EP0620898A1 - Pompe a cellules semi-rotative compacte et reglable. - Google Patents

Pompe a cellules semi-rotative compacte et reglable.

Info

Publication number
EP0620898A1
EP0620898A1 EP93901592A EP93901592A EP0620898A1 EP 0620898 A1 EP0620898 A1 EP 0620898A1 EP 93901592 A EP93901592 A EP 93901592A EP 93901592 A EP93901592 A EP 93901592A EP 0620898 A1 EP0620898 A1 EP 0620898A1
Authority
EP
European Patent Office
Prior art keywords
adjusting ring
recess
vane pump
pressure
housing
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
EP93901592A
Other languages
German (de)
English (en)
Other versions
EP0620898B1 (fr
Inventor
Bodo Stich
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.)
Daimler Benz AG
Original Assignee
Glyco Metall Werke Glyco BV 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 Glyco Metall Werke Glyco BV and Co KG filed Critical Glyco Metall Werke Glyco BV and Co KG
Publication of EP0620898A1 publication Critical patent/EP0620898A1/fr
Application granted granted Critical
Publication of EP0620898B1 publication Critical patent/EP0620898B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • 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

Definitions

  • the present invention relates to a vane pump with a housing, a sealing ring which is tightly guided in the housing and which can be moved transversely to its axial direction relative to a rotor mounted in the housing and encompassed by the adjusting ring, a suction area of the pump being increased by a volume increasing in the direction of rotation of the rotor between two adjacent vanes, the rotor and the adjusting ring, and a pressure range is defined by a decreasing volume of the vane in the direction of rotation, and at least one actuator is provided which adjusts the position of the adjusting ring as a function of the respective pump parameters
  • the pump parameters that influence the position of the adjusting ring can in particular be the delivery volume of the pump, but above all the pressure occurring on the pressure side.
  • a vane pump is also known from German Offenlegungsschrift No. 40 11 671, which essentially has the features specified above, but the arrangement and position of any actuators is not described. Apart from the special arrangement of actuators and the corresponding design of the adjusting ring, however, the vane pump described in DE 40 11 671 A1 is identical to the vane pump described in the present application, so that with regard to the other design and the advantageous properties associated with that application Reference can be made that goes back to the same inventor
  • the actuators require a considerable amount of space, as shown in particular by the closest prior art according to US Pat. No. 3,218,292 already mentioned.
  • oil pumps are regularly used as auxiliary units for other machines, in particular as lubricant pumps in motors and other machines, the additional space requirement is undesirable and often also has considerable disadvantages. It also increases the weight of the pump, which is also undesirable.
  • the control lines for the actuator or the actuators require additional bores and bushings in the housing so that the pump parameters mentioned can act on the actuators, which in turn change the collar position and thus regulate the pump parameters to a desired value.
  • the present invention has for its object to provide a vane pump with the features mentioned, which has a space-saving and or simple and cost-saving structure.
  • At least one cutout which is open to the outside of the adjusting ring and in the adjusting direction, is provided on the adjusting ring in the vicinity of its pressure region for receiving an actuator.
  • the actuator can be largely integrated into the Steilri ⁇ g itself or the recess provided thereon and requires little or no additional space in the housing outside the collar.
  • a double-walled design of the adjusting ring on the pressure side of the adjusting ring leads to the formation of an additional pressure chamber between the two walls forming the double wall, which lies radially outside the area covered by the rotor vanes (pressure space), radial openings in the wall facing the vane cells connecting the connection the pressure chamber and the pressure chamber.
  • the pressure chamber is thus emptied more easily and quickly, so that even at very high speeds of the rotor no excessively high pressure builds up and above all hard pressure surges are avoided.
  • the adjusting ring is not or only a little larger than without the recess for the actuator due to the additional recess to be provided according to the invention.
  • the inner wall of one Such recess can namely easily project into the pressure chamber, since the pressure chamber does not have to have a uniform cross section over the entire axial length of the adjusting ring in order to fulfill its function.
  • the collar wall can be double-walled to form a recess in the pressure area, the recess being formed between the inner and the outer wall.
  • the outer adjusting ring wall is in turn double-walled again at least in a partial area in order to provide the corresponding recess.
  • two cavities or recesses are provided on opposite sides of the adjusting ring, these cavities being open at least in the direction of adjustment.
  • the direction of adjustment is understood to mean the directions from which the actuator or the steep elements exert a force on the adjusting ring.
  • the two cavities are separated by an intermediate wall.
  • two oppositely acting actuators are provided on such a collar, which react in different ways to the displacement of the collar position and the pump parameters mentioned above. With a suitable selection, a desired state of equilibrium is then established.
  • cutouts or cavities mentioned preferably have a cylindrical cross section, since actuators in their simplest embodiment also often have a cylindrical cross section.
  • An embodiment of the invention is particularly preferred in which the outer wall of the adjusting ring in the pressure region, i.e. either the outer wall of the pressure chamber, or, if present, the outer wall of a pressure chamber additionally present radially outside the pressure chamber is itself double-walled at least in a partial area, the desired recess for receiving the actuator being formed between the two parts forming the double wall.
  • an embodiment of the invention is preferred in which a steep piston can be provided with pressure in one of the recesses.
  • the steep piston in a Correspondingly shaped recess is guided tightly and if, in addition, an opening is provided in the wall inwardly delimiting the recess, which creates a connection to the pressure chamber or to the pressure chamber of the pump. This opening is expediently provided at the inner end of the recess.
