EP0320795A2 - Pompe à vide avec palettes - Google Patents

Pompe à vide avec palettes Download PDF

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Publication number
EP0320795A2
EP0320795A2 EP88120517A EP88120517A EP0320795A2 EP 0320795 A2 EP0320795 A2 EP 0320795A2 EP 88120517 A EP88120517 A EP 88120517A EP 88120517 A EP88120517 A EP 88120517A EP 0320795 A2 EP0320795 A2 EP 0320795A2
Authority
EP
European Patent Office
Prior art keywords
rotor
bore
pump
vane
vacuum pump
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
EP88120517A
Other languages
German (de)
English (en)
Other versions
EP0320795B1 (fr
EP0320795A3 (en
Inventor
Siegfried Hertell
Dieter Otto
Robert Lange
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.)
Oerlikon Barmag AG
Original Assignee
Barmag AG
Barmag Barmer Maschinenfabrik AG
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 Barmag AG, Barmag Barmer Maschinenfabrik AG filed Critical Barmag AG
Publication of EP0320795A2 publication Critical patent/EP0320795A2/fr
Publication of EP0320795A3 publication Critical patent/EP0320795A3/de
Application granted granted Critical
Publication of EP0320795B1 publication Critical patent/EP0320795B1/fr
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
    • 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
    • F04C18/3441—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum

