WO2004011805A1 - Device for compressing gases - Google Patents
Device for compressing gases Download PDFInfo
- Publication number
- WO2004011805A1 WO2004011805A1 PCT/AT2003/000210 AT0300210W WO2004011805A1 WO 2004011805 A1 WO2004011805 A1 WO 2004011805A1 AT 0300210 W AT0300210 W AT 0300210W WO 2004011805 A1 WO2004011805 A1 WO 2004011805A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- seal
- piston
- cuts
- cylinder
- region
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
Definitions
- the present invention relates to a device according to the preamble of claim 1.
- Compressors of this type which compress gases by means of a piston moved in a cylinder by an electromechanical or other type of drive are known.
- a piston driven by means of a crank or a connecting rod is set in a reciprocating motion with a seal abutting the inner wall of the cylinder. This causes compression of the gas on one side of the piston.
- Such devices exist in various designs and sizes and are used in a wide variety of fields. Drive mechanisms of different types and performance are also used.
- the object of this invention is to propose a device of the type mentioned at the outset or a piston compressor with a seal which has an improved friction and sealing behavior on the inner wall of the cylinder in comparison with previously known embodiments of conventional seals.
- the cuts which are technically simple, advantageously designed according to claims 16 to 19 or 22 and 23, bring about a decisive improvement in the elasticity of the seal.
- the regular distribution of the cuts along the annular seal according to claim 20 and their preferred orientation according to claim 21 bring about balanced and quiet running properties of the piston.
- a quiet movement and longevity of the piston and the seal in the cylinder are achieved by the design features according to claim 2, 3, 4 and / or 11.
- An advantageous and effective embodiment of the sealing mechanism is described in the features of claims 5 to 7.
- the seal is advantageously stored and guided according to claims 8, 9 and / or 10.
- the positioning, shape and type of formation of the leaks according to claim 14 allow design-related variation options, depending primarily on the type and size of the piston or the entire compressor device. If the leaks are formed in the inner region of the support disk and the guide disk, they are arranged in alignment and enable the defined gas passage through this feature described in claim 15. The piston is essentially sealed in the cylinder. A gas passage from
- Working space in the unpressurized room is essentially determined by the leaks.
- Fig. 1 shows a schematic representation of a compressor arrangement including power supply, drive and hose connections.
- Fig. 2 shows an overview of the power transmission and compression mechanisms.
- Fig. 3 shows a schematic sectional view of the piston located in the cylinder.
- Fig. 4 shows a cross section through a seal.
- Fig. 5 shows a plan view of an annular seal with cuts.
- an electromechanical drive 1 is fed via a battery, not shown, which is connected via a cigarette lighter plug 9 and a cable 10 to a control console 12 and via a further cable 13 to the drive or electric motor 1.
- the power supply can be switched on and off with a rocker switch 11 located on the console 12. The one located in a drive chamber 3 or in the cylinder 2
- Compression mechanism is actuated via this drive 1 and the working medium, in this case air, is pressed via a pressure hose 5 fastened with a clamp 4 to the outlet 22 of the cylinder 2, via a manometer 6 for pressure control and via an outlet 8 to the destination object, for example car tires , 2 shows an overview, a drive shaft of the drive 1 in the drive chamber 3 is connected via a crank 23 to a push rod 14 which sets a piston 20 in a reciprocating motion in the cylinder 2, which moves the piston from the wall of the cylinder 2 and the piston 20 limited volume of the working space 26 in front of the piston 20 and the volume of the unpressurized space 24 behind the piston 20 changed.
- a check valve 27 prevents the air pressed out of the outlet 22 from flowing back into the working space 26.
- the piston 20, shown enlarged in FIG. 3 and located in the cylinder 2, comprises a plate-shaped guide disk 16 fixed to the push rod 14 on its head or work space side 26, and also a fixed to the push rod 14 and possibly permanently connected to the guide disk 16 in the inner region plate-shaped support disk 15 on its rear side or its side facing the unpressurized space 24 and an annular seal 17 lying against the wall of the cylinder 2.
- the guide disk 16 is in the inner region, a central part 28, preferably running parallel to the wall of the cylinder 2, and a terminal part peripheral flange 25 'articulated.
- the support disc 15 is also divided into an inner region, a middle part and a terminal peripheral flange 25.
- the height of the seal 17 is between the two peripheral flanges 25, 25 'of the support disc 15 and the guide disc 16 in the peripheral region of the piston 20. Between the seal 17, the support disk 15 and the guide disk 16 or their peripheral flanges 25, 25 'there is a free space 27.
