EP2745015B1 - Roots pump - Google Patents
Roots pump Download PDFInfo
- Publication number
- EP2745015B1 EP2745015B1 EP12745685.3A EP12745685A EP2745015B1 EP 2745015 B1 EP2745015 B1 EP 2745015B1 EP 12745685 A EP12745685 A EP 12745685A EP 2745015 B1 EP2745015 B1 EP 2745015B1
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- European Patent Office
- Prior art keywords
- pump
- stage
- rotary
- roots
- roots pump
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- 238000005086 pumping Methods 0.000 claims description 16
- 230000007423 decrease Effects 0.000 claims description 2
- 238000000638 solvent extraction Methods 0.000 claims 6
- 238000005192 partition Methods 0.000 description 15
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000004381 surface treatment Methods 0.000 description 1
- 239000013585 weight reducing agent 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
- 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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
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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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/082—Details specially related to intermeshing engagement type pumps
- F04C18/086—Carter
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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
- F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
- F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
- F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
Definitions
- the invention relates to a Roots pump.
- Roots pumps usually have two-toothed rotary lobes arranged in a pump chamber.
- the two rotary lobes are driven in opposite directions, so that gas is sucked in through a main inlet through the individual chambers and expelled again via a main outlet.
- the main inlet and the main outlet run in the radial direction and are arranged opposite one another.
- rotary pistons with multiple teeth, in particular three or four teeth are known.
- the gas is essentially pumped radially from a radially arranged main inlet to a radially arranged main outlet.
- Multistage Roots pumps are also known for achieving low pressures.
- Roots pumps of this type have a pair of rotary lobes per stage.
- the gas to be pumped is conveyed from an outlet of one pumping stage to the inlet of an adjacent pumping stage. This is done via connection channels.
- the connection channels can, as for example in US 2010/0158728 described, be arranged in the housing of the Roots pump, the connecting channels that surround the pump chambers in which the rotary lobes are arranged or are arranged radially outside the pump chambers. This is necessary to get gas from an im to convey the outlet of a pump stage arranged in the lower region of the Roots pump to an inlet of the adjacent pump stage arranged in the opposite, for example upper region of a Roots pump.
- Roots pumps of this type have the disadvantage that the design of the channels in the housing is technically complex. Furthermore, the housing for receiving the connecting channels must be designed with a large volume. This not only leads to large external dimensions of the Roots pump but also, in particular, to high costs. In addition to the complex manufacturing process, the high costs are also caused by the large amount of metal used.
- Roots pump with a plurality of multi-toothed rotary lobe pairs each forming a pump stage is known.
- the rotary lobes are each designed as three-tooth rotary lobes.
- Adjacent pump stages are connected to one another via connecting channels, the connecting channels being arranged in a z-shape in the partition walls.
- Roots pump which has a technically simple structure, the installation space required and the costs preferably also being reduced.
- the Roots pump according to the invention has several pairs of multi-toothed rotary lobes, each forming a pump stage.
- two rotary lobes with more than two teeth are provided for each pumping stage, it being preferred that the rotary lobes have at least four, in particular at least six teeth.
- the two rotary lobes of a pump stage rotate in opposite directions to transport the gas.
- the two shafts can be connected to one another via gears, so that only one of the two shafts has to be driven.
- Adjacent pump stages are connected to one another via connecting channels.
- adjacent pump stages can each have one or several connection channels can be connected to one another.
- the connecting channels are arranged in partition walls which separate adjacent pump stages from one another. The partition walls are thus provided between the piston chambers of adjacent pump stages.
- Roots pumps can be designed as dry-running pumps without oil lubrication, Roots pumps also have the advantage that the maintenance requirements are lower.
- Another advantage of the arrangement according to the invention of the connecting channels in partition walls is that, due to the shortness of the connecting channels, lower pressure losses occur.
- At least some of the connecting channels are preferably connected to the piston chambers in which the rotary piston pairs are arranged in such a way that a channel inlet opening and / or a channel outlet opening is swept over by a side wall of a rotary piston during operation.
- the channel inlet and / or channel outlet opening of at least one connecting channel is therefore not arranged radially in relation to a piston chamber, but axially.
- the opening is painted over not via a radially formed end face but via a side wall of a rotary piston.
- all the connecting channels are preferably arranged in intermediate walls that separate the pump stages from one another. Only one main inlet and / or one main outlet is not arranged in partition walls.
- the main inlet and / or the main outlet can be arranged axially or radially.
- the main inlet is preferably arranged radially opposite the main outlet. If, for example, gas is sucked in through a main inlet arranged on an upper side of the pump, in a preferred embodiment the gas is expelled at the radially opposite lower side of the pump.
- the main inlet is axially offset with respect to the main outlet, since the individual pump stages are arranged axially one behind the other, starting from the main inlet to the main outlet.
- the gas is transported from the first to the second stage through a connecting channel which is arranged in the center at a rotation angle of approx. 90 ° for the rotary lobes.
