EP2196671B1 - Piston vacuum pump - Google Patents
Piston vacuum pump Download PDFInfo
- Publication number
- EP2196671B1 EP2196671B1 EP09014531.9A EP09014531A EP2196671B1 EP 2196671 B1 EP2196671 B1 EP 2196671B1 EP 09014531 A EP09014531 A EP 09014531A EP 2196671 B1 EP2196671 B1 EP 2196671B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- bushing
- vacuum pump
- seal
- liner
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000001816 cooling Methods 0.000 claims description 18
- 230000033001 locomotion Effects 0.000 claims description 6
- 230000000737 periodic effect Effects 0.000 claims description 4
- 230000000694 effects Effects 0.000 claims 1
- 238000007789 sealing Methods 0.000 claims 1
- 239000002826 coolant Substances 0.000 description 31
- 239000007789 gas Substances 0.000 description 12
- 239000012530 fluid Substances 0.000 description 9
- 238000011161 development Methods 0.000 description 5
- 230000018109 developmental process Effects 0.000 description 5
- 239000000498 cooling water Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000000565 sealant Substances 0.000 description 1
Images
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
- F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
- F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
- F04B37/14—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high vacuum
-
- 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
- F04B39/06—Cooling; Heating; Prevention of freezing
-
- 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
- F04B39/06—Cooling; Heating; Prevention of freezing
- F04B39/064—Cooling by a cooling jacket in the pump casing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/126—Cylinder liners
-
- 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
- F04B53/143—Sealing provided on 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
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
- F04B53/166—Cylinder liners
Definitions
- the invention relates to a piston vacuum pump according to the preamble of the first claim.
- Reciprocating vacuum pumps for generating coarse and fine vacuums are known in the prior art.
- a dry runner i. without lubricants and sealants in the area of the pump chamber
- They are successful on the market due to their properties, for example their high suction capacity for light gases.
- the reciprocating piston of such a piston vacuum pump performs a reciprocating motion in a bushing.
- a gasket contacting this bushing seals the gap between the piston and the bush. This seal is subject to wear, which is increased by the freedom of lubricant.
- the DE 101 09 514 C1 describes a similar piston vacuum pump.
- the coolant which is in heat transferring contact with the bushing, absorbs heat from the bushing. This heat is created by the friction of the seal on the liner wall. The removal of heat leads to a cooling of the bushing and the seal. As a result, the service life of the seal is significantly extended. At the same time, the service intervals of the piston vacuum pump are extended.
- the cooling means comprises a closed circuit, comprising an evaporator and a condenser, in which the evaporator is in contact with the bushing.
- a closed circuit comprising an evaporator and a condenser, in which the evaporator is in contact with the bushing.
- this can be structurally particularly simple in that the bushing has a tangential bore in which the evaporator is arranged. This allows easy manufacture of the parts and easy assembly. The evaporator receives a very good thermal contact with the Bushing, so that a good heat dissipation and the life of the seal is significantly increased.
- the cooling means comprises a heat-conducting body, which has a higher thermal conductivity than a cylinder accommodating the bushing.
- the cooling means comprises a coolant channel, which is arranged in a cylinder receiving the bush, such that the bushing has its boundary surface facing it limited to the channel. In such a channel flows a heat receiving fluid, such as cooling water. Due to the claimed design, the fluid comes into direct contact with the liner, so that an excellent heat transfer is ensured. This results in a very good life extension.
- a cylinder 20 With the housing, a cylinder 20 is connected gas-tight, which receives a bush 22.
- the liner is fitted over a portion of its longitudinal axis with a shrink fit in the bore of the cylinder.
- a reciprocating piston 24 In the bushing is a reciprocating piston 24 which is connected via a connecting rod 26 with the crank pin. Through this connection, the reciprocating piston performs a periodic movement.
- the crankshaft drive, crankshaft pulley and crankpin causes reciprocating movement between two turning points.
- the first turning point 27 is located between the end of the crankcase facing the crank chamber and gas inlet holes 28 which are provided distributed over the circumference of the bushing and establish a gas connection to the inlet channel 30.
- This inlet channel surrounds the bushing at least in sections in the circumferential direction and in turn is in gas communication with the pump gas inlet 32.
