EP1989443A1 - Hubkolbenverdichter mit berührungsloser spaltdichtung - Google Patents
Hubkolbenverdichter mit berührungsloser spaltdichtungInfo
- Publication number
- EP1989443A1 EP1989443A1 EP07722864A EP07722864A EP1989443A1 EP 1989443 A1 EP1989443 A1 EP 1989443A1 EP 07722864 A EP07722864 A EP 07722864A EP 07722864 A EP07722864 A EP 07722864A EP 1989443 A1 EP1989443 A1 EP 1989443A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cylinder
- reciprocating compressor
- piston rod
- seal
- peripheral surface
- 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
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 11
- 230000006835 compression Effects 0.000 claims description 9
- 238000007906 compression Methods 0.000 claims description 9
- 238000005192 partition Methods 0.000 claims description 8
- 239000012530 fluid Substances 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 241000283690 Bos taurus Species 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000005056 compaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000002783 friction material Substances 0.000 description 1
- 239000003779 heat-resistant material Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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
- 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
- F04B25/00—Multi-stage pumps
-
- 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
- F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
-
- 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
- F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
- F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
Definitions
- the invention relates to a reciprocating compressor with at least two successively arranged along a cylinder axis working cylinders, in each of which a piston is guided axially movable, wherein the pistons have a common axially actuated piston rod which extends through a passage opening in a partition wall between the working cylinders , according to the preamble of claim 1.
- a contact seal in the form of a sealing ring is usually provided between the passage opening and the piston rod in order to seal the working cylinders arranged in series behind one another.
- the contact seals used so far provide friction, so that in view of the high number of compression strokes relatively large friction losses occur, which are reflected in high temperatures of up to 300 ° C in the gasket. For these reasons, a low-friction and heat-resistant material is necessary for the seals, which is correspondingly expensive.
- the present invention is the object of further developing a reciprocating compressor of the type mentioned in such a way that it is cheaper to manufacture. This object is achieved by the features of claim 1.
- the invention is based on the idea of sealing the working cylinders in the region of the piston rod exclusively by means of a non-contact seal in the form of an axial gap seal formed between a radially outer peripheral surface of the piston rod and a radially inner peripheral surface of the throughbore.
- the piston rod should extend through the through hole without interposing a separate contact seal.
- the invention uses the viscosity properties of the air, due to which compressed air with a rapid increase in pressure has a lower tendency to pass through a narrow gap than at a slower pressure increase. Against the background of the high number of compression strokes per unit time and thus rapid increase in pressure in the working cylinders, which is usual for reciprocating air compressors in compressed-air brake systems of commercial vehicles, a low leakage is consequently to be expected.
- the axially extending annular gap between the radially outer circumferential surface of the piston rod and the radially inner peripheral surface of the through bore forms a throttle, at which the gap flow loses pressure energy.
- the gap consequently lowers a high pressure level to a substantially low level as a result of the throttling.
- a labyrinth gap seal In order to form a labyrinth gap seal, it is particularly preferred to provide at least the radially inner peripheral surface of the through bore with radial grooves arranged at an axial distance from one another.
- the fluid flows from one chamber of the one higher pressure working cylinder to a lower pressure chamber of the other working cylinder through a plurality of constricted throttling points formed by the through holes between the grooves.
- the kinetic energy of the fluid flow is almost completely converted to frictional heat, i. converted into energy loss.
- the reciprocating compressor is reversing, wherein the leakage flow flowing through the gap seal from one working cylinder into the other working cylinder advantageously increases the volume of air to be compressed in the subsequent reversing movement of the piston rod.
- the invention could also be embodied in a multi-stage reciprocating compressor, which performs a multi-stage compression of the intake air and in which each cylinder is associated with a compression stage.
- the invention is used in a reciprocating compressor of an air brake system of a commercial vehicle for the reasons already mentioned above.
- FIG. 1 shows a cross-sectional view of a reciprocating compressor according to a preferred embodiment of the invention in a first position
- FIG. 2 shows the reciprocating compressor of Figure 1 in a second position.
