EP0003572A1 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP0003572A1
EP0003572A1 EP79100304A EP79100304A EP0003572A1 EP 0003572 A1 EP0003572 A1 EP 0003572A1 EP 79100304 A EP79100304 A EP 79100304A EP 79100304 A EP79100304 A EP 79100304A EP 0003572 A1 EP0003572 A1 EP 0003572A1
Authority
EP
European Patent Office
Prior art keywords
pump
vane
housing
channel
wing
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
EP79100304A
Other languages
German (de)
English (en)
Other versions
EP0003572B1 (fr
EP0003572B2 (fr
Inventor
Siegfried Dipl. Ing. Hertell
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 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=25773770&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0003572(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from DE19782804957 external-priority patent/DE2804957A1/de
Priority claimed from DE19787826176 external-priority patent/DE7826176U1/de
Application filed by Barmag Barmer Maschinenfabrik AG filed Critical Barmag Barmer Maschinenfabrik AG
Publication of EP0003572A1 publication Critical patent/EP0003572A1/fr
Publication of EP0003572B1 publication Critical patent/EP0003572B1/fr
Application granted granted Critical
Publication of EP0003572B2 publication Critical patent/EP0003572B2/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
    • F04C29/023—Lubricant distribution through a hollow driving shaft

Definitions

  • the invention relates to a vane machine of the type specified in the preamble of claim 1.
  • Vane cell machines of this type which operate as vacuum pumps, are mainly used to generate an auxiliary force for braking in motor vehicles.
  • Various lubricant systems for lubricating the moving parts are already known for these vane cell machines. These systems have generally proven themselves.
  • the vane machine is usually connected to the oil circuit of the motor vehicle engine. Very different operating conditions occur here, so that - depending on the application - it may be possible that not all parts of the machine are regularly supplied with lubricant.
  • These operating states can be, for example, an oil level that is too low and / or cold, viscous oil in winter.
  • the object of the present invention is therefore to improve the lubricant circuit of the vane machine and to design such that the functionality of the vane machine is guaranteed under all operating conditions.
  • the advantage of the invention is that by connecting the outlet channel and the lubricant run, an additional conveying effect occurs in the lubricant system, which ensures that the lubricant safely reaches all the necessary lubrication points.
  • the connection is possible at any point within the lubricant supply.
  • Claim 2 describes a special design of the outlet channel and the connection to the lubricant flow.
  • the development of the invention according to claim 3 is intended to ensure that only one direction of flow is reliably achieved regardless of the type and pressure level of the lubricant supply. This has the advantage that substantially smaller amounts of lubricant are sufficient than would be required without connecting the outlet channel and lubricant run.
  • a bearing of the pump shaft can advantageously be used as a throttle according to claim 4.
  • the annular channel according to claim 2 is particularly suitable for accommodating the bearing. It is also possible to mount the rotor of the vane machine on the fly.
  • the embodiment of the invention is proposed according to claim 5. This eliminates the additional effort for external lines. Furthermore, the danger is avoided that these external lines break, whereby the lubricant circuit is interrupted and serious damage to the vane machine occur.
  • the vane machine is used as a vacuum pump, there is the further advantage that the inner space of the hollow pump shaft and the vane foot spaces are under atmospheric pressure, as a result of which the lubricant can be injected into the hollow pump shaft. This eliminates the seal between the injection nozzle and the hollow pump shaft. Furthermore, the wings are essentially stressed by centrifugal forces, and the frictional power of the wings is kept low.
  • Claim 6 achieves a seal-free axial limitation of the ring channel.
  • Claim 7 describes a preferred alternative guide of the outlet channel of the vane machine. Here too, a sufficient conveying effect is exerted on the lubricant carried in the vane cell machine.