- the second turning point 33 is located near the end of the bushing facing away from the crank space. It is so dimensioned that the piston contacts the valve cover 34 and lifts off from the end of the bushing. This end of the bushing forms the valve seat on which the valve cover sits in the other phases of Hubkolbenhubes.
- the valve cover is provided with a layer 36 which causes a damping of the contact of the valve cover and the piston and a seal.
- the valve cover is biased by a valve spring 38 in the direction of bushing.
- a seal 48 is arranged between sleeve wall and reciprocating piston. This seals the gap between bushing and piston and thus the suction chamber against the crank chamber. This seal is subject to wear due to friction on the inner liner wall.
- a heat conducting body 50 is in heat transferring contact with the bushing.
- the material of this has a higher thermal conductivity than the material of the bushing receiving cylinder.
- an aluminum alloy is used for the cylinder.
- As a material for the heat-conducting copper is suitable. Other materials with even higher thermal conductivity than copper can be used advantageously.
- the heat-conducting body forms a heat connection between the bushing and the space outside the cylinder. It can be cooled by convection of the ambient air or by thermal contact with an external cooling circuit, not shown.
- the claimed embodiment of the piston vacuum pump is in Fig.2 shown in a section perpendicular to the piston axis through the cylinder. Compared to the first embodiment, the area of the cylinder is changed.
- the cylinder 220 surrounds the bush 222.
- a through hole 224 is provided, which connects the surface of the cylinder with the bushing.
- a bore 226 is provided in the bushing.
- Bore and through hole partially receive a heat pipe 230.
- the heat pipe has an evaporator 232 at the end of the evaporator and a condenser 234 at the end of the condenser.
- the heat pipe contains a fluid which changes from a liquid to a gaseous state in the evaporator. It absorbs heat from the liner. In the inner part 236 of the heat pipe, the vaporized fluid is supplied to the condenser end.
- the inner part may be a cavity
- a porous structure is used for the outer part 238, which causes the conveyance of the fluid with capillary forces.
- the Konsendatorende is located outside the cylinder and is in contact with a heat sink 240 in such a way that it absorbs the heat from the condenser end and radiates to the environment. If a convection cooling of the heat sink is not sufficient, the temperature of the leaf bushing to the desired extent to lower, the condenser end or the heat sink is forcibly cooled. This is possible with a fan or by connecting with coolants, for example with the heat exchanger of a cooling water circuit.
- FIG. 3 An unclaimed embodiment is in Fig. 3 shown. Compared to the other embodiments, the area of the cylinder is changed. Engine, crank mechanism and housing correspond to the previous embodiments. In this figure, the cylinder arrangement is shown in a section along the cylinder axis. The piston 324 moves within the bushing 322 received by the cylinder 320 between the first turning point 327 and the second turning point 333.
- the inlet bore 328 through which gas passes from the inlet channel 330 connected to the vessel to be evacuated or another pumping stage into the suction chamber 340.
- the inlet channel forms an annular space surrounding the bushing.
- the piston lifts the valve cover 334 provided with the valve layer 336 against the spring force of the valve spring 338 from the valve seat, so that the compressed gas is expelled from the pump chamber.
- the valve arrangement is arranged in the cylinder cover 346. Between the piston and liner seals the seal 348, so that no gas can escape the pump chamber via the gap between the piston and sleeve.
- the bushing has a bushing coating 323 on the side in contact with the seal.
- an annular coolant passage 350 surrounds the bushing.
- the piston speed is greatest, as far as a crank mechanism according to the first embodiment is used.
- the coolant channel circulates a fluid which receives heat from the liner, for example, cooling water, which has a temperature equal to or below the room temperature. So that the heat transfer takes place in the best possible way, the fluid comes directly into contact with the outer wall of the liner.
- the coolant thus comprises a coolant channel 350, which is arranged in such a cylinder receiving the bushing, that the bushing limits the boundary surface of the channel facing it.
- a seal 352 is arranged between coolant channel 350 and inlet channel 330. Another seal 360 seals the gap between the bushing and the cylinder and thus the coolant channel against the outlet chamber 342.
- the fluid is fed via a coolant inlet 354 into the coolant channel and then discharged to the coolant outlet 356.
