WO2002064978A1 - Kolben für einen kompressor - Google Patents
Kolben für einen kompressor Download PDFInfo
- Publication number
- WO2002064978A1 WO2002064978A1 PCT/EP2002/001522 EP0201522W WO02064978A1 WO 2002064978 A1 WO2002064978 A1 WO 2002064978A1 EP 0201522 W EP0201522 W EP 0201522W WO 02064978 A1 WO02064978 A1 WO 02064978A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- piston according
- section
- force introduction
- strut
- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
Definitions
- the invention relates to a piston for a compressor according to the preamble of claim 1.
- axial piston compressors are used to compress refrigerants, in which so-called swash plates serve as force transmission elements between the drive shaft and the piston.
- the compression generally takes place by periodic movement of the piston in the cylinder.
- the refrigerant is sucked in, compressed and expelled.
- the up and down movement of the piston is generated by the swash plate, which is connected to the rotating shaft of the compressor and forms an angle between approx. 60 ° and 90 ° with the axis of rotation.
- the rotary movement results in a stroke movement on the piston.
- One shoulder of the pistons engages around the swashplate and thus transmits the lifting movement to the pistons, converting the rotating into an oscillating movement.
- pistons have been assembled in two parts to represent the hollow shape. It is necessary to meet the two requirements of piston guidance and low oscillating mass.
- a quantity of lubricant introduced into the refrigerant is used to lubricate the pistons and the drive shaft of the compressor.
- the lubricant is continuously conveyed in the refrigerant circuit.
- the compressor is followed by a lubricant separator that does the job Separates lubricant from the refrigerant and from which the lubricant is returned to the compressor.
- DE 197 46 896 AI describes a compressor with a piston for compressing a gas, in which the rotation of a drive shaft converts into linear reciprocation of pistons by means of drive bodies such as swash plates.
- the aim here is to minimize the weight of the pistons by reducing the material without impairing the function of the sealing of the compression chamber and the compression of the gas in the chamber.
- the piston has two surfaces in the region of the compression chamber, which are in constant contact with the cylinder bore and thus seal the chamber.
- the piston has a space that opens towards the cylinder bore of the piston, the space being placed between the second surface and the skirt, which transmits the movement of the swash plate to the pistons. Good guidance of the piston in the cylinder bore in the event of transverse forces does not exist.
- DE 197 54 028 AI describes a piston for a compressor with the same function as mentioned above, which is characterized by two radial recesses offset by an angle of 180 ° between the sealing surface to the compression chamber and the skirt in the peripheral surface to reduce his weight.
- the piston can be guided in the event of transverse forces in the cylinder bore.
- the loads on the cylinder bore and piston are not evenly distributed, which can result in increased wear and tear.
- the piston has a surface over the entire cylinder bore between the two recesses, which has no function and thus only increases the weight.
- US Pat. No. 5,630,353 describes a piston corresponding to the above function, which, for weight relief, is arranged by ribs arranged in a star shape below the piston head and the necessary sealing of the compression chamber. These are demoulded radially and accordingly have no guidance over the entire cylinder circumference when transverse forces occur.
- EP 1 022 463 A2 describes a piston according to the above-mentioned function, which is made in two parts from different materials.
- the apron is made of metal and is combined with the cylindrical body that closes the compression chamber in a molding process. The body only finally gets its shape in this process. The connection of the two bodies takes place by a small hook on the apron, which is enclosed by the pressable material of the cylindrical body.
- a disadvantage of this solution is the fact that the entire axial tensile force acting on the piston must be transmitted from the connection between the apron and the cylindrical body.
- the object of the invention is to provide a piston which has a particularly low weight, is easy to manufacture and enables the compressor to be constructed and operated in a particularly simple manner.
- the piston according to the invention is characterized by a piston skirt, which is used to connect the piston crown and the force introduction section, to stiffen the piston as a whole and to adjust the distance between the piston crown and the force introduction section (dimensioning of the piston).
- This piston skirt is solid, ie not hollow, so that simple manufacture is possible.
- one or more solid struts preferably extend over most of the piston skirt, the struts jointly forming an arrangement with a preferably non-circular cross-sectional area, the circumference of which corresponds approximately to the circumference of the piston crown, so that there are line-like contact surfaces (running surfaces) between the piston skirt and the surrounding housing.
