EP0810373A2 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP0810373A2
EP0810373A2 EP97108655A EP97108655A EP0810373A2 EP 0810373 A2 EP0810373 A2 EP 0810373A2 EP 97108655 A EP97108655 A EP 97108655A EP 97108655 A EP97108655 A EP 97108655A EP 0810373 A2 EP0810373 A2 EP 0810373A2
Authority
EP
European Patent Office
Prior art keywords
locking
rotor
vane pump
control surfaces
pump according
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.)
Withdrawn
Application number
EP97108655A
Other languages
German (de)
English (en)
Other versions
EP0810373A3 (fr
Inventor
Thomas Dr. Nied-Menninger
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.)
LuK Fahrzeug Hydraulik GmbH and Co KG
Original Assignee
LuK Fahrzeug Hydraulik GmbH and Co KG
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 LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Publication of EP0810373A2 publication Critical patent/EP0810373A2/fr
Publication of EP0810373A3 publication Critical patent/EP0810373A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • F04C2/356—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 outer member
    • F04C2/3566—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 outer member the inner and outer member being in contact along more than one line or surface

Definitions

  • the invention relates to a vane pump with the features mentioned in the preamble of claim 1.
  • Vane pumps of the generic type have a housing in which a rotor is set in rotation.
  • the circumferential surface of the rotor has at least one control surface which, viewed in the circumferential direction, is delimited on both sides by separating regions.
  • the control surface and the separating areas interact with at least one locking wing, which is accommodated in a groove in the wall of the fixed housing and is pressed against the control surface.
  • the rotary movement of the rotor delimits spaces with variable volumes that are delimited by the blocking vanes. Due to the periodic change in the size of the volumes, a fluid is sucked in and released again at a pressure connection.
  • this object is achieved by a vane pump with the features mentioned in claim 1.
  • a vane pump with the features mentioned in claim 1.
  • at least four locking vanes and a multiple of 2 number of control surfaces are provided over the circumferential surface of the rotor, two control surfaces each being arranged opposite and identically formed and the number of control surfaces being greater than the number of locking wings, the radial forces caused by the oppositely arranged control surfaces in the respective pressure chambers, since these are directed in the opposite direction are.
  • the rotor can thus very advantageously be mounted "on the fly" on a free end of a drive shaft of a driving engine.
  • the at least four blocking vanes and at least six control surfaces divide the entire volume flow into overlapping partial volume flows, which, depending on the rotation of the rotor, overlap in time with the total volume flow. A uniform volume flow is thereby achieved, the volume flow pulsation of which is minimized.
  • control surfaces are provided over the peripheral surface of the rotor, which preferably cooperate with a total of four locking vanes.
  • Such a construction of the vane pump ensures that a particularly good distribution of the radial forces over the entire circumference of the rotor is possible, the sum of the radial forces acting on the rotary shaft of the rotor going to zero.
  • the contact pressure of the separating areas on the housing which also varied as a result of the radial force fluctuations that have occurred up to now, is essentially constant at a minimal level, so that the rotor is worn or the housing can be minimized. This enables a longer service life for the locking vane pump.
  • the condition applies that the sum of the squares of the radial positions of a locking wing just extending and a locking wing just entering is constant and equal to the sum of the squares of the maximum and minimum radial positions of the locking wing is.
  • the entire conveying behavior of the locking vanes as a function of the radial stroke of the locking vanes is very advantageously taken into account.
  • the special design of the contour takes into account a quadratic increase in the delivery rate over the wing stroke, so that the kinematic volume flow pulsation is drastically reduced when partial delivery flows are superimposed.
  • FIG. 1 shows a section of a vane pump 10.
  • the vane pump 10 has a housing 12 which has a circular pump chamber 14.
  • a rotor 16, which can be driven by a drive shaft 18, is mounted within the pump chamber 14.
  • the drive shaft 18 can be driven via a drive device (not shown), for example an electric motor, so that the rotor 16 can be set in rotation within the pump chamber 14. In the example shown, the rotor 16 can be driven counterclockwise.
  • the rotor 16 is disc-shaped and has on its circumferential surface 20 deviating from a circular contour several, in the example shown six, identically designed control surfaces 22 and separation regions 24.
  • the control surfaces 22 and separation regions 24 are - seen in the circumferential direction - always provided alternately, so that each Control surface 22 is delimited by two separation areas 24.
  • the maximum diameter of the rotor 16 is dimensioned such that its outer diameter in the region of the separating areas 24 practically corresponds to the inner diameter of the peripheral wall 26 of the pump chamber 14.
  • the diameter of the rotor 16 in the area of the separating areas 24 is larger than its diameter in the area of the control surfaces 22, which are quasi by radially drawn in Areas are formed.
  • the control surfaces 22 and the separating regions 24 thus form a contour of the peripheral surface 20, the course of which will be discussed in more detail with reference to FIGS. 2 to 4.
  • the width of the locking vanes 30 measured perpendicular to the plane of illustration of FIG. 1 corresponds approximately to the thickness of the rotor 16.