  • the counterforce required to have the adjusting ring in an equilibrium position is expediently applied by a compression spring which is received in a recess opposite the first recess and which is supported with its end protruding from the recess on the opposite housing wall.
  • a compression spring which is received in a recess opposite the first recess and which is supported with its end protruding from the recess on the opposite housing wall.
  • An embodiment of the invention is particularly preferred in which the inner wall of the housing is lined with a sheet-metal insert made of spring steel, which offers an essentially wear-free or at least very low-wear contact surface for the ends of the actuating elements which engage with it
  • an embodiment of the invention is preferred in which the adjusting ring is pivotably suspended on its side facing away from the actuators. You then get by with a single pair of eccentrically mounted actuators, which, however, during the pivoting of the adjusting ring necessarily also perform movements perpendicular to the actuating path, so that then in particular the aforementioned configurations with wear-free or low-wear sliding surfaces at the ends of the actuators and their areas of attack from Are advantage.
  • FIG. 1 and 2 show two mutually perpendicular sectional views of a vane pump according to the prior art
  • FIG. 1 denotes a housing, in the interior 14 of which a rotor 1 is arranged with a fixed axis, which rotates on a shaft 1 'and has guide slots 2' for vanes 2 running in the radial and axial direction.
  • the blades are resiliently biased from the center of the rotor 1 and are thus pressed outward in the radial direction.
  • the rotor 1 is surrounded by an essentially cylindrical interior of an adjusting ring 4.
  • the hatched surfaces of the adjusting ring 4 in FIG. 1 lie against the flat surface 16 of the housing 3, as can be seen in FIG.
  • the adjusting ring is essentially mirror-symmetrical, so that, on the opposite side, identical surfaces of the adjusting ring 4 rest on the housing in mirror image.
  • the adjusting ring also has openings 9 and 10 in the radial direction for the inflow or outflow of the conveyed medium.
  • the pumped medium flows through the housing bore 41 into the space 14 surrounding the adjusting ring 4, but in some cases also directly into the area 17 of the suction space 7 covered by the vane cells.
  • the vanes 2 in the vane cells 5 defined between adjacent vanes 2 take delivery medium from the suction chamber 7 and release it in the pressure chamber 8, since in the pressure area the volume of the vane cells 5 between the rotor and the lower one Wall 6 of the collar 4 decreases.
  • the pumped medium exits through openings 10 in the radial direction and into the pressure chamber 11 and from there through the axial opening 12 into the pressure-side bore 40 of the housing 3.
  • the mouth 13 of the bore 40 also in the area of the pressure chamber 8 lie and the wall 6 could rest against the walls 16 of the housing 3 in the pressure region of the adjusting ring, so that the vane cells could be emptied in the axial direction into a correspondingly designed mouth 13 (see FIG.
  • FIG. 1 the adjustment possibility of the adjusting ring 4 is indicated by the double arrow 18. If the adjusting ring 18 in FIG. 1 is shifted more to the left, when the suction chamber 7 or the pressure chamber 8 is swept over, the flight cell volume changes less than in the state shown in FIG. Accordingly, less pumped medium is pumped, so that, assuming a constant demand on the pressure side, the pressure in the pressure area decreases In Figures 1 and 2, however, there are corresponding actuators which move the adjusting ring relative to the rotor 1 and the housing 3 and so on Adjust delivery volume and pressure, not shown. Pistons and springs which act against one another generally serve as actuators, a corresponding piston generally being guided in the housing and being acted upon from the housing side by the pump medium which is branched off from the pressure side, for example from the bore 40.
  • pistons can move the ring in parallel, but the ring can also be suspended pivotably about an axis, as is shown in connection with the configuration of the pump according to the invention in FIGS. 3 and 4.
  • FIGS. 3 to 7 the adjusting ring is pivotably mounted about a shaft 30 received in the upper part of the housing.
  • the actuators 22, 23 are arranged just so that, conversely, as in Figure 1, the delivery volume is reduced when the collar from the left pans to the right, and is enlarged when it is panned from right to left.
  • the mode of operation of the vane pump shown in FIGS. 1 and 2 is identical to the air line pumps shown in FIGS. 3 to 6.
  • the special features of the new airline line pumps lie in the cutouts 20, 21 which are provided in the lower area, ie in the pressure area of the adjusting ring.
  • the adjusting ring 4 is double-walled in the pressure area to form an additional pressure chamber 11.
  • the pressure chamber 11 lies between the inner wall 6 and the outer wall 6 'of the adjusting ring.
  • the outer wall 6 'in turn is now double-walled in its central region. Concretely, one recognizes two cylindrical cavities 20, 21 which are open on opposite sides and separated by an intermediate wall 28, of which the cavity or the recess 20 has a piston 22 guided tightly in this recess receives, while the cavity 21 receives a helical compression spring 23.
  • the two cavities 20, 21 are open in opposite directions, the course of the cavities 20, 21 thus defined from the closed to the open end or vice versa Defined direction of adjustment, which must always run transversely to the axis of the rotor 1, which is no longer shown in FIGS. 3 to 6, and in any case has a radial component with respect to the rotor 1, since the vane volume is defined by the radial distance between the rotor surface and the inner surface of the adjusting ring 4 becomes.
  • the pumped medium flows from the pressure chamber 8 first in the radial direction into the pressure chamber 11 and from there through the axially directed opening 12 of the pressure chamber 11 into the mouth 13 of the housing bore 40.
  • the bulging of the inner wall of the cavities 20, 21 into this pressure chamber 11 only insignificantly hinders the flow of the conveying medium, since the free cross section between the wall 6 and the inner wall of the cutouts 20, 21 can easily be kept larger than the cross section of the bore 40 in the housing 3.
  • an opening 26 can also be seen in the wall of the cutout 20 towards the pressure chamber 11. Through this opening 26, the pumped medium also enters the cavity 20 and thus acts on the piston