- a strut is provided with a V, U, M, or W-shaped or otherwise wavy cross-section (oriented transversely to the piston axis).
- the curve of the strut which is curved transversely to the piston axis, results in high rigidity in the longitudinal direction of the piston and at the same time low weight.
- a one-piece production of the piston crown, piston skirt and force introduction section is preferably also provided.
- the piston skirt has at least one disk-shaped guide section whose cross-sectional area in shape and size corresponds at least approximately to the area of the piston head.
- the guide section serves in particular to support the piston in the surrounding housing and is aligned parallel to the piston head. It has a preferably round to elliptical cross section.
- the guide section is connected to the piston head via one or more struts, its height being small compared to the length of the struts or relative to the length of the piston skirt.
- the outer (peripheral) surface of the guide portion forms a tread that slides along the surrounding housing.
- the guide section is preferably connected to the piston head via an approximately central axis, the outer (circumferential) surfaces of the guide sections together with the outer (circumferential) surface of the piston head forming a uniform, geometrically interrupted running surface which slides along the surrounding housing.
- the piston skirt comprises a plurality of rib-shaped, radially extending struts.
- the struts preferably have a constant or decreasing thickness.
- the rib-shaped, radially extending struts are arranged in a star shape around a core. In particular, three or more struts are provided.
- At least one strut has a radially outer running surface for guiding the cylinder in the housing.
- the tread glides along the surrounding housing, and consequently it is preferably made as small as possible, a graphite-metal material pairing being particularly low-friction.
- the piston skirt has a plurality of struts which are arranged asymmetrically and / or non-uniformly in accordance with a force introduction lying outside the piston axis.
- the struts are preferably concentrated around the piston axis in the area of the greatest force introduction. In this way, the piston can be adapted particularly well to the load and can be of reduced weight.
- the piston skirt has a tubular guide section which has an at least partially cylindrical outer surface and at least partially surrounds the strut.
- the guide section forms a (first) hollow shape extending in the direction of the main axis of the piston (running direction), which has an inner strut from several sides, i.e. encloses at a distance of> 180 ° (to be viewed in the direction of the main axis of the piston) of the piston.
- an open side of the guide section facing away from the piston head Pocket formed with an approximately crescent-shaped cross-sectional area oriented transversely to the piston axis.
- the side of the guide section facing away from the piston head points in the direction of the force introduction section. It can be beveled for reasons of weight and friction.
- the other side of the force introduction section preferably connects directly to the piston head.
- an approximately constant cross section in the cylindrical, tubular guide section, an approximately constant cross section has a recess or notch running along the piston axis, which preferably has an opening angle of 20 ° to 120 °, in particular approximately 45 °.
- the recess forms a (second) negative hollow shape which is received in the tubular guide section.
- the outer surface of the guide section can be dimensioned and the mass of the piston can be changed.
- the deepest point of the notch is preferably arranged in the vicinity of the piston axis and is rounded for reasons of stability and production.
- the piston according to the invention is characterized by a piston skirt, a piston crown and a force introduction section, which are made in one piece from a non-organic and non-metallic material, preferably from a graphite, in particular a fine-grain graphite, the material in the temperature range between 0 and 200 ° C has an average thermal expansion of ⁇ 7 * 10 ⁇ 6 / ° C. All parts form a monolithic part, ie they have no structural cavities and undercuts with a linear expansion of more than 1 mm.
- the cutouts with a size of 0.1 ⁇ m to 1 mm mean diameter are connected in a network, wherein an open-pore piston body with an average size of the cavities of also 0.1 ⁇ m to 1 mm mean diameter is formed, with recesses on the surface, preferably on the guide surfaces, preferably the size 0.1 ⁇ m to 1 mm mean diameter in depth and in superficial extension arise.
- the pore volume can be up to 50% of the total volume.
- the proposed design enables operation of an air conditioning compressor with minimal quantity lubrication or without the addition of lubricants, the absorption and buffering of operating materials in the recesses and a supplementary function of the recesses also having a friction-reducing effect as a reservoir for abrasion materials (preferably the graphite piston) becomes.
- the surfaces of the piston are provided with an organic, inorganic or metallic coating in such a way that the geometric surface structure, formed by recesses in the size 0.1 ⁇ m to 1 mm in diameter and in depth in the superficial extent, is still largely depicted or preserved.
