EP0804684A1 - Verdichter - Google Patents
VerdichterInfo
- Publication number
- EP0804684A1 EP0804684A1 EP95939216A EP95939216A EP0804684A1 EP 0804684 A1 EP0804684 A1 EP 0804684A1 EP 95939216 A EP95939216 A EP 95939216A EP 95939216 A EP95939216 A EP 95939216A EP 0804684 A1 EP0804684 A1 EP 0804684A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- compressor according
- compressor
- working medium
- space
- 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
- 230000033001 locomotion Effects 0.000 claims abstract description 18
- 238000007906 compression Methods 0.000 claims description 31
- 230000006835 compression Effects 0.000 claims description 30
- 238000007599 discharging Methods 0.000 claims 1
- 238000013461 design Methods 0.000 description 22
- 238000011161 development Methods 0.000 description 9
- 230000018109 developmental process Effects 0.000 description 9
- 238000001816 cooling Methods 0.000 description 8
- 230000008901 benefit Effects 0.000 description 6
- 238000004939 coking Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 4
- 238000010276 construction Methods 0.000 description 4
- 230000006978 adaptation Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 239000002245 particle Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000012549 training Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
- F02B75/246—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type with only one crankshaft of the "pancake" type, e.g. pairs of connecting rods attached to common crankshaft bearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
- F01B9/026—Rigid connections between piston and rod; Oscillating pistons
-
- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
-
- 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
-
- 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
- F04B39/0016—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 with valve arranged in the piston
-
- 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
-
- 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
- F04B39/126—Cylinder liners
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18056—Rotary to or from reciprocating or oscillating
- Y10T74/18248—Crank and slide
- Y10T74/18256—Slidable connections [e.g., scotch yoke]
Definitions
- the invention relates to a compressor or compressor for compressing a working medium, in particular for generating compressed air, with at least one piston which can be moved back and forth in a working space for compressing the working medium, and a drive device for reciprocating the piston as well as with a feed device and a discharge device for feeding or removing the working medium.
- Compressible substances such as gases or vapors are used as working media, air being usually compressed in the conventional compressors. This compressed air is e.g. used in trucks as a transmission medium in brake devices.
- the object of the invention is to provide a compressor in which it is possible to seal the working chamber and the crank chamber from one another in a simple manner.
- crank loop drive is used as the drive device.
- crank loop drives for internal combustion engines.
- DE 32 18 311 C2 shows a crank loop drive which is particularly suitable for a two-stroke internal combustion engine. ne is provided, which is also operable without oil lubrication.
- DE 34 47 663 AI a multi-cylinder internal combustion engine is known, in which the conversion into a rotary movement takes place by means of a crank loop drive.
- Another embodiment of such a crank loop drive is described in DE 43 07 205 AI. With regard to the precise principle of operation and the mode of operation of the crank loop drive, reference can therefore be made in full to the publications mentioned.
- crank loop drive therefore offers the advantage that the rotary movement of a crankshaft is converted into a pure longitudinal movement of the pistons. This enables the sliding surface between the piston shaft and the bearing point in the compressor block to be securely sealed. If, according to the teaching of the invention, a crank loop drive is provided as the drive device of the compressor, it can thus be ensured that the working space is always sufficiently sealed from the crank space, which has the decisive advantage that the working space on both sides of the piston for the compression process can be used and that no oil particles can get into the work area.
- the workspace can be specified in claim 2
- both sides of the piston serve on the one hand as a pre-compression space and on the other hand as a main compression space, ie the piston movement can serve, for example, as an ejection movement and at the same time for suction. of still uncompressed working oil on the piston rear.
- the result is a two-stage compressor that first pre-compresses the working medium and then ejects it in a main compression stroke. While in the conventional single-stage compressor the dead volume that occurs due to component tolerances and the thermal expansion significantly deteriorates the delivery rate, the work of the dead volume is almost insignificant for the two-stage compressor, since the back expansion of the working medium there directly for pre-compression is being used.