- This connecting channel can run axially so that the gas enters a central chamber of the adjacent rotary lobes.
- the gas is then further in the direction of the outlet side conveyed and from this area reaches an inlet-side chamber of the next pumping stage through a channel arranged in particular at an angle or diagonally in the partition wall.
- multiple axially extending channels can be arranged between adjacent pump stages.
- the provision of axial channels has the particular advantage that the channels are technically simple to manufacture. These can be axial, in particular circular-cylindrical bores.
- partition walls in which such connection channels are arranged are preferably thicker in the axial direction than partition walls in which axial connection channels are provided. This makes it possible to design the connecting channels running at an angle without any curvature.
- the connecting channels In order to keep the power consumption of the pump as low as possible, the connecting channels have the largest possible cross-section. It is also possible to provide a plurality of channels running essentially parallel to one another in order to enlarge the cross section. Particularly in the case of the channels running obliquely in the partition walls, it must also be taken into account that they are designed to be as short as possible.
- the rotary lobes preferably have axially different widths, the width of the rotary lobes in particular decreasing in steps in the pumping direction. This reduces the volume of the individual chambers formed between the teeth of the rotary pistons.
- the two intermeshing rotary pistons have the same diameter and the same shape.
- Rotary pistons that mesh with one another can also have different tooth shapes.
- Roots pump results in an equalization of the load peaks over the rotation of the rotor and also an equalization of the heat of compression.
- the ones in the Figs. 1 and 2 three-toothed rotary lobes 10 shown schematically are in a first pumping stage ( Fig. 1 ) arranged in a pump chamber 12.
- the two rotary pistons 10 are each rotatably supported by a shaft (not shown) and are rotated in opposite directions in the direction of arrows 14 and 16, respectively.
- Gas is fed to a chamber 20 via a main inlet 18.
- the in Fig. 1 On the left rotary piston the gas is enclosed in the chamber 20, which is closed off by the curved region 22 of an outer wall. If you continue to rotate the in Fig. 1 left rotary piston in the direction of arrow 14, the chamber 20 is opened corresponding to the chamber designated 24 in this position.
- the chamber 24 encloses the entire lower area of the two rotary pistons, so that the areas 24, 26, 28 have the same pressure level. As a result, the gas originally located in the chamber 20 is pressed out through a connecting channel 30 running axially, ie parallel to the rotating shafts of the rotary pistons.
- the gas from the in Fig. 2 outlet 44 designated as the main outlet can be conveyed upwards again in the direction of a main inlet. According to the invention, this takes place through channels, which are not shown in this embodiment, and run diagonally or obliquely in an intermediate wall.
- Fig. 3-5 are six-tooth rotary piston pairs 48, 49 together with the first stage ( Fig. 3 ), a second stage ( Fig. 4 ) and a third stage ( Fig. 5 ) relevant connection channels are shown.
- a six-stage Roots pump ( Fig. 6 ) corresponds to the representation of Fig. 3 a first stage 50
- the representation in Fig. 4 a second stage 52
- the representation in Fig. 5 a third stage 54
- the fourth stage 56 essentially corresponds to the first stage ( Fig. 3 ), although the inlet does not take place radially but via an inclined or diagonal connecting channel 57.
- the fifth stage 58 corresponds to the second stage 52 or Fig.
- the individual rotary pistons 48 are carried by a common shaft 66.
- the rotary pistons 49 are carried by a common shaft 68.
- the two shafts 66, 68 are rotatably mounted in an upper housing half 70 and a lower housing half 72 and can be via not shown Gear wheels are connected to one another, so that only one of the two shafts 66, 68 has to be driven by a motor.
- Partition walls 74, 76, 78, 80, 82 are provided between adjacent pumping stages.
- at least one connecting channel 84, 86, 88, 90, 57 is arranged in each partition wall.
- connection channels are also possible which are arranged at least partially in an outer area, as is known from the prior art.
- the gas is sucked in through the main inlet 51.Instead of a radially arranged main inlet 51, this can also be used axially as an inlet 53 ( Fig. 3 ) be trained.
- an inclined inlet or a combination of different inlets is also possible, whereby the inlet merely feeds gas into the chamber 55 ( Fig. 3 ) must be done.
- the gas is then conveyed from the first pump stage 50 into the second pump stage 52 through a connecting channel 84 running axially, ie parallel to the shafts 66, 68.
- the connecting channel 84 is arranged in the intermediate wall 74.
- the gas is here based on the Figs. 1 and 2
- the principle described is conveyed via an intermediate chamber 57 into a chamber 59 connected to the connecting channels 84.
- the gas is then conveyed further ( Fig. 4 ) and flows from the second pumping stage 52 into the third pumping stage 54 through a connecting channel 86, which likewise runs axially.
- the connecting channel 86 is arranged in the intermediate wall 76.