- the surface of the seal 17 facing the inner wall of the cylinder 2 is concave outwards, in particular with a circular curvature, around the slightly oscillating one
- the seal 17 has on its side facing the working space 26 in
- a recess 43 is advantageously formed on the inner surface of the seal 17, into which a spring ring 18 is inserted, in particular firmly and preferably with a snug fit.
- This spring ring 18 is accordingly between the middle part 28 of the guide disk 16 and the head region 40 of the seal 17.
- the spring ring 18 can be moved up and down during a stroke movement of the piston 20 along or in front of this middle part 28 of the guide disk 16, its upward movement or its upward travel is limited by the peripheral flange 25 'of the guide disk 6.
- the seal 17 is pressed radially outward or against the side wall of the cylinder 2 by means of this spring ring 18 and prevents undesired gas passage there.
- a resilient clamping ring can also be used. In both cases, however, air can pass between the free space 27 and the work space 26 at this point.
- the height H of the seal 17, measured in the direction of movement of the piston 20, is less than the distance A measured between the inner sides of the peripheral flanges 25, 25 'of the support disk 15 and the guide disk 16. Accordingly, the movement amplitude of the seal 17 is based on the difference D. limited between the height H of the seal 17 and the distance A of the peripheral flanges 25, 25 'of the support plate 15 and the guide plate 16.
- this embodiment With a suction movement, that is to say with a movement of the piston 20 in the direction of the crank 23, this embodiment causes the seal 17 to be lifted from the support disk 15 by the amount D and thus enables gas to flow in via the free space 27 into the head-side working space 26 During the compression stroke, the seal 17 is pressed tightly against the peripheral flange 25 of the support disk 15 and gas passage is only possible due to the defined leaks 19 described below.
- the air compressed in the working space 26 is pressed out of the outlet 22 by a check valve 27 and is simultaneously prevented from flowing back into the working space 26 by this check valve 27.
- the seal 17 consists of a largely heat-stable and / or largely abrasion-resistant polymer, in particular with good running and sliding properties, preferably polytetrafluoroethylene (PTFE, Teflon) or polytetrafluoroethylene compounds, and can optionally be combined with carbon or carbon fibers and / or particles in one Proportion of 10 to 20% by weight, preferably from 15 to 25% by weight, of the PTFE or PTFE compound weight can be reinforced.
- PTFE polytetrafluoroethylene
- Teflon polytetrafluoroethylene
- the number of leaks 19, as well as their shape or cross-sectional shape, depends on the power of the drive mechanism, the amount of the initial counterpressure, the size and type of the compressor device, the shape of the piston, etc.
- the leaks 19 can be caused by bores, milled recesses, Sinkings or the like are formed, the shape of which is also determined by the production method. Accordingly, the leakages 19 can be round, angular or even irregularly shaped in cross section.
- the total cross-sectional area of the at least one leakage 19 is between 0.005 and 0.1 mm 2 , preferably 0.01 and 0.06 mm 2 , per cm 3 of stroke volume of the piston 20.
- the formation of the leaks 19 can take place in the support plate 15 and / or the guide plate 16, both in the outer regions, that is to say in the peripheral flanges 25, 25 ', in particular in the peripheral flange 25 of the support plate 15, and in the inner regions, whereby to It should be noted that, when formed in the firmly and flatly connected inner regions of the disks 15, 16, the leaks 19 are advantageously arranged in alignment. Furthermore, there is the possibility of forming leaks in the entire area of the seal 17, in particular in the end face of the seal 17 facing the inside of the peripheral flange 25 of the support disk 15.
- FIG. 4 shows a cross section through the seal 17.
- the recess 43 provided for the spring ring 18 and the somewhat thicker foot region 41.
- Cuts 45 are formed in the head region 40.
- the cuts 45 are made without material removal, that is, they are not milled, sawn or the like.
- the cuts 45 extend, starting from the upper end face of the head region 40 of the seal 17, at least to the beginning of the contact region 44 of the seal 17 with the inner wall of the cylinder 2, which in practice is due to the compression of the seal 17 against the wall of the cylinder 2 or by the tumbling movements of the piston 20.
- the cuts 45 extend from the upper end face of the head region 40 of the seal 17 to the theoretical contact line 42 of the concave seal 17, which is geometrically determined in FIG. 5, with the inner wall of the cylinder 2.
- the cuts 45, starting from the upper end face of the head region 40 of the seal 17, extend at least to the lower end of the recess 43.
- the cuts 45, measured from the upper end face of the head region 40 of the seal 17, extend to the beginning of the foot region 41 of the seal 17, that is to a maximum depth T.
- the cuts 45 completely penetrate the head region 40 of the seal 17.