- FIG. 3 is a cross-sectional view of a reciprocating compressor according to a further embodiment of the invention in a first position
- FIG. 4 shows the reciprocating compressor of Figure 2 in a second position.
- the reciprocating compressor 1 shown in Figure 1 is of the type in which a plurality, preferably two cylinders 2, 4 are connected in series, wherein in the cylinders 2, 4 axially guided pistons 6, 8 are connected to a common piston rod 10, which of an internal combustion engine, not shown for reasons of scale of the commercial vehicle for generating compressed air for the compressed air brake system is driven in a reversing manner.
- a common piston rod 10 which of an internal combustion engine, not shown for reasons of scale of the commercial vehicle for generating compressed air for the compressed air brake system is driven in a reversing manner.
- an independent compression operation of the input air without first the compressed air generated by the one cylinder 2 is fed into the other cylinder 4 or vice versa.
- the two cylinders 2, 4 each consist of a shell casing 12, 14, which are closed at the ends by bottom plates 18, 20, 22, 24 provided with passage openings 16.
- the cylinders 2, 4 axially interposed is also a partition 26, in which at least one continuous, each with the associated passage opening 16 in the bottom plates 18, 20, 22, 24 of the cylinder 2, 4 aligned input channel 28 and an output channel 30 and a through hole 32 is formed for the piston rod 10.
- the output channel 30 is connected via a transverse to it output connection 34 with a compressed air supply, not shown, and the input channel 28 with a likewise extending transversely to him input terminal 36 with the environment in connection.
- the through-openings 16 of the bottom plates 20, 22, which are arranged at the not the partition 26 facing the end of the shell housing 12, 14, are also aligned with input terminals 38, 42 and output terminals 40, 44, which in this bottom plates 20, 22 axially attached End pieces 46, 48 are formed.
- a central passage opening 50 for the piston rod 10 is present in the bottom plate 20 and in the end piece 48 of the one cylinder 2, which is contacted by a bovine seal 54 held in a radially inner groove 52 of the end piece 48.
- the pistons 6, 8 divide the cylinders 2, 4 respectively into a first cylinder chamber 56, 58 and into a second cylinder chamber 60, 62, the size of which depends on the respective position of the piston 6, 8.
- the ring seal 54 then serves to seal the first cylinder chamber 56 of the one cylinder 2 from the environment.
- the pistons 6, 8 also carry seals 64 at their radially outer circumferential surfaces, which seal the first cylinder chamber 56, 58 and the second cylinder chamber 60, 62 against each other.
- the previously described seals 54, 64 are all contact seals, that is, the seal 54, 64 contacts the tread associated therewith.
- an axial gap seal 66 is provided, which in the present case is preferably designed as a labyrinth gap seal.
- a smooth-cylindrical or stepped gap seal is possible.
- a narrow axial gap 66 is formed between a radially outer peripheral surface of the piston rod 10 and a radially inner circumferential surface of the through-opening 32 of the partition wall 26, which also otherwise between the two bottom plates 18, 24 and the piston rod 10 is present.
- At least the radially inner circumferential surface of the through-opening 32 of the partition wall 26 is also provided with radial grooves 68 arranged at an axial distance from one another.
- arrows 70 the flow path of compressed air
- black outlined arrows 72 the flow path sucked air
- black outlined and hatched arrows 74 the flow path of a cylinder 2, 4 in the other cylinder 2, 4 flowing air
- Arrows 76 drawn in narrow lines indicate the flow path of leakage flows.
- the air sucked into the second cylinder chambers 60, 62 as well as the leakage air 76 that has flowed into the second cylinder chamber 60 of the one cylinder 2 through the gap 66 are compressed and via the outlet connections 34, 40 supplied to the compressed air supply.
- new air is sucked into the first cylinder chambers 56, 58 via the input connections 36, 42. This in turn creates a now opposing leakage flow 76 through the gap, which feeds the first cylinder chamber 58 of the other cylinder 4 more air.
- each cylinder chamber 56, 58, 60, 62 first air is sucked in, compressed and ejected by increasing the volume, both piston surfaces of each piston 6, 8 acting in both directions acting surfaces.
