google Patents
Hydraulic system Download PDFInfo
- Publication number
- WO1999014505A1 WO1999014505A1 PCT/EP1998/005346 EP9805346W WO9914505A1 WO 1999014505 A1 WO1999014505 A1 WO 1999014505A1 EP 9805346 W EP9805346 W EP 9805346W WO 9914505 A1 WO9914505 A1 WO 9914505A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- pump
- valves
- variable
- hydraulic
- Prior art date
Links
Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
-
- 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
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/06—Pressure in a (hydraulic) circuit
- F04B2205/062—Pressure in a (hydraulic) circuit before a throttle
Definitions
- the invention relates to a hydraulic device for supplying hydraulic consumers with pressure medium according to the preamble of claim 1.
- Valves are arranged between a variable pump and two consumers, which control the quantity of pressure medium to be supplied to the consumers.
- the inputs of the valves are connected to one another.
- a pressure compensator is connected between each valve and the consumers assigned to this valve.
- Each pressure compensator keeps the difference between the inlet pressure of the pressure compensator and the highest load pressure of the consumers constant.
- the opening cross-section of the valve upstream of the pressure compensator acts as a measuring orifice.
- the manipulated variable of the pressure regulator is fed to an actuator which influences the flow rate of the variable pump.
- the pressure regulator keeps the difference between the pump pressure and the highest load pressure constant.
- a variable displacement pump 1 with an actuator 2 delivers hydraulic pressure medium from a tank 3.
- the pump pressure is designated p p .
- a line 5 leads from the output of the variable displacement pump 1 denoted by 4 to a valve block 6 with two valves 7 and 8, the inputs of which are connected to one another.
- a connection 9 of the valve block 6 forms the inlet of the valves 7 and 8.
- the pressure at the inlet of the valves 7 and 8 is denoted by p «.
- a pressure compensator 10 and a consumer 11 are connected downstream of the valve 7.
- the load pressure of the consumer 11 is designated p, 1 .
- valve 8 is followed by a pressure compensator 12 and a consumer 13.
- the load pressure of the consumer 13 is denoted by p, -.
- Two check valves 14 and 15 select the higher of the load pressures of consumers 11 and 13, respectively.
- the higher of the pressures p- - and p n - is denoted by p ⁇ , it is supplied to the pressure compensator 10 and the pressure compensator 11 as a reference variable.
- the pressure p ⁇ together with the pressure equivalent of a spring 10f acts on the pressure compensator 10 from one side.
- the pressure between the valve 7 and the pressure compensator 10 is denoted by p 7 , it acts on the pressure compensator 10 from the other side.
- the pressure p "adjusts itself to a value which is greater than the pressure p by the pressure equivalent of the spring 10f.
- the pressure denoted by p g between the valve 8 and the pressure compensator 12 is set to a value which is greater than the pressure P ⁇ by the pressure equivalent of the spring 12f.
- the pressure equivalent of the springs is 10f and 12f is negligibly small compared to the pressure p ⁇ , so that both the pressure p "between the valve 7 and the pressure compensator 10 and the pressure p" between the valve 8 and the pressure compensator 12 are practically equal to the pressure p ⁇ .
- the springs 10f and 12f are provided so that the pistons of the
- Print carriage 10 or 12 assume a defined position in the depressurized state. Since the inlets of valves 7 and 8 are connected to one another and the pressure at the outlet of valves 7 and 8 is kept at the same value by pressure compensators 10 and 12, the same pressure difference is established at valve 8 as at valve 7 .
- a pump regulator 16 is arranged in spatial proximity to the variable displacement pump 1.
- the pump controller 16 is the pressure p as the guide size and the pump pressure p as
- the actuator 2 is supplied with a pressure p 2 as the manipulated variable.
- the pump pressure p serves as the supply pressure for the pump regulator 16.
- the actuator 2 adjusts the delivery volume of the variable pump 1 until the pump pressure p has reached a value which is greater than the pressure p ⁇ " v by the pressure equivalent of the spring 16f.
- the pressure equivalent of the spring 16f is of the order of 20 bar.
- the line 5 between the output 4 of the variable displacement pump 1 and the connection 9 of the valve block 6 has a throttling effect.
- the same also applies to other components (not shown in FIG. 1) which restrict the pressure medium flow in line 5, such as, for. B. priority valves or accumulator loading valves.