- Coolant inlet and outlet are part of a cooling water installation in a simple design.
- the coolant is separated from the coolant inlet and the coolant outlet and transfers the heat to the latter via a heat exchanger. Between heat exchanger and coolant then a circulation pump is additionally provided.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Description
Die Erfindung betrifft eine Kolbenvakuumpumpe nach dem Oberbegriff des ersten Anspruchs.The invention relates to a piston vacuum pump according to the preamble of the first claim.
Im Stand der Technik sind Hubkolbenvakuumpumpen zur Erzeugung von Grob- und Feinvakua bekannt. Insbesondere als Trockenläufer, d.h. ohne Schmier- und Dichtmittel im Bereich des Schöpfraumes, sind sie aufgrund ihrer Eigenschaften, beispielsweise ihres hohen Saugermögens für leichte Gase, am Markt erfolgreich. Der Hubkolben einer solchen Kolbenvakuumpumpe führt in einer Laufbuchse eine reziprokierende Bewegung aus. Eine diese Laufbuchse berührende Dichtung dichtet den Spalt zwischen Hubkolben und Laufbuchse ab. Diese Dichtung unterliegt Verschleiß, der durch die Schmiermittelfreiheit erhöht wird.Reciprocating vacuum pumps for generating coarse and fine vacuums are known in the prior art. In particular, as a dry runner, i. without lubricants and sealants in the area of the pump chamber, they are successful on the market due to their properties, for example their high suction capacity for light gases. The reciprocating piston of such a piston vacuum pump performs a reciprocating motion in a bushing. A gasket contacting this bushing seals the gap between the piston and the bush. This seal is subject to wear, which is increased by the freedom of lubricant.
Verschiedene Lösungen zur Erhöhung der Standzeit dieser Dichtung sind bekannt. So schlägt die
Ferner ist aus der
Die
In der
Es ist eine Aufgabe der Erfindung, eine Kolbenvakuumpumpe zu schaffen, in der mit einfachen Mitteln die Standzeit der Dichtung verlängert wird.It is an object of the invention to provide a piston vacuum pump in which the life of the seal is extended by simple means.
Diese Aufgabe wird gelöst durch eine Kolbenvakuumpumpe mit den Merkmalen des ersten Anspruchs. Die abhängigen Anspruch 2 bis 4 geben vorteilhafte Weiterbildungen der Erfindung an.This object is achieved by a piston vacuum pump having the features of the first claim. The dependent claims 2 to 4 indicate advantageous developments of the invention.
Das Kühlungsmittel, welches mit der Laufbuchse in Wärme übertragendem Kontakt steht, nimmt Wärme von der Laufbuchse auf. Diese Wärme entsteht durch die Reibung der Dichtung an der Laufbuchsenwandung. Das Abführen der Wärme führt zu einer Kühlung der Laufbuchse und der Dichtung. Hierdurch wird die Standzeit der Dichtung deutlich verlängert. Damit verlängern sich gleichzeitig die Serviceintervalle der Kolbenvakuumpumpe.The coolant, which is in heat transferring contact with the bushing, absorbs heat from the bushing. This heat is created by the friction of the seal on the liner wall. The removal of heat leads to a cooling of the bushing and the seal. As a result, the service life of the seal is significantly extended. At the same time, the service intervals of the piston vacuum pump are extended.
Erfindungsgemäß umfasst das Kühlungsmittel einen geschlossenen, einen Verdampfer und einen Kondensator aufweisenden Kreislauf, bei dem der Verdampfer mit der Laufbuchse in Kontakt steht. Ein solcher Kreislauf ist ein effizientes Mittel, Wärme abzuführen. Große Wärmemengen können transportiert werden, so dass auch bei hohen Beanspruchungen der Kolbenvakuumpumpe, beispielsweise durch hohe Gaslasten, die Temperatur von Laufbuchse und Dichtung so niedrig gehalten wird, dass die Standzeit der Dichtung erheblich verlängert wird.According to the invention, the cooling means comprises a closed circuit, comprising an evaporator and a condenser, in which the evaporator is in contact with the bushing. Such a circuit is an efficient means of dissipating heat. Large amounts of heat can be transported, so that even at high loads of the piston vacuum pump, for example by high gas loads, the temperature of liner and seal is kept so low that the service life of the seal is considerably extended.
