EP0475041A1 - Machine - Google Patents

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Publication number
EP0475041A1
EP0475041A1 EP91112497A EP91112497A EP0475041A1 EP 0475041 A1 EP0475041 A1 EP 0475041A1 EP 91112497 A EP91112497 A EP 91112497A EP 91112497 A EP91112497 A EP 91112497A EP 0475041 A1 EP0475041 A1 EP 0475041A1
Authority
EP
European Patent Office
Prior art keywords
rotor
area
working machine
conveying
sealing area
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
EP91112497A
Other languages
German (de)
English (en)
Other versions
EP0475041B1 (fr
Inventor
Thomas Hiestand
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.)
KARL HIESTAND FLUIDTECHNIK
Original Assignee
KARL HIESTAND FLUIDTECHNIK
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 KARL HIESTAND FLUIDTECHNIK filed Critical KARL HIESTAND FLUIDTECHNIK
Publication of EP0475041A1 publication Critical patent/EP0475041A1/fr
Application granted granted Critical
Publication of EP0475041B1 publication Critical patent/EP0475041B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
    • 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
    • F04C2/3441—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 one line or continuous surface substantially parallel to the axis of rotation

Definitions

  • the invention relates to a working machine in the manner of a traction vane pump or a traction vane motor with a rotor rotatably arranged in a housing, which is used in a working chamber, which is provided in a conveying area and a sealing area of approximately the same length lying opposite it, as well as between these with inlet and Control areas equipped outlet openings is divided and has a curved inner wall on which in the rotor radially displaceably arranged slide abut sealingly in the conveying and sealing area, and wherein the conveying and sealing area are curved with different radii concentrically about the axis of rotation of the rotor and the radius of the delivery area is larger than the radius of the sealing area.
  • a rotary pump of this type is known from DE-A-3812794.
  • two oppositely arranged sliders are each formed by a plate and the plates are inserted into one another like a comb and slidably inserted in continuous slots machined into the rotor.
  • the plates are dimensioned in length so that the The sum of the radii of the conveying and sealing areas correspond, so that the slides in these areas lie sealingly against the inner wall of the working chamber, but with each revolution of the rotor the plates have to be moved twice in the slots by the height of the conveying chamber.
  • the slides which have a high weight, strike the wall several times in the control areas.
  • a high-speed machine is therefore of such a type because the operating noise caused by it is high and the wear caused by the impact is high suitable.
  • the object of the invention is therefore to design a working machine of the type mentioned in such a way that it is not only very versatile, in particular for conveying media and can also be used as a motor, but above all that the rotor is supported on both sides and runs quietly with low friction losses possible are.
  • the slides In the sealing area and the one adjustment area, the slides should not be additionally pressed against the inner wall of the housing by acting on the slides arranged opposite one another. Nevertheless, it should be ensured that these lie sealingly against the inner wall in the conveying and sealing area.
  • the construction effort, by means of which this can be accomplished, should be kept low, and the stability of the rotor should not be impaired.
  • this is achieved in a working machine of the aforementioned type in that in each case two slider-like slide chambers inserted into diametrically opposite slot-like receiving chambers are mutually supported via one or more linkages which are displaceably guided in the rotor in the conveying and sealing area, that the slide and / or the rotor are provided with cutouts through which the inner region of a receiving chamber is connected to one of the delivery chambers of the rotor provided next to it, and that the bushings of the linkages in the rotor are designed to be pressure-tight.
  • the rods can be formed in a simple embodiment by preferably two bolts arranged at a lateral distance from one another and symmetrically arranged in the rotor, which are sealingly guided radially displaceably in the rotor and on whose end faces the slides are supported in the conveying and sealing area.
  • the slide should be curved on their end face lying against the inner wall of the working chamber of the housing with a radius which corresponds to the radius of curvature of the conveying region of the working chamber.