- a diagonal or inclined channel 77 is provided in the intermediate wall 78, which is thicker in the axial direction than the other intermediate walls 74, 76, 80, 82.
- the gas is conveyed from the fourth pump stage 56 into the fifth pump stage 58 through a channel 88 running axially in the partition 80. Since the sixth pumping stage 60 is the last pumping stage in the exemplary embodiment shown, it is connected to the essentially radially extending main outlet 62.
- rotary lobes with different diameters and, in particular, different numbers of teeth can also be provided.
- a combination of rotary lobes with different tooth shapes is also possible. An example of this is shown in plan view in Figure 7 shown.
- a left rotary piston 92 has teeth which interact with five separately designed teeth of a right rotary piston 94.
Description
Die Erfindung betrifft eine Wälzkolbenpumpe.The invention relates to a Roots pump.
Wälzkolbenpumpen weisen üblicherweise zweizähnige, in einem Pumpraum angeordnete Drehkolben auf. Die beiden Drehkolben werden gegenläufig angetrieben, so dass durch die einzelnen entstehenden Kammern Gas durch einen Haupteinlass angesaugt und über einen Hauptauslass wieder ausgestoßen wird. Der Haupteinlass sowie der Hauptauslass verlaufen hierbei in radialer Richtung und sind einander gegenüberliegend angeordnet. Ferner sind auch mehrzähnige, insbesondere drei oder vier Zähne aufweisende Drehkolben bekannt. Auch hier erfolgt ein im Wesentlichen radiales Pumpen des Gases von einem radial angeordneten Haupteinlass zu einem radial angeordneten Hauptauslass.Roots pumps usually have two-toothed rotary lobes arranged in a pump chamber. The two rotary lobes are driven in opposite directions, so that gas is sucked in through a main inlet through the individual chambers and expelled again via a main outlet. The main inlet and the main outlet run in the radial direction and are arranged opposite one another. Furthermore, rotary pistons with multiple teeth, in particular three or four teeth, are known. Here, too, the gas is essentially pumped radially from a radially arranged main inlet to a radially arranged main outlet.
Zur Erzielung geringer Drücke sind ferner mehrstufige Wälzkolbenpumpen bekannt. Je Stufe weisen derartige Wälzkolbenpumpen ein Drehkolbenpaar auf. Hierbei wird das zu pumpende Gas von einem Auslass einer Pumpstufe zum Einlass einer benachbarten Pumpstufe gefördert. Dies erfolgt über Verbindungskanäle. Die Verbindungskanäle können, wie beispielsweise in
Aus
Aufgabe der Erfindung ist es, eine Wälzkolbenpumpe zu schaffen, die einen technisch einfachen Aufbau aufweist, wobei ferner der erforderliche Bauraum sowie die Kosten vorzugsweise reduziert werden sollen.It is the object of the invention to create a Roots pump which has a technically simple structure, the installation space required and the costs preferably also being reduced.
Die Lösung der Aufgabe erfolgt erfindungsgemäß durch die Merkmale des Anspruchs 1.The object is achieved according to the invention by the features of claim 1.
Die erfindungsgemäße Wälzkolbenpumpe weist mehrere jeweils eine Pumpstufe ausbildende, mehrzähnige Drehkolbenpaare auf. Hierbei sind je Pumpstufe zwei Drehkolben mit mehr als zwei Zähnen vorgesehen, wobei es bevorzugt ist, dass die Drehkolben mindestens vier, insbesondere mindestens sechs Zähne aufweisen. Die beiden Drehkolben einer Pumpstufe rotieren zum Transport des Gases gegenläufig. Vorzugsweise ist je Drehkolbenpaar einer der beiden Drehkolben auf einer gemeinsamen Welle angeordnet, so dass die Wälzkolbenpumpe zwei parallel zueinander verlaufende Wellen aufweist, wobei jede Welle je Pumpstufe einen der beiden Drehkolben trägt. Die beiden Wellen können über Zahnräder miteinander verbunden sein, so dass nur eine der beiden Wellen angetrieben sein muss.The Roots pump according to the invention has several pairs of multi-toothed rotary lobes, each forming a pump stage. Here, two rotary lobes with more than two teeth are provided for each pumping stage, it being preferred that the rotary lobes have at least four, in particular at least six teeth. The two rotary lobes of a pump stage rotate in opposite directions to transport the gas. There is preferably one per rotary piston pair of the two rotary lobes arranged on a common shaft, so that the Roots pump has two shafts running parallel to one another, each shaft carrying one of the two rotary lobes per pump stage. The two shafts can be connected to one another via gears, so that only one of the two shafts has to be driven.
