WO2004038242A1 - Helical rotary compressor - Google Patents
Helical rotary compressor Download PDFInfo
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- WO2004038242A1 WO2004038242A1 PCT/EP2003/011169 EP0311169W WO2004038242A1 WO 2004038242 A1 WO2004038242 A1 WO 2004038242A1 EP 0311169 W EP0311169 W EP 0311169W WO 2004038242 A1 WO2004038242 A1 WO 2004038242A1
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- WIPO (PCT)
- Prior art keywords
- bearing
- ball
- scroll compressor
- raceway
- compressor according
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
- F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
- F01C17/063—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with only rolling movement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/42—Pumps with cylinders or pistons
Definitions
- the invention relates to a scroll compressor according to the preamble of claim 1.
- scroll compressors also known as scroll compressors
- the compression takes place by means of a rotary movement.
- the compressors have a fixed scroll and a second scroll moving eccentrically to it on a circular path.
- the spirals touch at two to three pairs of contacts that form closed spaces.
- Such a generic scroll compressor is previously known from US 5,758,978.
- This has a fixed and a movable spiral, which is connected eccentrically to a rotary shaft in order to carry out an orbital movement without rotation about an axis.
- the movable spiral is supported in the housing for receiving the axial pressure load via an axial ball bearing, which has two annular bearing disks spaced apart from one another, orbit each other so that bearing balls arranged between them roll on associated circular paths.
- the two annular bearing disks have ball raceways with a different radius of curvature, these radii being larger than the radius of the bearing ball.
- the bearing balls are therefore only at one point on each bearing disc, which means that there is a two-point bearing.
- the invention is therefore based on the object of developing an axial bearing for a scroll compressor which, when there is a sudden change in pressure, which is associated with a changed axial load, causes less noise.
- this object is achieved according to the characterizing part of claim 1 in connection with the preamble in that the axial ball bearing is designed as a three-point ball bearing, one bearing disc of which has two contact zones and the other of which bearing disc has a contact zone.
- the main advantage of the design of the ball bearing according to the invention is that the two contact zones of a bearing disc enable the bearing balls to be guided precisely.
- This bearing disc encompasses the bearing balls in the broadest sense and therefore has two functions, firstly a management function and another a warehouse function.
- the associated other bearing disc has only one contact zone for the bearing balls, so that they can change their position within the entire ball raceways. This means that the bearing balls can always rest at different points on the ball raceways during orbit, so that the contact zones can change their position within the ball raceways.
- one bearing disc should have a ball raceway with a radius R2
- the other bearing disc should have a ball raceway composed of two raceway segments with the radii R3 and R4, the puncture points of which are spaced apart from one another, so that a contact point of the raceway segments lying in the center of this compound raceway is formed is, where R3 is equal to R4 and R2, R3, R4 are larger than a radius of the bearing balls.
- the Bearing disk with two contact zones formed a gap which is formed on the one hand by part of the raceway segments and on the other hand by part of the outer surface of the bearing balls.
- the radii R2, R3 and R4 of the bearing disks have the same amount.
- the same amount of radii ensures that such a bearing has the same osculation on both bearing disks, whereby in the context of the invention, osculation is to be understood as follows:
- Another variant of the three-point ball bearing according to the invention is set out in claim 6. This is characterized in that one bearing disc has a roof-like raceway composed of two flat surfaces that are inclined at an angle to one another, while the other bearing disc has a ball raceway with a radius R1 that is larger than a radius of the bearing balls.
- the annular bearing disks should be made of a hardenable iron material.
- Through-hardening is to be understood in a professional manner to achieve a uniform martensitic structure over the entire cross section of the bearing washers during the hardening process. This ensures that bearing disks produced in this way have a high fatigue strength that is sufficient for all applications.
- hardening materials come in In this context, unalloyed, low-alloyed or high-alloyed iron materials come into question. This can be, for example, steels of the brands C 45, C 55, Ck 67, C 75, 100 Cr 6 or 85 Mn 3.
- the annular bearing disks are to be produced by a non-cutting shaping process.
- non-cutting production is always particularly cost-effective, and on the other hand, this type of production ensures a favorable fiber orientation in the bearing washers, which has a positive effect on the durability properties.
- FIG. 1 shows a partial longitudinal section through a scroll compressor according to the prior art
- Figure 2 is a plan view of an annular bearing disc
- FIG. 3 shows a longitudinal section through an inventive three-point ball bearing for a scroll compressor
- FIG. 4 is an enlarged view of a partial longitudinal section through a further three-point ball bearing designed according to the invention. Detailed description of the drawings
- the scroll compressor shown schematically partially in FIGS. 1 and 2 has the housing 1, in the upper part of which the scroll 2 with its protruding scroll element 2a is arranged.
