EP2582978B1 - Luftgekühlter kolbenkompressor mit spezieller kühlluftführung - Google Patents

Luftgekühlter kolbenkompressor mit spezieller kühlluftführung Download PDF

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Publication number
EP2582978B1
EP2582978B1 EP11726126.3A EP11726126A EP2582978B1 EP 2582978 B1 EP2582978 B1 EP 2582978B1 EP 11726126 A EP11726126 A EP 11726126A EP 2582978 B1 EP2582978 B1 EP 2582978B1
Authority
EP
European Patent Office
Prior art keywords
air
cooling air
reciprocating compressor
cylinders
fan
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.)
Not-in-force
Application number
EP11726126.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2582978A1 (de
Inventor
Michael Hartl
Jürgen MENDEL
Jörg MELLAR
Matthias Fritz
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 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
Publication of EP2582978A1 publication Critical patent/EP2582978A1/de
Application granted granted Critical
Publication of EP2582978B1 publication Critical patent/EP2582978B1/de
Not-in-force legal-status Critical Current
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
    • 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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/064—Cooling by a cooling jacket in the pump casing
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
    • 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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/066—Cooling by ventilation

Definitions

  • the invention relates to an air-cooled piston compressor for use in vehicles, especially commercial vehicles, with a compressor having a plurality of cylinders, which is driven by a motor, which also has a fan for generating a cooling air flow for cooling, in particular the cylinder.
  • the field of application of the invention extends primarily to oil-free piston compressors in multi-cylinder design, which operate in one stage even at high operating pressures, wherein the cooling of the cylinder is performed via a cooling air flow.
  • compressor concepts are recently being tested in which the compressor is driven by an electric motor, which is supplied for example by a generator and a converter and is installed in places of the vehicle, where no cooling water is available, but often high ambient temperatures prevail.
  • the compressed air generated by the compressor is used in particular for the operation of the vehicle brakes.
  • oil-free compressing compressors of the type described above are needed, which work reliably with little effort in the smallest space at extreme ambient temperatures and with ei-LK: hv Low maintenance cover a high air requirement.
  • oil-free compressor concepts no oil filling of the compressor housing in the conventional sense is more available.
  • the lubrication on the piston raceways is replaced by a low-friction piston coating.
  • the rotating parts are supported by roller bearings with temperature-resistant, long-lasting grease filling. In the valves also guided parts are avoided, which could generate frictional heat.
  • air-cooled compressors are used rather.
  • Particularly air-cooled reciprocating compressors are often equipped in these applications with axial fans, which are mounted on one side of the crankshaft of the reciprocating compressor and driven by this.
  • These piston compressors are often designed in W, V or star design, so that the cooling air of the axial fan can be performed as evenly as possible over all cylinders. If, on the other hand, cylinders of other cylinders - for example in the case of a row arrangement - are concealed in the direction of cooling flow, there is a risk of overheating.
  • Such air-cooled reciprocating compressors are designed in two-stage or multi-stage operating pressures of over 8 bar, in order to keep the component temperatures low.
  • Such multi-stage compressor concepts are in the general state of the art often in brake air compressors in rail vehicle application in application. Some types work with simple baffles, through which the cooling air is passed as close as possible to the hidden cylinders, in order to cool them better.
  • the DE 101 38 070 C2 discloses a technical solution for lowering the temperatures in the crankcase of an oil-free two-stage compressor.
  • the change in volume caused by the piston movement is used to generate a cooling air flow.
  • the cooling air is used primarily for jacket cooling of the cylinder, but also for ventilation of the crankcase.
  • the disadvantage of this design is that the ventilation is not completely integrated in the compressor, but lateral cooling air supply and additional filter systems for cleaning the cooling air are required. Furthermore, can Contaminants and water accumulate in the crankcase. This solution was therefore unsuitable for single-stage compressor.
  • the DE 10 2004 042 944 A1 describes a reciprocating compressor with a crankcase ventilation in which the cooling air is diverted from the intake air of the compressor.
  • the disadvantage of this solution is that the cooling air is already preheated in the cylinder head and thus the efficiency and the thermal behavior of the compressor is deteriorated.
  • the temperature problem is solved by the crankcase; However, the temperature problem in the cylinder area remains.