- the thickness of the layer must be chosen so that the function of the recesses - absorption and buffering of operating materials (gases and liquids) of the compressor and as a reservoir for abrasion materials, preferably the piston - is retained.
- the force introduction section has a shoulder which engages around a force introduction means.
- a swivel or swash plate is provided as the force introduction means, which is attached in an inclined arrangement to a rotating axis and converts a rotational movement of the drive axis into a translational movement.
- the force introduction section is designed such that it can optimally engage the force introduction means and can transmit the forces into the piston, it is preferably designed as a U-shaped shoulder and equipped with pans for sliding blocks or similar bearing elements.
- a reinforcing element in the form of a U, L and / or hook-shaped inlay is assigned to the force introduction section.
- the inlay is provided in particular in order to reinforce the force introduction section or its shoulder, since the force introduction section or its shoulder represent highly stressed components.
- the inlay is at least partially encased by the force introduction section, but can extend through the entire piston.
- the inlay of the force introduction section is made from a different material, in particular from a metal.
- the intended toughness of the metallic inlay ensures an improved stability of the piston.
- FIG. 1 is a schematic representation of a piston according to the invention for a compressor
- FIG. 2 shows a section through the piston according to FIG. 1 perpendicular to the piston axis
- FIG. 3 shows a modified embodiment of the piston according to FIG. 1,
- Fig. 4 is a schematic representation of a section of another embodiment of the invention 1 with recesses in the surface
- FIG. 5 shows a first view of a fourth exemplary embodiment of the piston according to the invention
- FIG. 6 shows a second view of the piston according to FIG. 5 in the direction of arrow VI
- FIG. 7 is a third view of the piston of FIG. 5 in the direction of arrow VII,
- FIG. 8 is a fourth view of the piston of FIG. 5 in the direction of arrow VIII,
- Fig. 10 shows a second section through the piston of FIG. 5 in the direction of arrows X-X and
- FIG. 11 shows a spatial representation of the piston according to FIG. 5.
- a piston 1 for a refrigerant compressor of a motor vehicle air conditioning system is shown schematically in FIG.
- the piston 1 comprises a piston crown 2, a piston shaft 3 and a force introduction section 4.
- a plurality of such pistons are arranged in a housing in the refrigerant compressor in a circle around a rotatable drive shaft, all piston axes being aligned parallel to one another and parallel to the drive shaft.
- Each piston is guided in an essentially cylindrical bore of the housing (cylinder), in which it can move in a translatory and possibly also in a rotary manner.
- the cylinders open into a common working chamber through which the refrigerant is conveyed. The compression takes place through periodic movement of the Pistons held in the cylinders.
- the up and down movement of the piston is generated by a force introduction means in the form of a so-called swash plate, which is connected to the rotating drive shaft of the compressor and has a preferably variable angle between approximately 60 ° and 90 ° with respect to the axis of rotation.
- the rotary movement of the drive shaft is transformed into a stroke movement on the piston via the swash plate.
- the force introduction section 4 of the piston 1 is designed as a so-called piston shoulder, engages around the swash plate and thus transmits the stroke movement to the piston.
- Pans 4a are provided in the piston shoulder 4, in which sliding shoes made of ceramic (not shown) are pivotally mounted for angle compensation, the sliding shoes sliding over the swashplate during operation, which they grip around.
- piston crown 2 The outer diameter or the corresponding circumferences of piston crown 2, piston skirt 3 and force introduction section 4 are slightly smaller than the diameter of the cylinder, so that the piston can be displaced within the cylinder with a certain amount of play.
- the piston skirt 3, together with the piston crown 2 serves to guide the cylinder in order to avoid tilting.
- at least one piston ring is additionally installed in the area of the piston crown 2 in order to avoid compression losses (cf. also FIG. 3).
- the piston crown and piston skirt have elliptical cross sections.
- the piston 1 is in one piece and largely without constructive cavities, that is to say solid, the material used for Production of the piston a preferably fine-grained graphite is provided.
- the graphite is reinforced with carbon or glass fibers, the fibers preferably being arranged in such a way that optimum strength is achieved in the direction of loading.