- the other movably arranged spiral 3 engages with its spiral element 3a in the spiral element 2a of the fixedly arranged spiral 2, so that the compression space 4 is formed, which is reduced or enlarged when the two spirals 2 and 3 move relative to one another, so that a gaseous or liquid medium is conveyable.
- the spiral 3 is connected at its center to the crank pin 5 of the rotary shaft 6, so that when it rotates with the eccentricity e it performs an orbital movement with respect to the fixed spiral 2.
- the spiral 3 is supported via the axial ball bearing 7 in the housing 1.
- This has a lower bearing disc 7.1 fixedly arranged in the housing 1 and an upper bearing disc 7.2 movably arranged with the spiral 3.
- Bearing balls 7.3 are arranged between the two bearing disks 7.1, 7.2 and run on separate circular tracks 7.4, 7.5, the circular tracks 7.4 being stationary and the circular tracks 7.5 being movable.
- the three-point ball bearing 8 according to the invention shown in FIG. 3 has the movable upper bearing disk 8.1 and the fixedly arranged lower bearing disk 8.2, between which the bearing balls 8.3 are arranged.
- the upper raceway 8.1.1 is roof-like in longitudinal section and has two surfaces 8.1.1.1 running at an angle to one another, the common center of which is the raised point 8.1.1.2.
- the lower ball raceway 8.2.1 has the radius R1, which is larger than the radius of the bearing balls 8.3. This ensures that the raceway 8.1.1 of the upper bearing plate 8.1 has two contact zones and the raceway 8.2.1 of the lower bearing plate 8.2 has a contact zone, which is not in the exemplary embodiment are specified.
- the three-point ball bearing 9 according to the invention shown in FIG. 4 consists of the upper bearing disk 9.1 and the lower bearing disk 9.2, between which bearing balls 9.3 roll on associated raceways 9.1.1, 9.2.1.
- the ball track 9.2.1 has a radius R2 which is larger than the radius of the bearing balls 9.3.
- the raceway 9.1.1 of the upper bearing disk 9.1 is composed of the two raceway segments 9.1.1.1 and 9.1.1.2, to which the associated radii R3 and R4 belong, both of which have the same amount.
- Both career segments 9.1.1.1 and 9.1.1.2 have a point of contact 9.4 located in the center of career 9.1.1.
- the radii R3 and R4 of the raceway segments 9.1.1.1 and 9.1.1.2 are also larger than the radius of the bearing balls 9.3 and have puncture points that are spaced apart in the radial direction. This creates a gap 9.5, which is formed by a part of the raceway segments 9.1.1.1, 9.1.1.2 that meet at the point of contact 9.4 and a part of the lateral surface of the bearing balls 9.3.
- the upper bearing disk 9.1 is provided with two contact zones 9.1.1.1.1 and 9.1.1.2.1, while the raceway 9.2.1 of the lower bearing disk 9.2 has the contact zone 9.2.1.1.
- the bearing balls 9.3 are guided over the two named contact zones of the upper bearing disk 9.1, so that the contact zone 9.2.1.1 of the lower bearing disk 9.2 can shift from its central position in one of the two directions, if necessary.
- the radii R3 and R4 are always the same and can have a different value to the radius R2. If the three radii R2, R3, R4 are identical, the same bearing is present in the entire bearing. reference numeral
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Spiralverdichter scroll compressor
Anwendungsgebiet der ErfindungField of application of the invention
Die Erfindung betrifft einen Spiralverdichter nach dem Oberbegriff von Anspruch 1.The invention relates to a scroll compressor according to the preamble of claim 1.
Hintergrund der ErfindungBackground of the Invention
In derartigen Spiralverdichtern, auch als Scroll-Kompressoren bezeichnet, erfolgt die Verdichtung durch eine Drehbewegung. Die Verdichter besitzen eine feststehende Spirale und eine sich exzentrisch dazu auf einer Kreisbahn bewegende zweite Spirale. Die Spiralen berühren sich an zwei bis drei Kontaktpaaren, die in sich geschlossene Räume bilden. Ein solcher Scroll-Kompressor zeichnet sich durch folgende Vorteile aus:In such scroll compressors, also known as scroll compressors, the compression takes place by means of a rotary movement. The compressors have a fixed scroll and a second scroll moving eccentrically to it on a circular path. The spirals touch at two to three pairs of contacts that form closed spaces. Such a scroll compressor has the following advantages:
hoher Liefergrad im mittleren Drehzahlbereich, gute Drehzahlfestigkeit, gleichmäßiger Drehmomentverlauf, unempfindlich gegen Flüssigkeitsschläge, kompakte Bauweise, geräuscharm und keine oszillierenden Massen.High degree of delivery in the medium speed range, good speed stability, even torque curve, insensitive to liquid hammer, compact design, low noise and no oscillating masses.
