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
  • F01C21/10—Outer members for co-operation with rotary pistons; Casings
  • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
  • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
• • 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
  • F04C2230/00—Manufacture
  • F04C2230/60—Assembly methods
  • F04C2230/603—Centering; Aligning

Definitions

• the invention relates to a pump, in particular a vane pump or a roller cell pump, the vane or roller cell pump having a two-stroke contour ring and a rotor in which blades or rollers are mounted in a radially displaceable manner, with at least one, optionally two side plates which laterally seal the rotation group a housing and a housing cover, the rotor being driven by a shaft and the shaft being mounted in the housing and possibly in the cover.
• the invention particularly relates to a double-flow vane pump, this double-flow double-stroke vane pump being able to switch off one pump half by dividing it into two pump halves at higher speeds, and the pumped quantity of this pump half can be returned to the suction line.
• This switch-off is that the rotor and the stroke ring of the pump are no longer pressure-balanced in the radial direction, since almost no pressure is built up in the switched-off pump half.
• the lifting rings mounted on pins increase radially more radially from their original position due to the bending of the pins.
• the rotor mounted on the shaft is displaced from its original position in the opposite direction due to the shaft deflection.
• a pump in particular a vane pump or roller cell pump, the vane pump or roller cell pump having a two-stroke contour ring, a rotor in which blades or rollers are mounted in a radially displaceable manner, one or, if necessary, two side plates Housing and a housing cover, the rotor being driven by a shaft, the shaft being mounted in the housing and possibly in the cover, the lifting ring and at least one side plate being positioned relative to one another by at least one first pin and in that the first pin is the at least one Side plate does not penetrate.
• the at least one side plate and the housing or the cover are positioned relative to one another by a second pin, the second pin not penetrating the at least one side plate and having no contact with the contour ring.
• a second side plate is positioned with respect to one another by a third pin with the housing or the cover, the third pin not penetrating the second side plate and likewise not having any contact with the contour ring.
• the first and second, and possibly the third pin in the pump are arranged in the same through opening, but in different components.
• a pump is also preferred in which the first and second, and possibly the third pin each protrude into the middle of the respective side plate thickness. Also preferred is a pump in which the first and the second, and possibly the third pin are arranged in a so-called "pin hole”, that is to say that they represent a so-called “pin connection” in a round hole.
• Another pump according to the invention is characterized in that a fourth and a fifth pin are arranged in a so-called “elongated hole”, elongated holes being formed in the plates and round holes in the cover or, if appropriate, in the housing and in the lifting ring, and in that the fourth pin in principle like the first pin and the fifth pin are basically designed and arranged like the second pin.
• a pump is also preferred in which the bores are smooth throughout (ie do not represent stepped bores), so that the pins are only subjected to shear and not to bending.
• a pump is also preferred in which the two pins in the cover (the second and fifth) and the third pin in the housing are of the same length and have the same diameter. Furthermore, a pump is preferred in which the two pins (the first and the fourth) in the stroke ring are of the same length and have the same diameter. Another pump according to the invention is characterized in that the second, third and fifth pin have a different diameter than the first and fourth pin and therefore the holes in the side plates are made stepped. Furthermore, a pump is preferred in which the housing is cup-shaped. A pump is also preferred in which the rotating group is fixed to the cover. A pump according to the invention is characterized in that the shaft is additionally mounted in the cover.
• Figure 1 shows the representation of a vane rotation group under transverse force.
• FIG. 2 shows a cross section through a vane pump with pins according to the invention.
• FIG. 3 shows the behavior of the pins according to the invention under transverse force.
• FIG. 4 shows a gerotor pump using the pins according to the invention.
• FIG. 1 shows a rotary group of a vane pump with only one area under pressure under transverse force.
• a rotor 3 which contains radially movable blades 5 in slots and is rotatably driven by a shaft 7. Vane cells are formed between the vanes 5, the contour ring 1 and the rotor 3, which increase or decrease accordingly when rotated.
• the vane 9 z. B. is a pressure-promoting cell which, viewed in the direction of rotation 17, is reduced by the "fall" 18 and thus conveys fluid under pressure.
• the pressure range of the vane pump is additionally represented in this position by the pressure range 9.1 and 9.2.
• the lower pressure kidney 11 of the vane pump should in this case be switched to unpressurized circulation, so that no pressure builds up here, furthermore the two suction areas 13 and 15 of the vane pump are shown that on the one hand a reaction force 19 on the contour ring 1 wants to shift the contour ring 1 upwards, while on the other hand a pressure force component 21 on the rotor 3 wants to shift it down and thus can lead to an impermissibly large deflection of the shaft 7 if it does not have a correspondingly high strength.
• the contour ring 1 and side plates, not shown here contain through openings 23 and 25, by means of which they are connected to one another by means of pins and to a housing, not shown here, in which the shaft 7 is also mounted, so that the power cycle closes here.