Definitions

  • the invention relates to a vane vacuum pump according to the preamble of claim 1.
  • This pump is known from DE-OS 28 57 494 (Bag. 1170).
  • the inner bore of the rotor serves for the oil supply, the oil supply being effected via a throttle in such a way that a low, controllable pressure can be produced in the part of the rotor inner bore which extends over the axial working area of the rotor.
  • the vacuum of the pump housing can have the same effect in the end gaps between the rotor end walls and the adjacent pump covers. Therefore, essentially the same pressure forces act on the two end faces of the rotor, so that the known pump has the advantage that there is the same play on both end faces during the run.
  • This game can be kept very small by appropriate dimensioning and manufacturing, so that only small losses occur through this frontal gaps.
  • only a small pressure difference between the pump housing and the inner rotor bore can be produced, so that the losses are kept low not only by sealing gaps which are tolerated accordingly, but also by the low pressure difference.
  • the vane pump which is known from GB-PS 912 119, does not have these advantages.
  • This vane pump has the advantage that the rotor is floating and therefore the overall length of the pump is kept short.
  • the wing slots and wings are directed secantially in this pump. For this reason, pressure oil must be introduced into the wing foot spaces via the hollow shaft in order to always ensure that the wing heads rest securely on the circumferential wall of the housing.
  • the open end of the inner rotor bore is supported on a housing cover. This creates the disadvantage that the rotor is supported on this housing cover with high pressure and consequently rests on the opposite pump cover with a high contact pressure. This creates high friction.
  • the vane vacuum pump which is known from DE-PS 79 100 304 (Bag. 1055), also has a rotor with an inner bore. An injection nozzle is directed into this rotor, which, however, does not close the free end of the inner bore which projects into the crankcase of the motor vehicle. With this pump, the seal of the gaps between the wing slots and the wings and the other sealing gaps is only guaranteed if the oil supply is sufficiently large.
  • the measures according to claim 1 ensure that the lubricating oil flow between the inner rotor bore and the suction side of the vacuum pump is greatly reduced on the one hand, but on the other hand is so evened out that a sufficient amount of lubricating oil is always present and remains in the sealing gaps, despite a low supply.
  • This is due to the fact that a vacuum is created in the inner rotor bore with only a limited supply of lubricating oil, which essentially corresponds to the vacuum on the suction side or in the pump interior.
  • This is due to the inevitable leakage of the sealing gaps that are formed between the wing slots and the wings and possibly on the end faces of the rotor. Therefore, the pressure difference between the suction side of the pump and the inner bore of the rotor is very small, so that the oil production and the oil transport essentially takes place only by centrifugal force.
  • the type of oil supply to the inner bore essentially depends on the structural conditions of the motor vehicle engine from which the vane vacuum pump is supplied with lubricating oil.
  • a limited oil supply is essential to the invention.
  • the oil supply depends on the one hand on the delivery capacity of the oil pump and on the other hand on the consumption of the other lubrication points.
  • the oil supply to the vane vacuum pump is limited by installing a strong throttle or orifice or a flow control or flow limiting valve in the lubricating oil supply line to the inner bore.
  • the diameter of the bearing bore and the rotor shaft is preferably smaller than the diameter of the rotor.
  • the lubricating oil supply line can be connected centrally via a sealing rotary coupling to the otherwise closed rotor inner bore.
  • the measure according to claim 4 ensures that the sliding bearing of the rotor shaft of the vane pump is lubricated and sealed at the same time, so that leakage through the bearing end wall and the sliding bearing is excluded.
  • the plain bearing is provided in the axial area of the flange with which the vane vacuum pump is flanged to the motor.
  • the rotating fluid coupling is formed in that an annular channel is formed in the bearing bush and / or on the shaft, into which the lubricant supply line opens from the bearing bush and is connected to the inner rotor bore by radial channels.
  • the vane pump 1 is flanged to the crankcase 2 of a motor vehicle by flange 13.
  • the circular cylindrical rotor 5 is rotatably mounted in the pump housing 4.
  • the flange 13 of the pump housing forms the eccentric bearing bore 37.
  • the bearing bore 37 points into the crankcase and is centered therefor. It should be mentioned that the bearing bore 37 forms a sliding bearing for the bearing end of the rotor 5.
  • the rotor is mounted so that it is in circumferential contact with the housing at one point, the so-called bottom dead center.
  • the rotor is overhung on a shaft 20, which is integrally formed on one side as the bearing end on the rotor and has a smaller diameter than the rotor.
  • An inner bore 21 extends over the entire length of the rotor.
  • the rotor In the area of the housing, the rotor has a single guide slot 6, which lies in an axial plane, which penetrates the inner bore and whose axial length corresponds exactly to the axial length of the pump housing 4.
