DE1403578A1 - Centrifugal displacement pump and system for overdistilling liquids with the help of this pump - Google Patents

Description

PATIENTANWALTI

DR. W, SCHALE * DIPL-INa PgTgR WiRTH a E * MjDANNiNBERC DR. V. SCHMIED-KOWARZIK

raANXrURT AM MAIN

PW / Bu. o ».f» <N «HHirMiii« T ». »T Cade 127

THE NASH ENGINEERING COMPANY South Norwalk Connecticut UNITED STATES.

Centrifugal displacement pump and system for distilling over of liquids with the help of this pump

The invention relates generally to pumps and pump systems and in particular concerns a new centrifugal positive displacement pump, which with high output oasis, vapors or liquids or mixtures consisting of them durohsetet, as well as on an evaporator system in which such a pump is used

Although the invention is directed in particular to a rotating centrifugal pump which can only pump gases, other than oil or vapors, or only liquid or a mixture of these, the invention relates to it. erf auch'auf an improved evaporator ystem, ia the finds l improved pump application and arbelt welohes with a bie IM not achieved efficiency # | "; · ', ^: . ■>

90988570113

In evaporator systems, especially small systems, for example Distilling about 1,890 1 Jasser per day, it is difficult with the usual pumping equipment available to maintain the desired high vacuum in the condensation devices of these systems. In most cases a single device requires up to three separate pumps, including a distillate pump to remove the distillate that has been condensed after evaporation, a brine pump to remove the brine remaining in the evaporator and an air suction pump to remove the not condensable gases from the condenser. It is desirable that the evaporator be as high as possible Vacuum works to be able to use low temperature heat sources. It is also beneficial if the partial pressure the air in the condenser is reduced to a minimum, whereby the liquid is also almost is brought to its evaporation or boiling point. These Temperatures near the boiling point increase the difficulty of getting the liquids out of both the evaporator and the vaporizer to pump the condensation device. Still pumps common today and evaporator brine pumps require a positive Pressure height of about 1.80 m, so that the './asser is continuously removed can be. This is a disadvantage since such systems cannot be implemented in small vessels, v / o the space for such a height difference between the evaporator and the condensing device is not available.

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According to one embodiment of the invention, the above are. named disadvantages of evaporator operation are overcome by providing an improved type of evaporator which contains a single pump unit which consists of a single drive motor and a new liquid suction pump associated therewith. Both pumps work in a similar way and can, if necessary, pump gas continuously or, if mainly liquid is fed to them, also liquid. The pumps are preferably connected in such a way that the brine from the lower part of the evaporator continuously removed by a pump on one end of the motor, while the pump on the other end of the torch is used to continuously add the distillate; the condensation device and at the same time remove the air from the condensation device and maintain the vacuum in it. This latter pump also has the advantage that the air removed from the condensation device during the pumping process is not compressed. it can be combined with the final distillate obtained.

i-in lerknal essential "of the Verdampferr described above _v \ Vieri is the construction of the above erwähnton pump, which allows installation of the lumpe at the same level with the evaporator without a positive suction head is required, it iot essential that this pump both gas and liquid.

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Another feature of the invention is the combination a liquid ring air compressor and a centrifugal liquid pump, which are connected in series so that each pump element can work under conditions that were previously were considered impossible. It is normally not to be expected that such a combination would be possible since it It is not customary to connect a centrifugal liquid pump downstream of an air compressor as the second stage, because it is known is that the working of centrifugal liquid pumps affected by air entering the suction inlet? d.rd " However, the combination according to the invention shows advantages which emerge from the following description.

The liquid ring pump or compressor used as the main part is known in the art and therefore does not need any further details to be described. It is constructed in such a way that it can displace air or gas through the displacement effect of a liquid ring conveys and compresses, whereby this ring is driven by a rotor in an eccentric or elliptical housing -.vird. The kinetic energy imparted to the liquid ring is converted into pressure or compression work for the conveyed gas. The gas is proportionate because of its low density as a result of the displacement effect described above conveyed through the channels of the pump, and although at speeds of the order of magnitude of about 670 'to about 1,675 m / l-minute, as is the case with air and gas compressors is common. .