Ein solch gattungsgemäß ausgebildeter Spiralverdichter ist aus der US 5,758,978 vorbekannt. Dieser weist eine feststehende und eine bewegbare Spirale auf, die exzentrisch mit einer Drehwelle verbunden ist, um eine Orbitalbewegung ohne Drehung um eine Achse auszuführen. Durch das Zusammenwirken von feststehender und bewegbarer Spirale mit ihren ineinander greifenden Spiralanteilen ist ein in seinem Volumen veränderbarer Verdichtungsraum zur Förderung eines Mediums gebildet. Die bewegbare Spirale ist im Gehäuse zum Aufnehmen der Axialdruckbelastung über ein Axialkugellager abgestützt, das zwei voneinander beabstandete kreisringartige Lagerscheiben aufweist, die sich orbitierend zueinander bewegen, so dass zwischen diesen angeordnete Lagerkugeln auf zugehörigen Kreisbahnen abrollen. Die beiden kreisringartigen Lagerscheiben weisen Kugellaufbahnen mit einem unterschiedlichen Krümmungsradius auf, wobei diese Radien größer als der Radius der Lagerku- gel sind. Die Lagerkugeln liegen demnach immer nur in je einem Punkt an je einer Lagerscheibe an, dass heißt, es ist eine Zweipunktlagerung vorhanden.Such a generic scroll compressor is previously known from US 5,758,978. This has a fixed and a movable spiral, which is connected eccentrically to a rotary shaft in order to carry out an orbital movement without rotation about an axis. Through the interaction of the fixed and movable spiral with their interlocking spiral portions, a compression space that can be changed in terms of volume is formed to convey a medium. The movable spiral is supported in the housing for receiving the axial pressure load via an axial ball bearing, which has two annular bearing disks spaced apart from one another, orbit each other so that bearing balls arranged between them roll on associated circular paths. The two annular bearing disks have ball raceways with a different radius of curvature, these radii being larger than the radius of the bearing ball. The bearing balls are therefore only at one point on each bearing disc, which means that there is a two-point bearing.
Dabei ist von Nachteil, dass durch diese Zweipunktlagerung keine spielfreie Führung der Lagerkugeln durch die Lagerscheiben möglich ist. Bei einem plötzlichen Lastwechsel, der durch eine Druckänderung im Verdichtungsraum bedingt ist, entsteht ein störendes Geräusch, das durch eine Lageverschiebung der Lagerkugeln des Axiallagers verursacht wird. Dies ist möglich, weil die Lagerkugeln zwischen den beiden kreisringartigen Lagerscheiben spielbehaftet, dass heißt, nicht exakt geführt sind.The disadvantage here is that this two-point support means that the bearing balls cannot be guided through the bearing disks without play. In the event of a sudden load change, which is caused by a change in pressure in the compression chamber, there is a disturbing noise which is caused by a shift in the position of the bearing balls of the axial bearing. This is possible because the bearing balls between the two ring-shaped bearing disks have play, that is, are not guided exactly.
Zusammenfassung der ErfindungSummary of the invention
Der Erfindung liegt daher die Aufgabe zugrunde, eine Axiallagerung für einen Spiralverdichter zu entwickeln, die bei einer plötzlichen Änderung des Druckes, die mit einer veränderten axialen Belastung einhergeht, geringere Geräusche verursacht.The invention is therefore based on the object of developing an axial bearing for a scroll compressor which, when there is a sudden change in pressure, which is associated with a changed axial load, causes less noise.
Erfindungsgemäß wird diese Aufgabe nach dem kennzeichnenden Teil von Anspruch 1 in Verbindung mit dessen Oberbegriff dadurch gelöst, dass das Axialkugellager als ein Dreipunktkugellager ausgebildet ist, dessen eine Lagerscheibe zwei Kontaktzonen und dessen andere Lagerscheibe eine Kontaktzone aufweist.According to the invention, this object is achieved according to the characterizing part of claim 1 in connection with the preamble in that the axial ball bearing is designed as a three-point ball bearing, one bearing disc of which has two contact zones and the other of which bearing disc has a contact zone.