- the compression energy introduced into the dead volume is therefore not lost and therefore enables a considerably higher degree of efficiency or delivery rate.
- increase the delivery rate compared to 55% for a conventional series compressor to 80% for a crank-loop compressor with pre-compression.
- the degree of delivery is determined in the arrangement according to the invention by the volume of the precompression space.
- the dead volume that occurs here is, however, of less importance due to the lower pressure, since the re-expanding damage volume is not so extensive.
- the working medium in the pre-compression chamber is almost completely transferred to the main compression chamber and the dead volume that occurs there uses the energy introduced therein to support the return movement of the piston and thus for the pre-compression.
- valve devices can also be designed to be very simple and reliable. The design effort is thus significantly reduced and the structural design is considerably simplified.
- the fact that the space on both sides of the piston is used as a work space results in the advantage that the feed device is spatially separated from the discharge device, e.g. an arrangement on axially opposite sides of the piston according to the development of the invention specified in claim 4 is made possible.
- the feed device can thus e.g. be arranged in the compressor block, while the discharge device is provided in the cylinder head and the further line routing can be chosen as desired.
- the heating of the supplied working medium can thus be avoided by the removed working medium heated due to the printing process.
- a main design problem of conventional compressors is thus eliminated and the construction of the compressor is considerably simplified.
- An annular feed groove directed towards the working space in accordance with the development of the invention specified in claim 5 enables the sucked-in working medium to flow evenly into the pre-compression space.
- the piston is designed as a circular disk according to the further development of the invention specified in claim 6, this allows the same to be produced simply and inexpensively. Furthermore, the moving masses and the size of the friction surfaces can be kept small.
- the disk-shaped piston is preferably designed with a multiplicity of openings or passage holes, it is possible to dispense with overflow channels in the cylinder head.
- the working medium can flow in directly from the pre-compression chamber through the openings in the piston be transferred to the main compression room.
- the constructive outlay for the cylinder head is significantly reduced. Further, aconss ⁇ of the piston is achieved by the reduction in openings with which the size of the b edorfden mass is smaller.
- a uniform distribution of the openings on the piston according to the development of the invention specified in claim 8 enables a balanced pressure distribution on the piston.
- the load on the bearing is thus not one-sided and the wear on the running surfaces remains low.
- the piston preferably has a valve device at its openings, overflow of the working medium can be made possible, and at the same time the pre-compression chamber can be separated from the main compression chamber.
- the working medium can only flow into the main compression chamber while the opposite direction is blocked. A separation of the compression spaces is thus achieved in a simple manner and at the same time the possibility of direct transfer of the working medium is used without a detour via channels in the cylinder head. This further simplifies the design of the compressor.
- Pistons can be driven. It is therefore possible to create a double compression cylinder with a simple design and to increase the output significantly.
- This design also has the advantage that with only a few additional parts, e.g. a 2-, 4- or 8-cylinder version of the compressor is made possible.
- the compressor can thus be adapted to corresponding performance requirements with little effort.
- the design as a multi-cylinder arrangement also leads to a more uniform course of the drive torque in relation to the conventional compressors, which are usually only single-cylinder due to the size and the design effort.
- crank loop drive allows a low piston speed, which enables dry running. Furthermore, only small masses are moved and there are only slight fluctuations in tangential force, which is why the strength requirements for the structure are significantly reduced.
- the simple construction of the compressor according to the invention which has only a few components, permits inexpensive and simple manufacture and assembly. As the construction space comparison with conventional compressors shows, a compact design with small dimensions can also be achieved. Furthermore, a flexible redesign, e.g. the inlet device, depending on the conditions of the place of use without great design effort.
- FIG. 2 shows a sectional illustration of a compressor with a simplified drive device
- FIG. 3 shows a comparison of the installation space with a conventional compressor.
