EP1674726A1 - Compresseur à piston à fonctionemment à sec - Google Patents

Compresseur à piston à fonctionemment à sec Download PDF

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Publication number
EP1674726A1
EP1674726A1 EP04029955A EP04029955A EP1674726A1 EP 1674726 A1 EP1674726 A1 EP 1674726A1 EP 04029955 A EP04029955 A EP 04029955A EP 04029955 A EP04029955 A EP 04029955A EP 1674726 A1 EP1674726 A1 EP 1674726A1
Authority
EP
European Patent Office
Prior art keywords
bearing
piston
connecting rod
dry
running
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.)
Withdrawn
Application number
EP04029955A
Other languages
German (de)
English (en)
Inventor
Michael Hartl
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.)
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Knorr Bremse Systeme fuer Schienenfahrzeuge 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.)
Filing date
Publication date
Application filed by Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH, Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
Priority to EP04029955A priority Critical patent/EP1674726A1/fr
Priority to CNA2005800472637A priority patent/CN101111678A/zh
Priority to PCT/EP2005/013607 priority patent/WO2006066833A1/fr
Priority to CA002591491A priority patent/CA2591491A1/fr
Priority to JP2007545969A priority patent/JP2008524483A/ja
Priority to MX2007007237A priority patent/MX2007007237A/es
Publication of EP1674726A1 publication Critical patent/EP1674726A1/fr
Withdrawn legal-status Critical Current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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons

Definitions

  • the present invention relates to a dry-running piston compressor with a crankcase, on which at least one pot-like cylinder is arranged with an associated inner piston which is connected by means of a connecting rod with a crankshaft rotatably mounted in the crankcase, wherein the crankshaft-side end of the connecting rod via a like Rolling bearing executed connecting rod bearing is mounted on the crankshaft.
  • the field of application of the present invention extends primarily to the commercial and rail vehicle sector.
  • reciprocating compressors for the production of compressed air used which are needed in particular for the operation of the compressed air brake system.
  • the present invention relates to dry-running, that is oil-free piston compressor, which are particularly suitable for use in commercial and rail vehicle.
  • oil lubrication has the consequence that the compressed air is oily.
  • the condensate which accumulates in the subsequent air drying, must be collected because of the oil content for environmental reasons in heated containers and drained at regular intervals for disposal. This leads to an increased maintenance and disposal costs.
  • problems of emulsion formation in the oil circuit of conventional oil-lubricated reciprocating compressors which usually occur during winter operation at low load. Particular problems arise when using oil-lubricated piston compressor in commercial vehicles.
  • the dry running piston compressor has a crankcase for a crankshaft rotatably mounted therein. On the outside of the crankcase a plurality of pot-like cylinders are provided, each with associated inner piston, wherein the crankshaft via a connecting rod bearing as the first bearing with one end of the connecting rod is in communication to the rotational movement of the crankshaft in a linear movement for the at the other end of the connecting rod to convert a piston pin bearing stored as a second bearing piston.
  • the dry running piston compressor works without a lubricating oil in the crankcase.
  • the conrod bearing designed as a rolling bearing in an oil-free piston compressor was always dimensioned according to the regulations of the prior art. Such a regulation contains the document "FAG Rolling Bearings, WL 41 520/3 DB Catalog Edition 1999".
  • the classical bearing dimensioning for the present case of a connecting rod bearing takes place by determining the maximum piston force, which results from the piston surface multiplied by the maximum pressure acting on the piston surface.
  • L ( C / P ) p
  • C dynamic load rating
  • P bearing load
  • p lifetime exponent.
  • the bearing selection is ultimately based on the resulting from this formula load capacity by appropriate mathematical forming steps.
  • Basic load ratings of rolling bearings are standardized and are based on DIN ISO 281 and DIN ISO 76.
  • the dynamic load rating C is defined as the load of invariable size and direction, in which a sufficiently large quantity of identical bearings reaches a nominal service life of 1 million revolutions.
  • the core of the new train of thought is the fact that the kinetic energy of heavy pistons, as they are also used in dry running reciprocating compressors, due to the guide length of the heavy piston pin and the use of a rolling bearing on the piston is converted into the compression energy, which not only to improve the Vibration behavior but - here the cause - must lead to a relief of the rolling bearings on the connecting rod.
  • the ratio between the oscillating mass m osz of the piston drive, piston ring, piston pin bearing and the oscillating part of the connecting rod crank mechanism and the effective surface of the piston A piston should be in the range of 10 to 20.
  • a piston in cm 2 and m osz in g must be indicated.
  • a particularly minimal bearing load is created, which additionally contributes to the service life extension. Said ratio brings the benefit of the invention, especially in the field of the use of particularly heavy pistons. This would be in this case then pay attention.
  • the conical bearing to be formed in the manner of a roller bearing should preferably be designed in the form of at least one ball bearing.
  • the connecting rod bearing is designed as a double-row ball bearing, which causes a corresponding broadening of the space required for the connecting rod bearing;
  • the critical in terms of a minimal space dimension of the bearing diameter can be kept very low thereby.
  • For a double-row ball bearing has a smaller outer diameter compared to a comparable single-row ball bearing.
  • the connecting rod bearing should be equipped with a grease filling for permanent lubrication. This measure also contributes to maximizing the service life.
  • the dry-running piston compressor according to the invention can be designed as a single-cylinder or multi-cylinder compressor. Likewise, in the case of multi-cylinder compressors, multi-stage compression with at least one low-pressure stage and at least one high-pressure stage is possible.
  • a reciprocating compressor 1 is arranged within a payload or rail vehicle between a motor 2 for driving the vehicle and a support frame 3, not shown here.
  • the motor 2 for driving the vehicle also serves to drive the reciprocating compressor. 1
  • the reciprocating compressor 1 has a crankcase 4, to which a pot-like cylinder 5 is attached via a - not visible here - screw.
  • the cup-shaped cylinder 5 is provided with a cylinder head 6, through which - in a conventional manner - the suction of air from the atmosphere and the delivery of the compressed air generated in the cylinder 5 via a valve assembly integrated therein.
  • back and forth movable piston 7 For generating compressed air in the cylinder 5 back and forth movable piston 7 is provided.
  • the piston 7 is pivotally mounted on a connecting rod 8 and is at the opposite end via a connecting rod bearing 9 with the crankshaft 10 in connection.
  • the limiting circle K clarifies that in this conventional selection of the connecting rod bearing 9, the space between the engine 2 of the utility vehicle and the support frame 3 would not be sufficient to accommodate this dry-running reciprocating compressor here.
  • the prevailing space conditions are given by commercial vehicle manufacturers, however, as structural boundary conditions and normally provided for the installation of comparatively small-scale oil-lubricated piston compressor, which, however, cause the problems described above.
  • FIG. 2 the space conditions in a dry-running reciprocating compressor designed according to the invention are illustrated by comparison.
  • the crankcase 4 of this piston compressor 1 ' may have smaller outer dimensions, so that this fits into the limited space between the engine 2 and support frame 3 of the commercial vehicle.
  • the reason for this are the comparatively smaller connecting rod bearings 9, the diameter of which determines the construction space.
  • Rotation speed: n 2400 rpm aids: FAG Rolling Bearings, WL 41 520/3 DB Catalog Edition 1999
  • the bearing load P is 8860 N.
  • This bearing would therefore have a fairly large outer diameter of 120 mm .
  • Lifetime exponent p 3 for ball bearings
  • the bearing would reach a calculated running time of only 365 h, which however does not apply to the dry running piston compressor.
  • the practice shows that the much smaller bearing here reaches a duration of over 5000 h.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
EP04029955A 2004-12-17 2004-12-17 Compresseur à piston à fonctionemment à sec Withdrawn EP1674726A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP04029955A EP1674726A1 (fr) 2004-12-17 2004-12-17 Compresseur à piston à fonctionemment à sec
CNA2005800472637A CN101111678A (zh) 2004-12-17 2005-12-16 干式运行的活塞式压缩机
PCT/EP2005/013607 WO2006066833A1 (fr) 2004-12-17 2005-12-16 Compresseur fonctionnant a sec
CA002591491A CA2591491A1 (fr) 2004-12-17 2005-12-16 Compresseur fonctionnant a sec
JP2007545969A JP2008524483A (ja) 2004-12-17 2005-12-16 乾式ピストン圧縮機
MX2007007237A MX2007007237A (es) 2004-12-17 2005-12-16 Compresor con embolo seco.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04029955A EP1674726A1 (fr) 2004-12-17 2004-12-17 Compresseur à piston à fonctionemment à sec