Benachbarte Pumpstufen sind über Verbindungskanäle miteinander verbunden. Hierbei können benachbarte Pumpstufen jeweils über einen oder mehrere Verbindungskanäle miteinander verbunden sein. Erfindungsgemäß sind die Verbindungskanäle in Zwischenwänden angeordnet, die benachbarte Pumpstufen voneinander trennen. Die Zwischenwände sind somit zwischen den Kolbenräumen benachbarter Pumpstufen vorgesehen. Durch das erfindungsgemäße Anordnen der Verbindungskanäle in den Zwischenwänden können die Außenabmessungen der erfindungsgemäßen Wälzkolbenpumpe gegenüber dem Stand der Technik erheblich reduziert werden. Dies hat den Vorteil, dass aufgrund des geringeren Materialeinsatzes eine Kostenreduzierung erzielt werden kann. Des Weiteren können die in Zwischenwänden vorgesehenen Verbindungskanäle kostengünstiger hergestellt werden, da es möglich ist, die Verbindungskanäle durch gerade, insbesondere kreiszylindrische Kanäle bzw. Bohrungen auszubilden. Eine technisch schwierige Herstellung von radial außerhalb der Kolbenräume vorgesehenen gekrümmten Verbindungskanälen ist somit erfindungsgemäß nicht erforderlich. Die erfindungsgemäß sehr kompakt aufgebaute Wälzkolbenpumpe weist ferner den Vorteil auf, dass eine Gewichtsreduzierung sowie eine Reduzierung der Teileanzahl erzielt werden kann. Da Wälzkolbenpumpen als trockenlaufende Pumpen ohne Ölschmierung aufgebaut sein können, weisen Wälzkolbenpumpen ferner den Vorteil auf, dass die Wartungsanforderungen geringer sind.Adjacent pump stages are connected to one another via connecting channels. Here, adjacent pump stages can each have one or several connection channels can be connected to one another. According to the invention, the connecting channels are arranged in partition walls which separate adjacent pump stages from one another. The partition walls are thus provided between the piston chambers of adjacent pump stages. By arranging the connecting channels according to the invention in the partition walls, the external dimensions of the Roots pump according to the invention can be considerably reduced compared to the prior art. This has the advantage that a reduction in costs can be achieved due to the lower use of material. Furthermore, the connecting channels provided in the partition walls can be produced more cost-effectively, since it is possible to form the connecting channels by straight, in particular circular-cylindrical channels or bores. A technically difficult production of curved connecting channels provided radially outside the piston chambers is therefore not necessary according to the invention. The very compact Roots pump according to the invention also has the advantage that a weight reduction and a reduction in the number of parts can be achieved. Since Roots pumps can be designed as dry-running pumps without oil lubrication, Roots pumps also have the advantage that the maintenance requirements are lower.
Ein weiterer Vorteil der erfindungsgemäßen Anordnung der Verbindungskanäle in Zwischenwänden besteht darin, dass aufgrund der Kürze der Verbindungskanäle geringere Druckverluste auftreten.Another advantage of the arrangement according to the invention of the connecting channels in partition walls is that, due to the shortness of the connecting channels, lower pressure losses occur.
Vorzugsweise ist zumindest ein Teil der Verbindungskanäle mit den Kolbenräumen, in denen die Drehkolbenpaare angeordnet sind, derart verbunden, dass eine Kanaleintrittsöffnung und/ oder eine Kanalaustrittsöffnung von einer Seitenwand eines Drehkolbens im Betrieb überstrichen wird. Die Kanaleintritts- und/ oder Kanalaustrittsöffnung zumindest eines Verbindungskanals ist somit nicht radial, bezogen auf einen Kolbenraum, sondern axial angeordnet. Das Überstreichen der Öffnung erfolgt nicht über eine radial ausgebildete Stirnseite sondern über eine Seitenwand eines Drehkolbens.At least some of the connecting channels are preferably connected to the piston chambers in which the rotary piston pairs are arranged in such a way that a channel inlet opening and / or a channel outlet opening is swept over by a side wall of a rotary piston during operation. The channel inlet and / or channel outlet opening of at least one connecting channel is therefore not arranged radially in relation to a piston chamber, but axially. The opening is painted over not via a radially formed end face but via a side wall of a rotary piston.
Um einen möglichst kompakten und somit kostengünstigen Aufbau der erfindungsgemäßen Wälzkolbenpumpe zu ermöglichen, sind vorzugsweise sämtliche Verbindungskanäle in die Pumpstufen voneinander trennenden Zwischenwänden angeordnet. Lediglich ein Haupteinlass und/ oder ein Hauptauslass ist nicht in Zwischenwänden angeordnet. Der Haupteinlass und/ oder der Hauptauslass können axial oder radial angeordnet sein. Der Haupteinlass ist dem Hauptauslass vorzugsweise radial gegenüberliegend angeordnet. Erfolgt beispielsweise ein Ansaugen von Gas durch einen an einer Oberseite der Pumpe angeordneten Haupteinlass erfolgt somit in bevorzugter Ausführungsform das Ausstoßen des Gases an der radial gegenüberliegenden Unterseite der Pumpe. Selbstverständlich ist der Haupteinlass gegenüber dem Hauptauslass axial versetzt, da die einzelnen Pumpstufen axial hintereinander, ausgehend vom Haupteinlass zum Hauptauslass, angeordnet sind.In order to allow the Roots pump according to the invention to have a construction that is as compact as possible and therefore inexpensive, all the connecting channels are preferably arranged in intermediate walls that separate the pump stages from one another. Only one main inlet and / or one main outlet is not arranged in partition walls. The main inlet and / or the main outlet can be arranged axially or radially. The main inlet is preferably arranged radially opposite the main outlet. If, for example, gas is sucked in through a main inlet arranged on an upper side of the pump, in a preferred embodiment the gas is expelled at the radially opposite lower side of the pump. Of course, the main inlet is axially offset with respect to the main outlet, since the individual pump stages are arranged axially one behind the other, starting from the main inlet to the main outlet.