Der wesentliche Vorteil der erfindungsgemäßen Ausbildung des Kugellagers besteht darin, dass durch die zwei Kontaktzonen einer Lagerscheibe eine genaue Führung der Lagerkugeln möglich ist. Diese Lagerscheibe umfasst die Lagerkugeln im weitesten Sinne und hat demnach zwei Funktionen, zum einen eine Führungs- und zum anderen eine Lagerfunktion. Die zugehörige andere Lagerscheibe hingegen weist nur eine Kontaktzone für die Lagerkugeln auf, so dass diese innerhalb der gesamten Kugellaufbahnen ihre Lage verändern können. Dass heißt, die Lagerkugeln können während des Orbitierens immer an unterschiedlichen Stellen der Kugellaufbahnen anliegen, so dass die Kontaktzonen ihre Lage innerhalb der Kugellaufbahnen verändern können. Dies bedeutet, die zweite Lagerscheibe hat keine Führungsfunktion mehr, sondern nur eine reine Lagerfunktion. Durch diese ihre Lage ändernde Kontaktzonen der zweiten Lagerscheibe können neben der Geräuschverminderung zusätzlich Toleranzen ausgeglichen werden, so dass eine einfachere Herstellung des Spiralverdichters möglich ist.The main advantage of the design of the ball bearing according to the invention is that the two contact zones of a bearing disc enable the bearing balls to be guided precisely. This bearing disc encompasses the bearing balls in the broadest sense and therefore has two functions, firstly a management function and another a warehouse function. The associated other bearing disc, however, has only one contact zone for the bearing balls, so that they can change their position within the entire ball raceways. This means that the bearing balls can always rest at different points on the ball raceways during orbit, so that the contact zones can change their position within the ball raceways. This means that the second bearing disc no longer has a guiding function, but only a pure bearing function. Through these contact zones of the second bearing disk, which change their position, tolerances can be compensated in addition to the noise reduction, so that a simpler manufacture of the scroll compressor is possible.
Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen 2 bis 8 beschrieben.Advantageous developments of the invention are described in subclaims 2 to 8.
Aus den Ansprüchen 2 und 3 ist die Zuordnung der jeweiligen Kontaktzonen entnehmbar. So ist nach Anspruch 2 vorgesehen, dass die mit der bewegbaren Spirale verbundene Lagerscheibe zwei Kontaktzonen und die mit dem Gehäuse verbundene Lagerscheibe eine Kontaktzone aufweist. Die Umkehrung der Verfahrensweise geht aus Anspruch 3 hervor, wonach die mit der bewegbaren Spirale verbundene Lagerscheibe eine Kontaktzone und die mit dem Gehäuse verbundene Lagerscheibe zwei Kontaktzonen aufweisen soll.The assignment of the respective contact zones can be found in claims 2 and 3. It is provided according to claim 2 that the bearing disc connected to the movable spiral has two contact zones and the bearing disc connected to the housing has a contact zone. The reversal of the procedure is evident from claim 3, according to which the bearing disc connected to the movable spiral should have a contact zone and the bearing disc connected to the housing should have two contact zones.
Eine besonders vorteilhafte Ausbildung des beanspruchten Dreipunktkugella- gers ist in Anspruch 4 beschrieben. Danach soll eine Lagerscheibe eine Kugellaufbahn mit einem Radius R2 aufweisen, die andere Lagerscheibe eine aus zwei Laufbahnsegmenten mit den Radien R3 und R4 zusammengesetzte Kugellaufbahn besitzen, deren Einstichpunkte voneinander beabstandet sind, so dass ein im Zentrum dieser zusammengesetzten Kugellaufbahn liegender Be- rührungspunkt der Laufbahnsegmente gebildet ist, wobei R3 gleich R4 und R2, R3, R4 größer als ein Radius der Lagerkugeln sind. Auf diese Weise ist bei der Lagerscheibe mit zwei Kontaktzonen ein Spalt gebildet, der einerseits von einem Teil der Laufbahnsegmente und andererseits von einem Teil der Mantelfläche der Lagerkugeln gebildet ist.A particularly advantageous embodiment of the claimed three-point ball bearing is described in claim 4. According to this, one bearing disc should have a ball raceway with a radius R2, the other bearing disc should have a ball raceway composed of two raceway segments with the radii R3 and R4, the puncture points of which are spaced apart from one another, so that a contact point of the raceway segments lying in the center of this compound raceway is formed is, where R3 is equal to R4 and R2, R3, R4 are larger than a radius of the bearing balls. In this way, the Bearing disk with two contact zones formed a gap which is formed on the one hand by part of the raceway segments and on the other hand by part of the outer surface of the bearing balls.