- the respectively resulting leakage stream 76 is not blown out into the environment, but rather contributes to increasing the volume of air to be compressed in the subsequent reversing movement of the piston rod 10.
- the parts which are identical and function the same as in the preceding example are identified by the same reference numerals, but in each case with an additional apostrophe.
- the reciprocating compressor 1 ' has a multi-stage construction, ie during one stroke the air compressed by the one cylinder 2' in the first cylinder chamber 56 'is conducted into the second cylinder chamber 62' of the other cylinder 4 ' the Reversierhubes the piston rod 10 'to be subjected to a further compression before the compressed air is supplied via the output port 40' the compressed air reservoir.
- the first cylinder chamber 56 'of the one cylinder 2' has no output ports but is in fluid communication with the second cylinder chamber 62 'of the other cylinder 4' by means of a compressed air connection in the form of a compressed air channel 78. Furthermore, the second cylinder chamber 60 'of the one cylinder 2' with the first cylinder chamber 58 'of the other cylinder 4' through an overflow 80 'connected.
- the piston 8 'of the other cylinder 4' compresses the compressed air which is already precompressed in the second cylinder chamber 62 'by the one cylinder 2' and pushes it out into the compressed air reservoir via the outlet connection 40 '.
- the piston 6 'of the one cylinder 2' in turn pushes a small leakage flow 76 from the second cylinder chamber 60 'into the first cylinder chamber 58' of the other cylinder 4 'to assist the piston movement of the local piston 8' and to supply air for the next one To provide compaction process.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Actuator (AREA)
- Developing Agents For Electrophotography (AREA)
- Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
- Glass Compositions (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006007743.1A DE102006007743B4 (de) | 2006-02-20 | 2006-02-20 | Hubkolbenverdichter mit berührungsloser Spaltdichtung |
PCT/EP2007/001444 WO2007096127A1 (de) | 2006-02-20 | 2007-02-20 | Hubkolbenverdichter mit berührungsloser spaltdichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1989443A1 true EP1989443A1 (de) | 2008-11-12 |
EP1989443B1 EP1989443B1 (de) | 2009-08-12 |
Family
ID=37946719
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07722864A Not-in-force EP1989443B1 (de) | 2006-02-20 | 2007-02-20 | Hubkolbenverdichter mit berührungsloser spaltdichtung |
Country Status (8)
Country | Link |
---|---|
US (1) | US8147215B2 (de) |
EP (1) | EP1989443B1 (de) |
JP (1) | JP5119168B2 (de) |
CN (1) | CN101421514B (de) |
AT (1) | ATE439520T1 (de) |
BR (1) | BRPI0707982A2 (de) |
DE (2) | DE102006007743B4 (de) |
WO (1) | WO2007096127A1 (de) |
Families Citing this family (46)
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US7958731B2 (en) | 2009-01-20 | 2011-06-14 | Sustainx, Inc. | Systems and methods for combined thermal and compressed gas energy conversion systems |
US8448433B2 (en) | 2008-04-09 | 2013-05-28 | Sustainx, Inc. | Systems and methods for energy storage and recovery using gas expansion and compression |
US8474255B2 (en) | 2008-04-09 | 2013-07-02 | Sustainx, Inc. | Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange |
