EP1855009A1 - Machine rotative à lobes - Google Patents

Machine rotative à lobes Download PDF

Info

Publication number: EP1855009A1
Authority: EP; European Patent Office
Prior art keywords: oil; rotary piston; connecting channels; machine according; piston machine
Prior art date: 2006-05-11
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

EP06009779A

Other languages

German (de)

English (en)

Other versions

EP1855009B1 (fr

Inventor

Frank Beckmann

Hans-Ulrich Fleige

Ulrich Götzel

Björn IRTEL

Oliver Palm

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.)

Aerzener Maschinenfabrik GmbH

Original Assignee

Aerzener Maschinenfabrik GmbH

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.)

2006-05-11

Filing date

2006-05-11

Publication date

2007-11-14

2006-05-11 Application filed by Aerzener Maschinenfabrik GmbH filed Critical Aerzener Maschinenfabrik GmbH

2006-05-11 Priority to AT06009779T priority Critical patent/ATE416313T1/de

2006-05-11 Priority to ES06009779T priority patent/ES2317362T3/es

2006-05-11 Priority to EP06009779A priority patent/EP1855009B1/fr

2006-05-11 Priority to DE502006002255T priority patent/DE502006002255D1/de

2006-05-11 Priority to PL06009779T priority patent/PL1855009T3/pl

2007-05-10 Priority to US11/746,938 priority patent/US7510381B2/en

2007-11-14 Publication of EP1855009A1 publication Critical patent/EP1855009A1/fr

2008-12-03 Application granted granted Critical

2008-12-03 Publication of EP1855009B1 publication Critical patent/EP1855009B1/fr

Status Not-in-force legal-status Critical Current

2026-05-11 Anticipated expiration legal-status Critical

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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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
- 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
- F04C29/028—Means for improving or restricting lubricant flow