  • a single wing 7 is slidably guided in the guide slot 6.
  • the width of the wing corresponds to the axial length of the pump housing.
  • the wing 4 can be made in one piece. However, it can also have sealing strips at its ends, which are guided in grooves 9 of the wing 7 in a radial but sliding manner in the radial direction. Vent holes 10, which connect the bottom of the grooves 9 with the - seen in the direction of rotation - front of the wing, ensure that the highest pressure in the pump is always present in the grooves 9, so that the sealing strips 8 are pressed outwards.
  • the wing, including the sealing strip is so long that, thanks to the cross-sectional shape of the housing, which will be described later, it lies sealingly against the circumference of the housing 4 in every rotational position.
  • the wing ends are rounded with a radius r in each case. This radius is chosen to be as large as possible.
  • the circumferential wall of the pump housing 4 is determined such that it represents an equidistant cross-section to a Pascal spiral (conchoid) with the radius of curvature of the wing tips r as a distance.
  • the vane length and the outer diameter of the rotor 5 are first determined.
  • the difference between the length of the wing and the outside diameter determines the delivery volume of the pump. The difference is limited by strength and other considerations.
  • the rotor Since the rotor is mounted in the housing so that it is in circumferential contact with the housing at one point, the so-called bottom dead center, the wing 7 is completely immersed in the bottom dead center - as shown in FIG. 2 - in the guide slot 6 of the Rotor 5 a.
  • the Pascal spiral around the center M of the rotor 5 is now constructed for the centers of curvature K of the wing ends.
  • the peripheral wall of the pump housing 4 then results as the equidistant with the Distance r.
  • the centers of curvature K of the wing tips thus move on a Pascal spiral around the center of the rotor. This ensures that the wing always rests with its wing ends sealingly on the circumference of the pump housing 4.
  • the pump housing 4 has the suction inlet 11 with a check valve 31 arranged therein and an outlet 12 with a check valve 24 arranged therein.
  • the inlet 11 is offset by approximately 90 ° from the dead center position and the inlet 12 is in the region before bottom dead center - seen in direction of rotation 35.
  • the inlet valve 31 is designed as a mushroom valve. It is a mushroom-shaped rubber body, which is inserted with its style into a perforated valve plate and which rests with the edges of its head on the valve plate, sealingly enclosing the holes in the valve plate.
  • the head turns over in the suction direction in such a way that the suction opening is released. The head locks in the opposite direction.
  • the inlet 11 with the inlet valve 31 is shown offset in the circumferential direction in FIG. 1. Its geometric position results from FIG. 2.
  • the outlet which is only indicated schematically in FIGS. 1 and 2, opens into the crankcase of the motor vehicle engine via a check valve 24.
  • the check valve 24 is designed as a spring leaf valve which is clamped on one side.
  • the rotor has coupling tabs 16 on its bearing attachment. With these clutch flaps, the rotor is driven by the drive shaft 3 of the motor vehicle engine.
  • the drive shaft 3 can be, for example, the drive shaft for the injection pump.
  • a clutch disc 15 is attached, which distributed on the circumference Incisions 17 has.
  • the clutch tabs 16 of the bearing shoulder of the rotor engage in the notches 17 of the clutch disk without hindering the axial mobility of the rotor.
  • the rotor 5 is driven by the drive shaft 3 with the direction of rotation 35.
  • the vane 7 executes a relative movement in the guide slot and lies with its two ends in a sealing and sliding manner on the housing periphery of the pump housing 4.
  • the inner bore 21 of the rotor 5 is closed on one side by the housing cover 25.
  • the inner bore 21 is closed by wall 18.
  • the wall 18 is - seen in the axial direction - at the rotor end or outside the rotor, so that the wall 18 does not hinder the passage of the blades.
  • the wall 18 has a nozzle 23, through which the inner bore 21 is connected to the inside of the crankcase and above it to the atmosphere.
  • the supply of lubricating oil to the vane vacuum pump takes place from the lubricating oil pump (not shown) of the motor vehicle engine via an oil supply line 19.
  • the oil supply line continues as a bore 27 in the flange 13 and opens radially into the bearing bore 37 of the pump flange 13 Bore 27 with an annular channel 26 which is formed on the circumference of the bearing shoulder of the rotor.
  • the ring channel is preferably in the axial center of the bearing shoulder.
  • the ring channel is connected to the inner rotor bore 21 by a radial channel 28.
  • the lubricating oil pump only supplies a limited amount of oil to the vane vacuum pump shown.
  • volume flow limiting valves or volume flow control valves or orifices or throttles can be provided in the oil supply line, which are not shown here.
  • the radial channel 28 is designed as a throttle channel by dimensioning its cross section and its length.
  • the lubricating oil is supplied in a dosed, limited amount via line 19 when the motor vehicle engine and thus also the vane vacuum pump are in operation.