US8359856B2 (en) | 2008-04-09 | 2013-01-29 | Sustainx Inc. | Systems and methods for efficient pumping of high-pressure fluids for energy storage and recovery |
US8240140B2 (en) | 2008-04-09 | 2012-08-14 | Sustainx, Inc. | High-efficiency energy-conversion based on fluid expansion and compression |
US20110266810A1 (en) * | 2009-11-03 | 2011-11-03 | Mcbride Troy O | Systems and methods for compressed-gas energy storage using coupled cylinder assemblies |
EP2280841A2 (de) | 2008-04-09 | 2011-02-09 | Sustainx, Inc. | Systeme und verfahren zur energiespeicherung und & 8209;rückgewinnung unter verwendung von druckgas |
US8037678B2 (en) * | 2009-09-11 | 2011-10-18 | Sustainx, Inc. | Energy storage and generation systems and methods using coupled cylinder assemblies |
US8677744B2 (en) | 2008-04-09 | 2014-03-25 | SustaioX, Inc. | Fluid circulation in energy storage and recovery systems |
US8225606B2 (en) | 2008-04-09 | 2012-07-24 | Sustainx, Inc. | Systems and methods for energy storage and recovery using rapid isothermal gas expansion and compression |
US8479505B2 (en) | 2008-04-09 | 2013-07-09 | Sustainx, Inc. | Systems and methods for reducing dead volume in compressed-gas energy storage systems |
US8250863B2 (en) | 2008-04-09 | 2012-08-28 | Sustainx, Inc. | Heat exchange with compressed gas in energy-storage systems |
WO2009152141A2 (en) | 2008-06-09 | 2009-12-17 | Sustainx, Inc. | System and method for rapid isothermal gas expansion and compression for energy storage |
US7963110B2 (en) | 2009-03-12 | 2011-06-21 | Sustainx, Inc. | Systems and methods for improving drivetrain efficiency for compressed gas energy storage |
US8104274B2 (en) | 2009-06-04 | 2012-01-31 | Sustainx, Inc. | Increased power in compressed-gas energy storage and recovery |
DE102009047744A1 (de) * | 2009-12-09 | 2011-06-16 | BSH Bosch und Siemens Hausgeräte GmbH | Verdichter mit einer Pumpkammer |
US8191362B2 (en) | 2010-04-08 | 2012-06-05 | Sustainx, Inc. | Systems and methods for reducing dead volume in compressed-gas energy storage systems |
US8171728B2 (en) | 2010-04-08 | 2012-05-08 | Sustainx, Inc. | High-efficiency liquid heat exchange in compressed-gas energy storage systems |
US8234863B2 (en) | 2010-05-14 | 2012-08-07 | Sustainx, Inc. | Forming liquid sprays in compressed-gas energy storage systems for effective heat exchange |
US8495872B2 (en) | 2010-08-20 | 2013-07-30 | Sustainx, Inc. | Energy storage and recovery utilizing low-pressure thermal conditioning for heat exchange with high-pressure gas |
US8578708B2 (en) | 2010-11-30 | 2013-11-12 | Sustainx, Inc. | Fluid-flow control in energy storage and recovery systems |
CN102072134B (zh) * | 2011-01-26 | 2013-03-13 | 浙江鸿友压缩机制造有限公司 | 一种滑管式空气压缩机 |
US9856866B2 (en) | 2011-01-28 | 2018-01-02 | Wabtec Holding Corp. | Oil-free air compressor for rail vehicles |
US20120282114A1 (en) * | 2011-05-06 | 2012-11-08 | Tonand Brakes Inc. | Air pump |
EP2715075A2 (de) | 2011-05-17 | 2014-04-09 | Sustainx, Inc. | Systeme und verfahren für effizienten zweiphasigen wärmetransfer in druckluftenergiespeichersystemen |
US20130091835A1 (en) | 2011-10-14 | 2013-04-18 | Sustainx, Inc. | Dead-volume management in compressed-gas energy storage and recovery systems |
TWM423162U (en) * | 2011-10-21 | 2012-02-21 | Chanto Air Hydraulics Co Ltd | Pressure boosting cylinder with separated oil and gas |