Definitions

the invention relates to a two-shaft, dry-running rotary piston machine with two mounted in a housing via shafts and bearings with rolling elements rotary pistons, which are arranged horizontally and mesh with each other in opposite directions to define a delivery chamber, according to the preamble of claim 1.
Two-shaft rotary piston engines have two interlocking rotary pistons or rotors, which are rotated in a working space in the opposite direction, which is formed by axially parallel penetrating cylindrical housing bores for the rotors and frontally bounded by end walls. As a result, a conveying effect is generated.
Each rotor is attached to an associated shaft, which is rotatably received by rolling bearings in the housing. In general, one of the shafts is driven from the outside while the other shaft is rotated synchronously with the drive shaft by two intermeshing gears mounted on the shafts.
the arrangement of the two shafts - based on the operating position - one above the other, ie in a vertical plane, or even next to each other, ie in a horizontal plane.
the present invention relates only to twin-shaft rotary engines with the arrangement of the two shafts in a horizontal plane.
the drive-side oil chamber is characterized by the additional shaft passage to the environment. In most cases, the oil space in which the synchronizer wheels are located has higher oil temperatures.
the lubricating oil is distributed according to a) or b).
the lubricating oil is distributed to the consumption points by the moving machine parts themselves or by special additional equipment (sling rings, spray discs).
Such splash lubrication with splash disks and ⁇ lleitblechen is for example in DE 8405144 U1 disclosed.
the level of lubricant in the sump must be kept low to avoid unnecessary splashing and also to allow trouble-free oil return from the bearings. Wiper loss is understood to mean the effort required to move the rotating parts immersed in the sump. They cause an additional power consumption of the machine and an equally undesirable additional heating of the oil.
too low a level of the lubricant in the Oil sump too low lubrication of the bodies to be supplied with lubricant. The cooling of the oil takes place by heat exchange with the large wetted inner housing surfaces.
this form of lubricating oil supply is no longer sufficient, in particular due to lack of cooling of the bearings.
the mechanical power dissipation increases with the square of the velocity, i. H. a doubling of the speed results in a quadrupling of the friction loss.
the lubricating oil is then needed in addition to heat dissipation.
an oil pump is used with a separate cooler. The oil pump conveys the lubricating oil through lines and radiator to the oil injection nozzles, which supply a defined oil jet to the lubrication points (bearings, gears).
n * dm 0.5 to 4 * 10E6 mm / min can be covered (see Beitz, W .; Grote, K.-H .: Dubbel - Paperback for Mechanical Engineering. Verlag 1997, page G174, Annex G4 Table 3).
the invention is based on the idea to improve the cooling and lubricating efficiency of the lubricating oil in that without use of a separate oil pump and a separate oil cooler cooling by oil circulation between the two oil chambers is realized.
the invention provides that the at least two connecting channels are arranged and configured such that they allow such oil circulation without further components. More specifically, the invention provides that the connection cross sections of the at least two connecting channels to the oil chambers are at least partially disposed below the axis lines of the waves. This results in combination with the "diagonal" arranged spray elements that the oil flow generated by the spray elements can flow from one oil chamber into the other and back again.
Figs. 1 to 3 schematically show various views of a rotary piston engine 1 as an embodiment of the present invention.
the rotary piston machine 1 has two rotary pistons or rotors 8 which are not shown in detail in the figures and which are mounted in a housing 2 and are rotated in the opposite direction in order to produce a conveying effect.
Each rotor 8 is mounted on an associated shaft 4, which is rotatably received in the housing 2 by rolling bearings 6 with rolling elements 6 '(only a few of which are shown schematically).
one of the shafts is driven from the outside in a manner not shown here, while the other shaft is rotated synchronously with the drive shaft by two intermeshing gears 20 mounted on the shafts.
the arrows in Fig. 2 indicate the directions of rotation of the rotary piston 8.
the conveying direction of the rotary piston engine 1 selected as an embodiment is thus from top to bottom.
the rotary piston engine 1 has two oil chambers 10, which are arranged in the housing 2 at opposite end faces of the delivery chamber in the region of the roller bearings 6 and are provided to be at least partially filled with lubricating oil.
the drive-side oil chamber is characterized by the additional shaft passage to the environment.
the synchronizer 20th is also also the synchronizer 20th.
rotary piston engine shown is a dry-running rotary piston engine, ie, a rotary piston machine, in which no lubrication of the rotary piston is made, but the rotary pistons run without contact. Accordingly, the oil chambers 10 are sealed by the delivery chamber defined by the rotary piston.
each oil chamber 10 two spray elements or spray discs 12 are provided, wherein each oil chamber 10, a spray element 12 is arranged on the shafts 4 such that each shaft 4 carries a total of only one injection element 12.
the spray elements or spray discs 12 are thus arranged "diagonally".
the lubricant is taken from the immersed in the oil sump splash discs 12 from the bottom by towing and possibly additionally by notches on the circumference of the spray discs or similar measures and distributed in the oil space as droplets and fog. Due to the drag effect of the spray discs 12 in this case the oil is transported in the respective oil chamber 10 to the side of the shaft without spray disk.
the oil level is deformed, it forms an "oil mountain", whereby the effective immersion depth of the disc is reduced and the oil drain from the bearing of the adjacent shaft is obstructed.
the same process occurs in the opposite oil space. If the spray discs are now arranged diagonally (FIG. 3), the oil mountain and the oil valley of the two oil chambers 10 are located opposite each other.
connection cross-sections 14 'of the connection channels 14 are arranged on the oil spaces below the axis lines 4' of the shafts 4.
the connection cross sections 14' of the connecting channels 14 are also arranged below the rolling elements 6 '. In this way, the connection cross sections 14 'of the connecting channels 14 are partially or possibly completely below the free (oil) level of the lubricant 18 in the oil chambers 10.
connection cross sections 14 'of only one or both connection channels 14 are arranged completely below the free oil level, wherein in the latter case an additional pressure equalization line can be provided.
connection channels 14 or their connection cross-sections 14 'in the present embodiment are in the region of the opposite side walls 10' of the oil chambers 10.
the oil in the respective oil sump 10 is driven by the corresponding spray disk 12 and flows in the direction of the downstream connection channel 14 (the flow direction is indicated schematically by arrows in the figures).
the connecting channel 14 carries the oil to the opposite oil chamber 10.
the spray disk 12 in the opposite oil chamber 10 drives the oil further outward in the direction of the second, outer oil channel 14. This leads the oil back to the first oil chamber 10.
the surface of the oil connections can be provided with cooling fins.
Another advantage of the invention is the improved ease of maintenance since only one filling and drainage option must be provided by the connected oil chambers.
the connecting channels 14 are integrally molded with a housing cylinder 2 ', which surrounds the rotary piston 8.
an air layer 16 is provided between the connecting channels 14 and the housing cylinder 2 ', as best seen in Fig. 3. This ensures that the compression heat generated in the region of the rotary pistons 8 does not lead to undesired heating of the oil circulating in the connecting channels 16.
the configuration of the cross section of the connecting channels 14 is not particularly limited in the context of the present invention. However, it has proved to be advantageous if the connecting channels 14 have a large cross-section, for example a cross-section, in relation to a at standstill of the machine wetted by oil, rotary piston side end face 10 "of the oil space each at least 5%, preferably at least 10% and This results in a particularly efficient circulation of the oil with small "oil hills and valleys.” It is particularly preferred that the connecting channels 14 each have a substantially same cross section and this over the length of the respective Connecting channel is substantially constant.

