EP0428374B1 - Verdrängerpumpe-Anlagen - Google Patents

Verdrängerpumpe-Anlagen Download PDF

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Publication number
EP0428374B1
EP0428374B1 EP19900312361 EP90312361A EP0428374B1 EP 0428374 B1 EP0428374 B1 EP 0428374B1 EP 19900312361 EP19900312361 EP 19900312361 EP 90312361 A EP90312361 A EP 90312361A EP 0428374 B1 EP0428374 B1 EP 0428374B1
Authority
EP
European Patent Office
Prior art keywords
valve
overspill
bore
land
valve member
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.)
Expired - Lifetime
Application number
EP19900312361
Other languages
English (en)
French (fr)
Other versions
EP0428374A1 (de
Inventor
Ian Trevor Bristow
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.)
Dana Automotive Ltd
Original Assignee
Hobourn Automotive Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hobourn Automotive Ltd filed Critical Hobourn Automotive Ltd
Publication of EP0428374A1 publication Critical patent/EP0428374A1/de
Application granted granted Critical
Publication of EP0428374B1 publication Critical patent/EP0428374B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/063—Control by using a valve in a system with several pumping chambers wherein the flow-path through the chambers can be changed, e.g. between series and parallel flow
    • 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
    • F04B49/22—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 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F04C2/3447—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface the vanes having the form of rollers, slippers or the like

Definitions

  • This invention relates to positive displacement pump systems and is more particularly concerned with such systems in which deliveries from two positive displacement pump sources are available to be fed to a common supply passage.
  • a positive displacement pump system having first and second delivery passages for pumped fluid, a main discharge passage connected to receive a flow from the first delivery passage and to receive through a non-return valve a flow from the second delivery passage, a control orifice disposed in the main discharge passage at a location to receive the combined said flows, and a control valve for apportioning the flow from the second delivery passage between the main discharge passage and overspill porting and controlling the by-passing of a proportion of the flow from the first delivery passage through the overspill porting, said control valve comprising a valve member slidably mounted in a bore in a valve body, one end of which bore is in communication with the main discharge passage at a location upstream of said control orifice, a spring which is disposed in a spring chamber in the valve body and which urges the valve member towards said one end of the bore, said spring chamber communicating with the main discharge passage at a location downstream of the control orifice, said valve member having a first metering land between
  • the overspill porting comprises an annular overspill port extending about the valve bore, and the edge of the overspill port nearer the first land and the end of the first land nearer said one end of the valve bore are so shaped in relation to each other that on movement of the valve member against the spring loading, the communication between the by-pass port and said one end of the valve bore is, initially at least, less than fully annular as the valve member moves against the spring loading.
  • the progressive increase in the area of communication towards fully annular communication in these constructions may be achieved by providing peripheral notches in the said end face of the first and/or the second land or otherwise making the periphery of such end face non-circular. Alternatively notches may be cut in axial end edge of the port.
  • the system comprises a positive displacement pump 10 and in this instance of the well-known roller type and has two inlet ports 12, 13 and two outlet ports 14, 15 from which the pumped fluid flows into first and second delivery passages 16, 17 respectively.
  • the downstream end of delivery passage 16 is in direct communication with the upstream end of a main discharge passage 18.
  • the downstream end of the second delivery passage 17 communicates with the discharge passage 18 through a non-return valve 19.
  • a discharge orifice 20 is provided in the discharge passage 18.
  • the control valve 11 comprises a spool valve member 22 slidably mounted in a bore 24 in a body part 26.
  • One end of the bore 24 opens to the main discharge passage 18 upstream of the orifice 20.
  • the other end of the bore forms a chamber 27 housing a spring 28 which urges the valve member into abutment with a wall of the main discharge passage 18.
  • the chamber 27 communicates through a duct 25 with the passage 18 at a location downstream of the orifice 20 so that the pressure drop across the orifice opposes the force of the spring 28.
  • the valve member has first and second lands 29, 30 of which, in the position shown in Figure 1, the former is disposed between the main discharge passage and an annular overspill port 31 in the bore 24. Port 31 communicates through a passage 32 with a passage 33 leading to the inlet port 12. Land 30 is axially spaced from land 29 and, in the position shown in Figure 1, obstructs an annular by-pass port 34 which is in communication with the second delivery passage 17 at a location upstream of the non-return valve 19.
  • the lands 29,30 have in the periphery of their end portions nearer the main discharge passage a number of notches 35, 36 respectively opening to the end face.
  • Figure 1 shows the valve in its position in low-speed operation of the pump.
  • the pressure in the main discharge passage is low, and the lands 29 and 30 respectively prevent communication between the discharge passage 18 and the by-pass port 34 respectively and the overspill port 31, so that the whole flow from the second outlet port 15 flows through the non-return valve 19 and joins the flow from the first outlet port 14 in the main discharge passage leading to the point of utilisation.
  • the pump speed increases, assuming for the moment that the pressure at the downstream side of orifice 20 remains constant, the increase in pressure at the upstream side of the orifice urges the valve member to move against the spring force as shown in Figure 2.
  • valve member causes a sharp fall in the pressure in the second delivery passage 17 and a consequent reduction in the power requirement of the pump. Further increases in pump speed move the valve member further rightward permitting increased flow of fluid from the first delivery passage to pass through notches 35 to the overspill port 34.
  • the two lands 29, 30 of the valve member have fully planar end faces and notches 37, 38 are instead formed in the axial end faces 31b, 34b of the ports 31, 34 which co-operate with the lands in controlling the opening of the ports.
  • the notches 37, 38 operate in conjunction with the ends of the lands 29, 30 in exactly the same way as the notches 35, 36 operate in conjunction with the edges 31a of the ports in the arrangement of Figure 1.
  • the orifice 20 operates to maintain a constant flow to the point of utilisation, and if at any stage of operation, the pressure downstream of the orifice 20 falls, the resulting drop in pressure in chamber 27 causes the valve member to move to increase the amount of fluid passed to the overspill port. Conversely if the pressure downstream of orifice 20 rises, the resulting rise in pressure in chamber 27 causes the valve member to move to reduce the amount of fluid passed to the overspill port.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (5)

