WO2004053331A1 - Kolbenkompressor - Google Patents
Kolbenkompressor Download PDFInfo
- Publication number
- WO2004053331A1 WO2004053331A1 PCT/EP2003/013916 EP0313916W WO2004053331A1 WO 2004053331 A1 WO2004053331 A1 WO 2004053331A1 EP 0313916 W EP0313916 W EP 0313916W WO 2004053331 A1 WO2004053331 A1 WO 2004053331A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- cylinder
- gas
- compressed gas
- wall opening
- Prior art date
Links
Classifications
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- 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
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
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- 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
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
- F04B53/148—Pistons, piston-rods or piston-rod connections the piston being provided with channels which are coacting with the cylinder and are used as a distribution member for another piston-cylinder unit
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- 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
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
Definitions
- the invention relates to a piston compressor with a gas-bearing piston.
- Piston compressors with gas storage are used in Stirling coolers, piston vacuum pumps and other gas compressors.
- the gas storage of a piston in a cylinder enables a lubricant-free and low-resistance storage of the piston in the cylinder.
- Such a piston compressor is known from WO 96/15369.
- the piston compressor has a gas storage arrangement which has a compressed gas storage device which is connected to gas storage nozzles and supplies them with pressurized gas under pressure.
- the compressed gas reservoir is supplied by the gas which is compressed by the piston in a cylinder pressure chamber in a filling position of the piston and has a high gas pressure.
- a mechanical check valve for example in the form of a flap valve, is in the process of Compressed gas supply line is provided between the cylinder pressure chamber and the compressed gas storage.
- Mechanical check valves are subject to mechanical inertia, can jam or have leaks and are subject to wear.
- the object of the invention is therefore to provide a gas-bearing piston compressor with an improved inlet valve.
- the piston compressor according to the invention has an inlet valve in the course of the pressure gas feed line which is formed by a cylinder wall opening and a piston wall opening.
- the cylinder wall opening and the piston wall opening lie opposite one another in the filling position of the piston and form an open valve.
- the cylinder wall opening and the piston wall opening are closed by the respectively opposite piston wall and cylinder wall and form a closed valve.
- the cylinder wall opening and the piston wall opening are arranged relative to one another in such a way that the valve opens at high gas pressure and closes at low pressure in the compressed gas supply line. Opening and closing is not directly dependent on the gas pressure in the compressed gas supply line, but on the position of the piston.
- a check valve is not necessary, so that no moving mechanical parts are required for the inlet valve.
- the inlet valve formed by the cylinder wall opening and the piston wall opening works without delay, has a high degree of reliability and can be produced with relatively little effort.
- the cylinder wall opening and / or the piston wall opening is preferably designed as a circular groove.
- the cylinder wall opening and the piston wall opening face each other at every angle of rotation of the piston, so that the piston does not have to be guided in the cylinder with regard to its rotational position.
- the compressed gas feed line is arranged in the cylinder housing between the cylinder pressure chamber and the inlet valve.
- This arrangement is particularly useful when the compressed gas accumulator is arranged in the piston and when a single inlet valve is provided.
- the compressed gas is routed from the cylinder pressure chamber via the compressed gas feed line in the cylinder housing to the inlet valve.
- the compressed gas flows into the compressed gas storage in the piston.
- the inlet valve formed by the cylinder wall opening and the piston wall opening is closed again and the compressed gas in the compressed gas reservoir can no longer escape through the inlet valve. In this way, a simple supply of compressed gas to a piston is implemented in a cylinder.
- the compressed gas storage and the gas storage nozzles are arranged in the piston.
- the gas storage nozzles are connected directly to the compressed gas storage via supply lines in the piston.
- the compressed gas store can also be arranged in the housing.
- the compressed gas feed line is preferably arranged in the piston between the piston head facing the cylinder pressure chamber and the lateral piston wall. This arrangement makes sense in the case of a compressed gas reservoir provided on the housing or if several inlet valves are arranged one behind the other.