Landscapes

Engineering & Computer Science (AREA)
Mechanical Engineering (AREA)
General Engineering & Computer Science (AREA)
Applications Or Details Of Rotary Compressors (AREA)
Reciprocating Pumps (AREA)
General Details Of Gearings (AREA)
Valve Device For Special Equipments (AREA)
Valve-Gear Or Valve Arrangements (AREA)
Cereal-Derived Products (AREA)
Insulation, Fastening Of Motor, Generator Windings (AREA)
Permanent Magnet Type Synchronous Machine (AREA)

EP06009779A 2006-05-11 2006-05-11 Machine rotative à lobes Not-in-force EP1855009B1 (fr)

Priority Applications (6)

Application Number	Priority Date	Filing Date	Title
AT06009779T ATE416313T1 (de)	2006-05-11	2006-05-11	Drehkolbenmaschine
ES06009779T ES2317362T3 (es)	2006-05-11	2006-05-11	Maquina de piston giratorio.
EP06009779A EP1855009B1 (fr)	2006-05-11	2006-05-11	Machine rotative à lobes
DE502006002255T DE502006002255D1 (de)	2006-05-11	2006-05-11	Drehkolbenmaschine
PL06009779T PL1855009T3 (pl)	2006-05-11	2006-05-11	Maszyna z tłokami o ruchu obrotowym
US11/746,938 US7510381B2 (en)	2006-05-11	2007-05-10	Lubricating system for a rotary compressor

Applications Claiming Priority (1)

Application Number	Priority Date	Filing Date	Title
EP06009779A EP1855009B1 (fr)	2006-05-11	2006-05-11	Machine rotative à lobes

Publications (2)

Publication Number	Publication Date
EP1855009A1 true EP1855009A1 (fr)	2007-11-14
EP1855009B1 EP1855009B1 (fr)	2008-12-03

Family

ID=37114527

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP06009779A Not-in-force EP1855009B1 (fr)	2006-05-11	2006-05-11	Machine rotative à lobes

Country Status (6)