- the piston can be coated or enriched with a carbon-containing ceramic (carbide) and / or a nitrogen-containing ceramic (nitride) in total or on its contact or running surfaces.
- the use of such low-density materials enables a significant weight reduction compared to known piston shapes, the required component stability being ensured by the geometry of the piston.
- the piston can be cast, pressed and / or sintered in one piece.
- the piston is made of a fiber-reinforced plastic, if necessary.
- the piston is preferably characterized by a piston skirt 3, a piston crown 2 and a force introduction section 4, which is produced from a fine-grain graphite, in which carbon (hard firing) carbon is produced in particular by sintering in less than 60 hours , which is then graphitized at temperatures between 1800 and 3000 ° C and has a bending strength of preferably> 80 MPa. All parts are designed monolithically so that simple manufacture is possible.
- the graphite used preferably has a pore volume fraction of 16 to 50% by volume. This pore volume fraction automatically results in the case of a pore structure of the graphite with a pore fraction between approximately 6 and 16%. When the surfaces of the piston are machined, the pores are cut so that depressions and recesses are formed in the surface, in particular in the area of the running surface.
- they are all surfaces, but at least the outer guide surfaces with cutouts A with a size of 0.1 ⁇ m to 1 mm average diameter provided in depth and in the superficial extent (see FIG. 4).
- These are preferably produced by mechanical exposure of pores (present in the piston material - graphite or plastic) in the size mentioned (see above), but can also be produced by mechanical processing, by laser processing or by other chemical or physical ablation.
- These recesses are used in particular for receiving and buffering operating materials (gases and liquids) of the compressor and also as a reservoir for abrasion materials, preferably the piston, this abrasion being suitable as a lubricant, or at least as a lubricant in the deficient operation.
- the above-mentioned recesses and cavities with a size of 0.1 ⁇ m to 1 mm mean diameter during production and / or in operation are filled with metals or metallic alloys, here preferably metals and alloys with a specific weight below 5 g / cm 3 on the surface, preferably on the guide surfaces, to the extent that they are removed mechanically, chemically or physically, so that recesses A with a size of 0.1 ⁇ m to 1 mm mean diameter are created in depth and in the superficial extent.
- the piston shaft 3 has on the one hand a solid strut 5a which extends centrally, along the piston axis, and six rib-shaped, radially extending struts 5b and on the other hand a disk-shaped guide section 6.
- the struts 5a, 5b are narrow in relation to the diameter of the piston skirt 3; the guide section 6 is flat in relation to the height of the entire piston shaft 3 or in relation to the length of the struts 5a, 5b.
- the struts 5b are evenly arranged in a star shape around the central strut 5a; the cross section of the piston skirt in the area of the struts 5a, 5b is thus out of round, the circumference corresponding approximately to the circumference of the piston head.
- the struts 5b have narrow running surfaces 5d at their radially outer ends, which guide the piston can touch the cylindrical bore of the compressor housing (cylinder).
- any number of radially extending struts disposed about a central 'strut around can be provided, an uneven, asymmetrical distribution preferably taking place in accordance with the load on the piston during operation.
- a central, central strut may be dispensed with.
- struts are designed as individual columns aligned parallel to the piston axis.
- a plurality of individual struts are preferably arranged along the circumference of the piston skirt, one or more struts having a curved sliding or contact surface between the piston and the cylinder.
- the U-shaped force introduction section 4 has an inlay, which is preferably U-shaped or L-shaped.
- the inlay is designed in the shape of a hook and extends on the one hand through the entire force introduction section and on the other hand through the central strut 5a of the piston skirt.
- the inlay is made in one piece from a material with high strength, high toughness and / or rigidity, in particular from an aluminum or steel alloy. It is used in the manufacture of the piston 1 in the piston material, forms a firm connection to the piston and is then no longer separable.
- the inlay can be encased on all sides, partially or on one side by the plastic. The rest of the piston is irrelevant to the inlay integrally.
- the inlay lies in the region of the pans for mounting the sliding blocks on the outer surface of the piston. An inlay of this type increases the strength of the overall component, in particular, highly stressed areas can be reinforced.
- a lower part 7 of the piston skirt 3 'of a piston 1' is cylindrical, so that in this area all-round guidance of the piston 1' in the cylinder is ensured.