Nach einem weiteren Merkmal der Erfindung gemäß Anspruch 5 ist vorgesehen, dass die Radien R2, R3 und R4 der Lagerscheiben einen gleichen Betrag aufweisen. Durch den gleichen Betrag der Radien ist sichergestellt, dass ein solches Lager an beiden Lagerscheiben die gleiche Schmiegung aufweist, wobei im Sinne der Erfindung unter Schmiegung nachstehendes Verhältnis zu verstehen ist:According to a further feature of the invention according to claim 5 it is provided that the radii R2, R3 and R4 of the bearing disks have the same amount. The same amount of radii ensures that such a bearing has the same osculation on both bearing disks, whereby in the context of the invention, osculation is to be understood as follows:
Schmiegung =
Eine andere erfindungsgemäße Variante des Dreipunktkugellagers geht aus Anspruch 6 hervor. Diese ist dadurch gekennzeichnet, dass eine Lagerscheibe eine dachartige, aus zwei unter einem Winkel zueinander geneigt verlaufende ebenen Flächen zusammengesetzte Laufbahn aufweist, während die andere Lagerscheibe eine Kugellaufbahn mit einem Radius R1 aufweist, der größer als ein Radius der Lagerkugeln ist.Another variant of the three-point ball bearing according to the invention is set out in claim 6. This is characterized in that one bearing disc has a roof-like raceway composed of two flat surfaces that are inclined at an angle to one another, while the other bearing disc has a ball raceway with a radius R1 that is larger than a radius of the bearing balls.
Nach einem anderen zusätzlichen Merkmal gemäß Anspruch 7 sollen die kreisringartigen Lagerscheiben aus einem durchhärtbaren Eisenwerkstoff hergestellt sein. Unter Durchhärten ist dabei in fachgemäßer Weise das Erzielen eines gleichmäßigen martensitischen Gefüges über den gesamten Querschnitt der Lagerscheiben beim Härtevorgang zu verstehen. Dadurch ist sichergestellt, dass derartig hergestellte Lagerscheiben eine hohe Dauerfestigkeit aufweisen, die allen Anwendungsfällen genügt. Als durchhärtende Werkstoffe kommen in diesem Zusammenhang unlegierte, niedrig legierte oder hoch legierte Eisenwerkstoffe in Frage. Dies können beispielsweise Stähle der Marken C 45, C 55, Ck 67, C 75, 100 Cr 6 oder 85 Mn 3 sein.According to another additional feature according to claim 7, the annular bearing disks should be made of a hardenable iron material. Through-hardening is to be understood in a professional manner to achieve a uniform martensitic structure over the entire cross section of the bearing washers during the hardening process. This ensures that bearing disks produced in this way have a high fatigue strength that is sufficient for all applications. As hardening materials come in In this context, unalloyed, low-alloyed or high-alloyed iron materials come into question. This can be, for example, steels of the brands C 45, C 55, Ck 67, C 75, 100 Cr 6 or 85 Mn 3.
Schließlich sollen nach einem letzten Merkmal der Erfindung gemäß Anspruch 8 die kreisringartigen Lagerscheiben durch einen spanlosen Formgebungsprozeß hergestellt sein. Zum einen ist eine spanlose Fertigung immer besonders kostengünstig und zum anderen wird durch diese Fertigungsart ein günstiger Faserverlauf in den Lagerscheiben sichergestellt, der sich positiv auf die Dau- erfestigkeitseigenschaften auswirkt.Finally, according to a last feature of the invention according to claim 8, the annular bearing disks are to be produced by a non-cutting shaping process. On the one hand, non-cutting production is always particularly cost-effective, and on the other hand, this type of production ensures a favorable fiber orientation in the bearing washers, which has a positive effect on the durability properties.
Die Erfindung wird an nachstehenden Ausführungsbeispielen näher erläutert.The invention is explained in more detail using the following exemplary embodiments.