- a second inlet valve is provided in the course of the compressed gas supply line, which is formed by a second cylinder wall opening and a second piston wall opening and which opens in the filling position of the piston. In the filling position of the piston, the compressed gas flows through the two open inlet valves into the compressed gas reservoir.
- the sealing length in the gap between the piston and the cylinder in the non-full position of the piston is approximately as large as the piston stroke reduced by an opening diameter.
- the effective sealing length can be increased accordingly. This is necessary in particular in the case of a short piston stroke, in which the piston wall opening is not far from the cylinder wall opening when the piston is not in the full position.
- the blocking effect is considerably improved in the non-full position of the piston, i. H. the so-called gas leak is reduced.
- the inlet valves are preferably each at different angular and longitudinal positions of the cylinder. Three, four or more inlet valves can also be arranged in series one behind the other in the course of the gas feed line.
- an anti-rotation device which prevents the piston from rotating in the cylinder. This is particularly the case if multiple inlet valves required, which are arranged at certain fixed angles of rotation to each other.
- Each gas storage nozzle is preferably formed by a wire inserted into a nozzle bore. An annular gap is formed between the wire and the cylindrical bore wall, through which the gas flows out of the gas bearing nozzle in a throttled manner.
- each gas storage nozzle can be formed by a gas-permeable plug made of sintered material, for example made of stainless steel.
- the gas bearing nozzles are each in a transverse piston plane at the level of the two piston end areas. This achieves stable gas storage of the piston in the cylinder.
- the gas bearing nozzles can be provided in the piston, but can also be arranged in the cylinder housing.
- the gas bearing nozzles can also be partially arranged both in the piston and in the cylinder housing.
- the arrangement of the gas bearing nozzles in the piston has the advantage that they move with the movement of the piston and the radial stabilizing forces therefore always act on the piston in the same way.
- the arrangement of the gas bearing nozzles in the cylinder housing has the advantage that the compressed gas supply can largely be arranged in the fixed cylinder housing.
- the piston compressor has a pneumatic piston end position control device, wherein a constant pressure gas source generates a gas pressure that is constant in comparison to the piston pressure stroke and is directly connected to a cylinder wall opening. Furthermore, a control pressure accumulator is arranged in the piston and connected directly to a control pressure accumulator piston wall opening. The control pressure accumulator is in the filling position of the piston with the same bend constant gas pressure of the constant pressure gas source.
- a line is provided between the constant pressure gas source and a second cylinder wall opening, which forms a charging valve with the control pressure accumulator piston wall opening and which is opposite the control pressure accumulator piston wall opening in the end position of the piston, so that the gas pressure of the control pressure accumulator matches the gas pressure of the constant pressure. adjusted pressure gas source.
- the piston end position control device is provided in addition to the piston gas bearing, wherein a compressed gas reservoir is provided for the piston bearing and for the piston end position control device, and both devices work separately and independently of one another.
- the piston end position control device With the piston end position control device, a quantity of gas is transferred from the control pressure accumulator into the cylinder pressure chamber in a specific position of the piston, which is not the filling position or the end position. In this way, the amount of gas in the relevant cylinder pressure chamber is kept relatively constant. During the subsequent compression of the gas in the cylinder pressure chamber, the piston end position, which is determined by the gas pressure in the cylinder pressure chamber, is always in the same place. In this way, regulation of the piston end position of a free-floating piston is realized, i.e. a piston that is not mechanically coupled to a crankshaft or the like.
- the pneumatic piston end position control device does not have to be part of the piston compressor claimed, but can also serve as an independent end position control device for any type of piston cylinder arrangement.
- the piston compressor is part of a Stirling cooler with a cold finger.
- the cold finger is formed by a displacer piston in a cold finger cylinder housing.