  • From the DE 24 22 448 A1 is a compact arrangement of an air compressor unit with a drive unit, preferably an electric motor, for the compressed air procurement of brake systems for rail vehicles out.
  • the air compressor is coaxially coupled directly to the axis of the drive rotor and an air cooler is provided.
  • the air cooler wraps around the air compressor at least partially annular and has lamellae.
  • the fins are surrounded by a cooling air flow of a fan arranged on the axis of the air compressor.
  • the US 2,917,226A discloses an air-cooled compressor with an engine cylinder and a compressor cylinder, which are arranged perpendicular to each other, and with a common crankshaft and a crankcase with a support surface for the compressor cylinder.
  • a fan is designed as a turbocompressor and supplies the engine cylinder and the compressor cylinder with cooling air.
  • the fan is arranged in a space between the engine cylinder and the compressor cylinder. The arrangement of the fan in a separate room in particular increases the space requirement of the compressor.
  • an air-cooled reciprocating compressor with a two-cylinder compressor which is driven by a motor, and having a fan for generating a cooling air flow.
  • the fan is arranged on a connecting shaft and sucks in cooling air from the environment to the cooling air in a cylinder at least partially surrounding the cooling air duct, which is designed such that all cylinders of the compressor are uniformly flowed around with cooling air to promote.
  • the fan is designed as a radial fan.
  • the invention includes the technical teaching that a fan is mounted on a connecting shaft between the engine and the compressor, which sucks cooling air from the environment and promotes in a subsequent cooling air duct, wherein the cylinder at least partially surrounding the cooling air duct is designed such that all Cylinder cylinders arranged in series of the compressor are uniformly flowed around by the cooling air.
  • the advantage of the solution according to the invention manifests itself in particular in that piston and piston ring wear as well as the wear of the lubricants at the bearing points on all cylinders are uniformly low.
  • the air-cooled piston compressor according to the invention achieves long service lives without maintenance, so that the overhaul intervals of the vehicle or the vehicle life are achieved even without replacement.
  • the compressor of the piston compressor according to the invention can be performed oil-free and produces so far advantageous oil-free compressed air, which solves the hitherto commonly occurring in commercial vehicle Verkölungs- and coking problem in the brake system.
  • the freedom from oil of the compressor also solves the problem of condensate removal and emulsion binding in the oil.
  • the air-cooled piston compressor according to the invention can be used in commercial vehicles, since this is characterized by a sufficiently high power density at high speeds.
  • the flow around the cylinder of the compressor should mainly be done by the cooling air duct from two sides and perpendicular to the direction of rotation of the compressor. As a result, the cooling air flow can be evenly distributed to the points to be cooled and divided in adaptation to the number of components to be cooled.
  • cooling air duct along the flow direction constant in order to produce a uniform flow of cooling air, but to selectively select different cross-sections.
  • the cylinder which is closest to the fan, by cross-section throttling a experience reduced cooling air supply, so that remaining cylinders, which are arranged further away from the fan, receive approximately the same cooling air as said closer cylinder.
  • This advantage can be implemented solely by appropriate dimensioning of the cooling air forming component.
  • such a cooling air channel should be formed by a two-part plastic housing, the halves of which can be easily produced in molds with a simple mold division, preferably by injection molding.
  • the cooling air channel recombine the cooling air in the flow direction downstream of the cylinders, so that said cooling air can be directed out of the hot zone of the cylinders toward the outside via a common exhaust air duct. Since thereby consumed, so heated, cooling air does not flow out at different points of the compressor unit to the outside, the spent cooling air can be purposefully dissipate to the outside, if necessary, via a further hose extension.
  • the fan arranged between the motor and the compressor should be designed in the manner of a radial fan.
  • a radial fan can be arranged in a particularly space-saving manner between the said components without the outer geometric dimensions of the entire air-cooled piston compressor increasing disproportionately.
  • such a radial fan should initially blow away the cooling air drawn radially from the axis of rotation of the compressor, after which a deflection of the cooling air flow through the cooling air duct should first be effected in the axial direction of the compressor axis in order subsequently to move away from the compressor axis in the radial direction Cylinder to blow away.
  • This special cooling air flow guide can save space to create a sufficient cooling effect.
  • the cooling air should be sucked over circumferentially distributed openings arranged in the region of the drive side shaft end of the compressor or the driven side shaft end of the motor flange to from there from the radial fan in the cooling air duct to be pressed.