Kurze Beschreibung der ZeichnungenBrief description of the drawings
Es zeigen:Show it:
Figur 1 einen teilweisen Längsschnitt durch einen Spiralverdichter nach dem bisherigen Stand der Technik,FIG. 1 shows a partial longitudinal section through a scroll compressor according to the prior art,
Figur 2 eine Draufsicht auf eine kreisringartige Lagerscheibe nachFigure 2 is a plan view of an annular bearing disc
Figur 1 ,Figure 1,
Figur 3 einen Längsschnitt durch ein erfindungsgemäß ausgestaltetes Dreipunktkugellager für einen Spiralverdichter und3 shows a longitudinal section through an inventive three-point ball bearing for a scroll compressor and
Figur 4 eine vergrößerte Darstellung eines teilweisen Längsschnittes durch ein weiteres erfindungsgemäß ausgestaltetes Dreipunktkugellager. Ausführliche Beschreibung der ZeichnungenFigure 4 is an enlarged view of a partial longitudinal section through a further three-point ball bearing designed according to the invention. Detailed description of the drawings
Der in den Figuren 1 und 2 schematisch teilweise dargestellte Spiralverdichter weist das Gehäuse 1 auf, in dessen oberen Teil die Spirale 2 mit ihrem hervor- stehenden Spiralelement 2a angeordnet ist. Die andere bewegbar angeordnete Spirale 3 greift mit ihrem Spiralelement 3a in das Spiralelement 2a der fest angeordnete Spirale 2 ein, so dass der Verdichtungsraum 4 gebildet ist, der bei einer relativen Bewegung der beiden Spiralen 2 und 3 zueinander verkleinert oder vergrößert wird, so dass ein gasförmiges oder flüssiges Medium förderbar ist. Die Spirale 3 ist in ihrem Zentrum mit dem Kurbelzapfen 5 der Drehwelle 6 verbunden, so dass sie bei deren Drehung mit der Exzentrizität e gegenüber der fest angeordneten Spirale 2 eine Orbitalbewegung ausführt. Die Spirale 3 ist über das Axialkugellager 7 im Gehäuse 1 abgestützt. Dieses besitzt eine fest im Gehäuse 1 angeordnete untere Lagerscheibe 7.1 und eine mit der Spi- rale 3 bewegbar angeordnete obere Lagerscheibe 7.2. Zwischen beiden Lagerscheiben 7.1 , 7.2 sind Lagerkugeln 7.3 angeordnet, die auf separaten Kreisbahnen 7.4, 7.5 umlaufen, wobei die Kreisbahnen 7.4 stationär und die Kreisbahnen 7.5 bewegbar sind.The scroll compressor shown schematically partially in FIGS. 1 and 2 has the housing 1, in the upper part of which the scroll 2 with its protruding scroll element 2a is arranged. The other movably arranged spiral 3 engages with its spiral element 3a in the spiral element 2a of the fixedly arranged spiral 2, so that the compression space 4 is formed, which is reduced or enlarged when the two spirals 2 and 3 move relative to one another, so that a gaseous or liquid medium is conveyable. The spiral 3 is connected at its center to the crank pin 5 of the rotary shaft 6, so that when it rotates with the eccentricity e it performs an orbital movement with respect to the fixed spiral 2. The spiral 3 is supported via the axial ball bearing 7 in the housing 1. This has a lower bearing disc 7.1 fixedly arranged in the housing 1 and an upper bearing disc 7.2 movably arranged with the spiral 3. Bearing balls 7.3 are arranged between the two bearing disks 7.1, 7.2 and run on separate circular tracks 7.4, 7.5, the circular tracks 7.4 being stationary and the circular tracks 7.5 being movable.
Das in Figur 3 dargestellte erfindungsgemäße Dreipunktkugellager 8 weist die bewegbare obere Lagerscheibe 8.1 und die fest angeordnete untere Lagerscheibe 8.2 auf, zwischen denen die Lagerkugeln 8.3 angeordnet sind. Diese rollen auf zugehörigen Laufbahnen 8.1.1 , 8.2.1 ab, die als dachartige Kugeltransportrille und als kreisförmige Kugelaufnahmerillen um 360° umlaufend voneinander in Umfangsrichtung beabstandet ausgebildet sind. Die obere Laufbahn 8.1.1 ist im Längsschnitt gesehen dachartig ausgestaltet und weist zwei unter einem Winkel zueinander geneigt verlaufende Flächen 8.1.1.1 auf, deren gemeinsames Zentrum der erhöhte Punkt 8.1.1.2 ist. Die untere Kugellaufbahn 8.2.1 weist den Radius R1 auf, der größer als der Radius der Lager- kugeln 8.3 ist. Auf diese Weise ist sichergestellt, dass die Laufbahn 8.1.1 der oberen Lagerscheibe 8.1 zwei Kontaktzonen und die Laufbahn 8.2.1 der unteren Lagerscheibe 8.2 eine Kontaktzone hat, die im Ausführungsbeispiel nicht näher bezeichnet sind.The three-point ball bearing 8 according to the invention shown in FIG. 3 has the movable upper bearing disk 8.1 and the fixedly arranged lower bearing disk 8.2, between which the bearing balls 8.3 are arranged. These roll on associated raceways 8.1.1, 8.2.1, which are designed as roof-like ball transport grooves and as circular ball receiving grooves which are circumferentially spaced apart from one another by 360 °. The upper raceway 8.1.1 is roof-like in longitudinal section and has two surfaces 8.1.1.1 running at an angle to one another, the common center of which is the raised point 8.1.1.2. The lower ball raceway 8.2.1 has the radius R1, which is larger than the radius of the bearing balls 8.3. This ensures that the raceway 8.1.1 of the upper bearing plate 8.1 has two contact zones and the raceway 8.2.1 of the lower bearing plate 8.2 has a contact zone, which is not in the exemplary embodiment are specified.