- the throttling effect of these components is in a throttle 17 represented symbolically. Even if the throttling components summarized as throttle 17 consist only of the flow cross section of line 5, the pressure difference between the output 4 of the variable pump 1 and the / connection 9 of the valve block 6 is dependent on the pressure medium flow which flows through the throttle 17.
- the pump controller 16 keeps the difference between the pressures p and P Lma ⁇ / thus the sum of the pressure difference at the throttle 17 and from the pressure difference at the valve 7 constant, the pressure difference at the valve 7 changes - and equally the pressure difference at the valve 8 - opposite to the pressure difference at the throttle 17. If z. B. with partially open valves 7 and 8, the valve 8 opened even further, the pressure medium flow supplied to the consumer 13 increases. The pressure medium flow flowing through the throttle 17 increases accordingly. The increase in the pressure medium flow flowing through the throttle 17 leads to an increase in the pressure difference at the throttle 17. Since the pump regulator 16 keeps the difference between the pump pressure p p and the highest load pressure p ⁇ constant, the pressure difference at the valves 7 decreases and 8 accordingly.
- the reduction in the pressure difference at the valves 7 and 8 leads in particular to a reduction in the pressure medium flow flowing via the valve 7 to the consumer 11 and slows down the movement of the consumer 11.
- a control process compensates for the change in the speed of the consumer, which is dependent on changes in the pressure medium flow flowing through the throttle 17.
- Such compensation is, however, in applications in which the opening cross section of the valves 7 and 8, for. B. is specified by a potentiometer, i.e. not possible with pure controls of the opening cross-section without additional volume control.
- the invention has for its object to provide a hydraulic device of the type mentioned in the changes in the pressure medium flow between the variable displacement pump and the input of the valves that control the pressure medium flow to the consumers, do not affect the size of the pressure medium flow supplied to the consumers.
- the pump controller is arranged in the spatial vicinity of the variable displacement pump.
- the pump regulator is arranged in the spatial vicinity of the valves which control the pressure medium flow to the consumers. Additional chokes in the control lines, which lead to the actual value input of the pump controller, have a dampening influence on the control behavior of the pump controller.
- FIG. 1 shows the hydraulic device described at the beginning of the prior art in a schematic illustration
- FIG. 2 shows a first exemplary embodiment of a hydraulic device according to the invention, which is based on the hydraulic device shown in FIG. 1,
- FIG 3 is a further development of the hydraulic device shown in Figure 2 and
- Figure 4 shows a second embodiment of a hydraulic device according to the invention.
- FIG. 2 shows a first exemplary embodiment of a hydraulic device according to the invention. It is based on the hydraulic device shown in FIG. 1.
- the same reference numerals as in FIG. 1 are used for the same parts.
- the pump regulator is provided with the reference symbol 16 ', since it partially differs from the structure of the pump regulator 16 in FIG. 1.
- the valve block is provided with the reference number 6 '. It has a further connection 9 'which is connected to the connection 9 within the valve block 6'.
- the actual value input of the pump controller 16 ' is provided with the reference number 20.
- a throttle 21 is arranged between the output 4 of the variable displacement pump 1 and the actual value input 20 of the pump regulator 16 '.
- a line 22 leads from the actual value Input 20 of the pump regulator 16 'to the connection 9' of the valve block 6 '.
- the throttle 21 and the line 22 form a bypass to the throttle 17.
- the pressure difference p - p g drops.
- the pressure p 1 is fed to the actual value input 20 from the input of the valves 7 and 8.
- the throttle 21 decouples the pressure at the actual value input 20 of the pump regulator 16 'from the pump pressure p p at the output 4 of the variable pump 1.
- the throttle 21 limits the pressure medium flow via the line 22.
- the pump regulator 16' regulates the pressure p g so that it is greater than the pressure p ⁇ by the pressure equivalent of the spring 16f.
- the pump pressure p p is set to a value which is greater than the pressure p "by the pressure difference at the throttle 17. Changes in the pressure medium flow flowing through the throttle 17 only influence the level of the pump pressure p, but no longer have any influence on the pressure difference at the valves 7 and 8. Thus, the pressure medium flow to the consumers 11 and 13 is only from the opening cross section of the valves 7 and 8 are dependent and no longer on the pressure medium flow via the throttle 17.