  • this flange area no additional space for generating the openings for the radial fan is required.
  • this solution avoids further axial expansion of the air-cooled reciprocating compressor.
  • the filtered air passes into a connecting line between the cylinder head and the crankcase, where there flows a part for compression in the direction of the cylinder head and another part passes to the crankcase for the purpose of internal cooling of the bearings there existing.
  • the cooling air be guided into the crankcase in channels arranged separately from the cylinder.
  • the cooling air flowing through the crankcase housing internally preferably evenly to chambers and to Cooling components should be divided to achieve a particularly high efficiency of the internal cooling.
  • the intake and filtered air before being heated by the heat emitted by the cylinders through a manifold such that it goes to the cylinder head for compression and on the other hand, the crankcase for cooling on the one hand.
  • the cooling air can also be divided evenly into chambers and components to be cooled within the crankcase.
  • the cooling air duct as a soundproofing housing.
  • noise emissions can be avoided by the cooling air flow.
  • the noise protection measure already starts in the design of the cooling air duct itself.
  • cooling air duct with regard to the most compact possible structural adaptation to the existing geometric dimensions of the compressor, possibly other sound insulation measures can be taken, for example by integration of sound insulation materials. These can also cover other sound-emitting components of the crankcase, in particular cylinder heads and crankcases.
  • Fig.1 passes through an air filter 13 sucked and filtered air from the environment via an intake air line 14 in a branching therefrom connecting line 10 between the cylinder head 11 and the crankcase 12 of the compressor 2. Part of the air thus flows to the compression in the direction of the cylinder head 11 and the remaining part of the air flows into the crankcase 12 for cooling internal bearings.
  • the air drawn in from the outside is thus divided by the heat emitted by the compressor 2 before heating. Heated and therefore used cooling air leaves the cooling passage via a cooling air outlet 15.
  • a fan 4 is integrated, which is designed in the manner of a radial fan.
  • Both compressor 2 and electric motor 3 are designed in self-centering flange design and are bolted together via the intermediate fan 4. The air enters via radial openings 8.
  • the air-cooled piston compressor has inside two cylinders 1a and 1b, which are shown here from below looking.
  • the two cylinders 1a and 1b are part of the single-stage and oil-free compressor 2, which is driven by the electric motor 3.
  • the fan 4 is arranged on a driven by the motor 3 and passed through to the compressor 2 common connecting shaft 5, about which the fan 4 rotates at the engine speed to suck cooling air from the environment and to promote in a fan 4 subsequent cooling air duct 6.
  • the cooling air duct 6 which completely surrounds the cylinders 1a and 1b in the further course is designed such that the two cylinders 1a and 1b of the compressor 2, arranged in series, are uniformly circulated with cooling air, as described above.
  • the cooling air duct 6 forwards the used cooling air in the direction of flow after the two cylinders 1a and 1b into a common exhaust air duct, from where the used cooling air is led together to the outside.
  • the cooling air guide is controlled such that the fan 4 initially blows away the cooling air radially from the axis of rotation of the compressor 2, after which a deflection of the cooling air flow through the cooling air duct 6 takes place first in the axial direction of the compressor axis and then again in the radial direction of the Compressor axis away over the cylinders 1a and 1b is blown away.
  • the air-cooled piston compressor has circumferentially distributed openings 8 of a flange 9 of the motor 3, from where the cooling air enters the fan 4 to save space.
  • a connecting line 10 is provided, which directs a portion of the intake air for compression in the cylinder 1a and 1b, but branches off another part for internal cooling.
  • the filtered air to be compressed passes through the connecting line 10 in the in Fig. 3 shown region of the cylinder head 11, which covers both cylinders 1a and 1b and - not shown - includes intake and exhaust valves.
  • the other part of the filtered air flows through the crankcase 12 of the compressor 2 for internal cooling.
  • the internal bearings are supplied with cooling air.
  • a part of the cooling air channel 6 surrounds the two cylinders 1a and 1b from the outside, to ensure the desired uniform flow around the two cylinders 1a and 1b arranged in series with cooling air.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP11726126.3A 2010-06-18 2011-06-14 Luftgekühlter kolbenkompressor mit spezieller kühlluftführung Not-in-force EP2582978B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010024346A DE102010024346A1 (de) 2010-06-18 2010-06-18 Luftgekühlter Kolbenkompressor mit spezieller Kühlluftführung
PCT/EP2011/059782 WO2011157681A1 (de) 2010-06-18 2011-06-14 Luftgekühlter kolbenkompressor mit spezieller kühlluftführung