  • the two control areas each under a radius which is larger than the radius of the sealing area of the working chamber and which merges into the radii of the conveying and sealing area and the inlet opening and / or the outlet opening should each be kidney-shaped Clearance must be assigned, which preferably run approximately concentrically to the control areas or approximately concentrically to the rotor and extend in whole or in part over their length.
  • the rotor should have an outer diameter that corresponds to twice the radius of the sealing area of the working chamber, while, when conveying liquid media, the outer diameter should be smaller than twice the radius of the sealing area.
  • the slides can also be made from a low-weight material. And in order to ensure a good lateral seal, these sealing washers should be arranged on both sides of the rotor on the same diameter range.
  • the slides according to the invention are each used in receiving chambers, the bottom of which is connected to one of the adjacent delivery chambers, and two oppositely arranged slides are supported by a linkage, the bushings of which are pressure-tight in the rotor are, it is possible to apply the same pressure medium pressure to the inner end faces of the slides in the conveying area and in the adjustment area assigned to the pressure side as their outer end faces, so that almost no forces have to be supported on the housing in the sealing area and in the other adjustment area.
  • the slides are thus hydrostatically balanced and do not influence the respectively opposite slides, but they are still in contact with the inner wall of the working chamber in a sealing manner, controlled by the sealing area, via the linkage. Accordingly, even with rotors rotating at high speeds, it is ensured that the friction losses and the wear on the slides and the housing caused by them are low and that no high operating noises occur, and therefore a long service life of the proposed working machine is guaranteed.
  • the bushings can rather be designed as bores.
  • the rotor can also be supported on both sides, so that the bushings of the linkage and the receiving chambers can be sealed in a pressure-tight manner without difficulty. This also has a favorable effect on the operating behavior and the service life of the machine. And since the slider and the linkage can be designed with low mass and can be slid easily in the receiving chambers or bushings, trouble-free operation is ensured despite the low construction costs, even at high speeds of the rotor.
  • the work machine shown in FIGS. 1 and 2 and designated 1 serves for conveying liquid or gaseous media and essentially consists of a housing 2, into which a working chamber 3 with a curved inner wall 4 is incorporated, as well as a rotor inserted therein 11, which can be driven by a motor (not shown) by means of a shaft 12 led out of the housing 2.
  • a sealing washer 5 and 6 and a flange 7 and 8 are arranged laterally next to the housing 2 and are clamped together by screws 9.
  • the rotor 11 is rotatably mounted in the flanges 7 and 8, and the passage of the shaft 12 through the flange 7 is sealed by means of a seal 10.
  • the linkages 21, 22 and 23 are each formed by two bolts 24, 24 ', 25, 25', 26, 26 ', which are arranged at a lateral distance from one another and which bores 27, 27', 28, 28 are machined into the rotor 11 'and 29, 29' are used sealingly.
  • the pump 1 has an inlet opening 31 and an outlet opening 33, to which recesses 32 and 34, respectively, which are kidney-shaped, are assigned.
  • the working chamber 3 of the housing 2 is, as shown in Figure 2, divided into a conveying area marked with F and a diametrically opposite sealing area D, and between these a control area St1 or St2 is provided.
  • the conveying area F as well as the sealing area D are concentrically curved to the axis of rotation A of the rotor 11, namely with the different radii R1 and R2.
  • the radius R 1 is larger than the radius R 2 and the difference between these forms the height of the feed cells between two of the slides 18, 19, 20, 18 ', 19' and 20 '.
  • cutouts 35, 35 ', 36, 36' and 37, 37 ' are incorporated into the side surfaces of the slides 18, 18', 19, 19 'and 20, 20', through which the lower region 15 '', 16 '' and 17 '' of the receiving chambers 15, 15 ', 16, 16' and 17, 17 'with one of the adjacent delivery chambers of the rotor 11, in the exemplary embodiment shown with that of the respective receiving chamber 15, 15', 16, 16 ' and 17, 17 'subsequent delivery chamber is connected.
  • the pressure medium pressure prevailing in the delivery chambers is thus introduced into the lower region 15 ′′, 16 ′′ and 17 ′′ of the receiving chambers 15, 15 ′, 16, 16 ′ and 17, 17 ′ and therefore acts because the bushings 24 pass through , 24 ', 25, 25' and 26, 26 'are made pressure-tight in the rotor 11, also on the inner end faces of the slide 18, 18 '19, 19' and 20, 20 ', so that they are hydrostatically balanced and no force acts on the opposite slide.