- FIG. 3 shows a development of the hydraulic device shown in FIG. 2.
- the pump regulator is provided with the reference symbol 16 ′′ since it contains a further throttle 23 compared to the pump regulator 16 ′ shown in FIG. 2.
- the throttle 23 is arranged between the output 4 of the variable pump 1 and the throttle 21.
- the connection point of the two throttles is provided with the reference numeral 24.
- the supply pressure 3 for the pump regulator 16 "of the variable pump 1 is the pressure at the connection point 24 of the throttles 23 and 21. This pressure lies between the pump pressure p and the pressure p q at the inlet of the valves 7 and 8.
- the throttle 21 stabilizes the control process. So that enough pressure medium is still available for a quick adjustment of the variable displacement pump 1, the flow cross section of the throttle 23 is advantageously larger than the flow cross section of the throttle 21.
- Actual value input 20 of the pump regulator 16 "and the connection 9 'of the pump block 6' only allows a pressure medium flow from the pump regulator 16" to the valve block 6 '. It prevents transmission of pressure peaks of the valves 7 or 8 to the actual value input 20 of the pump regulator 16 ". Also in FIG. 2, the check valve 25 in the line 22 between the actual value input 20 of the pump regulator 16 'and the valve block 6' be provided.
- FIG. 4 shows a second embodiment of the hydraulic device according to the invention. 1 to 3, the pump controller 16, 16 'or 16 "is arranged in the spatial vicinity of the variable displacement pump 1, in FIG. 4 the pump controller is integrated in the valve block. It is therefore located in the spatial vicinity of the valves 7 and 8.
- the valve block is provided with the reference symbol 6 "and the pump regulator with the reference symbol 16"'.
- the pressure p "at the input of the valves 7 and 8 is fed to the actual value input 20 of the pump regulator 16"' via two throttles 26 and 27 which correspond to the chokes 23 and 21 in FIG. 3.
- the connection point of the chokes 26 and 27 is provided with the reference number 28.
- the pressure at connection point 28 is the supply pressure p ⁇ ⁇ ITlclX for the pump controller 16 "'.
- the throttle 26 allows a reduction in the supply pressure ⁇ r ⁇ .x. Die
- the control pressure p 1 serving as the manipulated variable for the actuator 2 of the variable pump 1 is supplied to the variable pump 1 via a line 29.
- the pressure difference at the valves 7 and 8 is independent of the height of the pressure medium flow flowing through the throttle 17.
- only two lines 5 and 29 are required between the variable displacement pump 1 and the valve block 6 ′′.
- a line is also required which is from leads the valve block 6 'to the tank 3. This line was not shown in Figures 2 and 3, since it was not necessary there for understanding the invention.
- two non-return valves 14 and 15 are provided for selecting the highest load pressure p ⁇ .
- the selection of the highest load pressure can of course also be done with a shuttle valve or - with more than two consumers - with a shuttle valve chain.
- the load pressure of uncontrolled consumers is usually not taken into account when selecting the highest load pressure in order to keep the energy consumption as low as possible.