Gemäß einer ersten Weiterbildung lässt sich dies konstruktiv besonders einfach gestalten, indem die Laufbuchse eine tangentiale Bohrung aufweist, in welcher der Verdampfer angeordnet ist. Dies erlaubt eine einfache Herstellung der Teile und eine leichte Montage. Der Verdampfer erhält einen sehr guten Wärmekontakt zur Laufbuchse, so dass eine gute Wärmeableitung entsteht und die Standzeit der Dichtung deutlich erhöht wird.According to a first development, this can be structurally particularly simple in that the bushing has a tangential bore in which the evaporator is arranged. This allows easy manufacture of the parts and easy assembly. The evaporator receives a very good thermal contact with the Bushing, so that a good heat dissipation and the life of the seal is significantly increased.
In einer nicht beanspruchten beispielhaften Ausführungsmöglichkeit umfasst das Kühlungsmittel einen Wärmeleitkörper, welcher eine höhere Wärmeleitzahl als ein die Laufbuchse aufnehmender Zylinder aufweist. Dies stellt eine einfache Bauform dar, die bei geringen Beanspruchungen der Kolbenvakuumpumpe durch geringe Gaslasten eine ausreichende Kühlung und damit Standzeitverlängerung bewirkt. In einer weiteren nicht beanspruchten beispielhaften Ausführungsmöglichkeit umfasst das Kühlungsmittel einen Kühlmittelkanal, der derart in einem die Laufbuchse aufnehmenden Zylinder angeordnet ist, dass die Laufbuchse die ihr zugewandte Begrenzungsfläche des Kanals begrenzt. In einem solchem Kanal strömt ein Wärme aufnehmendes Fluid, beispielsweise Kühlwasser. Durch die beanspruchte Gestaltung gelangt das Fluid in direkten Kontakt mit der Laufbuchse, so dass ein hervorragender Wärmeübergang gewährleistet ist. Hieraus resultiert eine sehr gute Standzeitverlängerung.In an exemplary embodiment not claimed, the cooling means comprises a heat-conducting body, which has a higher thermal conductivity than a cylinder accommodating the bushing. This represents a simple design, which causes low cooling of the piston vacuum pump by low gas loads sufficient cooling and thus service life extension. In a further exemplary embodiment which is not claimed, the cooling means comprises a coolant channel, which is arranged in a cylinder receiving the bush, such that the bushing has its boundary surface facing it limited to the channel. In such a channel flows a heat receiving fluid, such as cooling water. Due to the claimed design, the fluid comes into direct contact with the liner, so that an excellent heat transfer is ensured. This results in a very good life extension.
Die bisher genannten Weiterbildungen werden verbessert, indem das Kühlungsmittel auf halbem Weg zwischen einem ersten und einem zweiten Umkehrpunkt der periodischen Bewegung angeordnet ist. An dieser Stelle ist die Relativgeschwindigkeit der Dichtung gegenüber der Laufbuchse am größten. Damit ist dort die Kühlung am wirkungsvollsten. Eine solche Anordnung ist einfacher als eine Kühlung über die komplette Laufbauchsenoberfläche und spart Kosten bei Teilen und Montageaufwand ein. Die Standzeitverlängerung wird daher mit geringem Aufwand erreicht.The above-mentioned developments are improved by the coolant is arranged midway between a first and a second reversal point of the periodic movement. At this point, the relative speed of the seal against the liner is greatest. This is where the cooling is most effective. Such an arrangement is simpler than cooling over the entire barrel trough surface and saves costs in parts and assembly work. The service life extension is therefore achieved with little effort.
