EP0043459A2 - Dispositif de réglage pour un ensemble de plusieurs pompes entraînées par une source d'énergie commune - Google Patents

Dispositif de réglage pour un ensemble de plusieurs pompes entraînées par une source d'énergie commune Download PDF

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Publication number
EP0043459A2
EP0043459A2 EP81104452A EP81104452A EP0043459A2 EP 0043459 A2 EP0043459 A2 EP 0043459A2 EP 81104452 A EP81104452 A EP 81104452A EP 81104452 A EP81104452 A EP 81104452A EP 0043459 A2 EP0043459 A2 EP 0043459A2
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EP
European Patent Office
Prior art keywords
line
pressure
control
delivery
pumps
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP81104452A
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German (de)
English (en)
Other versions
EP0043459A3 (en
EP0043459B1 (fr
Inventor
Dietrich Kuchenbecker
Erich Eckhardt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Linde GmbH
Original Assignee
Linde GmbH
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Filing date
Publication date
Application filed by Linde GmbH filed Critical Linde GmbH
Publication of EP0043459A2 publication Critical patent/EP0043459A2/fr
Publication of EP0043459A3 publication Critical patent/EP0043459A3/de
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Publication of EP0043459B1 publication Critical patent/EP0043459B1/fr
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery

Definitions

  • the invention relates to a control device - in particular a power control device - for a unit comprising a plurality of pumps driven by a common primary energy source - preferably a piston internal combustion engine, in particular a diesel engine - of which at least one, preferably several, but not all, can be adjusted in terms of their stroke volume per revolution , wherein the control device furthermore has a control pressure auxiliary pump which is constant with respect to the delivery volume per revolution and is driven by the same primary energy source, in the delivery line of which an immutable or - depending on the setting of the primary energy source - adjustable throttle point is arranged, the gradient between the pressures before and Behind this throttle point, the control pressure chambers of a hydraulically controlled drain valve, which is connected to a discharge line connected to the delivery line of the control pressure auxiliary pump, is applied i the actuators of the individual adjustable pumps are each connected to an actuating piston which is displaceable in an actuating cylinder.
  • a common primary energy source - preferably a piston internal combustion engine,
  • the object of the invention is to improve the control function of such a device and, in particular, to avoid vibrations, the improvement also being able to be achieved by tapping a path in which further refinements are possible.
  • the drain line is connected in the flow direction upstream of the throttle point to the delivery line of the auxiliary control pressure pump and that a control pressure line branches off from the drain line upstream of the drain valve, to which all setting members are connected, the drain valve being opened in normal operation is and closes when the pressure drop at the throttle point in accordance with the extent of the drop in the pressure drop, with the result that the pressure increases in the control pressure line leading to the adjusting members as the flow rate of the control pressure auxiliary pump decreases.
  • This can be an essential achieve more sensitive, but also faster response than with the previously known devices. The consequence of this is that vibrations do not occur as easily as in the previously known devices.
  • a control device of the generic type for a pump unit consisting of several pumps in which the actuating cylinder or actuators assigned to the adjustable pump or pumps are acted upon by the delivery pressure of the respectively assigned pump.
  • the actuating cylinders connected to the actuators of the individual pumps are acted upon directly by the delivery pressure, while the cylinder acted upon by the auxiliary control pressure pump is operatively connected to the actuators via intermediate members (DE-OS 26 03.563).
  • intermediate members DE-OS 26 03.563
  • control piston acted upon by the control pressure influences the setting of a pressure limiting valve connected to the control pressure line leading to the setting members.
  • control pistons in the control cylinders act on a control plate which is supported against a spring and which influences the setting of the pressure relief valve mentioned.
  • the power control characteristic can be changed entirely or only in a partial region at the pressure limiting valve can be obtained by selection.
  • the course of the pressure in the control pressure line can be determined depending on the delivery pressure by selecting the spring stiffness. Because either the pressure determined by the limit load valve or the pressure determined by the pressure relief valve acts in the control pressure line, rapid delivery pressure-dependent intervention is achieved without basically canceling or changing the limit load control characteristic as long as the delivery pressure-dependent intervention does not take place.
  • the intervention point of the delivery pressure-dependent signal is influenced by suitable dimensioning of the high pressure spring on the pressure relief valve and thus determines from which point the limit load control is overridden.
  • the oversteering results in faster processing of the signal dependent on the delivery pressure and thereby stabilization of the control loop.