- a compressor 1 has a compressor block 2, a crank loop drive 3 and two cylinder heads 4.
- the compressor block 2 has an inlet pipe sleeve 5 and an inlet line system 6 as a supply device for the working medium (namely air), and an outlet pipe sleeve 7 and an outlet line system 8 as a discharge device for the compressed or compressed working medium; an inner cavity 9 is also provided.
- crank loop drive 3 In the inner cavity 9 of the compressor block 2, the crank loop drive 3 is accommodated. This has a crank loop frame 10 on which a link 11 is formed. A sliding block 12 is guided in the backdrop 11. The sliding block 12 is guided by a crank pin 13 mounted off-center on a crankshaft and thus converts the e.g. rotary motion applied by the crankshaft of an internal combustion engine of a truck into a longitudinal movement of the crank loop frame 10 .mu.m.
- crank loop frame 10 two disk-shaped pistons 14 are attached to the crank loop frame 10. These lie on one axis and face each other. Since a crank loop is used as the drive, the two pistons 14 perform a linear back and forth movement.
- a respective working space 15 an d an outlet channel 16 is formed in the cylinder heads 4.
- a liner 17 is fastened in the working space 15.
- air is drawn into the working space 15 by the piston movement.
- the air flows via the inlet pipe sleeve 5 and the inlet line system 6 via an annular feed groove 6a through a valve plate 18 arranged on the compressor block 2 into the working space 15.
- Valve fins are arranged on the valve plate 18 in such a way that they only flow in one direction Allow work space 15 inside.
- the piston 14 then reverses its direction of movement and moves towards the annular feed groove 6a of the inlet line system 6.
- the valve plate 18 attached there prevents the air from flowing back. This is thus pre-compressed and flows through openings 19 in the piston 14 and a valve device 20 arranged behind it into the working space which now arises on the other side of the piston.
- the centers of the openings 19 are arranged on the same radius around the center of the disk-shaped piston 14 and are evenly distributed thereon.
- the extent of the delivery quantity of the compressor 1 is determined by the quantity of the working medium drawn in in the 1st stage, the pre-compression stage. Since the working medium is not so highly compressed at this stage, the proportion of back expansion from the dead spaces is also lower. The arrangement thus receives a much higher degree of delivery.
- valve plate 21 is pretensioned in such a way that it only opens at a certain, presettable pressure.
- the valve plate 21 When the valve plate 21 is opened, the compressed air is finally expelled into the outlet channel 16 and flows out via the outlet line system 8 of the compressor block 2 through the outlet pipe sleeve 7 as compressed air (compressed air).
- pre-compressed air is then introduced through the openings 19 and the valve device 20 of the piston 14 into the working space.
- a piston shaft 22 can be guided in the compressor block 2 without problems and can be sealed by means of a sealing device 23 with respect to the inner cavity 9 of the compressor block 2, which houses the crank loop drive 3. It can thus be avoided that oil particles get into the working space 15 and cause oil coking of the valve devices. This means that devices for cooling the compressor are not required and the design effort is significantly reduced.
- the compression spaces on both sides of the piston 14 are sealed off from one another by a further sealing device 24, which is arranged on the circumference of the piston 14.
- a second compressor of the same type can easily be connected to the drive shaft of the compressor according to the invention with a few other components and thus e.g. a cylinder star arrangement are formed.
- An 8-cylinder compressor can be formed from two 4-cylinder compressors connected to the drive shaft, and further combination possibilities are open at any time. An individual adaptation to the respective performance requirements is therefore possible without great effort.
- the simple design of the compressor also enables adaptation to individual circumstances without major design changes.
- Another arrangement e.g. the inlet or outlet device can be carried out with little effort.
- the crank loop drive 3 also has coated scenes 11, which allow the sliding block 12 to run dry.
- pistons 30 are driven directly by a crank pin 33 which is mounted off-center on a crankshaft, which is only shown in the drawing.