  1. Verdrängerpumpe-Anlage mit einem ersten und zweiten Ablaufkanal für gepumpte Flüssigkeit, einem Hauptabflußkanal, der zur Aufnahme einer Durchflußmenge von dem ersten Ablaufkanal und zur Aufnahme einer Durchflußmenge von dem zweiten Ablaufkanal über ein Rückschlagventil angeschlossen ist, einer Regulierungsausflußöffnung, die in dem Hauptabflußkanal an einer Stelle zur Aufnahme der vereinten Durchflußmengen angeordnet ist, und einem Regelventil zum Dosieren der Durchflußmenge von dem zweiten Ablaufkanal zwischen dem Hauptabflußkanal und Überlaufkanal und zum Regulieren des Umleitens eines Teiles der Durchflußmenge von dem ersten Ablaufkanal durch den Überlaufkanal, wobei das Regelventil ein Ventilelement umfaßt, das verschiebbar in einer Bohrung in einem Ventilkörper befestigt ist, wobei ein Ende der Bohrung mit dem Hauptabflußkanal an einer Stelle stromaufwärts der Regulierungsausflußöffnung verbunden ist, sowie mit einer Feder, die in einer Federkammer in dem Ventilkörper angeordnet ist und das Ventilelemente zu dem einen Ende der Bohrung vorspannt, wobei die Federkammer mit dem Hauptabflußkanal an einer Stelle stromabwärts der Regulierungsausflußöffnung in Verbindung steht, welches Ventilelement einen ersten Steuerkolben zwischen dem einen Ende der Ventilbohrung und dem Überlaufkanal aufweist sowie einen zweiten Steuerkolben, die zwischen der Federkammer und dem Überlaufkanal angeordnet ist, und der Ventilkörper eine ringförmige Umgehungsöffnung aufweist, die veränderbar durch den zweiten Steuerkolben verschlossen wird und mit dem zweiten Ablaufkanal an einer Stelle stromaufwärts des Rückschlagventils in Verbindung steht, wobei die Umgehungsöffnung und der axiale Endteil des zweiten Steuerkolbens, der dem Überlaufkanal näher liegt, in bezug zueinander so geformt sind, daß bei Bewegung des Ventilelements entgegen der Federbelastung die Verbindung zwischen der Umgehungsöffnung und dem Raum in der Ventilbohrung an der axialen Seite des zweiten Steuerkolbens, die dem einen Ende der Ventilbohrung näher liegt, zumindest anfangs weniger als vollständig ringförmig ist, wenn sich das Ventilelement entgegen der Federbelastung bewegt.
  2. Pumpenanlage nach Anspruch 1, wobei der Überlaufkanal eine ringförmige Überlauföffnung umfaßt, die um die Ventilbohrung verläuft, und der Rand der Überlauföffnung, der dem ersten Steuerkolben näher liegt, und das Ende des ersten Steuerkolbens, das dem Ende der Ventilbohrung näher liegt, in bezug zueinander so geformt sind, daß bei Bewegung des Ventilelements entgegen der Federbelastung die Verbindung zwischen der Umgehungsöffnung und dem einen Ende der Ventilbohrung zumindest anfangs weniger als vollständig ringförmig ist, wenn sich das Ventilelement entgegen der Federbelastung bewegt.
  3. Pumpenanlage nach Anspruch 2, wobei der Umfang der Endflächen des ersten und zweiten Steuerkolbens nicht kreisförmig ist.
  4. Pumpenanlage nach Anspruch 3, wobei in der Endfläche des ersten und/oder zweiten Steuerkolbens Kerben entlang des Umfanges ausgebildet sind.
  5. Pumpenanlage nach Anspruch 2, wobei die Kerben in dem axialen Endausgang des Überlaufteils und des Umgehungsteils ausgebildet sind, die mit den entsprechenden Steuerkolben zusammenwirken.
EP19900312361 1989-11-13 1990-11-13 Verdrängerpumpe-Anlagen Expired - Lifetime EP0428374B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB898925592A GB8925592D0 (en) 1989-11-13 1989-11-13 Positive displacement pump systems
GB8925592 1989-11-13

