EP1789681B1 - Kolbenkompressor mit einem internen kühlluftstrom im kurbelgehäuse - Google Patents

Kolbenkompressor mit einem internen kühlluftstrom im kurbelgehäuse Download PDF

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Publication number
EP1789681B1
EP1789681B1 EP05778871A EP05778871A EP1789681B1 EP 1789681 B1 EP1789681 B1 EP 1789681B1 EP 05778871 A EP05778871 A EP 05778871A EP 05778871 A EP05778871 A EP 05778871A EP 1789681 B1 EP1789681 B1 EP 1789681B1
Authority
EP
European Patent Office
Prior art keywords
crankcase
cooling air
cylinder head
cylinder
cooling
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.)
Active
Application number
EP05778871A
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German (de)
English (en)
French (fr)
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EP1789681A1 (de
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
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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 EP1789681A1 publication Critical patent/EP1789681A1/de
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Publication of EP1789681B1 publication Critical patent/EP1789681B1/de
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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
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings

Definitions

  • the invention relates to a reciprocating compressor, in particular a reciprocating compressor for generating compressed air, which comprises at least one piston connected to a roller bearing with a crankshaft connected to a roller bearing which performs a lifting movement in an associated cylinder and the compression of a connection unit integrated in the cylinder head
  • Intake air causes, via an inlet valve due to a generated by the piston movement negative pressure in the crankcase cooling air from the intake into the crankcase and escapes due to the overpressure generated in the crankcase via an exhaust valve from the crankcase and thus an internal cooling air flow in the crankcase can be generated ,
  • Such reciprocating compressors are usually used wherever compressed air is needed, but the compressed air generating unit must be space-saving and thus small-sized while having high power densities, which are mainly used in commercial vehicles or rail vehicles such reciprocating compressors.
  • the compressed air generated by the piston compressor is increasingly used in addition to the operation of the brake system for the operation of the air suspension system.
  • the high pressures required by the air suspension within short intervals of time can be generated with such reciprocating compressors.
  • oil-lubricated reciprocating compressors were used in commercial vehicles in particular, oil-free compressor concepts could not prevail because the necessary component service life could not be achieved due to the high component temperatures resulting from the high power density in the smallest possible space.
  • Novel compressor concepts based on reciprocating compressors allow oil-free operation if they are provided with a cooling air flow rate.
  • the oil-free operating mode was developed especially for maintenance and environmental reasons.
  • the prior art shows various concepts, wherein active cooling components such as fan means are used for heat dissipation.
  • the DD 238 645 A1 discloses a solution in which the air moved by a fan air flows through both the compressor unit and the drive motor.
  • a disadvantage of this variant is in addition to the noise of the contaminated outdoor air, which is passed through the crankcase, which can be deposited impurities and can also form accumulations of water in the crankcase due to the pressure changes.
  • an external filter system and possibly a Wasserabscheidesystem is required, which, however, increases the maintenance and service intervals shortened.
  • the DE 101 38 070 C2 shows a reciprocating compressor according to the preamble of claim 1, wherein the periodic pressure fluctuation generated in the crankcase by the lifting movement of the working piston via a valve pairing is used to generate a cooling air flow in the crankcase.
  • an inlet valve opens when the piston performs the lifting movement in the direction of the cylinder head and increases the volume of the crankcase, because the resulting negative pressure air flows through the inlet valve into the crankcase.
  • the downward movement creates an overpressure in the crankcase and a remote from the inlet valve outlet valve opens.
  • the possibility is further used to remove the cooling air of the intake to make even for the cooling air flow of the crankcase already purified air available.
  • the intake air is freed of impurities by upstream cleaning agents, which occupies an essential position especially in commercial vehicle construction, since the operating environment is usually heavily polluted.
  • upstream cleaning agents which occupies an essential position especially in commercial vehicle construction, since the operating environment is usually heavily polluted.
  • the dew point of the water vapor contained in the air can be reached, which causes a condensation of the water vapor and thus water formation in the system.