  • Claim 10 describes an advantageous embodiment of the second machine bearing.
  • a further embodiment of the invention is characterized in that the wing foot spaces have an external connection (connecting bores) in one end wall of the housing, the external connection extending over a circular arc coaxial with the rotor axis of rotation, which circular arc starting in the direction of rotation of the pump from bottom dead center to a maximum to top dead center.
  • the external connection can create a connection to the atmosphere. Only air, but also oil - under pressure or without pressure - can flow into the wing foot space when the wing is extended.
  • the pump housing 1 consists of a pump housing 1, which bears with its connecting flange on the schematically indicated motor housing 2.
  • the motor housing 2 houses the oil reservoir 14. It is fastened by means of suitable connecting elements, for example screws and washers.
  • the pump housing 1 is closed by a cover 3, which also contains the suction opening 4.
  • the bored-out pump shaft 5 is mounted at the level of the fastening in the engine block in a first slide bearing 6 and shortly before the pump chamber in a second slide bearing 7.
  • the first slide bearing 6 is formed by the housing 1.
  • the second slide bearing 7 is an exchangeable slide bearing which is fitted into an annular channel 8 in the housing 1. This ring channel 8 runs from the pump chamber to the first slide bearing 6.
  • the slide bearing 7 has one or more axially extending lubrication grooves 7.1 distributed over the circumference and one or more oil return grooves 7.2.
  • the upper cantilevered end of the pump shaft 5 carries four radially arranged wings 9 which can extend and retract radially.
  • a pump is described for example in DE utility model 77 07 853.
  • the wing root spaces 10 are connected to the bore in the pump shaft 5 via a radial annular space 11 (recess in the cover 3). Furthermore, the wing root spaces 10 are connected to the second slide bearing 7 via a further annular space 12 in the pump housing.
  • the pump outlet channel 13 runs from a suitable point in the pump chamber diagonally in the pump housing 1 to the ring channel 8. It leaves the ring channel 8 diametrically to its inlet and - when using the vane machine in a motor vehicle engine - opens into the motor housing.
  • the pump shaft 5 is driven by a suitable drive - when used in a motor vehicle engine - for example via a gear pair from the camshaft. It evacuates the storage space of a brake booster (not shown here) via the intake manifold 4.
  • lubricated oil is usually injected through the bored pump shaft 5.
  • the oil is usually delivered under pressure from the engine oil pump (oil reservoir 14).
  • the oil is introduced into the pump shaft 5 at such a pressure that it reaches the annular space 11. From there it arrives at the wing foot spaces 10. It also reaches the wing foot spaces 10 through the bores for the coupling pins 15, which are arranged on the underside of the wing. Because of the centrifugal forces, it is distributed from the wing foot spaces 10 to the sliding surfaces of the wings in the housing 1 or on the cover 3.
  • the oil from the wing foot spaces 10 passes through the ring channel 12 to the second bearing 7.
  • the flow through the bearing 7 occurs through the oil return grooves 7.2 and is supported by the fact that the air flowing out through the pump outlet channel 13 passes through the ring channels 18 below the bearing 7. This creates a suction effect that can propagate through the grooves 7.2 in the bearing 7 into the annular space 12 and the wing root spaces 10.
  • the bearing 7 is supplied with oil via the lubrication groove (s) 7.1.
  • the oil entering the ring channel 8 is largely discharged into the engine compartment (oil reservoir 14) with the compressed air. A portion of the oil from the ring channel 8 is used to lubricate the first bearing 6.
  • the air entering the engine compartment is returned to the air filter via a line due to environmental protection regulations. The oil collects again in the oil pan, where it can be collected again by the oil pump.
  • the pump outlet channel 13.1 does not run to the annular channel 8, but in spiral turns to the annular space 12. The spiral turns are therefore necessary so that the rotating vanes 9 do not get caught on the outlet channel 13.1.