  • the length of the locking vanes 30 measured in the radial direction is less than the depth of the grooves 28.
  • the thickness of the locking vanes 30 is somewhat less than the width of the grooves 28, so that the locking wings 30 are mounted and guided in a radial direction against the force of an elastic element, for example a compression spring 32.
  • the locking wings 30 are acted upon by the compression spring 32 with a compressive force and pressed against the peripheral surface 20 of the rotor 16.
  • the contact surface of the locking vanes 30 on the rotor 16 is rounded, preferably in the form of a circular arc, so that there is practically a linear contact with the peripheral surface 20 of the rotor 16.
  • the compressive force of the compression springs 32 is chosen so strong that the locking vanes 30 are pressed against the peripheral surface 20 of the rotor 16 at all drive speeds.
  • a total of four grooves 28 with locking vanes 30 movably mounted therein are provided, which are each arranged at an angle of 90 ° to one another in the peripheral wall 26 of the housing 12.
  • the six separating areas 24 are arranged at an angle of 60 ° over the circumference of the rotor 16, so that the control surfaces 22 located between the separating areas 24 are also offset from one another by an angle of 60 °.
  • the separating areas 24 and the control surfaces 22 all have exactly the same curve shape, that is to say the same contour, so that in the case of a straight line at any point through the drive shaft 18 there is an equal distance between the peripheral surface 20 at its two intersections with the peripheral surface 20 and the peripheral wall 26 of the pump chamber 14 or the drive shaft 18.
  • the control surfaces 22 have a first contour section 64 and a second contour section 66 which merge into one another via a section 68 which is curved in the form of a circular arc.
  • the first contour section 64 lies in front of the contour section 66.
  • the contour sections 64 and 66 each transition from or to a separating region 24 into the circular section 68.
  • a pressure outlet 34 and a suction inlet 36 are assigned to each blocking wing 30.
  • the pressure outlet 34 is here arranged in the direction of rotation of the rotor 16 indicated by the arrow 38 in front of the blocking wing 30 and the suction inlet 36 in each case after the blocking wing 30.
  • the pressure outlet 34 is formed, for example, by a bore 40 opening into the peripheral wall 26 of the pump chamber 14 and opening into a pressure connection 42.
  • the suction inlet 36 is one formed by the housing 12 connecting channel 44 which opens into a suction port 46.
  • the pressure connections 42 assigned to the locking vanes 30, that is to say four in the example shown, are brought together within a housing area which is no longer shown in FIG. 1 to form a common pressure connection of the locking vane pump 10.
  • the suction connections 46 each assigned to a locking vane 30 are also brought together to form a common suction connection of the locking vane pump 10.
  • the vane pump 10 shown in FIG. 1 performs the following function, it being clear that the section of the housing 12 shown here is arranged pressure-tight within an entire housing of the vane pump 10.
  • pressure plates can be provided on both sides of the rotor 16, which enable the pump chamber 14 to be closed in a pressure-tight manner and which have the corresponding passages for the pressure connections or suction connections.
  • the rotor 16 is set in rotation via the drive shaft 18.
  • the locking vanes 30 are pressed by the compression springs 32 against the peripheral surface 20 of the rotor 16. Due to the formation of the separating areas 24 and the control surfaces 22, the locking vanes 30 experience a radial movement (stroke) during the rotation of the rotor 16. In the area of the separating areas 24, the outer circumference of which practically corresponds to the inner circumference of the circumferential wall 26, the locking vanes 30 are in their radially outermost position.
  • the locking wings 30 pressed radially inwards by the spring force of the compression spring 32 corresponding to the contour of the control surface 22.
  • the contour of the control surfaces 22 results in chambers 48 in the region of each control surface, which have a certain volume. All chambers 48 have volumes of the same size.
  • a control surface 22 is located in the area of a locking wing 30, the chamber 48 is divided into two areas 50 and 52 by the locking wing 30, which has a rounded edge sealingly against the peripheral surface 20.
  • the areas 50 and 52 change their volumes in accordance with the direction of rotation 38 of the rotor 16.
  • the area 50 lying in front of the blocking wing in the direction of rotation changes its volume from a maximum which corresponds to the total volume of the chamber 48 to a minimum which ideally corresponds to the value zero.
  • the decrease in volume over time is determined here by the course of the contour sections 64, 66 and 68 of the control surface 22, as will be explained in more detail with reference to FIGS. 2 to 4.
  • the area 52 located after the blocking wing 30 changes its volume from a minimum, which ideally corresponds to the value zero, to a maximum, which corresponds to the volume of the chamber 48.
  • a fluid to be conveyed is sucked from the suction inlet 36 within the area 52 by enlarging the area 52 up to the total volume of the chamber 48.
  • the fluid is moved in the direction of the nearest pressure outlet 34 and expelled there under pressure. This happens through the in the Area 50 reducing volume, so that the fluid is pressed under pressure in the direction of arrow 54 from the pressure ports 42.
  • the chambers 48 shown below or above have a reducing area 50 and an increasing area 52.