  • the radial bore 27 and the annular channel 26 on the one hand form a sealing liquid coupling for the lubricating oil. Through this coupling, the lubricating oil is transferred to and into the rotating rotor 5.
  • the ring channel 26 serves to distribute the lubricating oil to the slide bearing of the bearing bore 37. The uniform distribution of the oil also results in a sealing of the slide bearing.
  • the oil passes through the radial channel 28 into the inner bore 21.
  • Vacuum also arises in the rest of the pump chamber, since the outlet 12 of the pump is closed from the atmosphere by a check valve 24. Via the sealing gaps between the wing slot 6 and the wing 7 as well as the pump cover 25 and the rotor 5, this negative pressure also arises in the inner bore 21 of the rotor during operation.
  • the level of this negative pressure depends on the delivery capacity of the lubricating oil pump and the other consumption or on the quantity of oil supplied to the vane vacuum pump or on the throttling of the oil flow made available to the vane vacuum pump. If the quantity of lubricating oil is very limited, i.e. e.g. very strong throttling of the lubricating oil flow in the radial channel 28 creates a very high vacuum in the inner bore 21.
  • the pressure difference between the inner bore 21 and the rest of the pump housing is therefore reduced to almost zero during operation. Therefore, the oil that has been pumped into the inner bore 21 is not driven into the sealing gaps by the pressure difference, but only by centrifugal force. This ensures that the oil is subjected to only a slight promotion, so that in the seal gap creates an even oil film with little movement. This measure greatly reduces the oil consumption, but also makes the lubricating and sealing effect of the oil more uniform.
  • the inner bore 21 of the rotor can be hermetically sealed. If such a valve is not present, there is a risk that, when the motor vehicle engine is at a standstill, oil will continue to be sucked in due to the negative pressure in the pump housing and in the inner bore 21 until the negative pressure is released. The sucked-in oil collects at the lowest point of the pump housing. When starting up, the oil must be expelled from the pump housing. This can result in pressure surges that lead to breakage. This applies in particular if the motor vehicle engine starts with the wrong direction of rotation, as can occur with diesel engines. For this reason, the inner bore 21 is provided with a nozzle 23.
  • the nozzle 23 is designed so that it only allows small amounts of air to pass through. It therefore does not hinder the build-up of the negative pressure in the inner bore 21. On the other hand, it ensures that the vacuum in the inner bore 21 is quickly released when the motor vehicle engine is at a standstill. This prevents the suctioning and accumulation of large quantities of oil when the vane vacuum pump is at a standstill.
  • the nozzle 23 can also be designed with a larger cross-section, so that even during operation, a small amount of air is always sucked in via the nozzle 23 in such a way that the vacuum created in the inner bore is not formed in full. This measure allows the pressure difference between the inner bore and the rest of the pump chamber to be increased in a targeted manner if greater oil production between the inner bore and the pump chamber is desired and the oil production should therefore be based not only on centrifugal force but also on the pressure difference.
  • the lubricating oil is supplied to the vane vacuum pump from the lubricating oil pump (not shown) of the motor vehicle engine via an oil supply line through the housing cover 25.
  • the oil supply line ends in a disk-shaped recess 22.
  • the diameter of the disk-shaped recess 22 is not larger than the diameter of the inner bore 21.
  • a radial channel 28 extends from the inner bore 21.
  • the radial channel 28 opens into an annular groove 26.
  • the annular groove 26 lies on the circumference of the bearing shaft 20 of the rotor, specifically in its central axial area.
  • the ring channel has no further connection to the outside, except through the inevitable gaps in the bearing bore.
  • an axial lubrication groove can also be provided in the bearing bore in order to ensure an even distribution of the lubricating oil in the slide bearing.
  • the lubricating oil is supplied through the oil supply channel 19, specifically through the pump cover 4.
  • the pump cover 4 has a circular disc-shaped recess 32 on the side facing the rotor.
  • the outer diameter of this circular disc-shaped recess essentially corresponds to the diameter of the inner bore 21.
  • the oil supply line 19 opens into this circular disc-shaped recess 32.
  • a throttle 23 can be present as in the other exemplary embodiment.
  • the function of the throttle 23 reference can also be made to the explanations for the previous exemplary embodiment.
  • FIG. 3 The embodiment of FIG. 3 is characterized in that no rotating fluid coupling is required for the oil supply into the inner bore 21.
  • an oil-filled ring channel is provided in the axial area of the slide bearing, which serves on the one hand to lubricate the slide bearing and on the other hand to seal the slide bearing and the sealing gap between the rotor and the bearing-side pump cover.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP88120517A 1987-12-12 1988-12-08 Pompe à vide avec palettes Expired - Lifetime EP0320795B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3742277 1987-12-12
DE3742277 1987-12-12