• a vane pump is shown in cross section in FIG.
• the shaft 7 is mounted in a housing 27 by means of a bearing 29 and sealed by a seal 37.
• the housing is closed by a housing cover 31, in which the shaft 7 is mounted in a second bearing 33.
• the contour ring 1, the rotor 3 with blades not shown here and the side plates 39 and 41 form the rotation group.
• the rotor 3 is axially fixed on the shaft by a retaining ring 35.
• the cam ring 1 is connected to the side plates 39 and 41 above via a first pin 43.1 and below via a fourth pin 43.4.
• the side plate 39 is also connected to the housing 27 by a short third pin 43.3.
• the side plate 41 is connected to the housing cover 31 via a short second pin 43.2 and a short fifth pin 43.5.
• the displacement between the contour ring 1 and the rotor 3 is decidedly less and is practically realized only through the play predetermined by the pin bores and the pins.
• the smaller displacement between the lifting ring 1 and the rotor 3 leads to a decidedly lower noise development of the pump in the single-flow delivery mode.
• FIGS. 3.1 and 3.2 show the displacement of the three-part precision pen system based on the games, with FIG. 3.2 corresponding to a variant with offset pens. represents claim 11. It can be seen that the contour ring 1 is shifted upwards relative to the middle pin 43.1 and is in contact with the pin 43.1 from below. The game of the exact hole connection is represented by the upper gap 45.
• the pin 43.1 in turn rests in the side plates 39 and 41 on the upper side, so that a lower gap 46 and 47 is formed here in each case.
• the plate 39 in turn rests on the underside of the pin 43.3, which in turn comes to rest on the upper side in the housing 27 and thus forms a lower gap 48.
• FIG. 1 An internal gear pump of the orbit pump type is shown as an example in FIG.
• a toothed wheel 51 is arranged in an internally toothed toothed ring 50, which at the same time represents the outer contour of the pump part.
• An eccentric 52 is arranged within the gear 51 so as to be rotatable, which can slide with respect to the gear 51 with sliding bearings and, during this rotary movement, pushes the gear 51 one after the other into the tooth gaps of the external gear 50.
• the eccentric 52 is arranged on an eccentric shaft 53.
• the pump chambers which are currently performing compression work and thereby building up pressure, are marked with shaded areas 54. Similar to the vane pump described above, these pressure fields provide a reaction force that acts on the one hand on the outer toothed ring 50 and on the other hand on the gear 51 and wants to remove both parts from one another in the pressure area.
• the external toothed ring 50 can be mounted in a pump housing in a relatively stable and immovable manner. The impact of these pressure fields via the gear wheel 51 and the eccentric 52 on the shaft 53, which drives the eccentric and is stressed by the compressive forces on bending, is more critical.
• This type of pump arrangement can also be used appropriate design according to the previously described, multi-part bolt principle convert the load state of the bend into a load state of the shear, the drive of the inner wheel then being transmitted via corresponding couplings.
• FIG. 4.2 the same pump arrangement is shown with a different eccentric position, which means that the pressure field is continuously shifted. So you have the load case of a circumferential pressure field, while in the vane pump the pressure fields were dependent on the design of the cam ring and its position.
• the stroke ring displacement can be kept very low and the noise when the pump half is switched off and the other pump half is greatly improved under operating pressure.
• the holes in the cam ring 1 must not be offset, but must be smooth throughout It just arises an additional displacement of the cam ring 1 and the plates 39, 41 due to the play of the holes and the pins.
• the addition of the individual games is significantly less than the displacement of the cam ring when a "pin hole” bends. Due to the bearing of the "pin hole” in the cover 31 and housing 27, the "pin hole” is claimed in two sections.
• a pin 43.3 is fixed in the pump housing 27 in a bore (round hole) and positions the side plate 39 in the rotation group space of the pump housing. Half of this precision pin 43.3 extends into the round hole in the side plate 39.
• a further precision pin 43.1 is also continuously in the lifting ring 1 in a round hole and half projects into the side plate 39 and half into the side plate 41 in a round hole connection.
• Another pin 43.2 extends halfway into the side plate 41 and is fixed in the cover 31 in a round hole.
• the two so-called “slot pins" (43.4, 43.5) are arranged in the pump as follows: A “slot pin” 43.5 is fixed in the cover 31 in a round hole and extends halfway into the slot in the side plate 41.
• Another “slot pin” 43.4 is continuously in the lifting ring 1 in a round hole and protrudes half into the elongated hole in the side plate 41 and half into the elongated hole in the side plate 39.
• the elongated holes in the pressure and side plates compensate for the different spacing of the round holes in the cover 31 and in the lifting ring 1 due to the manufacturing tolerances, and the cover 31 and the lifting ring 1 can be installed without jamming.
• the two pins 43.2 and 43.5 which are mounted in the cover 31, and the pin 43.3, which is seated in the housing 27, should be of the same diameter and length.
• the two pins 43.1 and 43.4, which sit in the cam ring, should also have the same diameter and the same length.
• the bores of the second side plate 41 and the first side plate 39 can be made approximately offset in the middle of the plate in accordance with FIG. 3.2 and the diameters can be of different sizes in accordance with the different pin diameters. Since with the appropriate pin arrangement "Slot pins" 43.4, 43.5 only have to absorb the torque and therefore only slight forces occur, the division of the pins can also be omitted here.