  • the area 50 is pressed out of the fluid (shown hatched) into the pressure outlet 34, while at the same time a fluid is drawn into the area 52 via the suction inlet 36.
  • the chambers 48 shown on the left or right in the illustration just reach the locking vanes 30, so that in the "snapshot" shown, these chambers 48 begin to empty themselves via the pressure outlet 34.
  • the rotor 16 is supported without lateral force, the rotor 16 is optimally guided over the separating regions 24 on the peripheral wall 26 of the pump chamber 14.
  • the separation areas 24 thus have a constant sealing effect between two adjacent chambers 48.
  • the material load on the rotor 16 and the housing 12 is reduced during operation.
  • the housing 12 thus remains largely free of mechanical stresses during the rotation of the rotor 16.
  • the delivery volumes conveyed by each of the chambers 48 are virtually superimposed to form a total delivery flow.
  • the arrangement of the four locking vanes 30 and the six control surfaces 22 results in a superimposition of partial volume flows which are different in size according to the current position of the rotor 16 and which unite at the pressure connection of the locking vane pump 10 to form a common volume flow.
  • FIG. 1 The stroke of a blocking wing 30 over half a revolution of the rotor 16 is illustrated on the basis of FIG.
  • a fixed point A is drawn on the rotor 16 in FIG. 1, which defines a current angle of 0 ° with respect to a blocking wing 30.
  • the point A lies exactly in the middle of a separating area 24 in the explanation, which is exemplary here.
  • FIG. 2 shows the radial position h of a locking vane 30 over half a revolution of the rotor 16, it being clear that the sequence is repeated again in the 6-stroke locking vane pump shown in FIG. 1.
  • the radial position is plotted here over the current angle, i.e. from 0 to 180 °.
  • a total of three characteristic curves are drawn in to illustrate the invention, the solid line and the dashed line representing sinusoidal contours according to prior art locking vane pumps.
  • the characteristic curve of the vane pump 10 according to the invention is shown with a dash-dot line.
  • the radial position h of the locking vanes 10 remains at a maximum in the area of the separating areas 24 and at a minimum in the area of the contour sections 68 of the control surfaces 22. These areas are designed so that there is no radial movement of the locking vanes 30.
  • the contour profile between the separating areas 24 and the contour sections 68 is selected such that, at any position of the rotor 16, the sum of the squares of the radial position h of the locking wing 30 of a straight, radially extended locking wing 30 in the region of a contour section 64 of the control surfaces 22 and one straight radially retracting locking wing 30 are always constant in the region of a contour section 66 of a control surface 22. This sum of the squares of the radial positions of an extending and retracting locking wing 30 are also equal to the sum of the squares of the minimum and maximum radial positions h.
  • a locking wing 30 has the angular position 12.5 °, it assumes a radial position h 1 and extends straight, a second, subsequent locking wing 30 then has the angular position 102.5 ° and has a radial position of h 2 and is just entering.
  • the sum of the squares of h 1 and h 2 is the same over the entire contour of the peripheral surface 20. This means that when the rotor 16 rotates, the angular positions of the locking vanes 30 shift by exactly the same angular increments.
  • the first locking wing 30 is located itself in its extending phase and the second blocking wing 30 in its retracting phase.
  • the sum of the squares of the radial positions h 1 and h 2 is also equal to the sum of the squares of the minimum radial position h min and the maximum radial position h max .
  • four locking wings 30 are provided, the same relationship applying to the two additional locking wings 30 not considered in FIG. 2.
  • the radial acceleration curves of the locking vanes 30 are plotted in FIG. Again, the acceleration curves embodying the prior art with a continuous line and with a dashed line are compared with the acceleration curve marked with a dash-dot line in accordance with the contour of the peripheral surface 20 according to the invention.
  • the locking wing 30 When traversing the contour section 64, the locking wing 30 experiences a negative acceleration up to a minimum value, from which the acceleration rises continuously beyond the zero point to a maximum value, in order to continuously decrease from there again to the value zero when the contour section 68 is reached.
  • the locking wing 30 does not experience any radial acceleration.
  • the volume flow is plotted against the current angle of the rotor 16.
  • the solid and dashed line according to the prior art are again compared with the dash-dot line according to the contour according to the invention.
  • the contour according to the invention means that the kinematic volume flow pulsation determined by the contour profile of the peripheral surface 20 is extremely low.
  • the kinematic volume flow pulsation can assume values of less than 0.3%.
  • the invention is not limited to the exemplary embodiment shown with four locking vanes 30 and six control surfaces 22, but can be used with any locking vane pump 10 in which a multi-stroke contour causes partial delivery flows to be superimposed to form a total delivery flow.
  • the blocking vane pump 10 can preferably be used in motor vehicles as a transmission or power steering pump or as a fuel pressure pump. Depending on the speed of the rotor 16, a uniform delivery behavior, that is to say delivery behavior essentially free of pulsations, can be set in a wide delivery flow range.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP97108655A 1996-05-30 1997-05-29 Pompe à palettes Withdrawn EP0810373A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19623242A DE19623242C1 (de) 1996-05-30 1996-05-30 Sperrflügelpumpe
DE19623242 1996-05-30