Publications (1)

Publication Number Publication Date
EP1674726A1 true EP1674726A1 (fr) 2006-06-28

Family

ID=34927824

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04029955A Withdrawn EP1674726A1 (fr) 2004-12-17 2004-12-17 Compresseur à piston à fonctionemment à sec

Country Status (6)

Country Link
EP (1) EP1674726A1 (fr)
JP (1) JP2008524483A (fr)
CN (1) CN101111678A (fr)
CA (1) CA2591491A1 (fr)
MX (1) MX2007007237A (fr)
WO (1) WO2006066833A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112240275A (zh) * 2020-08-27 2021-01-19 蚌埠翔云压缩机制造有限公司 一种具有良好除湿性的天然气压缩机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20100037604A (ko) * 2007-06-15 2010-04-09 가부시키가이샤 한도오따이 에네루기 켄큐쇼 표시 장치

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5152677A (en) * 1990-04-18 1992-10-06 Bauer Kompressoren Gmbh Dry-running reciprocating compressor
DE10042212A1 (de) * 2000-08-28 2002-03-14 Knorr Bremse Systeme Schwingungsarmer Kolbenkompressor für Fahrzeuge
DE10109514C1 (de) * 2001-02-28 2002-07-11 Knorr Bremse Systeme Trockenlaufender Kolbenverdichter (Kurbeltriebschmierung)
US20030180161A1 (en) * 2002-03-25 2003-09-25 I-Min Hsiao Oil-free air compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5152677A (en) * 1990-04-18 1992-10-06 Bauer Kompressoren Gmbh Dry-running reciprocating compressor
DE10042212A1 (de) * 2000-08-28 2002-03-14 Knorr Bremse Systeme Schwingungsarmer Kolbenkompressor für Fahrzeuge
DE10109514C1 (de) * 2001-02-28 2002-07-11 Knorr Bremse Systeme Trockenlaufender Kolbenverdichter (Kurbeltriebschmierung)
US20030180161A1 (en) * 2002-03-25 2003-09-25 I-Min Hsiao Oil-free air compressor

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
ESCHMANN P.: "Die Waelzlagerpraxis - Hanbuch für die Berechnung und Gestaltung von Lagerungen", 1978, R. OLDENBOURG VERLAG GMBH, MUENCHEN, ISBN: 3-486-31102-6, pages: 425 - 427, XP003000105

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112240275A (zh) * 2020-08-27 2021-01-19 蚌埠翔云压缩机制造有限公司 一种具有良好除湿性的天然气压缩机

Also Published As

Publication number Publication date
CN101111678A (zh) 2008-01-23
WO2006066833A1 (fr) 2006-06-29
JP2008524483A (ja) 2008-07-10
MX2007007237A (es) 2007-08-14
CA2591491A1 (fr) 2006-06-29

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