Anhand von Ausführungsbeispielen soll die Erfindung näher erläutert und die Vorteile vertieft werden. Es zeigen:
-
Fig. 1 : Schnitt durch eine Kolbenvakuumpumpe, umfassend einen Wärmeleitkörper als Kühlungsmittel (nicht beasnpruchtes Ausführungsbeispiel). -
Fig. 2 : Schnitt senkrecht zur Kolbenachse durch die Zylinderanordnung einer Kolbenvakuumpumpe gemäß des in den Patentansprüchen definierten Ausführungsbeipiels. -
Fig. 3 : Schnitt entlang der Hubkolbenachse durch die Zylinderanordnung einer Kolbenvakuumpumpe, umfassend einen Kühlmittelkanal als Kühlungsmittel (nicht beasnpruchtes Ausführungsbeispiel). -
Fig. 4 : Schnitt senkrecht zur Kolbenachse durch die Zylinderanordnung einer Kolbenvakuumpumpe gemäß einer Weiterbildung des obigen, nicht beanspruchten Ausführungsbeipiels. Ein nicht beanspruchtes Beispiel einerKolbenvakuumpumpe 1 mit einemGehäuse 2 ist inFig. 1 gezeigt. Das Gehäuse beherbergt eine inWellenlagern 6 und 7 drehbargelagerte Welle 4. Die Welle trägtPermanentmagnete 8, welche mitfeststehenden Spulen 10 derart zusammenwirken, dass die Welle in Drehung versetzt wird. Spulen und Permanentmagnete bilden in diesem Sinne den Antrieb diese Kolbenvakuumpumpe. Die für die Drehung notwendige Bestromung der Spulen geschieht durch eine nicht gezeigte Steuerelektronik. Ein Ende der Welle ragt in den Kurbelraum 12. Mit diesem Ende der Welle ist eineKurbelscheibe 14 verbunden, die einenKurbelzapfen 16 trägt. Je nach Gestaltung des Gehäuseteils, der den Antrieb und die Lagerung umfasst, ist eineWellendichtung 18 zum Kurbelraum notwendig, so dass dieser evakuiert werden kann.
-
Fig. 1 : Section through a piston vacuum pump, comprising a heat-conducting body as a cooling means (unsuitable embodiment). -
Fig. 2 : Section perpendicular to the piston axis through the cylinder arrangement of a piston vacuum pump according to the Ausführungsbeipiels defined in the claims. -
Fig. 3 : Section along the Hubkolbenachse through the cylinder assembly of a piston vacuum pump, comprising a coolant channel as a cooling means (unused embodiment). -
Fig. 4 : Section perpendicular to the piston axis through the cylinder arrangement of a piston vacuum pump according to a development of the above, not claimed Ausführungsbeipiels. An unclaimed example of apiston vacuum pump 1 with ahousing 2 is shown in FIGFig. 1 shown. The housing houses ashaft 4 rotatably mounted in 6 and 7. The shaft carriesshaft bearings permanent magnets 8 which cooperate withstationary coils 10 in such a way that the shaft is rotated. Coils and permanent magnets form in this sense the drive this piston vacuum pump. The necessary for the rotation energization of the coils is done by a control electronics, not shown. One end of the shaft protrudes into the crank chamber 12. Connected to this end of the shaft is acrank disk 14, which carries acrank pin 16. Depending on the design of the housing part, which includes the drive and the storage, ashaft seal 18 to the crankcase is necessary so that it can be evacuated.
Mit dem Gehäuse ist ein Zylinder 20 gasdicht verbunden, welcher eine Laufbuchse 22 aufnimmt. Die Laufbuchse ist über einen Teil ihrer Längsachse mit einem Schrumpfsitz in die Bohrung des Zylinders eingepasst. In der Laufbuchse befindet sich ein Hubkolben 24, der über einen Pleuel 26 mit dem Kurbelzapfen verbunden ist. Durch diese Verbindung führt der Hubkolben eine periodische Bewegung aus. In dem in