- the cold finger has its own pressurized gas Storage and associated gas storage nozzles for storing the displacer piston, or alternatively, a common compressed gas storage is used outside the piston.
- the cold finger compressed gas accumulator is connected to the piston compressor compressed gas accumulator by a cold finger gas supply line.
- a cold finger valve is arranged, which is formed by a piston wall opening and a cylinder wall opening of the piston compressor and is open in a filling position of the piston compressor piston.
- compressed gas is conducted from the piston compressor compressed gas storage into the cold finger compressed gas storage provided for this purpose. This is expediently carried out at the moment when the piston of the piston compressor is in its filling position, since the highest gas pressure for supplying the compressed gas accumulator is present at this time.
- the cold finger valve between the two compressed gas accumulators is therefore also opened, so that the compressed gas flows from the cylinder pressure chamber of the piston compressor into both the piston compressor compressed gas accumulator and the cold finger compressed gas accumulator. In this way, the use of flutter valves or other mechanical valves to shut off the compressed gas in the cold finger compressed gas storage is avoided.
- FIG. 1 shows a first embodiment of a piston compressor in a filling position of the piston
- 2 the piston compressor of FIG. 1 in a non-full position of the piston
- FIG. 3 shows a second embodiment of a piston compressor in a filling position of the piston
- FIG. 4 shows the piston compressor of FIG. 3 in a non-full position of the piston
- FIG. 5 shows a third embodiment of a piston compressor in a filling position of the piston
- FIG. 6 shows the piston compressor of FIG. 5 in a non-full position of the piston
- FIG. 7 A fourth embodiment of a piston compressor with a piston end position control device in a filling position of the piston
- Fig. 8 the piston compressor of Figure 7 in a non-full position of the piston
- FIG 9 shows a fifth exemplary embodiment of a piston compressor as part of a Stirling cooler with a cold finger in the filling position of the piston compressor piston.
- FIGS. 1-8 show several exemplary embodiments of a piston compressor, as used, for example, as part of a Stirling cryocooler.
- a Stirling cryocooler with a piston compressor is shown in FIG. 9.
- a first embodiment of a piston compressor 10 is shown in FIGS. 1 and 2.
- the piston compressor 10 is essentially formed by a piston 12 which oscillates in a cylinder 14 between two end positions, each of which is shown in FIGS. 1 and 2.
- a compressed gas feed line 18 is provided, which connects a cylinder pressure space 20 at one cylinder end to a cylinder wall opening 22 in the lateral cylinder wall 24.
- the piston 12 has four gas bearing nozzles 28 in two planes, which are connected to one another by transverse channels 30 and a longitudinal channel 32. At least three gas storage nozzles must be provided on each level.
- the transverse and longitudinal channels 30, 32 together form a compressed gas store 34, which has a sufficient volume of compressed gas for supplying the gas storage nozzles 28 with compressed gas during a cycle.
- the compressed gas accumulator 34 formed by the channels 30, 32 also has a connecting channel 36 which opens into a piston wall opening 38 in the lateral piston wall 40.
- a circumferential circular groove 39 is assigned to the piston wall opening 38 and extends over the entire circumference of the lateral cylinder wall 24.
- the cylinder wall opening 22 and the piston wall opening 38 together form an inlet valve 42 through which, in the filling or end position of the piston 12 shown in FIG. 1, compressed gas flows from the cylinder pressure chamber 20 into the compressed gas reservoir 34. In the non-full position shown in Figure 2, the inlet valve 42 is blocked. In the non-full position of the piston 12, the pressurized gas from the pressurized gas accumulator 34, as in FIG the filling position, slowly released again via the gas storage nozzles 28.
- the gas bearing nozzles 28 each have an inserted wire in an axial bore, which wire forms an annular gap in the axial bore. In this way, a pressure drop is realized in the gas storage nozzle, which prevents the gas retained in the compressed gas storage 34 from escaping under pressure from escaping too quickly.