- Piston shaft 31 formed sliding surface 32 as a counter surface for the crank pin 33.
- a backdrop and a sliding block are not necessary here.
- the piston shaft 31 is formed in the area of the sliding surface 32 such that a spring 34 can tension the piston 30 against the crank pin 33. This also guarantees the piston return movement.
- the remaining parts, in particular the compression section and the cylinders, correspond to those of the first exemplary embodiment, so that reference is made to this.
- FIG 3 shows the compact design of the compressor according to the invention in a comparison of the installation space with a conventional compressor of the same output. It is clear from this comparison that the compressor according to the invention takes up significantly less space.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19501220 | 1995-01-17 | ||
DE19501220A DE19501220A1 (de) | 1995-01-17 | 1995-01-17 | Verdichter |
PCT/DE1995/001706 WO1996022464A1 (de) | 1995-01-17 | 1995-12-01 | Verdichter |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0804684A1 true EP0804684A1 (de) | 1997-11-05 |
EP0804684B1 EP0804684B1 (de) | 1999-03-10 |
Family
ID=7751660
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95939216A Expired - Lifetime EP0804684B1 (de) | 1995-01-17 | 1995-12-01 | Verdichter |
Country Status (4)
Country | Link |
---|---|
US (1) | US5879145A (de) |
EP (1) | EP0804684B1 (de) |
DE (2) | DE19501220A1 (de) |
WO (1) | WO1996022464A1 (de) |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19706066A1 (de) | 1997-02-17 | 1997-11-20 | Hans Dipl Ing Unger | Kompressor, insbesondere für die Drucklufterzeugung in Kraftfahrzeugen |
DE19739662A1 (de) * | 1997-09-10 | 1999-03-11 | Bosch Gmbh Robert | Ventilanordnung in einem Kolbenverdichter |
DE19755771A1 (de) * | 1997-12-16 | 1999-06-24 | Ludwig Wagenseil | Verbrennungskraftstoff betriebene Hydropumpe |
US6663361B2 (en) * | 2000-04-04 | 2003-12-16 | Baker Hughes Incorporated | Subsea chemical injection pump |
WO2003102418A1 (en) * | 2002-05-31 | 2003-12-11 | Lg Electronics Inc. | Yoke mechanism for compressor |
AU2002306129A1 (en) * | 2002-05-31 | 2003-12-19 | Xiufeng Gao | Multi-stage compressor |
US6832900B2 (en) * | 2003-01-08 | 2004-12-21 | Thomas Industries Inc. | Piston mounting and balancing system |
KR20050066322A (ko) * | 2003-12-26 | 2005-06-30 | 삼성전자주식회사 | 압축기 |
ITVI20040051A1 (it) | 2004-03-12 | 2004-06-12 | Gentilin Srl | Compressore volumetrico alternativo |
US20060045749A1 (en) * | 2004-08-30 | 2006-03-02 | Powermate Corporation | Air compressor utilizing an electronic control system |
US7481627B2 (en) * | 2004-08-30 | 2009-01-27 | Mat Industries Llc | Air compressor tools that communicate with an air compressor |
US20060045751A1 (en) * | 2004-08-30 | 2006-03-02 | Powermate Corporation | Air compressor with variable speed motor |
DE102004061233B3 (de) * | 2004-12-20 | 2006-07-13 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Trockenlaufender Verdichter, insbesondere Taumelscheibenverdichter, mit einer Kolbenstangenlagerung |
US7475627B2 (en) * | 2005-09-27 | 2009-01-13 | Ragain Air Compressors, Inc. | Rotary to reciprocal power transfer device |