  • the previously known border Load control has the disadvantage that the speed of the primary energy source drops very sharply due to the sluggishness of the response, or is pressed before it is sufficiently regulated back. This disadvantage is avoided by the override by the delivery pressure-dependent signal.
  • a device according to the invention which engages the intervention of the delivery pressure-dependent signal, which can be scanned hydraulically or electrically / electronically, can be retrofitted to a limit load control according to claim 1.
  • the configuration of the adjusting elements according to claim 7 can be useful on the one hand, because adjusting elements designed in this way result in an advantageous control function given the control pressure available.
  • the use of this embodiment of the adjusting elements can be expedient if the adjustable pumps are basically provided with adjusting elements designed in this way due to series production, as can be the case in particular with adjustable pumps in the form of a swivel slide.
  • Such a configuration of the setting elements has already been proposed by German patent application P 29 30 139.1. The object is achieved with the control method according to the invention.
  • the primary energy source is the diesel engine 1, which drives the gear train 3, 4, 5 via the shaft 2, from which the adjustable pumps 6 and 7 and the pump 8 are driven.
  • the pump 6 delivers into the delivery line 9 and the pump 7 delivers into the delivery line 10. Both pumps 6 and 7 draw in from the pressureless container 11.
  • the pump 8 is connected in a closed circuit to the hydraulic motor 14 via the lines 12 and 13. If the pump unit 6, 7, 8 is part of the drive system of an excavator, the hydraulic motor 14 can be the slewing gear motor, for example.
  • the pump 8 can (as shown symbolically) be an adjustable pump, but can also preferably be a constant pump.
  • Parts 2 to 14 are part of the main drive unit.
  • the diesel engine 1 also drives the auxiliary control pressure pump 16 via a secondary shaft 15, which also draws in from the container 11 and whose flow rate per revolution cannot be changed.
  • the control pressure auxiliary pump delivers into the control pump main line 17, which is secured by a pressure relief valve 18 and which leads to the limit load valve 19.
  • a throttle point 20 is provided in the control pump main line 17, which has the task of building up a pressure in the control pump main line 17 which is dependent on the delivery flow of the control pressure auxiliary pump 16, or has the task that one of the drive speed of the drive speed at this throttle point 20 Control pressure auxiliary pump 16 dependent pressure drop arises.
  • This pressure drop is taken off at the connection points 21 and 22, the pressure in the main control pump line 17 upstream of the throttle point 20 being fed through the control pressure line 23 to the one control pressure chamber of the drain valve 24 and the pressure in the main control pump line 17 after the throttle point 20 is fed via line 25 to the other control pressure chamber of the drain valve 24. If the pressure drop between the branch points 21 and 22 is large, the drain valve 24 is open; if the pressure drop drops below a predetermined limit value, the drain valve 24 closes.
  • a control pressure line 27 is connected to the control pump main line 17 at a connection point 26 (which can also be identical to the connection point 21 or branch off from the line 23), in which a constant throttle point 28 is arranged and which leads to the drain valve 24 and from which branches off a control pressure line 29 which leads to the actuating cylinders 30 and 31 of the pumps 6 and 7, wherein in each of the actuating cylinders 30 and 31 an actuating piston is displaceable which is connected to the actuator of the respectively associated pump is.
  • the mode of operation is as follows: If the diesel engine 1 is running at its intended speed, the auxiliary control pressure pump 16 delivers an intended delivery flow into the main control pump line 17, so that a predetermined pressure drop arises at the throttle point 20, which keeps the drain valve 24 open.
  • the control pressure line 19 is thus connected to the open drain valve 24, while the constant throttle point 18 prevents the medium from the control pump main line 17 from flowing through the drain valve 24 without pressure.
  • the actuating cylinders 30 and 31 are therefore also depressurized, the pumps 6 and 7 are therefore set to their position of maximum delivery volume per revolution.
  • a branch line 33 is connected to the control pump main line 17 behind the throttle point 20 or behind the limit load valve 19 at a further connection point 32.
  • a secondary line 35 is connected to the control pressure line 29 at a connection point 34.
  • the branch line 33 and the secondary line 35 lead to a high-pressure activation valve 36.
  • a pressure-limiting valve 37 is connected to the line 33, the setting value of which is determined by the pretension of the low-pressure spring 38.
  • the secondary line 35 is connected to the secondary line 33 at the connection point 39.
  • a check valve 40 is arranged in the secondary line 35.
  • the low pressure spring 38 is supported against a spring plate 41, which is rigidly connected via a plunger 42 to the plate 43 against which the control pressure pistons 44 and 45 are supported, the control pressure piston 44 being pressurized via line 46 from the delivery line 9 and the control piston 45 is pressurized via the line 47 from the delivery line 10.
  • the plate 43 is supported against a high pressure spring 48, which is supported on the other hand in the housing.
  • a throttle point 49 is also arranged in line 33.