- a plug made of sintered material e.g. B. made of stainless steel.
- the gas slowly escapes over the entire cycle.
- the gas pressure in the compressed gas accumulator 34 decreases so slowly that there is sufficient gas pressure practically over the entire movement cycle of the piston 12 to hold the piston 12 in the middle of the cylinder.
- the gas bearing nozzles 28 are arranged distributed over the piston length and the piston circumference and act as throttles.
- the gas storage nozzles 28 are continuously supplied with compressed gas from the compressed gas store 34.
- the compressed gas flowing out of the gas bearing nozzles 28 forms a gap between the piston 12 and the cylinder housing 16, through which the piston 12 is held in the middle of the cylinder and moves back and forth in the cylinder housing 16 without contact.
- the throttle resistance of the gas bearing nozzles 28 is approximately the same order of magnitude as the throttle resistance of the gas flow between the piston 12 and the cylinder 14 when the piston 12 is approximately in the radial center of the cylinder 14.
- the pressure in the gap between the piston 12 and the cylinder 14 in the vicinity of the gas bearing nozzles 28 is approximately half the pressure in front of the gas bearing nozzles, ie as that Pressure within the compressed gas accumulator 34.
- the pressure is approximately the same on all sides of the piston 12. As soon as a force acts on the piston 12, the piston 12, yielding to the force, moves towards the cylinder wall 24 in the radial direction. As a result, the gap between the piston wall 40 and the cylinder wall 24 is reduced in this region.
- a gas pressure which is above the transfer pressure is required in the compressed gas storage 34.
- the required gas pressure is always taken from the cylinder pressure chamber 20 in the filling position of the piston 12 shown in FIG. 1, which always has a high gas pressure at this time.
- the inlet valve 42 formed by the cylinder wall opening 22 and the piston wall opening 38 is opened, so that the gas under high pressure can flow from the cylinder pressure space 20 into the compressed gas store 34.
- the piston 12 has left its filling position, the cylinder wall opening 22 faces the piston wall 40 and the piston wall opening 38 the cylinder wall 24, so that the inlet valve 42 is closed.
- the cylinder 14 is subjected to a constant gas pressure, for example atmospheric pressure.
- the piston is driven by a drive, not shown, for example by a fixed electromagnet in connection with a piston spring or by a magnet which drives the piston and moves in the axial direction.
- reference numerals of the exemplary embodiment of FIGS. 1 and 2 increased by 100 are adopted insofar as they relate to the same parts. The same applies correspondingly to the other exemplary embodiments, in which the reference numerals are increased by 200, 300 or 400.
- a plurality of inlet valves 142, 144, 146, 148 are arranged in series in the course of the compressed gas supply line 118, 160, 162, 164.
- a section of the compressed gas supply line 164 in the piston 112 is arranged between an opening 170 in the piston head 172 and a second piston wall opening 174, which forms the inlet valve 148 with a second cylinder wall opening 176.
- the remaining inlet valves 142, 144, 146 are each formed by a piston wall opening and a cylinder wall opening opposite in the filling position of the piston. All four inlet valves 142-148 open the filling position of the piston 112 shown in FIG. 3 and are closed in the non-filling position of the piston 112 shown in FIG. 4, since the respectively opposite cylinder wall and piston wall openings of the inlet valves 142-148 do not lie opposite one another, but through the opposite piston or cylinder wall are blocked.
- inlet valves 142-148 increases the so-called sealing length, ie the length of the piston-cylinder gap between the piston wall opening and the cylinder wall opening of the same inlet valve.
- sealing length is quadrupled in this way, so that the gas leakage flow is considerably reduced in this way. This is particularly necessary in the case of a piston compressor which has only a short piston stroke, which in turn results in a short sealing length between the two wall openings of an inlet valve.
- Another section of the compressed gas supply line 160 runs in the piston 112 between a third and a fourth inlet valve 144, 146.