  • isolated water separators may be upstream of the compressor means. In a tap of the cooling air from the intake pipe with an addition to the filter system upstream water separator is also ensured that when flowing through the filtered and dried cooling air through the crankcase there can form no amounts of water that would cause considerable damage, in particular to the bearings.
  • the principle of the internal pump for cooling air promotion based on the piston movement, can be used because the low pressure stage has a large piston area and the high pressure stage via a small piston area, which also over the crank stroke due to the piston surface difference also a periodically changing pressure curve in the Crankcase is created.
  • a refrigerant compressor which comprises a motor unit and a compressor unit. Cooling air is supplied to the compressor housing via a suction gas pipe and a shut-off valve, with part of this cooling air being conducted via the engine unit, while the remaining part of the cooling air passes directly into the compressor unit. The cooling air used for cooling the engine is then also led to the compressor unit.
  • a disadvantage of such a design is that the cooling air routed via the engine is also heated to a high degree, and therefore, in the following, sufficient cooling of the roller bearings in the crankcase is no longer possible.
  • crankcase ventilation for an oil-free piston compressor which conveys a clean cooling air into the crankcase for cooling thermally stressed components in the crankcase, in particular rolling bearings, and which has a low temperature on entry into the crankcase ,
  • the invention includes the technical teaching that the diversion of the cooling air from the intake pipe itself or in the cylinder head is arranged and the cooling air via at least one outside of the cylinder passing pipe connection between the cylinder head and the crankcase is adopted to prevent heating of the cooling air ,
  • This solution has the advantage of not exposing the cooling air to the heat generated in the area of the connection unit, but to branch off the intake line away from this heat source and lead directly into the crankcase.
  • the previously known solution which initially leads the cooling air through channels on the lateral surface of the cylinder, causes a heating of the cooling air, even before it reaches the crankcase.
  • the cooling of the Cylinder and the cylinder head can be carried out in the inventive solution by a second, separate cooling air flow, so that must not be waived cooling of these components.
  • the pipe connection is arranged on the outside of the housing and passes the cooling air to the components with the highest temperatures, such as cylinder and cylinder head. Due to the freely arranged pipe connection, the temperature of the cooling air can also be further reduced via a heat dissipation based on convection via the pipe surface, before it enters the crankcase.
  • Another measure improving the invention provides that the guided over the at least one pipe joint cooling air at a point in the crankcase is introduced, in the vicinity of the thermally loaded components such as the rolling bearings are arranged in the crankcase and the cooling air flows through the crankcase (2) diagonally to achieve maximum cooling effect. Due to the variable design of the pipe connection, it is possible to choose the entry point of the cooling air into the crankcase so that the components to be cooled are located directly in the cooling air flow. This advantage can be applied precisely in the case of the roller bearings, which are arranged fixedly in the crankcase, such as the crankshaft bearing in the crankcase, in that the cooling air flows directly against the roller bearings and cools them.
  • connection for the cooling air between the cylinder head and the crankcase consists of at least two individually arranged and mutually parallel pipe connections to increase the available pipe surface for cooling.
  • the advantage of the arrangement of at least two pipe connections is in addition to the enlarged surface for convection cooling also the possibility to arrange the pipe connections so symmetrical that the entry points of the cooling air supply both the engine side and the end arranged in the crankcase bearings of the crankshaft with cooling air directly.
  • the cooling air is guided from a cooling air chamber in the cylinder head into the pipe joint, wherein the cooling air chamber is filled via the inlet valve with cooling air and distributes it to the pipe joints. In general, it is sufficient if two pipe connections are provided.
  • An advantage of a lamella valve is the low design complexity and high reliability. Due to the small footprint and the flat design of a louver valve, this can be optimally integrated in the cooling air chamber of the cylinder head or in the valve plate, adjacent to the main inlet valve of the compressor.
  • a screw means of the crankcase, cylinder and cylinder head consists of at least one tie rod extending through the pipe joint or a screw means of crankcase, cylinder and cylinder head consists of the pipe joint.
  • the number of items can be reduced by the pipe connection in addition to the cooling air flow also fulfills the mechanical function of the screw.