  • a check valve 50 is also expediently arranged in the control pressure line 29 between the limit load valve 19 and the connection point 34 for the secondary line 35.
  • the mode of operation is as follows: If the sum of the delivery pressures in the delivery lines 9 and 10 is so low that the sum of the forces exerted by the control pistons 44 and 45 on the control plate 43 is smaller than the force of the high-pressure spring 48, the pressure relief valve is 37 set to the lowest conceivable pressure. However, if the delivery pressure rises in at least one of the delivery lines 9 and 10, the plate 43 is displaced against the force of the high-pressure spring 48 and the preload of the low-pressure spring 38 is increased, so that the pressure relief valve 37 is set to a higher pressure. This increases the pressure in line 33 and thus also the pressure in secondary line 35.
  • check valve 40 opens with the result that line 33 is present Pressure is now also present in the control pressure line 29 and acts on the actuating cylinders 30 and 31. However, if the pressure determined by the limit load valve 19 is higher than the set pressure of the pressure relief valve 37, the check valve 40 closes and the pressure in the control pressure line 29 is determined exclusively by the limit load valve 19.
  • the check valve 50 can be provided so that the two check valves 40 and 50 ensure that the higher of the two pressures determined by the limit load valve 19 and the high-pressure activation valve 36 prevails in the control pressure line 29 and acts on the actuating cylinders 30 and 31.
  • the maximum pressure that can arise in line 33 and thus in the secondary line 35 is determined by the further low-pressure consumers, which are no longer shown in the drawing, to which the control pump main line 17 leads behind the connection point 32.
  • FIG. 2 differs from the embodiment according to FIG. 1 in that the pressure relief valve 37 is connected in a different way.
  • line 51 is connected to the second connection of drain valve 24, which is opposite the connection connected to line 27, and pressure relief valve 37 is connected in this line 51, while the rest of the parts with the same reference number are the same as in FIG. 1.
  • the mode of operation is as follows: As already mentioned in connection with FIG. 1, if the pressure drop between the connection points 21 and 22 is large enough, the drain valve 24 is opened. The pressure in line 27 and thus in line 29 is determined by the pressure relief valve 37 in the embodiment according to FIG. 2 with the drain valve 24 open. If this is switched to free flow, the control pressure line 29 is also depressurized. However, if the pressure relief valve 37 is set to a higher pressure due to the increase in the sum of the pressures in the lines 46 and 47, the pressure in the line 51 thus increases, which pressure passes through the drain valve 24 to the line 27 and thus to the control pressure line 29 reports, so that this higher pressure also acts on the actuating cylinders 30 and 31.
  • the drain valve 24 closes and, by its closed position, determines the congestion in front of the drain valve 24 and thus in the line 27 and thus in the control pressure line 29 the setting of the pressure relief valve 37 already has an increased pressure in the line 51, this superimposes the throttling action in the closing drain valve 24.
  • This block 52 is shown in FIG. 3 in a sectional view.
  • the control pump main line 17 is connected via a connection part 61 in such a way that it leads to a space 62 in part 73 of the entire housing 52.
  • this space 62 there is a component 60 which contains a baffle plate which prevents the flow flowing axially through the line 17 from exerting a dynamic effect on the control piston 56.
  • a secondary bore 63 is connected to the space 62, in which a part 54 is arranged, which has a bore, which represents the throttle point 20, behind which the drain line 55 branches off, to the other consumers of low pressure, not shown and not dealt with further leads.
  • a component 58 is screwed into the control piston 56, which contains a narrower bore, which forms the throttle point 28.
  • the control piston 56 is supported against a spring which holds the control piston 56 in its closed position when the pressure drop between the pressure in the space 62 and the pressure in the line 25 is too small. If the pressure drop is sufficient, the control piston 56 in FIG. 3 is displaced upwards so far that the control cone part 65 lies in front of the mouth of the line 27. In its most upwardly displaced position, the control piston 56 bears against the support screw 66, so that the transverse bores 67 in the control piston 56 lie in front of the mouths of the line 27. This is the normal operating situation.
  • the control piston 53 of the pressure relief valve is supported against the low pressure spring 38, which is supported on the other hand against the intermediate plate 43, against which the control pistons 44 and 45 are supported and which is connected to a pot-like part 68, on the flange on the left in the drawing, the high pressure spring 48 is supported.
  • the components in Figure 3 with an upright axis thus form the drain valve 24, while the pressure relief valve 37 is shown with a horizontal axis.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
EP81104452A 1980-06-28 1981-06-10 Dispositif de réglage pour un ensemble de plusieurs pompes entraînées par une source d'énergie commune Expired EP0043459B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3024399 1980-06-28
DE19803024399 DE3024399A1 (de) 1980-06-28 1980-06-28 Regeleinrichtung fuer ein aggregat aus mehreren, von einer gemeinsamen primaerenergiequelle angetriebenen pumpe