  • FIGS. 3 and 5 essentially differ only in the sheet 25 made of spring steel inserted into the housing 3 in FIG. 5 and the cap 27 of the compression spring 23.
  • FIG. 5 shows a state of the pump, in which relatively low pressure, a relatively large amount of pumped medium is pumped; the adjusting ring has an almost maximum deflection to the left and thus a maximum eccentricity with respect to the rotor 1 (not shown), the center of which, however, can be thought, for example, at the intersection of the dash-dotted lines 32, 33.
  • the housing design is much simpler in the embodiments according to the invention than in the prior art, in which piston guides and in particular also bores or lines which feed the pressurized medium to the piston were required.
  • the compression spring also need not be stored in the housing. Instead, the corresponding components are all arranged on the adjusting ring, which anyway and especially in the example of the double-walled design with a pressure chamber 11 requires a certain volume, which is not significantly increased by the additional recesses for the actuators.
  • the housing 3 can thus be made much simpler and more compact overall.
  • the piston expediently has a preferably spherically rounded end face 24 and the compression spring 23 is provided with a cap 27 which is likewise rounded on its outside.
  • the inner surface of the housing 3 in the area where the piston 22 or its end face 24 and the cap 27 of the compression spring 23 engage with the housing inner wall is designed with a sheet 25 made of spring steel.
  • the materials of the cap 27 and the end face 24 of the Pistons 22 are preferably selected so that they slide easily on the spring steel of the plate 25.
  • the spring steel sheet 25 is preferably inserted in one piece in the lower region of the housing 3 and could optionally be clamped with the ends under corresponding projections or a shoulder on the inner wall of the housing 3. This insertion of the spring steel sheet 25 in one piece facilitates the assembly process and lowers the production costs.
  • Figure 6 shows in an axial section through the housing and the collar only one variant in the design of the openings 10 between the pressure chamber and the pressure chamber, which are shown in the example of Figure 6 as two parallel, circumferential slots, with the axial ends of the collar 4 still Sections 6a of the wall 6 of the collar have remained.
  • FIG. 4 only in the central region, both on the pressure side and on the suction side, has a wall section 6 remained, which serves as a guide for the wings 2.
  • FIGS. 4 and 6 Compared to the prior art shown in FIG. 2, the embodiments of FIGS. 4 and 6 only differ in that the suction-side openings 31 in the Housing wall are provided, which lies opposite the housing wall, in which the pressure-side openings 13 are provided.
  • both openings lie on one side of the housing, in particular if, as shown in FIGS. 4 and 6, the housing consists of a cavity which is essentially open on one side and which after the rotor has been installed and collar is only provided with a wall or a lid that closes the open side of the housing
  • the invention also includes embodiments in which the adjusting ring 4 is completely closed along its circumference and only in the axial direction it is possible for the conveying medium to flow into or out of the vane cells formed between the rotor and the adjusting ring.
  • the suction-side opening 31 and the pressure-side opening 13 have to be arranged in the area of the vane cells 5.
  • the recesses 20 and 21 can then be formed by a double-walled design of the lower wall 6 of the adjusting ring 4. Such an embodiment is shown in FIGS. 7 and 8.
  • the cylindrical cavity 20 is connected via an opening 26 to the pressure chamber inside the collar 4 'and a piston 22 is guided tightly in the cavity 20 so that it is pressed out of the cylindrical cavity 20 when the pressure rises, on the Supports the inner wall of the housing 3 and, due to the reaction force, presses the adjusting ring 4 'in the direction of lower eccentricity.
  • a spring 23 is in turn arranged, which applies a corresponding counterforce, so that an equilibrium state is established between the spring force and the pump pressure.
  • either the lower cavities 20, 21 can be molded or cast directly, but the adjusting ring can also be made separately first, whereupon a tube which is closed in the middle is simply welded to the underside of the adjusting ring 4 'after the opening 26 was made, for example, in the form of a bore, in the cross-sectional view according to FIG. 7 it is also not necessary for the adjusting ring 4 'to be guided with its maximum (horizontal) diameter into the region of the cavities 20, 21; The outer surface of the adjusting ring 4 'runs parallel to its inner surface in a circular shape to tightly over a tubular extension which forms the cavities 20, 21 mentioned.
  • the vane cell pump according to the invention is relatively inexpensive and, above all, can be manufactured with low weight and small dimensions.
  • the somewhat more complex design of the adjusting ring is easily compensated for by corresponding savings in the design of the housing, so that overall the advantageous properties of the new airline pumps outweigh them.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • External Artificial Organs (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Une pompe à cellules semi-rotative comprend un boîtier (3), une bague de réglage (4) guidée étanche dans le boîtier (3) et mobile transversalement au sens axial d'un rotor (1) qui est monté dans le boîtier (3) et entouré par la bague de réglage (4). La zone d'aspiration (7, 14) de la pompe est définie par le volume croissant dans le sens de rotation du rotor (1) d'une cellule rotative (5) formée entre deux pales adjacentes (2), le rotor (1) et la bague de réglage, et la zone de refoulement (8, 11) est définie par le volume décroissant dans le sens de rotation de la cellule rotative (5). Au moins un organe de réglage (22, 23) ajuste la position de la bague de réglage (4) en fonction des paramètres respectifs de la pompe. Afin d'obtenir une pompe à cellules semi-rotative ayant une construction compacte et/ou simple et économique, au moins un évidement (20, 21) de réception d'un organe de réglage (22, 23) ouvert vers le côté extérieur de la bague de réglage (4) est ménagé dans la bague de réglage (4) à proximité de la zone de refoulement (8, 11).
EP93901592A 1992-01-09 1992-12-15 Pompe a cellules semi-rotative compacte et reglable Expired - Lifetime EP0620898B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4200305 1992-01-09
DE4200305A DE4200305C2 (de) 1992-01-09 1992-01-09 Regelbare Flügelzellenpumpe in kompakter Bauweise
PCT/DE1992/001059 WO1993014318A1 (fr) 1992-01-09 1992-12-15 Pompe a cellules semi-rotative compacte et reglable