Der erste Umkehrpunkt 27 liegt zwischen dem dem Kurbelraum zugewandten Ende der Laufbuchse und Gaseinlassbohrungen 28, die über den Umfang der Laufbuchse verteilt vorgesehen sind und eine Gasverbindung zum Einlasskanal 30 herstellen. Dieser Einlasskanal umgibt die Laufbuchse wenigstens abschnittsweise in Umfangsrichtung und steht wiederum in Gasverbindung mit dem Pumpengaseinlass 32.The
Der zweite Umkehrpunkt 33 liegt nahe dem dem Kurbelraum abgewandten Ende der Laufbuchse. Er ist dabei so bemessen, dass der Hubkolben den Ventildeckel 34 berührt und vom Ende der Laufbuchse abhebt. Dieses Ende der Laufbuchse bildet den Ventilsitz auf dem der Ventildeckel in den anderen Phasen des Hubkolbenhubes sitzt. Der Ventildeckel ist mit einer Schicht 36 versehen, die eine Dämpfung der Berührung von Ventildeckel und Hubkolben und eine Abdichtung bewirkt. Der Ventildeckel ist durch eine Ventilfeder 38 in Richtung Laufbuchse vorgespannt. Befindet sich der Hubkolben in der Nähe des zweiten Umkehrpunktes, wird Gas aus dem Schöpfraum 40 in die Auslasskammer 42 ausgestoßen. Von dort gelangt es dann zum Pumpengasauslass 44, der zusammen mit der Auslasskammer, Ventildeckel und Ventilfeder in einem mit dem Zylinder gasdicht verbundenen Zylinderdeckel 46 angeordnet ist.The
Zwischen Laufbuchseninnwand und Hubkolben ist eine Dichtung 48 angeordnet. Diese dichtet den Spalt zwischen Laufbuchse und Hubkolben und damit den Schöpfraum gegen den Kurbelraum ab. Diese Dichtung ist durch die Reibung an der Laufbuchseninnenwand Verschleiß ausgesetzt.Between sleeve wall and reciprocating piston a
Ein Wärmeleitkörper 50 steht in Wärme übertragendem Kontakt mit der Laufbuchse. Das Material dieses Wärmeleitkörpers weist eine höhere Wärmeleitzahl auf als das Material des die Laufbuchse aufnehmenden Zylinders. Typischerweise wird für den Zylinder eine Aluminiumlegierung verwendet. Als Material für den Wärmeleitkörper ist Kupfer geeignet. Andere Materialien mit noch höherer Wärmeleitzahl als Kupfer sind vorteilhaft verwendbar. Der Wärmeleitkörper bildet eine Wärmeverbindung zwischen Laufbuchse und dem Raum außerhalb des Zylinders. Er kann durch Konvektion der Umgebungsluft oder durch Wärmekontakt mit einem nicht gezeigten externen Kühlkreislauf gekühlt werden. Das beanspruchte Ausführungsbeispiel der Kolbenvakuumpumpe ist in
Das Verdampferende ist in der Bohrung angeordnet und steht in Kontakt mit der Innenwand der Bohrung und damit mit der Laufbuchse. Der Kontakt entsteht beispielsweise durch eine möglichst enge Passung, so dass Wärme leicht übertragen werden kann. Die Wärmeübertragung kann durch Ausfüllen etwaig zwischen Verdampferende und Innenwand der Bohrung verbleibenden Leerräumen mit Wärmeleitpaste verbessert werden.The evaporator end is disposed in the bore and is in contact with the inner wall of the bore and thus with the liner. The contact arises, for example, by a close fit as possible, so that heat can be easily transferred. The heat transfer can be improved by filling any gaps between the end of the evaporator and the inner wall of the bore with thermal grease.