DE102006007743B4 (de) * | 2006-02-20 | 2016-03-17 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Hubkolbenverdichter mit berührungsloser Spaltdichtung |
US8328538B2 (en) * | 2007-07-11 | 2012-12-11 | Gast Manufacturing, Inc., A Unit Of Idex Corporation | Balanced dual rocking piston pumps |
CN101963145B (zh) * | 2010-11-04 | 2013-04-10 | 浙江鸿友压缩机制造有限公司 | 一种空气压缩机润滑装置 |
US9856866B2 (en) | 2011-01-28 | 2018-01-02 | Wabtec Holding Corp. | Oil-free air compressor for rail vehicles |
CN102777343B (zh) * | 2012-06-20 | 2015-03-04 | 杭州海胜制冷设备有限公司 | 单驱动多缸压缩机结构 |
CN104728080B (zh) * | 2015-03-28 | 2016-03-23 | 孙万春 | 大推力对置式往复泵 |
WO2018132591A1 (en) * | 2017-01-11 | 2018-07-19 | Bristol Compressors International, Llc | Fluid compressor |
EP3699428B1 (de) * | 2017-10-19 | 2022-05-25 | Active Tools International (HK) Ltd. | Zylinder eines luftkompressors, luftkompressor, fahrzeugsitz und fahrzeug |
CN114109771A (zh) * | 2021-10-25 | 2022-03-01 | 浙江鸿音机电科技有限公司 | 一种往复活塞式压缩机 |
US11913441B2 (en) * | 2021-12-29 | 2024-02-27 | Transportation Ip Holdings, Llc | Air compressor system having a hollow piston forming an interior space and a check valve in a piston crown allowing air to exit the interior space |
CN115263723B (zh) * | 2022-08-25 | 2024-01-30 | 瑞立集团瑞安汽车零部件有限公司 | 缸体、空气压缩机和商用车 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR364091A (fr) * | 1906-02-03 | 1906-08-14 | Platt Iron Works Company | Compresseurs à air |
US1266595A (en) * | 1913-03-06 | 1918-05-21 | Gen Chemical Corp | Process of making carbon-dioxid and solid sodium sulfite. |
US2229545A (en) * | 1939-01-30 | 1941-01-21 | Harry A Beckstrom | Engine |
GB611057A (en) * | 1945-10-10 | 1948-10-25 | Prec Developments Co Ltd | Improvements relating to valve arrangements for reciprocating hydraulic pumps |
GB840499A (en) * | 1958-04-22 | 1960-07-06 | Sidney Owen Grimsdick | Dosing device |
DE2033820C3 (de) * | 1970-07-08 | 1975-05-15 | Patrick Joseph Dublin Walls | Brennkraftmaschine |
BE861533A (nl) * | 1977-12-06 | 1978-03-31 | Bullaert Daniel E | Nieuwe aandrijfmechanismen voor olievrije compressoren en warmtepompen |
US4242878A (en) * | 1979-01-22 | 1981-01-06 | Split Cycle Energy Systems, Inc. | Isothermal compressor apparatus and method |
US5252045A (en) * | 1990-05-11 | 1993-10-12 | Toyo Engineering Corporation | Dual piston reciprocating vacuum pump |
EP0795085B1 (de) * | 1994-04-11 | 2000-09-13 | Enzo Mencarelli | Tauchpumpe mit doppelexzentem angetriebenem,koaxial gegenüberliegenden kolben |
-
1995
- 1995-01-17 DE DE19501220A patent/DE19501220A1/de not_active Withdrawn
- 1995-12-01 WO PCT/DE1995/001706 patent/WO1996022464A1/de active IP Right Grant
- 1995-12-01 EP EP95939216A patent/EP0804684B1/de not_active Expired - Lifetime
- 1995-12-01 US US08/875,619 patent/US5879145A/en not_active Expired - Lifetime
- 1995-12-01 DE DE59505338T patent/DE59505338D1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9622464A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO1996022464A1 (de) | 1996-07-25 |
DE19501220A1 (de) | 1996-07-18 |
DE59505338D1 (de) | 1999-04-15 |
EP0804684B1 (de) | 1999-03-10 |
US5879145A (en) | 1999-03-09 |
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