- Circumferential grooves 8 are optionally provided for one or more piston rings.
- a central strut 5a' and a rib-like strut 5b 'running in the radial direction are provided, which extend in the direction of the Piston axis has an outer tread 5d '.
- the strut 5b serves on the one hand to support the piston on the cylindrical bore in which it is guided, and on the other hand to stiffen the piston 1' in the area in which the force introduction section 4 'has a large lever arm with respect to the piston axis.
- a piston 1 of the invention is illustrated.
- the piston can be formed from a fine-shaped graphite as well as from another injection-moldable material, such as magnesium, aluminum, ceramics, etc.
- the piston skirt 3 ⁇ ⁇ has a tubular guide section 6 , x which has an at least partially cylindrical outer surface and at least partially encompasses a strut 5 , ⁇ .
- the guide section 6 , ⁇ forms a (first) hollow shape which extends in the direction of the main axis of the piston (running direction) and which extends the inner strut 5 from several sides, ie over an angular range of the piston (to be considered in the direction of the main axis of the piston) more than 300 °, encloses at a distance.
- a pocket 9 is formed between the tubular guide section 6 Applications and the strut 5 ⁇ on the side of the guide section facing away from the piston head 2 ⁇ with an approximately crescent-shaped cross-sectional area oriented transversely to the piston axis (see in particular FIG. 9).
- the side facing away from the piston crown side 6a of the guide portion 6 ⁇ ⁇ points in the direction of the force introduction portion 4 ⁇ ⁇ . It can be beveled for reasons of weight and friction.
- the other Page 6b ⁇ of the force introduction section preferably connects directly to the piston head 2 , ⁇ (cf. FIG. 10).
- the strut 5 ⁇ has a wavy, in particular approximately V-shaped course in the transverse direction of the piston and merges seamlessly into the guide section 6 in the circumferential direction. This results in sufficient stiffness in the longitudinal direction of the piston with an extremely low mass of the piston skirt 3 ⁇ .
- the strut 5 ⁇ can be corrugated in a different manner, in particular in a W, M or U shape.
- a pocket 9 is formed between strut 5 , ⁇ and guide section ⁇ ,, toward the side facing away from the piston crown.
- a notch 10 is formed on the side of the strut 5 ⁇ ⁇ opposite the pocket 9, which has an approximately constant cross section in the direction of the piston axis, which corresponds to the wave profile of the strut 5 ⁇ .
- the Einkerburig preferably has an opening angle of 20 ° to 120 °, in particular approximately 45 °.
- the recess forms a (second) negative hollow shape, which is received in the tubular guide section 6 ⁇ and corresponds to the pocket 9.
- the outer surface of the guide section can be dimensioned and the mass of the piston can be changed.
- the deepest point T of the notch (corresponding to the valley of the wave profile of the strut 5 ⁇ ) is preferably arranged in the vicinity of the piston axis and is rounded for reasons of stability and production.
- the guide section 6 results in a comparatively large contact surface between the piston and a guide cylinder which can be dimensioned as required, wherein reduced surface pressures can be achieved. DaimlerChrysler AG
- Piston (1) for a compressor in particular a refrigerant compressor of an air conditioning system, with
- piston crown (2), the piston skirt (3) and the force introduction section (4) are arranged one behind the other in the direction of the piston axis, that means that they are, d a ß
- the piston skirt (3) has a massive strut (5a, 5b) aligned approximately parallel to the piston axis, the cross-sectional area of which is smaller than the area of the piston crown (2).