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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)
• Fluid-Driven Valves (AREA)
• Eye Examination Apparatus (AREA)

Applications Claiming Priority (3)

Publications (2)

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ID=7711058

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Country Status (9)

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• 2002
  • 2002-12-20 DE DE50210177T patent/DE50210177D1/de not_active Expired - Lifetime
  • 2002-12-20 AU AU2002367132A patent/AU2002367132A1/en not_active Abandoned
  • 2002-12-20 WO PCT/DE2002/004677 patent/WO2003056179A1/fr active IP Right Grant
  • 2002-12-20 DE DE10297705T patent/DE10297705D2/de not_active Expired - Fee Related
  • 2002-12-20 DE DE10259895A patent/DE10259895A1/de not_active Withdrawn
  • 2002-12-20 AT AT02805733T patent/ATE362588T1/de not_active IP Right Cessation
  • 2002-12-20 US US10/500,000 patent/US7520732B2/en not_active Expired - Lifetime
  • 2002-12-20 JP JP2003556674A patent/JP4490103B2/ja not_active Expired - Lifetime
  • 2002-12-20 EP EP02805733A patent/EP1461534B1/fr not_active Expired - Lifetime
  • 2002-12-23 FR FR0216503A patent/FR2835573B1/fr not_active Expired - Fee Related
  • 2002-12-24 IT IT002766A patent/ITMI20022766A1/it unknown

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