- An anti-rotation device is provided in the cylinder 114, which prevents the piston 112 from rotating in the cylinder 114.
- the anti-rotation device can be designed, for example, as a non-circular configuration of the magnetic parts of the motor fastened to the piston 112, which face the corresponding magnetic pole shoes.
- both the piston 212 and the cylinder 214 have gas bearing nozzles 228, 229.
- a second inlet valve 250 is provided for supplying the cylinder-side gas bearing nozzles 229, which is connected to the first one Inlet valve 242 is connected by the piston-side compressed gas accumulator 34. Via the second inlet valve 250, a cylinder-side compressed gas reservoir 252 is supplied with compressed gas in the filling position of the piston 212 shown in FIG. 5.
- the piston 212 is driven by a motor 260 which essentially has an electromagnet 262 which interacts with a permanently magnetic part of the piston.
- the piston 212 can have a reduced outer circumference in the area of the electromagnet 262, as a result of which the cylinder 114 can also include the axial length of the motor 260. As a result, the manufacturing costs are reduced and the storage quality is increased.
- FIGS. 7 and 8 show a fourth exemplary embodiment of a piston compressor, the bearing of the piston in the cylinder being omitted in the illustration.
- the piston compressor 310 has a piston 312 which oscillates in a gas bearing in a cylinder 314 and is supported with compressed gas, as described in the exemplary embodiments shown in FIGS. 1-6.
- the piston end position control device described below can also be operated with other piston-cylinder arrangements.
- the piston end position control device shown in FIGS. 7 and 8 serves to control the end position of the piston 312 in its filling position, which is shown in FIG.
- the filling position must therefore always be maintained precisely because this is the only way to ensure that the piston wall opening and the cylinder wall opening of an intake valve are exactly aligned with one another and that the intake valve formed by them has a sufficiently large opening cross-section and a sufficient has a sufficiently long opening time so that the piston compressor compressed gas storage can be fully charged again.
- the piston compressor 310 has a constant pressure gas source 350, in which there is always a constant gas pressure.
- the constant pressure gas source 350 is connected via a line 352 to a cylinder wall opening 354 which, in FIG. 7, shows the end or filling position of the piston 312 in alignment with a piston wall opening 356 and together with this forms an opened charging valve 358.
- a control pressure accumulator 360 is provided in the piston 312, and the gas pressure of the compressed gas source 350 is applied to it in the filling position of the piston 312.
- a line 364 is provided in the cylinder housing 362, which connects the cylinder pressure chamber 366 to a second cylinder wall opening 368.
- the second cylinder wall opening 368 forms with the piston wall opening 356 an unloading valve 370 which is opened in the non-end position of the piston 312 shown in FIG. 8, so that the gas pressure of the regulating pressure accumulator 360 and the cylinder space 366 align.
- a second corresponding piston end position control device can be provided to regulate the right end position of the piston 312.
- electromagnet 260 and / or the ferromagnetic parts which are not rotationally symmetrical are designed . are connected to the piston 212, there is also guidance in the axis of rotation, so that a mechanical rotation lock can be omitted.
- FIG. 9 shows a Stirling cryocooler 400 which is formed by a piston compressor 10 and a cold finger 460.
- the cold finger 460 in turn is formed by a displacer piston 462 which oscillates in a cold finger cylinder housing 464.
- the displacer piston 462 is gas-supported in the cold finger housing.
- the cold finger 460 has a cold finger compressed gas storage 466.
- gas bearing nozzles 468 are provided in the cylinder housing 464 for mounting the displacer piston 462.
- the gas storage nozzles 468 are fed with compressed gas from the compressed gas storage 466.
- the piston compressor compressed gas storage 34 is connected to the cold finger compressed gas storage 466 by a cold finger gas supply line 470.
- a cold finger valve 480 is provided, which is formed by a piston wall opening 482 and a cylinder wall opening 484 of the piston compressor 10 and opened in a ' filling position of the piston compressor piston 12 shown in FIG. 9 is.