Publications (2)

Publication Number Publication Date
EP0620898A1 true EP0620898A1 (fr) 1994-10-26
EP0620898B1 EP0620898B1 (fr) 1995-08-02

Family

ID=6449225

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93901592A Expired - Lifetime EP0620898B1 (fr) 1992-01-09 1992-12-15 Pompe a cellules semi-rotative compacte et reglable

Country Status (10)

Country Link
US (1) US5484271A (fr)
EP (1) EP0620898B1 (fr)
JP (1) JPH07502796A (fr)
KR (1) KR100209862B1 (fr)
AT (1) ATE125905T1 (fr)
BR (1) BR9207029A (fr)
DE (2) DE4200305C2 (fr)
ES (1) ES2078816T3 (fr)
MX (1) MX9300092A (fr)
WO (1) WO1993014318A1 (fr)

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WO2010135548A1 (fr) * 2009-05-20 2010-11-25 Tuthill Corporation Pompes à déplacement variable et systèmes de commande de pompes à palettes
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Also Published As

Publication number Publication date
MX9300092A (es) 1993-07-01
DE59203138D1 (de) 1995-09-07
DE4200305C2 (de) 1995-06-08
BR9207029A (pt) 1995-12-05
WO1993014318A1 (fr) 1993-07-22
JPH07502796A (ja) 1995-03-23
EP0620898B1 (fr) 1995-08-02
ES2078816T3 (es) 1995-12-16
KR100209862B1 (ko) 1999-07-15
KR940703971A (ko) 1994-12-12
DE4200305A1 (de) 1993-07-15
US5484271A (en) 1996-01-16
ATE125905T1 (de) 1995-08-15

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