TWM423163U (en) * | 2011-10-21 | 2012-02-21 | Chanto Air Hydraulics Co Ltd | Pressure boosting cylinder with invisible loop |
US20130280095A1 (en) * | 2012-04-20 | 2013-10-24 | General Electric Company | Method and system for reciprocating compressor starting |
US9429146B2 (en) * | 2012-04-25 | 2016-08-30 | John J. Fong | Pressure intensifier |
KR20130134345A (ko) * | 2012-05-30 | 2013-12-10 | 주식회사 미래브이씨 | 전자기식 공기 압축기 |
JP2016500549A (ja) * | 2012-11-05 | 2016-01-14 | オースティン バイオイノベーション インスティテュート イン アクロンAusten Bioinnovation Institute In Akron | 低容量シリンジピペット |
KR101384226B1 (ko) | 2012-12-27 | 2014-04-14 | 재단법인 전북자동차기술원 | 전자기식 공기 압축기 |
DE102013101502A1 (de) | 2013-02-14 | 2014-08-14 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Luftversorgungsanlage mit elektronischem Umrichter |
KR101556612B1 (ko) | 2013-09-17 | 2015-10-01 | 이종희 | 편방향 피스톤 로드를 가지는 왕복동 실린더 |
KR20160127927A (ko) * | 2015-04-28 | 2016-11-07 | 임주생 | 병렬 인버터 회로를 적용한 전자기식 공기 압축기 |
US10001120B2 (en) | 2015-08-31 | 2018-06-19 | Bendix Commercial Vehicle Systems Llc | Lightweight compressor crankcase assembly and method |
CN105402102B (zh) * | 2015-12-11 | 2023-08-01 | 珠海格力电器股份有限公司 | 一种单缸往复活塞式压缩机 |
CN106439028B (zh) * | 2016-12-05 | 2018-06-01 | 中国航天空气动力技术研究院 | 平衡式运动件密封结构 |
CN107693331B (zh) * | 2017-11-15 | 2020-04-03 | 张云 | 一种用于排痰背心的振动气体发生装置 |
CN107929029B (zh) * | 2017-11-15 | 2020-01-31 | 盐城市艾琪儿妇产医院有限公司 | 一种排痰机气体振动发生装置 |
CN107638283B (zh) * | 2017-11-15 | 2019-09-24 | 河南省人民医院 | 一种可调节排痰机振动气体发生装置 |
CN108061030A (zh) * | 2017-12-12 | 2018-05-22 | 九江大安自控工程有限公司 | 一种往复式压缩机上的余隙气量调节系统 |
EP3718844B1 (de) * | 2019-04-05 | 2023-02-08 | KNORR-BREMSE Systeme für Nutzfahrzeuge GmbH | Kolbenanordnung für ein entladungsventil eines luftkompressors |
CN110454354B (zh) * | 2019-08-21 | 2020-11-20 | 浙江西菱股份有限公司 | 一种基于电机传动的光伏铸锭使用的真空泵 |
CN113969881A (zh) * | 2021-11-25 | 2022-01-25 | 郑州铁路职业技术学院 | 一种无电机直动型无油活塞式空气压缩机 |
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-
2006
- 2006-02-20 DE DE102006007743.1A patent/DE102006007743B4/de not_active Expired - Fee Related
-
2007
- 2007-02-20 AT AT07722864T patent/ATE439520T1/de active
- 2007-02-20 EP EP07722864A patent/EP1989443B1/de not_active Not-in-force
- 2007-02-20 WO PCT/EP2007/001444 patent/WO2007096127A1/de active Application Filing
- 2007-02-20 BR BRPI0707982-6A patent/BRPI0707982A2/pt not_active IP Right Cessation
- 2007-02-20 JP JP2008555685A patent/JP5119168B2/ja not_active Expired - Fee Related
- 2007-02-20 CN CN2007800127886A patent/CN101421514B/zh not_active Expired - Fee Related
- 2007-02-20 US US12/279,966 patent/US8147215B2/en not_active Expired - Fee Related
- 2007-02-20 DE DE502007001299T patent/DE502007001299D1/de active Active
Non-Patent Citations (1)
Title |
---|
See references of WO2007096127A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN101421514A (zh) | 2009-04-29 |
DE502007001299D1 (de) | 2009-09-24 |
EP1989443B1 (de) | 2009-08-12 |
US8147215B2 (en) | 2012-04-03 |
DE102006007743A1 (de) | 2007-08-23 |
BRPI0707982A2 (pt) | 2011-05-17 |
US20090220364A1 (en) | 2009-09-03 |
JP5119168B2 (ja) | 2013-01-16 |
ATE439520T1 (de) | 2009-08-15 |
JP2009527683A (ja) | 2009-07-30 |
CN101421514B (zh) | 2011-04-20 |
DE102006007743B4 (de) | 2016-03-17 |
WO2007096127A1 (de) | 2007-08-30 |
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