Insbesondere bei Drehkolben mit drei oder mehr Zähnen ist es erfindungsgemäß vorsgesehen, axial in den Zwischenwänden verlaufende Verbindungskanäle vorzusehen. Dies ist dadurch realisierbar, dass eine zwischen zwei benachbarten Zähnen angeordnete Kammer das Gas nicht erst nach einer Drehung der Drehkolben um ca. 180°, sondern bereits bei einem geringeren Drehwinkel ausstößt. Bei einer derartig bevorzugten Ausführungsform der erfindungsgemäßen Wälzkolbenpumpe muss das Gas zwischen zwei Stufen somit nicht von einer haupteinlassseitigen Kammer bis zu einer hauptauslassseitigen Kammer transportiert werden. Beispielsweise erfolgt bei dreizähnigen Drehkolben das Ansaugen des Gases durch einen Haupteinlass an einer Oberseite der Pumpe. Der Transport des Gases von der ersten zur zweiten Stufe erfolgt durch einen Verbindungskanal, der mittig bei einem Drehwinkel von ca. 90° der Drehkolben angeordnet ist. Dieser Verbindungskanal kann axial verlaufen, so dass das Gas in eine mittige Kammer der benachbarten Drehkolben eintritt. In dieser Pumpstufe wird das Gas sodann weiter in Richtung der Auslassseite gefördert und gelangt von diesem Bereich durch einen insbesondere schräg bzw. diagonal in der Zwischenwand angeordneten Kanal wieder in eine einlassseitige Kammer der nächsten Pumpstufe. Insbesondere bei Drehkolben mit mehr als drei Zähnen können zwischen benachbarten Pumpstufen mehrfach axial verlaufende Kanäle angeordnet sein. Das Vorsehen axialer Kanäle hat insbesondere den Vorteil, dass die Herstellung der Kanäle technisch einfach ist. Es kann sich hierbei um axiale, insbesondere auch kreiszylindrische Bohrungen handeln.In particular in the case of rotary pistons with three or more teeth, provision is made according to the invention to provide connecting channels running axially in the intermediate walls. This can be achieved in that a chamber arranged between two adjacent teeth does not only expel the gas after the rotary pistons have rotated by approx. 180 °, but rather already at a smaller angle of rotation. In such a preferred embodiment of the Roots pump according to the invention, the gas does not have to be transported between two stages from a chamber on the main inlet side to a chamber on the main outlet side. For example, in the case of three-tooth rotary lobes, the gas is sucked in through a main inlet on an upper side of the pump. The gas is transported from the first to the second stage through a connecting channel which is arranged in the center at a rotation angle of approx. 90 ° for the rotary lobes. This connecting channel can run axially so that the gas enters a central chamber of the adjacent rotary lobes. In this pumping stage, the gas is then further in the direction of the outlet side conveyed and from this area reaches an inlet-side chamber of the next pumping stage through a channel arranged in particular at an angle or diagonally in the partition wall. In particular in the case of rotary lobes with more than three teeth, multiple axially extending channels can be arranged between adjacent pump stages. The provision of axial channels has the particular advantage that the channels are technically simple to manufacture. These can be axial, in particular circular-cylindrical bores.
Um auch die schräg bzw. diagonal in den Zwischenwänden verlaufenden Verbindungskanäle technisch einfach ausgestalten zu können, sind Zwischenwände, in denen derartige Verbindungskanäle angeordnet sind, vorzugsweise in axiale Richtung dicker als Zwischenwände, in denen axiale Verbindungskanäle vorgesehen sind. Hierdurch ist es möglich, auch die schräg verlaufenden Verbindungskanäle gerade ohne Krümmung auszugestalten.In order to be able to design the connection channels running obliquely or diagonally in the partition walls in a technically simple manner, partition walls in which such connection channels are arranged are preferably thicker in the axial direction than partition walls in which axial connection channels are provided. This makes it possible to design the connecting channels running at an angle without any curvature.