- the compressed gas storage 466 of the cold finger 460 is also supplied with compressed gas in this way.
- the cold finger valve 480 is configured in the same way as the piston compressor inlet valve 42. The compressed gas flows in the filling position of the piston compressor piston 12 into the cold finger compressed gas storage 466 and is released over the entire movement cycle of the displacer piston 462 via the cold finger gas bearing nozzles 468.
- the Stirling cooler shown is a split Stirling cooler, with an overflow line 490 supplying the cold finger 460 with gas from the piston compressor 10.
- the displacer piston 462 is supported exclusively in the "warm" half of the cold finger cylinder housing 464 by the gas bearing nozzles 468 lying in two transverse planes. This arrangement of the cold finger gas bearing nozzles 468 prevents the relatively warm gas flowing out of the cold finger gas bearing nozzles 468 from heating the cold side of the cold finger 460.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004558036A JP4603365B2 (ja) | 2002-12-12 | 2003-12-09 | ピストンコンプレッサ |
US10/537,639 US7415829B2 (en) | 2002-12-12 | 2003-12-09 | Piston compressor |
AU2003288244A AU2003288244A1 (en) | 2002-12-12 | 2003-12-09 | Piston compressor |
IL168485A IL168485A (en) | 2002-12-12 | 2005-05-09 | Piston compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10257951.2 | 2002-12-12 | ||
DE10257951A DE10257951A1 (de) | 2002-12-12 | 2002-12-12 | Kolbenkompressor |
Publications (1)
Publication Number | Publication Date |
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WO2004053331A1 true WO2004053331A1 (de) | 2004-06-24 |
Family
ID=32403777
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2003/013916 WO2004053331A1 (de) | 2002-12-12 | 2003-12-09 | Kolbenkompressor |
Country Status (9)
Country | Link |
---|---|
US (1) | US7415829B2 (de) |
JP (1) | JP4603365B2 (de) |
KR (1) | KR20050085547A (de) |
CN (1) | CN100402846C (de) |
AU (1) | AU2003288244A1 (de) |
DE (1) | DE10257951A1 (de) |
IL (1) | IL168485A (de) |
TW (1) | TW200417687A (de) |
WO (1) | WO2004053331A1 (de) |
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WO2013167124A3 (de) * | 2012-05-11 | 2014-01-09 | Aerolas Gmbh Aerostatische Lager-Lasertechnik | Kolben-zylinder-einheit |
EP2871620A1 (de) * | 2013-11-07 | 2015-05-13 | Labor Strauss Sicherungsanlagenbau Ges. m. b. H | Rauchdetektionsanordnung |
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- 2003-12-09 JP JP2004558036A patent/JP4603365B2/ja not_active Expired - Fee Related
- 2003-12-09 WO PCT/EP2003/013916 patent/WO2004053331A1/de active Application Filing
- 2003-12-09 KR KR1020057010607A patent/KR20050085547A/ko not_active Application Discontinuation
- 2003-12-09 AU AU2003288244A patent/AU2003288244A1/en not_active Abandoned
- 2003-12-09 CN CNB2003801057011A patent/CN100402846C/zh not_active Expired - Fee Related
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Also Published As
Publication number | Publication date |
---|---|
AU2003288244A1 (en) | 2004-06-30 |
JP2006509944A (ja) | 2006-03-23 |
US20060090477A1 (en) | 2006-05-04 |
CN1723347A (zh) | 2006-01-18 |
CN100402846C (zh) | 2008-07-16 |
DE10257951A1 (de) | 2004-07-01 |
TW200417687A (en) | 2004-09-16 |
JP4603365B2 (ja) | 2010-12-22 |
IL168485A (en) | 2008-04-13 |
KR20050085547A (ko) | 2005-08-29 |
US7415829B2 (en) | 2008-08-26 |
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