  • a separate screw connection of the crankcase, cylinder and cylinder head can be omitted and the pipe connections are clamped mechanically with the tie rods, with the bracing additionally a sealing effect between the pipe joint and the crankcase or the cylinder head can be achieved because the pipe connection is pressure-loaded by the tension in the longitudinal direction.
  • this is mechanically clamped such that both the mechanical tensile forces are absorbed and the function of the cooling air guide can be adopted and thus the number of individual parts can be reduced.
  • the transition from the pipe joint to the crankcase and the cylinder head has at least one sealing element in order to avoid leaks.
  • This sealing element can be made of a plastic-based O-ring consist of or be made of a comparable sealing element such as a brass sealing ring, as this is given a higher thermal stability and improved aging resistance.
  • An additional measure to further improve the cooling of the entire reciprocating compressor is that the cooling air passes before entering the pipe connection via at least one flow channel within the cylinder head and / or the cylinder and causes cooling, wherein the temperature of the cooling air in the subsequent flow through the pipe connection
  • an active cooling unit or based on convection cooling is again reduced and that the pipe joint on the lateral surface has heat sinks to enhance the heat dissipation by convection.
  • This principle of intercooling allows the entry of low temperature cooling air into the crankcase, although previously the thermally stressed region of the cylinder and the cylinder head is previously cooled with the same cooling air.
  • the flow channel not shown in the cylinder jacket and / or in the cylinder head thereby passes the cooling air past the thermally loaded components and is then guided into the pipe joint.
  • heat sinks are provided on the outside of the pipe connection in order thereby to increase the surface area and to enhance the effect of the convection cooling. Cooling by active cooling media is also applicable, but they require additional design effort.
  • a cross section through a reciprocating compressor with a laterally arranged pipe connection A cross section through a reciprocating compressor with a laterally arranged pipe connection.
  • the reciprocating compressor 1 shown in the figure consists of a crankcase 2, a cylinder 3 and a cylinder head 4, which is composed of a valve plate 5 and a connection unit 6.
  • a piston 7 carries out a lifting movement, which is generated via a crankshaft 8 and a connecting rod 9 arranged as a connection.
  • the air located in the cylinder 3 is drawn by the downward movement of the piston 7 in the cylinder 3 and compressed during the upward movement of the piston 7.
  • the terminal unit 6 has a main inlet valve and a main outlet valve in addition to a suction line 11 and an outlet line 12, wherein the main inlet valve is in the downward position of the piston 7 in its open position and air from the intake pipe 11 moves into the cylinder 3 and closes in the upward movement.
  • the main exhaust valve is during the downward movement of the piston 7 in the closed position, and opens in the upward movement of the piston 7, whereby the thus compressed air is led out of the cylinder 3 via the output line 12 and an external consumer feeds.
  • the cylinder 3 is detachably connected via a screw 18 with the crankcase 2.
  • the crankshaft 8 is rotatably supported by rolling bearings 10 in the crankcase 2, wherein the connecting rod 9 is also rotatably mounted on roller bearings 10 'on the cranked portion of the crankshaft 8.
  • sealing elements 17 are arranged such that they seal the transitions of the pipe joint 15 to valve plate 5 and crankcase 2 and prevent an air side stream and thus the ingress of impurities.
  • cooling air thus flows directly into the crankcase and leaves it again via the outlet valve 14 when the piston 7 in the cylinder 3 makes a downward movement and thus causes an overpressure in the crankcase 2.
  • the rolling bearings 10 in the crankcase 2 are directly cooled by the incoming cooling air, wherein the cooling air is introduced in a manner not shown here with two symmetrically arranged pipe joints 15 in such a way in the crankcase 2, that the rolling bearings 10 are directly flowed with cooling air.
  • the roller bearing 10 'between the crankshaft 8 and the connecting rod 9 also undergoes cooling through contact with the cooling air in the crankcase 2.
  • the exhaust valve 14 is disposed on the bottom side of the crankcase 2 to remove any impurities and water accumulations from the crankcase 2 and to minimize the burden of external contamination due to the bottom-side arrangement.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP05778871A 2004-09-02 2005-08-31 Kolbenkompressor mit einem internen kühlluftstrom im kurbelgehäuse Active EP1789681B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004042944A DE102004042944B4 (de) 2004-09-02 2004-09-02 Kolbenkompressor mit einem internen Kühlluftstrom im Kurbelgehäuse
PCT/EP2005/009367 WO2006024510A1 (de) 2004-09-02 2005-08-31 Kolbenkompressor mit einem internen kühlluftstrom im kurbelgehäuse