Publications (3)

Publication Number Publication Date
EP0043459A2 true EP0043459A2 (fr) 1982-01-13
EP0043459A3 EP0043459A3 (en) 1982-01-20
EP0043459B1 EP0043459B1 (fr) 1984-09-12

Family

ID=6105778

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81104452A Expired EP0043459B1 (fr) 1980-06-28 1981-06-10 Dispositif de réglage pour un ensemble de plusieurs pompes entraînées par une source d'énergie commune

Country Status (5)

Country Link
US (1) US4405287A (fr)
EP (1) EP0043459B1 (fr)
JP (1) JPS5746082A (fr)
BR (1) BR8104068A (fr)
DE (1) DE3024399A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3143539A1 (de) * 1981-11-03 1983-05-11 Linde Ag, 6200 Wiesbaden Steuereinrichtung fuer ein stufenlos einstellbares, vorzugsweise hydrostatisches getriebe
DE3323278C2 (de) * 1983-06-28 1986-05-22 Hydromatik GmbH, 7915 Elchingen Regelvorrichtung für mehrere aus hydrostatischen Getrieben bestehende Antriebsaggregate
US4739616A (en) * 1985-12-13 1988-04-26 Sundstrand Corporation Summing pressure compensation control
JPH01220706A (ja) * 1988-02-25 1989-09-04 Komatsu Ltd 油圧式掘削機の油圧制御装置
US4984427A (en) * 1989-09-01 1991-01-15 Kabushiki Kaisha Kobe Seiko Sho Control circuit for hydraulic actuator
US5600952A (en) * 1995-09-26 1997-02-11 Aurora Technology Corporation Auxilliary drive apparatus
JPH10141310A (ja) * 1996-11-13 1998-05-26 Komatsu Ltd 圧油供給装置
US8117837B1 (en) * 2003-12-17 2012-02-21 Sauer-Danfoss Inc. Hydrostatic transmission having integrated pressure compensated load sensing auxiliary pump
CN102305204A (zh) * 2011-08-22 2012-01-04 广西玉柴重工有限公司 转速感应式变量恒流泵
US11725647B2 (en) * 2021-05-18 2023-08-15 Hamilton Sundstrand Corporation On-demand dual variable displacement positive displacement pumping system

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841795A (en) * 1972-07-17 1974-10-15 Caterpillar Tractor Co Combined engine speed and pressure responsive control for variable displacement pumps
FR2300914A1 (fr) * 1975-02-12 1976-09-10 Bosch Gmbh Robert Dispositif de regulation pour pompes reglables
GB1496141A (en) * 1975-04-22 1977-12-30 Priestman Bros Ltd Hydraulic systems
US4080979A (en) * 1977-03-22 1978-03-28 Caterpillar Tractor Co. Combined summing and underspeed valve
GB2032140A (en) * 1978-09-22 1980-04-30 Komatsu Mfg Co Ltd Hydraulic control system for variable-displacement pumps

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2603563C2 (de) * 1976-01-30 1986-02-20 Linde Ag, 6200 Wiesbaden Steuereinrichtung für ein aus mindestens zwei Pumpen bestehendes Pumpen-Aggregat
JPS5364802A (en) * 1976-11-24 1978-06-09 Komatsu Ltd Input torque control equipment in hydraulic pump
DE2813486C2 (de) * 1977-03-31 1986-06-26 Kabushiki Kaisha Komatsu Seisakusho, Tokio/Tokyo Steuervorrichtung für Hydraulikpumpen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841795A (en) * 1972-07-17 1974-10-15 Caterpillar Tractor Co Combined engine speed and pressure responsive control for variable displacement pumps
FR2300914A1 (fr) * 1975-02-12 1976-09-10 Bosch Gmbh Robert Dispositif de regulation pour pompes reglables
GB1496141A (en) * 1975-04-22 1977-12-30 Priestman Bros Ltd Hydraulic systems
US4080979A (en) * 1977-03-22 1978-03-28 Caterpillar Tractor Co. Combined summing and underspeed valve
GB2032140A (en) * 1978-09-22 1980-04-30 Komatsu Mfg Co Ltd Hydraulic control system for variable-displacement pumps

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Bauelemente der Ölhydraulik" *
HYDRAULIC PNEUMATIC MECHANICAL POWER, Band 23, No. 271, Juli 1977, A.T. CLEMENTS "Power Economy with Hydrostatic Transmission, Seiten 257-261 *

Also Published As

Publication number Publication date
BR8104068A (pt) 1982-03-16
EP0043459A3 (en) 1982-01-20
US4405287A (en) 1983-09-20
JPS5746082A (en) 1982-03-16
EP0043459B1 (fr) 1984-09-12
DE3024399A1 (de) 1982-01-21

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