Publications (2)

Publication Number Publication Date
EP0428374A1 EP0428374A1 (de) 1991-05-22
EP0428374B1 true EP0428374B1 (de) 1994-07-13

Family

ID=10666206

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900312361 Expired - Lifetime EP0428374B1 (de) 1989-11-13 1990-11-13 Verdrängerpumpe-Anlagen

Country Status (3)

Country Link
EP (1) EP0428374B1 (de)
DE (1) DE69010631T2 (de)
GB (1) GB8925592D0 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2320955B (en) 1997-01-03 1999-08-04 Hobourn Automotive Ltd Flow control valve
EP1008754B1 (de) 1998-12-11 2004-03-10 Dana Automotive Limited Verdrängerpumpe-Anlagen
US6641372B2 (en) * 2000-01-21 2003-11-04 Delphi Technologies, Inc. Dual discharge hydraulic pump and system therefor

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2074618A (en) * 1934-08-01 1937-03-23 Clyde A Roeder Pumping system
US2192512A (en) * 1937-01-07 1940-03-05 F E Twiss Co Inc Pump
GB681625A (en) * 1950-05-03 1952-10-29 Hobson Ltd H M Improvements in hydraulic pumps
GB1376732A (en) * 1971-04-16 1974-12-11 Lucas Industries Ltd Hydraulic pumps
DE2817173A1 (de) * 1978-04-20 1979-10-25 Rexroth Gmbh G L Radialkolbenpumpe
DE3034377A1 (de) * 1980-09-12 1982-04-22 Krauss-Maffei AG, 8000 München Stromregelventil

Also Published As

Publication number Publication date
DE69010631D1 (de) 1994-08-18
GB8925592D0 (en) 1990-01-04
EP0428374A1 (de) 1991-05-22
DE69010631T2 (de) 1994-10-27

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