- the preferably 6 to 12, in particular 8 to 10, here 9 cuts 45 are distributed along the circumference of the annular seal 17 and at equal distances from one another and are inclined relative to the radius R of the seal 17 in the same direction, preferably at an angle a between 30 and 80 °, especially between 40 and 70 °.
- the surfaces of the cuts 45 are flat and are aligned perpendicular to the plane spanned by the seal 17.
- the cuts 45 are advantageously identical to one another or have the same shape or dimensions. Leakage is understood to mean a constantly open (gas) passage connection between the space in front and behind the piston.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP03737736A EP1527278B1 (en) | 2002-07-24 | 2003-07-23 | Device for compressing gases |
AT03737736T ATE530769T1 (en) | 2002-07-24 | 2003-07-23 | DEVICE FOR COMPRESSING GASES |
AU2003245104A AU2003245104A1 (en) | 2002-07-24 | 2003-07-23 | Device for compressing gases |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ATA1127/2002 | 2002-07-24 | ||
AT0112702A AT414270B (en) | 2002-07-24 | 2002-07-24 | DEVICE FOR COMPACING GASES |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004011805A1 true WO2004011805A1 (en) | 2004-02-05 |
Family
ID=30773867
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AT2003/000210 WO2004011805A1 (en) | 2002-07-24 | 2003-07-23 | Device for compressing gases |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1527278B1 (en) |
AT (2) | AT414270B (en) |
AU (1) | AU2003245104A1 (en) |
WO (1) | WO2004011805A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5993644B2 (en) * | 2012-07-20 | 2016-09-14 | 株式会社日立産機システム | Reciprocating compressor |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1116445A (en) * | 1954-08-10 | 1956-05-08 | Tecalemit | Seal for scraper piston used for emptying drums |
AU412693B1 (en) * | 1967-06-27 | 1971-04-27 | Manilyn Air Compressors Pty. Limited | Improvements in or relating to air compressors |
GB1396230A (en) * | 1972-07-21 | 1975-06-04 | Linde Ag | Pistons for reciprocating machines |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2274304A (en) * | 1939-09-05 | 1942-02-24 | Clarence J Perry | Piston |
US3897072A (en) * | 1973-02-12 | 1975-07-29 | Crane Packing Co | Slit ring with connecting membrane |
JPS62255666A (en) * | 1986-04-28 | 1987-11-07 | N D C Kk | Piston member for strut |
DE3710403A1 (en) * | 1987-03-28 | 1988-10-06 | Lechler Elring Dichtungswerke | COMPLETE PISTON |
DE4203384C2 (en) * | 1992-02-06 | 1994-10-20 | Hunger Walter Dr Ing E H | Piston of a piston engine |
DE4429097A1 (en) * | 1994-08-17 | 1996-02-22 | Thurner Bayer Druckguss | Piston compressor for gaseous media |
DE19514918C2 (en) * | 1995-04-22 | 1999-01-07 | Mtu Friedrichshafen Gmbh | Pistons for internal combustion engines |
DK28697A (en) * | 1997-03-14 | 1998-09-15 | Man B & W Diesel As | Piston for an internal combustion engine, in particular a two-stroke diesel engine |
DE29717654U1 (en) * | 1997-10-02 | 1998-11-12 | Alusuisse Bayrisches Druckgus | Piston for a piston compressor |
DE29814962U1 (en) * | 1998-08-20 | 1999-11-04 | Alusuisse Bayrisches Druckgus | Piston for a piston compressor |
-
2002
- 2002-07-24 AT AT0112702A patent/AT414270B/en not_active IP Right Cessation
-
2003
- 2003-07-23 WO PCT/AT2003/000210 patent/WO2004011805A1/en not_active Application Discontinuation
- 2003-07-23 EP EP03737736A patent/EP1527278B1/en not_active Expired - Lifetime
- 2003-07-23 AT AT03737736T patent/ATE530769T1/en active
- 2003-07-23 AU AU2003245104A patent/AU2003245104A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1116445A (en) * | 1954-08-10 | 1956-05-08 | Tecalemit | Seal for scraper piston used for emptying drums |
AU412693B1 (en) * | 1967-06-27 | 1971-04-27 | Manilyn Air Compressors Pty. Limited | Improvements in or relating to air compressors |
GB1396230A (en) * | 1972-07-21 | 1975-06-04 | Linde Ag | Pistons for reciprocating machines |
Also Published As
Publication number | Publication date |
---|---|
EP1527278B1 (en) | 2011-10-26 |
AU2003245104A1 (en) | 2004-02-16 |
ATA11272002A (en) | 2006-01-15 |
ATE530769T1 (en) | 2011-11-15 |
EP1527278A1 (en) | 2005-05-04 |
AT414270B (en) | 2006-10-15 |
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