Das in Figur 4 dargestellte erfindungsgemäße Dreipunktkugellager 9 besteht aus der oberen Lagerscheibe 9.1 und der unteren Lagerscheibe 9.2, zwischen denen auf zugehörigen Laufbahnen 9.1.1 , 9.2.1 Lagerkugeln 9.3 abrollen. Die Kugellaufbahn 9.2.1 weist einen Radius R2 auf, der größer als der Radius der Lagerkugeln 9.3 ist. Die Laufbahn 9.1.1 der oberen Lagerscheibe 9.1 ist aus den zwei Laufbahnsegmenten 9.1.1.1 und 9.1.1.2 zusammengesetzt, zu denen die zugehörigen Radien R3 und R4 gehören, die beide einen gleichen Betrag aufweisen. Beide Laufbahnsegmente 9.1.1.1 und 9.1.1.2 haben einen im Zentrum der Laufbahn 9.1.1 liegenden Berührungspunkt 9.4. Die Radien R3 und R4 der Laufbahnsegmente 9.1.1.1 und 9.1.1.2 sind ebenfalls größer als der Radius der Lagerkugeln 9.3 und weisen Einstichpunkte auf, die in radialer Richtung voneinander beabstandet sind. Dadurch entsteht ein Spalt 9.5, der von einem Teil der im Berührungspunkt 9.4 sich vereinenden Laufbahnsegmente 9.1.1.1 , 9.1.1.2 und einem Teil der Mantelfläche der Lagerkugeln 9.3 gebildet ist. Wie die Figur 4 weiter zeigt, ist die obere Lagerscheibe 9.1 mit zwei Kontaktzonen 9.1.1.1.1 und 9.1.1.2.1 versehen, während die Laufbahn 9.2.1 der unteren Lagerscheibe 9.2 die Kontaktzone 9.2.1.1 besitzt. Die Führung der Lagerkugeln 9.3 wird über die beiden genannten Kontaktzonen der oberen Lagerscheibe 9.1 realisiert, so dass sich die Kontaktzone 9.2.1.1 der unteren Lagerscheibe 9.2 aus ihrer Mittellage in eine der beiden Richtungen verschieben kann, falls erforderlich. Die Radien R3 und R4 sind immer gleich und können einen unterschiedlichen Wert zum Radius R2 annehmen. Bei Gleichheit der drei genann- ten Radien R2, R3, R4 liegen im gesamten Lager gleiche Schmiegungen vor. BezugszeichenThe three-point ball bearing 9 according to the invention shown in FIG. 4 consists of the upper bearing disk 9.1 and the lower bearing disk 9.2, between which bearing balls 9.3 roll on associated raceways 9.1.1, 9.2.1. The ball track 9.2.1 has a radius R2 which is larger than the radius of the bearing balls 9.3. The raceway 9.1.1 of the upper bearing disk 9.1 is composed of the two raceway segments 9.1.1.1 and 9.1.1.2, to which the associated radii R3 and R4 belong, both of which have the same amount. Both career segments 9.1.1.1 and 9.1.1.2 have a point of contact 9.4 located in the center of career 9.1.1. The radii R3 and R4 of the raceway segments 9.1.1.1 and 9.1.1.2 are also larger than the radius of the bearing balls 9.3 and have puncture points that are spaced apart in the radial direction. This creates a gap 9.5, which is formed by a part of the raceway segments 9.1.1.1, 9.1.1.2 that meet at the point of contact 9.4 and a part of the lateral surface of the bearing balls 9.3. As FIG. 4 also shows, the upper bearing disk 9.1 is provided with two contact zones 9.1.1.1.1 and 9.1.1.2.1, while the raceway 9.2.1 of the lower bearing disk 9.2 has the contact zone 9.2.1.1. The bearing balls 9.3 are guided over the two named contact zones of the upper bearing disk 9.1, so that the contact zone 9.2.1.1 of the lower bearing disk 9.2 can shift from its central position in one of the two directions, if necessary. The radii R3 and R4 are always the same and can have a different value to the radius R2. If the three radii R2, R3, R4 are identical, the same bearing is present in the entire bearing. reference numeral
1 Gehäuse 9.2 untere Lagerscheibe1 housing 9.2 lower bearing washer
2 feststehende Spirale 9.2.1 Laufbahn2 fixed spiral 9.2.1 career
2a Spiralelement 9.2.1.1 Kontaktzone2a spiral element 9.2.1.1 contact zone
3 bewegbare Spirale 9.3 Lagerkugel3 movable spiral 9.3 bearing ball
3a Spiralelement 9.4 Berührungspunkt3a spiral element 9.4 point of contact
4 Verdichtungsraum 9.5 Spalt4 Compression chamber 9.5 gap