Publications (2)

Publication Number Publication Date
EP2582978A1 EP2582978A1 (de) 2013-04-24
EP2582978B1 true EP2582978B1 (de) 2018-12-19

Family

ID=44509969

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11726126.3A Not-in-force EP2582978B1 (de) 2010-06-18 2011-06-14 Luftgekühlter kolbenkompressor mit spezieller kühlluftführung

Country Status (8)

Country Link
US (1) US8992187B2 (zh)
EP (1) EP2582978B1 (zh)
JP (1) JP5896996B2 (zh)
CN (1) CN102947589B (zh)
BR (1) BR112012032373A2 (zh)
DE (1) DE102010024346A1 (zh)
RU (1) RU2567901C2 (zh)
WO (1) WO2011157681A1 (zh)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9856866B2 (en) * 2011-01-28 2018-01-02 Wabtec Holding Corp. Oil-free air compressor for rail vehicles
US20150219083A1 (en) * 2014-02-06 2015-08-06 Bendix Commercial Vehicle Systems Llc Vehicle Air Compressor Apparatus for a Heavy Vehicle Air Braking System
DE102014113598A1 (de) 2014-09-19 2016-03-24 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Mehrstufiger Kolbenkompressor mit einer äußeren Kühlluftführung
FR3042549A1 (fr) * 2015-10-20 2017-04-21 Willy Delbarba Caisson de production d'air comprime "sans huile" pour application ferroviaire
FR3042550A1 (fr) * 2015-10-20 2017-04-21 Willy Delbarba Dispositif de modification des compresseurs lubrifies en compresseurs "sans huile" embarques sur les trains
EP3232058B1 (de) * 2016-04-12 2018-08-01 J.P. Sauer & Sohn Maschinenbau GmbH Kolbenkompressor
BR102016015357B1 (pt) * 2016-06-30 2022-09-27 Schulz Compressores Ltda Compressor de ar de dois estágios
US20180112594A1 (en) * 2016-10-21 2018-04-26 Michel Arseneau Balanced rotary engine
CN107575359A (zh) * 2017-09-19 2018-01-12 瑞立集团瑞安汽车零部件有限公司 车用卧式活塞式两级空气压缩机
US10752373B2 (en) * 2017-11-16 2020-08-25 Textron Innovation Inc. Air management systems for stacked motor assemblies
CN110219793B (zh) * 2019-07-15 2024-01-26 耐力股份有限公司 一种二级压缩的无油活塞式压缩机
CN114243999B (zh) * 2021-12-24 2023-04-07 浙江安美德汽车配件有限公司 一种带有消音环结构的汽车交流发电机及其散热方法
CN115681091B (zh) * 2022-12-30 2023-07-25 武义广利机电有限公司 一种空压机机头

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DE2422448A1 (de) * 1974-05-09 1975-11-13 Knorr Bremse Gmbh Kompakte anordnung einer luftpressereinheit mit dem antriebsaggregat

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DE1089921B (de) * 1956-01-11 1960-09-29 Hans List Dipl Ing Dr Techn Luftgekuehlter Motorkompressor
US2917226A (en) * 1956-01-11 1959-12-15 List Hans Air-cooled engine compressor
US4350475A (en) * 1980-03-20 1982-09-21 International Telephone And Telegraph Corporation Integrated oil-less high capacity air compressor
JPS59183089A (ja) * 1983-03-31 1984-10-18 Jidosha Kiki Co Ltd コンプレツサ
DE10138070C2 (de) 2001-08-03 2003-05-22 Knorr Bremse Systeme Kolbenkompressor mit einem Kühlluftstrom
JP3695438B2 (ja) * 2002-10-15 2005-09-14 株式会社デンソー 移動体の冷却システム
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Also Published As

Publication number Publication date
EP2582978A1 (de) 2013-04-24
JP5896996B2 (ja) 2016-03-30
RU2013102237A (ru) 2014-07-27
CN102947589B (zh) 2016-08-03
DE102010024346A1 (de) 2011-12-22
US20130108487A1 (en) 2013-05-02
RU2567901C2 (ru) 2015-11-10
US8992187B2 (en) 2015-03-31
JP2013528745A (ja) 2013-07-11
BR112012032373A2 (pt) 2016-11-08
WO2011157681A1 (de) 2011-12-22
CN102947589A (zh) 2013-02-27

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