  • the air enriched with lubricating oil is pressed due to the pumping action of the pump through the bearing 7 and the grooves 7.2 arranged therein. The air / oil mixture is then discharged from the annular duct 8 into the engine compartment in the manner described in FIG. 1.
  • motor housing 2 should be understood to mean any other housing to which the machine is attached. Preference is given to housings which contain a lubricant supply for the machine, since in these cases no external lubricant supply and discharge lines have to be provided. However, if external lines are used, it is possible to feed the lubricant through the cover 3 directly into the annular space 11 and to remove it from the annular space 12 with the exhaust air. This discharge line is then connected to any suitable lubricant reservoir 14.
  • Fig. 3 the section through another embodiment of a vane pump was made such that the two visible vanes 104 are at the same distance from the axis of rotation.
  • the pump shaft 102 is rotatably supported in the slide bearings 114 and 115.
  • the pump shaft 102 supports the rotor 103 in a rotationally fixed manner.
  • Each wing 104 has two pins 105 which slide in bores 106 in the rotor 103 and in the pump.
  • the pins 105 opposite wings 104 are arranged at the same height. This has the advantage that if a wing 104 is jammed, the opposite wing can push it over the pins 105.
  • the pump shaft 102 is designed as a hollow shaft and has a flange 107 in the direction of its drive. Attached to this flange is the driver 108, the free end of which is attached to the driver disk 109 of a pump drive motor, the shaft 110 of which is sketched in FIG. 3.
  • the driver 108 is arranged in a housing 111 which at the same time carries the pump housing 101 and contains the inlet and outlet channels of the pump. At the other end, the housing 111 is flanged to the motor housing, for example of a motor vehicle.
  • the driver 108 is drilled out at the level of the pump shaft 102, i.e. the opening of the hollow shaft is not completely closed.
  • the lubricant usually oil, is supplied under pressure through the lubricant line 112 arranged in the axis of rotation of the pump drive motor shaft 110.
  • the rigid feed line 113 is screwed or pressed into this shaft 110 in its axial extension. This feed line 113 ends in the pump shaft 102.
  • the front end of the pump shaft 102 ends in a storage chamber 116. From this chamber 116, an axially arranged groove 117 runs through the front slide bearing 114, which is formed by a sintered metal bush 122.
  • the rear slide bearing 115 is formed by the housing 111, which in this case consists of aluminum or an aluminum alloy.
  • a bore 121 leads to this bearing, which is inclined at an angle to the horizontal.
  • several holes 121 can of course be arranged. These bores 121 end in an annular space 120 which connects the individual wing foot spaces 119 on the end face.
  • the annular space 120 does not extend as far as the pump shaft 102 in order not to reduce the bearing width. With appropriate bearing dimensions, it is of course also possible to extend the annular space 120 to the pump shaft 102.
  • the bore 121 can also be formed as an axially extending groove.
  • the lubricating oil required for lubrication passes through the lubricant line 112 and the supply line 113 into the pump shaft 102.
  • the supply of the bearing 115 with oil is supported by the retracting and extending movement of the vanes 104, since the oil present in the vane spaces 119 is displaced into the annular space 120 and thus into the bore 121 by the retracting movement of the vanes 104.
  • This displacement effect is dependent on the diameter of the bore 106 or the gap between the pins 105 and the inner wall of the bores 106.
  • passage openings (connecting bores) 125 are provided which connect the annular space 120 to the driver space 127.
  • the driver space 127 is connected to the oil sump of the pump drive via return lines (not shown here).
  • the passage openings 125 are arranged in a range from bottom dead center to almost 100 ° (angular degree) in the direction of rotation of the pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP79100304A 1978-02-06 1979-02-02 Pompe à palettes Expired - Lifetime EP0003572B2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE2804957 1978-02-06
DE19782804957 DE2804957A1 (de) 1978-02-06 1978-02-06 Fluegelzellenmaschine
DE7826176U 1978-09-02
DE19787826176 DE7826176U1 (de) 1978-09-02 1978-09-02 Fluegelzellenpumpe