Um die Leistungsaufnahme der Pumpe möglichst gering zu halten, weisen die Verbindungskanäle einen möglichst großen Querschnitt auf. Es ist möglich, zur Querschnittsvergrößerung auch mehrere, im Wesentlichen parallel zueinander verlaufende Kanäle vorzusehen. Insbesondere bei den schräg in den Zwischenwänden verlaufenden Kanälen ist ferner zu berücksichtigen, dass diese möglichst kurz ausgestaltet sind.In order to keep the power consumption of the pump as low as possible, the connecting channels have the largest possible cross-section. It is also possible to provide a plurality of channels running essentially parallel to one another in order to enlarge the cross section. Particularly in the case of the channels running obliquely in the partition walls, it must also be taken into account that they are designed to be as short as possible.
Zur Erhöhung der Kompression weisen die Drehkolben vorzugsweise axial unterschiedliche Breiten auf, wobei die Breite der Drehkolben insbesondere stufenweise in Pumprichtung abnimmt. Hierdurch werden die einzelnen zwischen den Zähnen der Drehkolben ausgebildeten Kammern im Volumen verringert.To increase the compression, the rotary lobes preferably have axially different widths, the width of the rotary lobes in particular decreasing in steps in the pumping direction. This reduces the volume of the individual chambers formed between the teeth of the rotary pistons.
In bevorzugter Ausführungsform weisen die beiden miteinander kämmenden Drehkolben denselben Durchmesser und dieselbe Form auf. Es ist jedoch auch möglich, Drehkolben mit unterschiedlichem Durchmesser und unterschiedlicher Zähnezahl vorzusehen, wobei die Drehkolben sodann unterschiedliche Rotationsgeschwindigkeiten aufweisen. Ebenso können miteinander kämmende Drehkolben auch unterschiedliche Zahnformen aufweisen.In a preferred embodiment, the two intermeshing rotary pistons have the same diameter and the same shape. However, it is also possible to use rotary lobes with different diameters and Provide different number of teeth, the rotary lobes then have different speeds of rotation. Rotary pistons that mesh with one another can also have different tooth shapes.
Durch die erfindungsgemäße Ausgestaltung der Wälzkolbenpumpe ist insbesondere eine Vergleichmäßigung der Belastungsspitzen über der Rotordrehung und auch eine Vergleichmäßigung der Verdichtungswärme erzielt.The design of the Roots pump according to the invention in particular results in an equalization of the load peaks over the rotation of the rotor and also an equalization of the heat of compression.
Nachfolgend wird die Erfindung anhand bevorzugter Ausführungsformen unter Bezugnahme auf die anliegenden Zeichnungen näher erläutert.The invention is explained in more detail below on the basis of preferred embodiments with reference to the accompanying drawings.
Es zeigen:
- Fig. 1
- eine schematische Ansicht eines dreizähnigen Druckkolbenpaars einer ersten Pumpstufe,
- Fig. 2
- eine schematische Ansicht eines dreizähnigen Druckkolbenpaars einer zweiten benachbarten Pumpstufe,
- Fig. 3
- eine schematische Ansicht eines sechszähnigen Drehkolbenpaars einer ersten Stufe,
- Fig. 4
- eine schematische Ansicht eines sechszähnigen Drehkolbenpaars einer zweiten Stufe,
- Fig. 5
- eine schematische Ansicht eines sechszähnigen Drehkolbenpaars einer dritten Stufe,
- Fig. 6
- eine schematische Schnittansicht einer sechsstufigen Wälzkolbenpumpe, die entsprechend den
Fig. 3 - 5 schematisch dargestellte, sechszähnige Drehkolben aufweist, und - Fig. 7
- eine schematische Draufsicht einer alternativen Ausführungsform eines Drehkolbenpaares.
- Fig. 1
- a schematic view of a three-toothed pressure piston pair of a first pump stage,
- Fig. 2
- a schematic view of a three-toothed pressure piston pair of a second adjacent pump stage,
- Fig. 3
- a schematic view of a six-tooth rotary piston pair of a first stage,
- Fig. 4
- a schematic view of a six-tooth rotary piston pair of a second stage,
- Fig. 5
- a schematic view of a six-tooth rotary piston pair of a third stage,
- Fig. 6
- a schematic sectional view of a six-stage Roots pump, which corresponds to the
Fig. 3-5 having six-toothed rotary lobes shown schematically, and - Fig. 7
- a schematic plan view of an alternative embodiment of a rotary piston pair.