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- Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP02719824A EP1360414A1 (de) | 2001-02-14 | 2002-02-14 | Kolben für einen kompressor |
DE10290528T DE10290528D2 (de) | 2001-02-14 | 2002-02-14 | Kolben für einen Kompressor |
JP2002564266A JP2005505713A (ja) | 2001-02-14 | 2002-02-14 | コンプレッサ用ピストン |
US10/834,898 US6925925B2 (en) | 2001-02-14 | 2003-08-12 | Piston for a compressor |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10107424.7 | 2001-02-14 | ||
DE2001107424 DE10107424A1 (de) | 2001-02-14 | 2001-02-14 | Kolben für einen Kompressor |
DE10145305.1 | 2001-09-14 | ||
DE10145305A DE10145305A1 (de) | 2001-02-14 | 2001-09-14 | Kolben für einen Kompressor |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/834,898 Continuation-In-Part US6925925B2 (en) | 2001-02-14 | 2003-08-12 | Piston for a compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002064978A1 true WO2002064978A1 (de) | 2002-08-22 |
Family
ID=26008527
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2002/001522 WO2002064978A1 (de) | 2001-02-14 | 2002-02-14 | Kolben für einen kompressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US6925925B2 (de) |
EP (1) | EP1360414A1 (de) |
JP (1) | JP2005505713A (de) |
DE (2) | DE10145305A1 (de) |
WO (1) | WO2002064978A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10235813B4 (de) * | 2002-08-05 | 2004-07-22 | Brueninghaus Hydromatik Gmbh | Gleitschuh und Verfahren zum Herstellen von erhabenen Anlageflächen eines Gleitschuhs |
DE10360352B4 (de) * | 2003-12-22 | 2016-03-24 | Volkswagen Ag | Taumelscheibenkompressor für eine CO2 - Klimaanlage mit einer Spaltdicke von 5 bis 20 µm zwischen Hubkolben und Kompressionszylinder |
EP2586334A1 (de) * | 2011-10-31 | 2013-05-01 | Elfa International AB | Haltevorrichtung |
CH707789A1 (de) * | 2013-03-25 | 2014-09-30 | Liebherr Machines Bulle Sa | Kolben für eine Axialkolbenmaschine. |
US11773837B1 (en) * | 2022-06-03 | 2023-10-03 | T/CCI Manufacturing, L.L.C. | Compressor |
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JPH07189897A (ja) * | 1993-12-27 | 1995-07-28 | Toyota Autom Loom Works Ltd | 揺動斜板式圧縮機におけるピストン |
JPH0953563A (ja) * | 1995-08-11 | 1997-02-25 | Toyota Autom Loom Works Ltd | 片側ピストン式可変容量圧縮機 |
US5630353A (en) | 1996-06-17 | 1997-05-20 | General Motors Corporation | Compressor piston with a basic hollow design |
DE19754028A1 (de) | 1996-12-06 | 1998-06-10 | Toyoda Automatic Loom Works | Kolbenkompressor |
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US4425837A (en) * | 1981-09-28 | 1984-01-17 | General Motors Corporation | Variable displacement axial piston machine |
US4574591A (en) * | 1983-08-29 | 1986-03-11 | Helix Technology Corporation | Clearance seals and piston for cryogenic refrigerator compressors |
DE69635266T2 (de) * | 1995-11-24 | 2006-05-18 | Calsonic Kansei Corp. | Schiefscheibenverdichter |
JP2000337250A (ja) * | 1999-05-28 | 2000-12-05 | Toyota Autom Loom Works Ltd | 斜板式圧縮機 |
EP1061255A3 (de) * | 1999-06-15 | 2001-05-09 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Kolben für einen Taumelscheibenkompressor mit hohlem Kolbenkopf |
EP1087136B1 (de) * | 1999-09-24 | 2007-11-14 | Kabushiki Kaisha Toyota Jidoshokki | Taumelscheibenkompressorkopf mit Fase |
JP2002031233A (ja) * | 2000-07-12 | 2002-01-31 | Sanden Corp | 中空ピストン |
-
2001
- 2001-09-14 DE DE10145305A patent/DE10145305A1/de not_active Withdrawn
-
2002
- 2002-02-14 WO PCT/EP2002/001522 patent/WO2002064978A1/de not_active Application Discontinuation
- 2002-02-14 EP EP02719824A patent/EP1360414A1/de not_active Withdrawn
- 2002-02-14 DE DE10290528T patent/DE10290528D2/de not_active Expired - Fee Related
- 2002-02-14 JP JP2002564266A patent/JP2005505713A/ja not_active Abandoned
-
2003
- 2003-08-12 US US10/834,898 patent/US6925925B2/en not_active Expired - Fee Related
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DE10145305A1 (de) | 2003-04-10 |
JP2005505713A (ja) | 2005-02-24 |
EP1360414A1 (de) | 2003-11-12 |
DE10290528D2 (de) | 2004-04-29 |
US20040244579A1 (en) | 2004-12-09 |
US6925925B2 (en) | 2005-08-09 |
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