Publications (3)

Publication Number Publication Date
EP0003572A1 true EP0003572A1 (fr) 1979-08-22
EP0003572B1 EP0003572B1 (fr) 1984-07-04
EP0003572B2 EP0003572B2 (fr) 1991-12-11

Family

ID=25773770

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79100304A Expired - Lifetime EP0003572B2 (fr) 1978-02-06 1979-02-02 Pompe à palettes

Country Status (2)

Country Link
EP (1) EP0003572B2 (fr)
DE (1) DE2967081D1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3734573A1 (de) * 1986-10-18 1988-04-28 Barmag Barmer Maschf Fluegelzellenpumpe
EP0320795A2 (fr) * 1987-12-12 1989-06-21 Barmag Ag Pompe à vide avec palettes
EP2559903A1 (fr) * 2011-08-17 2013-02-20 Wabco Automotive UK Limited Pompe à vide améliorée
DE102018102393A1 (de) * 2018-02-02 2019-08-08 J.D. Neuhaus Holding Gmbh & Co. Kg Lamellenmotor

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1676103A (en) * 1927-02-16 1928-07-03 Henry L Buck Lubricating and sealing system for rotary compressors
GB480522A (en) * 1936-05-23 1938-02-23 Bendix Aviat Corp A new or improved rotary vacuum pump
US2827226A (en) * 1954-06-17 1958-03-18 Thompson Prod Inc Refrigeration apparatus
GB864580A (en) * 1959-08-20 1961-04-06 Dewandre Co Ltd C Improvements in or relating to rotary exhausters
GB912119A (en) * 1960-05-18 1962-12-05 Dewandre Co Ltd C Improvements in or relating to rotary exhausters and the like
FR2155583A5 (fr) * 1971-10-04 1973-05-18 Borg Warner
FR2384137A1 (fr) * 1977-03-15 1978-10-13 Barmag Barmer Maschf Machine multicellulaire a ailettes

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1676103A (en) * 1927-02-16 1928-07-03 Henry L Buck Lubricating and sealing system for rotary compressors
GB480522A (en) * 1936-05-23 1938-02-23 Bendix Aviat Corp A new or improved rotary vacuum pump
US2827226A (en) * 1954-06-17 1958-03-18 Thompson Prod Inc Refrigeration apparatus
GB864580A (en) * 1959-08-20 1961-04-06 Dewandre Co Ltd C Improvements in or relating to rotary exhausters
GB912119A (en) * 1960-05-18 1962-12-05 Dewandre Co Ltd C Improvements in or relating to rotary exhausters and the like
FR2155583A5 (fr) * 1971-10-04 1973-05-18 Borg Warner
FR2384137A1 (fr) * 1977-03-15 1978-10-13 Barmag Barmer Maschf Machine multicellulaire a ailettes

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3734573A1 (de) * 1986-10-18 1988-04-28 Barmag Barmer Maschf Fluegelzellenpumpe
DE3734573C2 (de) * 1986-10-18 1998-12-17 Barmag Barmer Maschf Flügelzellen-Vakuumpumpe
EP0320795A2 (fr) * 1987-12-12 1989-06-21 Barmag Ag Pompe à vide avec palettes
EP0320795A3 (en) * 1987-12-12 1990-02-07 Barmag Ag Vane-type vacuum pump
CN103857916A (zh) * 2011-08-17 2014-06-11 沃布科汽车（英国）有限公司 改进的真空泵
WO2013024117A3 (fr) * 2011-08-17 2013-08-22 Wabco Automotive Uk Limited Pompe à vide perfectionnée
EP2559903A1 (fr) * 2011-08-17 2013-02-20 Wabco Automotive UK Limited Pompe à vide améliorée
CN103857916B (zh) * 2011-08-17 2016-07-06 沃布科汽车（英国）有限公司 汽车真空泵
US9683570B2 (en) 2011-08-17 2017-06-20 Wabco Automotive Uk Limited Vacuum pump
US10371148B2 (en) 2011-08-17 2019-08-06 Wabco Automotive Uk Limited Vacuum pump
DE102018102393A1 (de) * 2018-02-02 2019-08-08 J.D. Neuhaus Holding Gmbh & Co. Kg Lamellenmotor
WO2019149753A1 (fr) * 2018-02-02 2019-08-08 J.D. Neuhaus Holding Gmbh & Co. Kg Moteur à piston rotatif à palettes
US11448071B2 (en) 2018-02-02 2022-09-20 J.D. Neuhaus Holding Gmbh & Co. Kg Vane motor

Also Published As

Publication number Publication date
EP0003572B1 (fr) 1984-07-04
DE2967081D1 (en) 1984-08-09
EP0003572B2 (fr) 1991-12-11

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