5 Kurbelzapfen5 crank pins
6 Drehwelle e Exzentrizität 7 Axialkugellager6 rotary shaft e eccentricity 7 axial ball bearings
7.1 untere Lagerscheibe R1 , R27.1 lower bearing washer R1, R2
7.2 obere Lagerscheibe R3, R4 Radien7.2 upper bearing washer R3, R4 radii
7.3 Lagerkugel7.3 bearing ball
7.4 Kreisbahn7.4 circular path
7.5 Kreisbahn7.5 circular path
8 Dreipunktkugellager8 three-point ball bearings
8.1 obere Lagerscheibe8.1 upper bearing disc
8.1.1 Laufbahn8.1.1 Career
8.1.1.1 Fläche8.1.1.1 area
8.1.1.2 Punkt8.1.1.2 point
8.2 untere Lagerscheibe8.2 lower bearing disc
8.2.1 Laufbahn8.2.1 Career
8.3 Lagerkugel8.3 bearing ball
9 Dreipunktkugellager9 three-point ball bearings
9.1 obere Lagerscheibe9.1 upper bearing disc
9.1.1 Laufbahn9.1.1 Career
9.1.1.1 Laufbahnsegment9.1.1.1 Career segment
9.1.1.1.1 Kontaktzone9.1.1.1.1 Contact zone
9.1.1.2 Laufbahnsegment9.1.1.2 Career segment
9.1.1.2.1 Kontaktzone9.1.1.2.1 Contact zone
9.2 9.2
Claims
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AU2003273966A AU2003273966A1 (en) | 2002-10-18 | 2003-10-09 | Helical rotary compressor |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US41969702P | 2002-10-18 | 2002-10-18 | |
| US60/419,697 | 2002-10-18 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2004038242A1 true WO2004038242A1 (en) | 2004-05-06 |
Family
ID=32176477
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/EP2003/011169 Ceased WO2004038242A1 (en) | 2002-10-18 | 2003-10-09 | Helical rotary compressor |
Country Status (2)
| Country | Link |
|---|---|
| AU (1) | AU2003273966A1 (en) |
| WO (1) | WO2004038242A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7448806B2 (en) * | 2002-02-20 | 2008-11-11 | Nsk Ltd. | Rotation support device for compressor pulley |
| CN106065899A (en) * | 2015-04-23 | 2016-11-02 | 斯凯孚公司 | Rolling bearing, high-speed bearing device and compressor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63266215A (en) * | 1987-04-22 | 1988-11-02 | Daikin Ind Ltd | Ball joint mechanism |
| JPH04128581A (en) * | 1990-09-19 | 1992-04-30 | Tokico Ltd | scroll compressor |
| US5758978A (en) * | 1996-04-05 | 1998-06-02 | Ntn Corporation | Thrust ball bearing |
| JPH11210766A (en) * | 1997-11-07 | 1999-08-03 | Nippon Seiko Kk | 3-point contact ball bearing |
| EP1118783A2 (en) * | 2000-01-21 | 2001-07-25 | INA Wälzlager Schaeffler oHG | Thrust ball bearing |
-
2003
- 2003-10-09 WO PCT/EP2003/011169 patent/WO2004038242A1/en not_active Ceased
- 2003-10-09 AU AU2003273966A patent/AU2003273966A1/en not_active Abandoned
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63266215A (en) * | 1987-04-22 | 1988-11-02 | Daikin Ind Ltd | Ball joint mechanism |
| JPH04128581A (en) * | 1990-09-19 | 1992-04-30 | Tokico Ltd | scroll compressor |
| US5758978A (en) * | 1996-04-05 | 1998-06-02 | Ntn Corporation | Thrust ball bearing |
| JPH11210766A (en) * | 1997-11-07 | 1999-08-03 | Nippon Seiko Kk | 3-point contact ball bearing |
| EP1118783A2 (en) * | 2000-01-21 | 2001-07-25 | INA Wälzlager Schaeffler oHG | Thrust ball bearing |
Non-Patent Citations (3)
| Title |
|---|
| PATENT ABSTRACTS OF JAPAN vol. 0130, no. 65 (M - 797) 14 February 1989 (1989-02-14) * |
| PATENT ABSTRACTS OF JAPAN vol. 0163, no. 91 (M - 1298) 19 August 1992 (1992-08-19) * |
| PATENT ABSTRACTS OF JAPAN vol. 1999, no. 13 30 November 1999 (1999-11-30) * |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7448806B2 (en) * | 2002-02-20 | 2008-11-11 | Nsk Ltd. | Rotation support device for compressor pulley |
| CN106065899A (en) * | 2015-04-23 | 2016-11-02 | 斯凯孚公司 | Rolling bearing, high-speed bearing device and compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| AU2003273966A1 (en) | 2004-05-13 |
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