Die in den
Entsprechend wird durch den in
Bei der nächsten Pumpstufe (
Zur Ausbildung einer dritten Stufe muss das Gas vom in
In den
Zwischen benachbarten Pumpstufen sind Zwischenwände 74, 76, 78, 80, 82 vorgesehen. Im dargestellten Ausführungsbeispiel ist in jeder Zwischenwand zumindest ein Verbindungskanal 84, 86, 88, 90, 57 angeordnet. Ferner sind zusätzlich auch Verbindungskanäle möglich, die, zumindest teilweise in einem Außenbereich, wie aus dem Stand der Technik bekannt, angeordnet sind. Im dargestellten Ausführungsbeispiel erfolgt das Ansaugen des Gases durch den Haupteinlass 51. Anstelle eines radial angeordneten Haupteinlasses 51 kann dieser auch axial als Einlass 53 (
Anschließend erfolgt das Fördern des Gases von der ersten Pumpstufe 50 in die zweite Pumpstufe 52 durch einen axial, d.h. parallel zu den Wellen 66, 68 verlaufenden Verbindungskanal 84. Der Verbindungskanal 84 ist in der Zwischenwand 74 angeordnet. Das Gas wird hierbei entsprechend des anhand den
Das Gas wird sodann weitergefördert (
Bei einem Weiterfördern des Gases (
Das Fördern des Gases von der vierten Pumpstufe 56 in die fünfte Pumpstufe 58 erfolgt durch einen axial in der Zwischenwand 80 verlaufenden Kanal 88. In die nächste Pumpstufe 60 erfolgt das Fördern wiederum durch einen axialen Kanal 90, der in der Zwischenwand 82 vorgesehen ist. Da es sich bei der sechsten Pumpstufe 60 im dargestellten Ausführungsbeispiel um die letzte Pumpstufe handelt, ist diese mit dem im Wesentlichen radial verlaufenden Hauptauslass 62 verbunden.The gas is conveyed from the
Da, wie insbesondere aus den
Anstelle identisch ausgebildeter Drehkolben können auch Drehkolben mit unterschiedlichem Durchmesser und insbesondere unterschiedlicher Zähnezahl vorgesehen sein. Außerdem ist eine Kombination von Drehkolben möglich, die unterschiedliche Zahnformen aufweisen. Ein Beispiel hierfür ist in Draufsicht in
Claims (8)
- A Roots pump comprisinga plurality of pairs of multi-toothed rotary pistons (10; 48, 49), each forming a pump stage (50, 52, 54, 56, 58),wherein each rotary piston (10; 48, 49) is formed as an at least three-toothed rotary piston (10; 48, 49), andconnection channels (30, 34, 77, 84, 86, 88, 90) connecting respective adjacent pump stages (52, 54, 56, 58, 60),wherein at least one of the connection channels (30, 34, 77, 84, 86, 88, 90) is arranged in partitioning walls (74, 76, 78, 80, 82) separating the pump stages (50, 52, 54, 56, 58, 60),characterized in thatat least one of the connection channels (30, 34, 77, 84, 86, 88, 90) arranged in partitioning walls (74, 76, 78, 80, 82) separating the adjacent pump stages (50, 52, 54, 56, 58, 60) extends exclusively in an axial direction..
- The Roots pump of claim 1, characterized in that, in operation, a channel inlet opening and/or a channel outlet opening of at least one connection channel (30, 34, 77, 84, 86, 88, 90) is swept over by a side wall of a rotary piston (10, 48, 49).
- The Roots pump of claim 1 or 2, characterized in that all connection channels (30, 34, 77, 84, 86, 88, 90) are arranged in partitioning walls (74, 76, 78, 80, 82) separating the adjacent pump stages (50, 52, 54, 56, 58, 60).
- The Roots pump of one of claims 1-3, characterized in that a main inlet (51) is arranged radially opposite a main outlet (62).
- The Roots pump of claim 4, characterized in that with more than two pump stages (50, 52, 54, 56, 58, 60), a connection channel (77) connecting a pump stage (54) with an adjacent pump stage (56) extends obliquely in the corresponding partitioning wall (78) and substantially transversely to the plane formed by the two shaft axes (66, 68).
- The Roots pump of claim 5, characterized in that partitioning walls (78) including oblique connection channels (77) are thicker than partitioning walls (74, 76, 80, 82) including axial connection channels (84, 86, 88, 90).
- The Roots pump of one of claims 1-6, characterized in that one of the two rotary pistons (10; 48, 49) of each rotary piston pair (10; 48, 49) is arranged on a common shaft (66, 68).