Publications (2)

Publication Number Publication Date
EP1789681A1 EP1789681A1 (de) 2007-05-30
EP1789681B1 true EP1789681B1 (de) 2009-07-29

Family

ID=35124312

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05778871A Active EP1789681B1 (de) 2004-09-02 2005-08-31 Kolbenkompressor mit einem internen kühlluftstrom im kurbelgehäuse

Country Status (11)

Country Link
US (1) US8308447B2 (pt)
EP (1) EP1789681B1 (pt)
CN (1) CN100501160C (pt)
AT (1) ATE438036T1 (pt)
BR (1) BRPI0514877B1 (pt)
CA (1) CA2578843A1 (pt)
DE (2) DE102004042944B4 (pt)
HK (1) HK1110374A1 (pt)
MX (1) MX2007002495A (pt)
RU (1) RU2362051C2 (pt)
WO (1) WO2006024510A1 (pt)

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DE102006012174A1 (de) * 2006-03-16 2007-09-20 Pari GmbH Spezialisten für effektive Inhalation Inhalationstherapiegerätekompressor
DE102007042318B4 (de) * 2007-09-06 2017-11-30 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kompakter trockenlaufender Kolbenverdichter
EP2161451A1 (de) * 2008-09-09 2010-03-10 HAUG Kompressoren AG Kolbenkompressor
CN101699069B (zh) * 2009-11-16 2012-05-02 浙江鸿友压缩机制造有限公司 低噪声往复活塞式空气压缩机
CN101776061A (zh) * 2010-03-05 2010-07-14 浙江鸿友压缩机制造有限公司 活塞阀控进气无油润滑空气压缩机
DE102010024346A1 (de) 2010-06-18 2011-12-22 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Luftgekühlter Kolbenkompressor mit spezieller Kühlluftführung
US9856866B2 (en) 2011-01-28 2018-01-02 Wabtec Holding Corp. Oil-free air compressor for rail vehicles
CN102822523A (zh) * 2011-02-24 2012-12-12 张永升 具有内循环管路装置的低油耗活塞式空气压缩机
TWI405899B (zh) * 2011-05-23 2013-08-21 Sanyang Industry Co Ltd Cleaning device for stepless speed change system
CN102359444B (zh) * 2011-11-01 2014-08-13 中国石油集团济柴动力总厂成都压缩机厂 适用于天然气工业的高速大功率往复活塞式压缩机
DE102013101498A1 (de) * 2013-02-14 2014-08-28 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Kurbeltriebanordnung eines vorzugsweise ölfreien Kolbenverdichters
US20150322937A1 (en) * 2014-05-09 2015-11-12 Westinghouse Air Brake Technologies Corporation Oil-free compressor crankcase cooling arrangement
RU2622584C1 (ru) * 2016-03-15 2017-06-16 Теймураз Нодарович Кечиян Способ повышения давления газов
US11002270B2 (en) 2016-04-18 2021-05-11 Ingersoll-Rand Industrial U.S., Inc. Cooling methods for electrically operated diaphragm pumps
GB2551251A (en) 2016-04-18 2017-12-13 Ingersoll-Rand Company Cooling methods for electrically operated diaphragm pumps
CN107218204B (zh) * 2017-07-11 2020-06-23 江苏恒达动力科技发展股份有限公司 一种带有压缩空气缓冲的曲轴箱
US11333140B2 (en) * 2019-06-11 2022-05-17 Caterpillar Inc. Cooling block for multi-cylinder air compressor
CN111828285B (zh) * 2020-07-02 2021-01-08 北京建筑大学 一种空压机机体、冷却气管及空压机

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Also Published As

Publication number Publication date
US20070292289A1 (en) 2007-12-20
DE502005007800D1 (de) 2009-09-10
EP1789681A1 (de) 2007-05-30
ATE438036T1 (de) 2009-08-15
BRPI0514877A (pt) 2008-06-24
MX2007002495A (es) 2007-10-10
CN101010511A (zh) 2007-08-01
BRPI0514877B1 (pt) 2018-03-13
RU2007111955A (ru) 2008-10-10
HK1110374A1 (en) 2008-07-11
US8308447B2 (en) 2012-11-13
DE102004042944B4 (de) 2009-09-10
DE102004042944A1 (de) 2006-03-23
CA2578843A1 (en) 2006-03-09
WO2006024510A1 (de) 2006-03-09
CN100501160C (zh) 2009-06-17
RU2362051C2 (ru) 2009-07-20

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