Das Konsendatorende befindet sich außerhalb des Zylinders und steht mit einem Kühlkörper 240 derart in Kontakt, dass dieser die Wärme vom Kondensatorende aufnimmt und an die Umgebung abstrahlt. Sollte eine Konvektionskühlung des Kühlkörpers nicht ausreichen, die Temperatur der Laubuchse in gewünschtem Maße abzusenken, wird das Kondensatorende oder der Kühlkörper zwangsgekühlt. Dies gelingt mit einem Lüfter oder durch Verbinden mit Kühlmitteln, beispielsweise mit dem Wärmetauscher eines Kühlwasserkreislaufs.The Konsendatorende is located outside the cylinder and is in contact with a
Vorteilhaft sind Verdampferende und Kondensatorende derart gegenüber der Schwerkraftrichtung 260 orientiert, dass das Kondensatorende höher als das Verdampferende liegt.Advantageously, the end of the evaporator and the end of the condenser are oriented with respect to the direction of
Ein nicht beanspruchtes Ausführungsbeispiel ist in
Im ersten Umkehrpunkt gibt er die Einlassbohrung 328 frei, durch die Gas aus dem mit dem zu evakuierenden Gefäß oder einer weiteren Pumpstufe verbundenen Einlasskanal 330 in den Schöpfraum 340 gelangt. Der Einlasskanal bildet einen ringförmigen Raum, der die Laufbuchse umgibt.In the first reversal point, it releases the inlet bore 328, through which gas passes from the
Am zweiten Umkehrpunkt hebt der Kolben den mit der Ventilschicht 336 versehenen Ventildeckel 334 gegen die Federkraft der Ventilfeder 338 vom Ventilsitz ab, so dass das verdichtete Gas aus dem Schöpfraum ausgestoßen wird. Die Ventilanordnung ist im Zylinderdeckel 346 angeordnet. Zwischen Kolben und Laufbuchse dichtet die Dichtung 348 ab, so dass kein Gas dem Schöpfraum über den Spalt zwischen Kolben und Laufbuchse entweichen kann. Um den Verschleiß der Dichtung herabzusetzen, weist die Laufbuchse auf der mit der Dichtung in Berührung kommenden Seite eine Laufbuchsenbeschichtung 323 auf.At the second reversal point, the piston lifts the
Etwa auf halber Höhe zwischen den Umkehrpunkten umgibt ein ringförmiger Kühlmittelkanal 350 die Laufbuchse. In diesem Bereich ist die Kolbengeschwindigkeit am größten, soweit ein Kurbeltrieb nach dem ersten Ausführungsbeispiel zum Einsatz kommt. In dem Kühlmittelkanal zirkuliert ein Fluid, welches Wärme von der Laufbuchse aufnimmt, beispielsweise Kühlwasser, welches eine Temperatur in Höhe der oder unterhalb der Raumtemperatur besitzt. Damit die Wärmeübergabe bestmöglich stattfindet, gelangt das Fluid direkt in Kontakt mit der Außenwand der Laufbuchse. Das Kühlungsmittel umfasst also einen Kühlmittelkanal 350, der derart in einem die Laufbuchse aufnehmendem Zylinder angeordnet ist, dass die Laufbuchse die ihr zugewandte Begrenzungsfläche des Kanals begrenzt. Um Austreten von Fluid in den Einlasskanal zu verhindern, ist zwischen Kühlmittelkanal 350 und Einlasskanal 330 eine Dichtung 352 angeordnet. Eine weitere Dichtung 360 dichtet den Spalt zwischen Laufbuchse und Zylinder und damit den Kühlmittelkanal gegen die Auslasskammer 342 an.At about halfway between the reversal points, an
Das Fluid wird über einen Kühlmittelzulauf 354 in den Kühlmittelkanal eingespeist und dann an den Kühlmittelablauf 356 abgegeben. Kühlmittelzulauf und -ablauf sind in einer einfachen Ausführung Teil einer Kühlwasserinstallation. In einer Weiterbildung ist das Kühlmittel von Kühlmittelzulauf und Kühlmittelablauf getrennt und gibt die Wärme über einen Wärmetauscher an diese ab. Zwischen Wärmetauscher und Kühlmittel ist dann zusätzlich eine Umwälzpumpe vorgesehen.The fluid is fed via a
Die in
Für alle der gezeigten Beispiele hat es sich als vorteilhaft erwiesen, das Kühlungsmittel in Bezug zur Längsachse der Laufbuchse kürzer als den Abstand der Umkehrpunkte zu gestalten. Dies erlaubt eine einfache, kostengünstige Konstruktion und sorgt trotzdem für ausreichende Kühlung. Die Ausdehnung des Kühlmittels beträgt zwischen einem Fünftel und der Hälfte des Abstandes zwischen den Umkehrpunkten.For all of the examples shown, it has proven to be advantageous to design the coolant with respect to the longitudinal axis of the bushing shorter than the distance of the reversal points. This allows a simple, inexpensive construction and still provides sufficient cooling. The expansion of the coolant is between one-fifth and one-half of the distance between the reversal points.