Country	Link
US (1)	US7510381B2 (fr)
EP (1)	EP1855009B1 (fr)
AT (1)	ATE416313T1 (fr)
DE (1)	DE502006002255D1 (fr)
ES (1)	ES2317362T3 (fr)
PL (1)	PL1855009T3 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US8932033B2 (en) *	2009-12-21	2015-01-13	Eaton Corporation	Supercharger timing gear oil pump
EP2612035A2 (fr)	2010-08-30	2013-07-10	Oscomp Systems Inc.	Compresseur à refroidissement par injection de liquide
US9267504B2 (en)	2010-08-30	2016-02-23	Hicor Technologies, Inc.	Compressor with liquid injection cooling
US9828995B2 (en) *	2014-10-23	2017-11-28	Ghh Rand Schraubenkompressoren Gmbh	Compressor and oil drain system
EP4015823A1 (fr)	2020-12-16	2022-06-22	Aerzener Maschinenfabrik GmbH	Unité de moteur à piston rotatif pourvu de dispositif d'alimentation en lubrifiant

Citations (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US20030035738A1 (en) *	2001-08-14	2003-02-20	Deok-Kyeom Kim	Roots vacuum pump
DE10197228T5 (de) *	2001-10-23	2004-04-22	Taiko Kikai Industries Co., Ltd.	Gekapselter mechanischer Booster

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US1066815A (en) *	1912-06-04	1913-07-08	Herbert Thomas Herring	Rotary pump.
US1582961A (en) *	1924-12-26	1926-05-04	Berrenberg Reinold	High-vacua pump
US2361146A (en) *	1939-09-21	1944-10-24	Montelius Carl Oscar Josef	Pump
DE2402029B2 (de) *	1974-01-17	1980-04-24	1000 Berlin	Schmiervorrichtung für Rotationskolbenverdichter
DE3344953A1 (de) *	1983-12-13	1985-06-20	Leybold-Heraeus GmbH, 5000 Köln	Zweiwellen-vakuumpumpe mit getrieberaum-evakuierung
DE8405144U1 (de)	1984-02-21	1987-05-07	Leybold-Heraeus GmbH, 5000 Köln	Einrichtung zur Schmierölversorgung des Zahnradpaares einer Zweiwellen-Vakuumpumpe
DE3540959A1 (de)	1984-12-22	1986-07-03	Leybold-Heraeus GmbH, 5000 Köln	Oelfoerdereinrichtung fuer vakuumpumpen
US5044895A (en) *	1984-12-22	1991-09-03	Leybold Aktiengesellschaft	Oil supply device for a rotary machine
JPS6429690A (en) *	1987-07-22	1989-01-31	Hitachi Ltd	Shaft sealing device for screw vacuum pump
DE8714166U1 (de)	1987-10-23	1988-01-14	Verhülsdonk, Burkhard, 49624 Löningen	Vorrichtung zum Zuführen von Öl od. dgl. Schmiermittel aus einem einen Ölsumpf enthaltenden Gehäuse eines Zahnradgetriebes

2006
- 2006-05-11 AT AT06009779T patent/ATE416313T1/de not_active IP Right Cessation
- 2006-05-11 DE DE502006002255T patent/DE502006002255D1/de active Active
- 2006-05-11 PL PL06009779T patent/PL1855009T3/pl unknown
- 2006-05-11 EP EP06009779A patent/EP1855009B1/fr not_active Not-in-force
- 2006-05-11 ES ES06009779T patent/ES2317362T3/es active Active
2007
- 2007-05-10 US US11/746,938 patent/US7510381B2/en active Active

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US20030035738A1 (en) *	2001-08-14	2003-02-20	Deok-Kyeom Kim	Roots vacuum pump
DE10197228T5 (de) *	2001-10-23	2004-04-22	Taiko Kikai Industries Co., Ltd.	Gekapselter mechanischer Booster

Also Published As

Publication number	Publication date
ES2317362T3 (es)	2009-04-16
US20070274851A1 (en)	2007-11-29
DE502006002255D1 (de)	2009-01-15
US7510381B2 (en)	2009-03-31
PL1855009T3 (pl)	2009-04-30
ATE416313T1 (de)	2008-12-15
EP1855009B1 (fr)	2008-12-03

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