- the valves used for this are not shown in FIGS. 1 to 4, since they are not necessary for an understanding of the invention.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP98947447A EP1015773A1 (en) | 1997-09-16 | 1998-08-22 | Hydraulic system |
JP2000512013A JP2001516854A (en) | 1997-09-16 | 1998-08-22 | Hydraulic device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE1997140579 DE19740579A1 (en) | 1997-09-16 | 1997-09-16 | Hydraulic device |
DE19740579.7 | 1997-09-16 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1999014505A1 true WO1999014505A1 (en) | 1999-03-25 |
Family
ID=7842438
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1998/005346 WO1999014505A1 (en) | 1997-09-16 | 1998-08-22 | Hydraulic system |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1015773A1 (en) |
JP (1) | JP2001516854A (en) |
DE (1) | DE19740579A1 (en) |
WO (1) | WO1999014505A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107165879B (en) * | 2017-06-29 | 2018-12-11 | 湖南十开科技有限公司 | A kind of flow prior control loop |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3844405A1 (en) * | 1988-12-30 | 1990-07-05 | Rexroth Mannesmann Gmbh | Valve arrangement for a hydraulic system |
DE3844399A1 (en) * | 1988-12-30 | 1990-07-12 | Rexroth Mannesmann Gmbh | Variable-displacement pump for a plurality of consumers which can be actuated independently of one another |
DE4036720A1 (en) * | 1990-11-17 | 1992-05-21 | Linde Ag | CONTROL CIRCUIT FOR THE LOAD-INDEPENDENT DISTRIBUTION OF A PRESSURE FLOW |
-
1997
- 1997-09-16 DE DE1997140579 patent/DE19740579A1/en not_active Withdrawn
-
1998
- 1998-08-22 JP JP2000512013A patent/JP2001516854A/en active Pending
- 1998-08-22 WO PCT/EP1998/005346 patent/WO1999014505A1/en not_active Application Discontinuation
- 1998-08-22 EP EP98947447A patent/EP1015773A1/en not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3844405A1 (en) * | 1988-12-30 | 1990-07-05 | Rexroth Mannesmann Gmbh | Valve arrangement for a hydraulic system |
DE3844399A1 (en) * | 1988-12-30 | 1990-07-12 | Rexroth Mannesmann Gmbh | Variable-displacement pump for a plurality of consumers which can be actuated independently of one another |
DE4036720A1 (en) * | 1990-11-17 | 1992-05-21 | Linde Ag | CONTROL CIRCUIT FOR THE LOAD-INDEPENDENT DISTRIBUTION OF A PRESSURE FLOW |
Non-Patent Citations (1)
Title |
---|
"GRUNDLAGEN DER HYDRAULISCHEN SCHALTUNGSTECHNIK", OLHYDRAULIK UND PNEUMATIK, vol. 38, no. 8, 1 January 1994 (1994-01-01), pages 449/450, 453/454, XP000195314 * |
Also Published As
Publication number | Publication date |
---|---|
DE19740579A1 (en) | 1999-03-18 |
JP2001516854A (en) | 2001-10-02 |
EP1015773A1 (en) | 2000-07-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE2651325C2 (en) | ||
DE60105849T2 (en) | HYDRAULIC VALVE SYSTEM WITH PRINTED CARRIER | |
EP1710446B1 (en) | Hydraulic control device and control block | |
EP0275968A2 (en) | Control device for a hydrostatic transmission for at least two users | |
DE69416636T2 (en) | Liquid control system | |
EP0016719B1 (en) | Hydraulic motor control device | |
WO2006037318A1 (en) | Hydraulic control arrangement | |
EP3748168A1 (en) | Hydraulic drive system with two pumps and energy recovery | |
DE4036720A1 (en) | CONTROL CIRCUIT FOR THE LOAD-INDEPENDENT DISTRIBUTION OF A PRESSURE FLOW | |
DE3149026A1 (en) | CONTROL DEVICE FOR TWO OVER ONE BRANCH HYDRAULIC ACTUATORS SUPPLIED BY A HIGH PRESSURE PUMP | |
EP2171289A1 (en) | Control device for at least two hydraulic drives | |
EP0190431B1 (en) | Hydraulic system | |
EP1200743A1 (en) | Hydraulic steueranordnung zur bedarfstromgeregelten (load-sensing-geregelten) druckmittelversorgung von vorzugsweise mehreren hydraulischen verbrauchern | |
EP2126371B1 (en) | Valve arrangement | |
DE1951429B2 (en) | HYDRAULIC CONTROL SYSTEM, IN PARTICULAR FOR MULTIPLE HYDRAULIC MOTORS | |
DE4025638C1 (en) | ||
WO2007039249A1 (en) | Hydraulic control device | |
WO1999014505A1 (en) | Hydraulic system | |
DE3027819A1 (en) | DEVICE FOR REGULATING A VARIABLE PUMP | |
DE3844399C2 (en) | Control arrangement for several independently operable hydraulic consumers and their use | |
DE3528781C2 (en) | ||
EP3258116B1 (en) | Hydraulic module with pressure-controlled 2-way flow control valve | |
DE10119276B4 (en) | Hydraulic control circuit | |
DE4041033C2 (en) | ||
EP1253327A1 (en) | Hydraulic control circuit |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): JP US |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
DFPE | Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 1998947447 Country of ref document: EP Ref document number: 09508844 Country of ref document: US |
|
WWP | Wipo information: published in national office |
Ref document number: 1998947447 Country of ref document: EP |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: 1998947447 Country of ref document: EP |