Publications (3)

Publication Number Publication Date
EP0320795A2 true EP0320795A2 (fr) 1989-06-21
EP0320795A3 EP0320795A3 (en) 1990-02-07
EP0320795B1 EP0320795B1 (fr) 1991-07-10

Family

ID=6342537

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88120517A Expired - Lifetime EP0320795B1 (fr) 1987-12-12 1988-12-08 Pompe à vide avec palettes

Country Status (3)

Country Link
EP (1) EP0320795B1 (fr)
DE (1) DE3863633D1 (fr)
ES (1) ES2022973B3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2640699A1 (fr) * 1988-12-21 1990-06-22 Bar Ag Ag Pompe a vide a ailettes
GB2234784A (en) * 1989-08-09 1991-02-13 Medizin Labortechnik Veb K Oil pump for rotating vacuum pumps
EP0515929A1 (fr) * 1991-05-29 1992-12-02 LuK Automobiltechnik GmbH & Co. KG Pompe à vide à palettes
DE19964598B4 (de) * 1998-09-30 2013-12-12 Ixetic Hückeswagen Gmbh Vakuumpumpe
JP2018507980A (ja) * 2015-03-25 2018-03-22 ピアーブルグ パンプ テクノロジー ゲゼルシャフト ミット ベシュレンクテル ハフツングＰｉｅｒｂｕｒｇ Ｐｕｍｐ Ｔｅｃｈｎｏｌｏｇｙ ＧｍｂＨ 車両用機械式真空ポンプ

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB912119A (en) * 1960-05-18 1962-12-05 Dewandre Co Ltd C Improvements in or relating to rotary exhausters and the like
DE2737659A1 (de) * 1977-08-20 1979-03-01 Volkswagenwerk Ag Fluegelzellenpumpe zur erzeugung eines unterdruckes
EP0003572A1 (fr) * 1978-02-06 1979-08-22 b a r m a g Barmer Maschinenfabrik Aktiengesellschaft Pompe à palettes
GB2069610A (en) * 1980-02-14 1981-08-26 Bosch Gmbh Robert Vacuum pump
DE3519741A1 (de) * 1984-06-09 1986-01-02 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Fluegelzellenvakuumpumpe
DE3734573A1 (de) * 1986-10-18 1988-04-28 Barmag Barmer Maschf Fluegelzellenpumpe

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB912119A (en) * 1960-05-18 1962-12-05 Dewandre Co Ltd C Improvements in or relating to rotary exhausters and the like
DE2737659A1 (de) * 1977-08-20 1979-03-01 Volkswagenwerk Ag Fluegelzellenpumpe zur erzeugung eines unterdruckes
EP0003572A1 (fr) * 1978-02-06 1979-08-22 b a r m a g Barmer Maschinenfabrik Aktiengesellschaft Pompe à palettes
GB2069610A (en) * 1980-02-14 1981-08-26 Bosch Gmbh Robert Vacuum pump
DE3519741A1 (de) * 1984-06-09 1986-01-02 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Fluegelzellenvakuumpumpe
DE3734573A1 (de) * 1986-10-18 1988-04-28 Barmag Barmer Maschf Fluegelzellenpumpe

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2640699A1 (fr) * 1988-12-21 1990-06-22 Bar Ag Ag Pompe a vide a ailettes
GB2234784A (en) * 1989-08-09 1991-02-13 Medizin Labortechnik Veb K Oil pump for rotating vacuum pumps
EP0515929A1 (fr) * 1991-05-29 1992-12-02 LuK Automobiltechnik GmbH & Co. KG Pompe à vide à palettes
DE19964598B4 (de) * 1998-09-30 2013-12-12 Ixetic Hückeswagen Gmbh Vakuumpumpe
JP2018507980A (ja) * 2015-03-25 2018-03-22 ピアーブルグ パンプ テクノロジー ゲゼルシャフト ミット ベシュレンクテル ハフツングＰｉｅｒｂｕｒｇ Ｐｕｍｐ Ｔｅｃｈｎｏｌｏｇｙ ＧｍｂＨ 車両用機械式真空ポンプ
US10696280B2 (en) 2015-03-25 2020-06-30 Pierburg Pump Technology Gmbh Vacuum pump with rotor shaft supported by friction bearings

Also Published As

Publication number Publication date
EP0320795B1 (fr) 1991-07-10
EP0320795A3 (en) 1990-02-07
ES2022973B3 (es) 1991-12-16
DE3863633D1 (de) 1991-08-14

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