Claims (4)
- A piston vacuum pump (1) comprising a liner (22; 222; 322; 422); a reciprocating piston (24; 224; 324; 424) movably arranged in the liner; a seal (48) arranged at the reciprocating piston for sealing the space between the reciprocating piston and the liner; and a drive which effects a periodic movement of the reciprocating piston,
characterized in that
a cooling means (230) is in heat transferring contact with the liner; in that the cooling means (230) has a closed circuit having an evaporator (232) and a condenser (234); and in that the evaporator (232) is in contact with the liner (22; 222; 322; 422). - A piston vacuum pump in accordance with claim 1,
characterized in that
the cooling means (230) comprises a cooling body (240) which is in contact with an end of the condenser (234). - A piston vacuum pump in accordance with claim 1 or claim 2,
characterized in that
the liner has a tangential bore (226) in which the evaporator (232) is arranged. - A piston vacuum pump in accordance with any one of the preceding claims, characterized in that
the cooling means (230) is arranged halfway between a first reversal point (27; 327) and a second reversal point (33; 333) of the periodic movement.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008061897A DE102008061897A1 (en) | 2008-12-11 | 2008-12-11 | Vacuum pump |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2196671A2 EP2196671A2 (en) | 2010-06-16 |
EP2196671A3 EP2196671A3 (en) | 2016-07-06 |
EP2196671B1 true EP2196671B1 (en) | 2018-01-24 |
Family
ID=41401624
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP09014531.9A Active EP2196671B1 (en) | 2008-12-11 | 2009-11-20 | Piston vacuum pump |
Country Status (2)
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EP (1) | EP2196671B1 (en) |
DE (1) | DE102008061897A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014201473A1 (en) * | 2014-01-28 | 2015-07-30 | Neuman & Esser Gmbh & Co. Kg | PISTON ROD FOR PISTON COMPRESSORS AND PISTON COMPRESSOR |
EP3067560B1 (en) | 2015-03-12 | 2020-11-18 | Pfeiffer Vacuum GmbH | Vacuum pump with at least one pump stage |
DE102022106046A1 (en) * | 2022-03-16 | 2023-09-21 | Knf Neuberger Gmbh | Pump with a pressure chamber and a cooling system |
DE102022125508A1 (en) | 2022-10-04 | 2024-04-04 | Technische Universität Dresden, Körperschaft des öffentlichen Rechts | Sealing system for a device for compressing a fluid and device for compressing a fluid with the sealing system |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR332224A (en) * | 1903-05-19 | 1903-10-19 | Henry Bland | Improvements in compressors |
GB293605A (en) * | 1927-09-28 | 1928-07-12 | Sidney Zaleski Hall | Improvements in air compressors and vacuum pumps |
DE577185C (en) * | 1931-02-07 | 1933-05-30 | Rudolf Pawlikowski Dipl Ing | Cylinder type for internal combustion engines |
DE1190959B (en) * | 1961-02-17 | 1965-04-15 | Linde Eismasch Ag | Refrigerant piston compressor with cooled cylinder wall |
JPS5857092A (en) * | 1981-10-01 | 1983-04-05 | Honda Motor Co Ltd | Air pump device |
US5921755A (en) * | 1997-04-21 | 1999-07-13 | Dry Vacuum Technologies, Inc. | Dry vacuum pump |
DE19847159C2 (en) * | 1998-10-13 | 2001-12-06 | Hans Unger | Compressor for generating oil-free compressed air |
DE10109514C1 (en) * | 2001-02-28 | 2002-07-11 | Knorr Bremse Systeme | Dry-running piston compressor, for rail vehicles, has lubricating nipples for external lubrication of the big end and/or gudgeon pin bearings to give long intervals between overhauls |
DE102004061224B4 (en) * | 2004-12-20 | 2010-09-09 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Piston-cylinder arrangement, in particular for a swash plate compressor |
DE102006012532A1 (en) | 2006-03-18 | 2007-09-20 | Pfeiffer Vacuum Gmbh | Sealing arrangement for a reciprocating vacuum pump |
-
2008
- 2008-12-11 DE DE102008061897A patent/DE102008061897A1/en not_active Withdrawn
-
2009
- 2009-11-20 EP EP09014531.9A patent/EP2196671B1/en active Active
Non-Patent Citations (1)
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None * |
Also Published As
Publication number | Publication date |
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EP2196671A2 (en) | 2010-06-16 |
DE102008061897A1 (en) | 2010-06-17 |
EP2196671A3 (en) | 2016-07-06 |
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