- The Roots pump of one of claims 1-7, characterized in that the axial width of the rotary pistons (10; 48, 49) of individual pump stages (50, 52, 54, 56, 58, 60) decreases in particular in the pumping direction.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202011104491U DE202011104491U1 (en) | 2011-08-17 | 2011-08-17 | Roots |
PCT/EP2012/065406 WO2013023954A2 (en) | 2011-08-17 | 2012-08-07 | Roots pump |
Publications (2)
Publication Number | Publication Date |
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EP2745015A2 EP2745015A2 (en) | 2014-06-25 |
EP2745015B1 true EP2745015B1 (en) | 2021-10-06 |
Family
ID=46640681
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12745685.3A Active EP2745015B1 (en) | 2011-08-17 | 2012-08-07 | Roots pump |
Country Status (9)
Country | Link |
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US (1) | US9476423B2 (en) |
EP (1) | EP2745015B1 (en) |
JP (1) | JP6076343B2 (en) |
KR (1) | KR101905228B1 (en) |
CN (1) | CN103732923B (en) |
DE (1) | DE202011104491U1 (en) |
RU (1) | RU2631579C2 (en) |
TW (1) | TWI611101B (en) |
WO (1) | WO2013023954A2 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
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CN103334928B (en) * | 2013-06-09 | 2016-08-10 | 李锦上 | Energy-conservation wave piston compressor |
DE202017001029U1 (en) | 2017-02-17 | 2018-05-18 | Leybold Gmbh | Multi-stage Roots pump |
DE102019103577A1 (en) * | 2019-02-13 | 2020-08-13 | Gebr. Becker Gmbh | Rotary lobe pump |
FR3117176B1 (en) * | 2020-12-04 | 2023-03-24 | Pfeiffer Vacuum | Vacuum pump |
GB2608381A (en) * | 2021-06-29 | 2023-01-04 | Edwards Korea Ltd | Stator assembly for a roots vacuum pump |
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FR660528A (en) * | 1928-09-17 | 1929-07-12 | Cfcmug | Multi-cell roots compressor for high pressures |
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GB2111126A (en) | 1981-12-09 | 1983-06-29 | British Oxygen Co Ltd | Rotary positive-displacement fluid-machines |
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GB8513684D0 (en) * | 1985-05-30 | 1985-07-03 | Boc Group Plc | Mechanical pumps |
JPH0733834B2 (en) * | 1986-12-18 | 1995-04-12 | 株式会社宇野澤組鐵工所 | Inner partial-flow reverse-flow cooling multistage three-leaf vacuum pump in which the outer peripheral temperature of the housing with built-in rotor is stabilized |
FR2642479B1 (en) | 1989-02-02 | 1994-03-18 | Alcatel Cit | MULTI-STAGE ROOTS VACUUM PUMP |
FR2656658B1 (en) * | 1989-12-28 | 1993-01-29 | Cit Alcatel | MIXED TURBOMOLECULAR VACUUM PUMP, WITH TWO ROTATION SHAFTS AND WITH ATMOSPHERIC PRESSURE DISCHARGE. |
DE4038704C2 (en) * | 1990-12-05 | 1996-10-10 | K Busch Gmbh Druck & Vakuum Dr | Rotary lobe pump |
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DE19629174A1 (en) * | 1996-07-19 | 1998-01-22 | Leybold Vakuum Gmbh | Claw pump for producing vacuum |
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JP4747437B2 (en) * | 2001-05-08 | 2011-08-17 | 株式会社豊田自動織機 | Oil leakage prevention structure in vacuum pump |
TWI237093B (en) * | 2003-10-23 | 2005-08-01 | Ind Tech Res Inst | Multi-staged vacuum pump |
GB0515905D0 (en) | 2005-08-02 | 2005-09-07 | Boc Group Plc | Vacuum pump |
JP4767625B2 (en) * | 2005-08-24 | 2011-09-07 | 樫山工業株式会社 | Multi-stage Roots type pump |
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-
2011
- 2011-08-17 DE DE202011104491U patent/DE202011104491U1/en not_active Expired - Lifetime
-
2012
- 2012-07-24 TW TW101126538A patent/TWI611101B/en active
- 2012-08-07 US US14/238,611 patent/US9476423B2/en active Active
- 2012-08-07 KR KR1020147003957A patent/KR101905228B1/en active IP Right Grant
- 2012-08-07 CN CN201280039495.8A patent/CN103732923B/en active Active
- 2012-08-07 JP JP2014525400A patent/JP6076343B2/en active Active
- 2012-08-07 EP EP12745685.3A patent/EP2745015B1/en active Active
- 2012-08-07 RU RU2014109852A patent/RU2631579C2/en active
- 2012-08-07 WO PCT/EP2012/065406 patent/WO2013023954A2/en active Application Filing
Non-Patent Citations (1)
Title |
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None * |
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CN103732923B (en) | 2016-09-21 |
CN103732923A (en) | 2014-04-16 |
DE202011104491U1 (en) | 2012-11-20 |
WO2013023954A2 (en) | 2013-02-21 |
RU2014109852A (en) | 2015-09-27 |
EP2745015A2 (en) | 2014-06-25 |
KR20140049555A (en) | 2014-04-25 |
KR101905228B1 (en) | 2018-10-05 |
RU2631579C2 (en) | 2017-09-25 |
WO2013023954A3 (en) | 2013-12-19 |
US9476423B2 (en) | 2016-10-25 |
US20140205483A1 (en) | 2014-07-24 |
TWI611101B (en) | 2018-01-11 |
JP2014521887A (en) | 2014-08-28 |
JP6076343B2 (en) | 2017-02-08 |
TW201314032A (en) | 2013-04-01 |
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