  • the linkages 21, 22 and 23 or the bolts 25, 25 ', 26, 26' and 27, 27 'forming them and the respectively associated slides 18, 18', 19, 19 'and 20, 20' are dimensioned in this way that their length and height correspond to the sum of the radii R1 and R2 of the conveying and sealing area F and D. This ensures that, despite the hydraulic compensation of the slides 18, 18 ', 19, 19', 20, 20 'in the conveying area F, they nevertheless lie sealingly on the inner wall 4 of the working chamber 3. And since the end faces 30 of the slide 18, 18 ', 19, 19', 20, 20 'are curved with a radius which corresponds to the radius of curvature R1 of the conveying area F, a reliable flat seal is given.
  • the pressure medium is sucked in through the driven rotor 11 in the control region St 1 via the inlet opening 31 and the kidney-shaped recess 32 and is conveyed into the conveying region F curved about the axis of rotation A of the rotor 11.
  • this area is sealed off from the outlet opening 33 and the enclosed pressure medium is pressed into the outlet line 33 by the slide 20'; pressure is thus built up as a function of the back pressure.
  • the subsequent slide 19' has reached the conveying area F and the enclosed pressure medium is now further conveyed by this.
  • the slider 18, 18 ', 19, 19', 20, 20 ' are thus only guided when passing through the conveying and sealing area F and D through the linkages 21, 22, 23, in the larger dimensioned control area St2 assigned to the pressure side they are also hydrostatically balanced and can be easily adjusted using the adjustment curve of the St2 control area. Striking noises do not occur, especially since the slides 18, 18 ', 19, 19', 20, 20 'can be designed with low mass, even with a rotor 11 rotating at high speeds.
  • the work machine shown in FIGS. 4 to 8 and designated 41 is constructed in the same way as the work machine 1 according to FIGS. 1 to 3.
  • a housing 42 there is in turn a rotor in a working chamber 43 provided with a curved inner wall 44 51 used, which can be driven by means of a shaft 52 and whose working chamber 43 is sealed by lateral sealing disks 45 and 46.
  • the rotor 51 is supported on both sides by bearings 53 and 54 in flanges 47 and 48, which are clamped together by screws 49, and the passage of the shaft 42 is sealed in the flange 47 by a seal 50.
  • the working machine 41 has four sliders 58, 58 'and 59, 59' which are arranged in one plane and are arranged opposite one another in pairs and are inserted radially displaceably in slot-like receiving chambers 55, 55 'and 56, 56'.
  • a linkage 61 or 61 ' which is common to the slides 58, 58' and 59, 59 ', supports each other in the conveying and sealing area.
  • the rods 61 and 61 'consist as can be seen in particular from FIGS. 5 and 8, of discs 62 or 62' with a cylindrical or square outer lateral surface and inserted in a central recess 60 or 60 'of the rotor 51 on this adjoining bolts 63, 63 'and 64, 64', which are guided so as to be displaceable in a pressure-tight manner in bores 65, 65 'and 66, 66' machined into the rotor 51.
  • the recesses 60 and 60 ' are each designed as bores, the diameter of which is at least larger than the diameter of the cylindrical disk 62 or the diagonal of the square disk 62 by at least the adjustment path of the sliders 58, 58' and 59, 59 ''.
  • the disk 62 or 62 ' can perform an oscillating movement when the rotor 51 rotates, nevertheless, the coupling of two opposing slides 58, 58 'and 59, 59' is provided in the conveying and sealing area, the line of action of a pair of slides running through the axis of rotation of the rotor 51.
  • the slides 58, 58 'and 59, 59' are hydraulically balanced in the conveying area and in a pressure-side adjustment area of the working machine 41.
  • recesses 67, 67 ' are incorporated into the slides 58, 58' and 59, 59 ', which are connected to one of the delivery chambers adjacent to the respective receiving chamber 55, 55' and 56, 56 '.
  • a bore 69 can also be machined into the rotor 51, as shown in FIG. 8, through which the base of a receiving chamber is connected to the subsequent delivery chamber.
  • the work machine 41 according to FIG. 5 is also equipped with an inlet opening 71 with an associated kidney-shaped recess 72 and an outlet opening 73 with an associated kidney-shaped recess 74.
  • the slides 58, 58 ', 59, 59', as shown in FIG has cutouts 68 in order to reduce their weight.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)
EP91112497A 1990-08-16 1991-07-25 Machine Expired - Lifetime EP0475041B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4025897A DE4025897A1 (de) 1990-08-16 1990-08-16 Arbeitsmaschine
DE4025897 1990-08-16