Publications (2)

Publication Number Publication Date
EP0810373A2 true EP0810373A2 (fr) 1997-12-03
EP0810373A3 EP0810373A3 (fr) 1999-07-07

Family

ID=7796617

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97108655A Withdrawn EP0810373A3 (fr) 1996-05-30 1997-05-29 Pompe à palettes

Country Status (4)

Country Link
US (1) US5989002A (fr)
EP (1) EP0810373A3 (fr)
JP (1) JPH1054376A (fr)
DE (1) DE19623242C1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109779868A (zh) * 2019-02-12 2019-05-21 中国民航大学 多缸星型内腔泵
GB2600666A (en) * 2021-04-13 2022-05-04 Univ Jiangsu Quick startup device for centrifugal pump

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6530357B1 (en) * 1998-11-18 2003-03-11 Viktor Prokoflevich Yaroshenko Rotary internal combustion engine
DE102004030330B4 (de) * 2004-06-23 2009-08-13 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Sperrschieberpumpe
DE102006048989A1 (de) * 2006-10-17 2008-04-24 J. Eberspächer GmbH & Co. KG Fördereinrichtung, insbesondere zum Fördern von Brennstoff zu einem Fahrzeugheizgerät
CN109812414A (zh) * 2019-04-10 2019-05-28 中国民航大学 凸轮腔式容积泵
RU2740664C2 (ru) * 2019-07-01 2021-01-19 АКЦИОНЕРНОЕ ОБЩЕСТВО "Центральный научно-исследовательский институт автоматики и гидравлики" (АО "ЦНИИАГ") Быстроходный пластинчатый насос многократного действия
DE102021132296A1 (de) 2021-12-08 2023-06-15 Nidec Gpm Gmbh Sperrflügelpumpe mit hydraulischer Sperrflügelbetätigung
DE102022128492A1 (de) * 2022-10-27 2024-05-02 Valeo Powertrain Gmbh Sperrflügelpumpe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2786421A (en) * 1953-11-24 1957-03-26 Hamilton Gordon Rotary pump or motor
FR2247124A5 (en) * 1973-10-04 1975-05-02 Rineer Hydraulics Rotary hydraulic engine with sliding vanes - has vanes of different thicknesses and loading on rotor and stator

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1093486A (en) * 1963-10-11 1967-12-06 F N R D Ltd Improvements in and relating to rotary pumps and motors
US3782867A (en) * 1972-04-03 1974-01-01 Rineer Hydraulics Fluid power converter
DE2913110A1 (de) * 1979-04-02 1980-10-23 Barmag Barmer Maschf Verdraengungsmaschine, insbesondere pumpe
DE3122648A1 (de) * 1981-06-06 1982-12-23 Jörg Dipl.-Ing. 8904 Friedberg Siemer Drehkolbenmaschine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2786421A (en) * 1953-11-24 1957-03-26 Hamilton Gordon Rotary pump or motor
FR2247124A5 (en) * 1973-10-04 1975-05-02 Rineer Hydraulics Rotary hydraulic engine with sliding vanes - has vanes of different thicknesses and loading on rotor and stator

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109779868A (zh) * 2019-02-12 2019-05-21 中国民航大学 多缸星型内腔泵
GB2600666A (en) * 2021-04-13 2022-05-04 Univ Jiangsu Quick startup device for centrifugal pump
GB2600666B (en) * 2021-04-13 2023-08-02 Univ Jiangsu Quick startup device for centrifugal pump

Also Published As

Publication number Publication date
EP0810373A3 (fr) 1999-07-07
US5989002A (en) 1999-11-23
JPH1054376A (ja) 1998-02-24
DE19623242C1 (de) 1998-01-08

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