Publications (2)

Publication Number Publication Date
EP0475041A1 true EP0475041A1 (fr) 1992-03-18
EP0475041B1 EP0475041B1 (fr) 1995-11-29

Family

ID=6412324

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91112497A Expired - Lifetime EP0475041B1 (fr) 1990-08-16 1991-07-25 Machine

Country Status (2)

Country Link
EP (1) EP0475041B1 (fr)
DE (2) DE4025897A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107387402A (zh) * 2017-08-24 2017-11-24 金湖县常盛动力机械配件有限公司 设有安全阀的滑片式输油泵

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4326627B4 (de) * 1993-08-07 2004-10-07 Zf Friedrichshafen Ag Flügelzellenpumpe

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2124539A (en) * 1937-02-24 1938-07-26 James B Brelsford Botary pump blade
US2495771A (en) * 1945-10-15 1950-01-31 Richer Ella Diametrically cooperating vane pump
GB703761A (en) * 1950-12-18 1954-02-10 Louis Widdows Improvements in or relating to slidable-vane rotary pumps
US3301194A (en) * 1965-04-29 1967-01-31 Dover Corp Vane-type rotary pump
DE1628275A1 (de) * 1965-04-28 1970-08-20 Hydrovane Compressor Rotierende Pumpe
US3858559A (en) * 1970-12-04 1975-01-07 Jr Albert Raymond Thomas Coupled vane rotary fluid device
DE3150569A1 (de) * 1981-12-21 1983-06-30 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Fluegelzellenpumpe
DE3324994A1 (de) * 1982-08-16 1984-02-16 Robert C. 8000 München Groll Drehkolben-maschine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2124539A (en) * 1937-02-24 1938-07-26 James B Brelsford Botary pump blade
US2495771A (en) * 1945-10-15 1950-01-31 Richer Ella Diametrically cooperating vane pump
GB703761A (en) * 1950-12-18 1954-02-10 Louis Widdows Improvements in or relating to slidable-vane rotary pumps
DE1628275A1 (de) * 1965-04-28 1970-08-20 Hydrovane Compressor Rotierende Pumpe
US3301194A (en) * 1965-04-29 1967-01-31 Dover Corp Vane-type rotary pump
US3858559A (en) * 1970-12-04 1975-01-07 Jr Albert Raymond Thomas Coupled vane rotary fluid device
DE3150569A1 (de) * 1981-12-21 1983-06-30 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Fluegelzellenpumpe
DE3324994A1 (de) * 1982-08-16 1984-02-16 Robert C. 8000 München Groll Drehkolben-maschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107387402A (zh) * 2017-08-24 2017-11-24 金湖县常盛动力机械配件有限公司 设有安全阀的滑片式输油泵
CN107387402B (zh) * 2017-08-24 2020-01-31 金湖县常盛动力机械配件有限公司 设有安全阀的滑片式输油泵

Also Published As

Publication number Publication date
DE59106979D1 (de) 1996-01-11
EP0475041B1 (fr) 1995-11-29
DE4025897A1 (de) 1992-02-20

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