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It is known in the art "that a machine for compressing gas is not capable of conveying liquid at the same speed and outlet pressure. The liquid cannot be conveyed at the same speeds as are possible with gases The reason for this lies in the great difference between the densities of gases and liquids. Should a positive, ie pressure-generating compressor, "for example a piston pump, take in only water instead of gas at its suction port during normal operation, the pump would either stop immediately, or your cylinder head may fly out or some other damage occurs. In a conventional liquid ring pump, instead of gas, only liquid would be taken up at the suction opening during normal operation, or there would be no gas for pumping in such a pump, for example in the so-called "dead end condition", see above The pump would not stop or be damaged, as would be the case with a displacement pressure pump, but the pump would develop cavitation phenomena. Such an effect on a liquid ring pump is sometimes called "queering" or "stalling". If the pump is left to run under these conditions for a long time, the rotor blades and the pump housing are damaged by cavitation phenomena. A liquid ring pump should always be supplied with air, which is pumped together with the liquid supplied to it, in order to meet the cooling and operating conditions.

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'Jegen the phenomena described above is ^a' liquid ring pump never used on purpose in those cases where the suction opening can be completely closed or where no gas can enter their Einlaßöffnimg because the gas supply could be prevented. This would be the case if the pump were used to "remove air and non-condensables from the condenser or evaporator system. As soon as most of the air is removed from the condenser and there is practically no gas flow, the vacuum pump or fills the compressor with its cooling and sealing liquid and the turbulence or cavitation effect arises. The damage described above is more a consequence of cavitation phenomena on the inner parts than a failure due to high loads, as would be the case with a positive displacement pump.

In the combination according to the invention "it is ensured that "The liquid ring compressor is also exclusively liquid pumps without air supply, without cavitation phenomena or damage to the pump or the compressor occurring.

It is known in the art that a centrifugal fluid pump Can not work if there is not a substantial volume proportion of air in the air entering the suction opening . There is a liquid-air mixture. In a usual

909885/0313

For centrifugal pumps, this limit is around three percent volume per cent of air in the liquid. This also applies if steam is present when sucking in, in order to prevent the presence of steam, the suction opening is always kept under pressure to such an extent that evaporation occurring at the inlet is suppressed. The extent of this pressure action is often given as ITPSTI, or positive suction height above the vapor pressure of the liquid under the conditions under which it arrives at the pump suction inlet, conventional centrifugal pumps require a positive suction height of about 6.6 m for continuous pumping. The best developed for this condition Xondensatorpunpen operate satisfactorily at a Lliüdestsaughöhe of about 1.20 m. Some zn special purposes, serving Koiidensatorpumpen been developed which operate with a positive Hettosaughöhe of not more than 60 cm, but usually this means a substantially reduced capacity "in given size of the pump used.

The invention provides a combination of a centrifugal liquid pump and a flow ring pump to pump liquids which are at their boiling point or at a positive Iletto suction height of Hull. This novel Zoiaoination a Flüssigkeitsringpiampe ir.it a ZentrifugalflässiglveitspuBipe result tn an even su descriptive 'Jeise a single Zentrifugalmasciiine, gases, vapors! Liquids or mixtures of these ■ effective and can promote a Uindestsaughöhe oline Bescliädigung the pump.

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It is difficult in some babbling to get the required positive Net suction height when using normal pumps or evaporators and to create or maintain condensation devices, especially on ships in which the required spatial height is sometimes not available. The invention makes it possible to have the pump directly on the side of the evaporator to attach yourself. You do not necessarily have to be attached below the evaporator to the usually known Pumps to create the necessary positive net suction head.

It is not only necessary to suck off the distillate at or near the boiling point β «, but also to remove the air from the condenser in order to increase the efficiency of the condenser and to keep the partial pressure of the air as close to zero as in the main part is possible the "evaporator It is also desirable to keep the Tem * temperature as low as possible heat sources with ^·;. applying low temperature for evaporator purposes to be able to _f what higher requirements · pump up at the performance of the vacuum · *. In this way, a maximum amount of heat can be extracted from the initially available heat source - and as a result of the low temperature at which the heat is extracted, fewer salts or other minerals are precipitated from the brine and, as a result, the inner parts of the evaporator less encrusted and slagged * ""! *

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A disadvantage "of known evaporators that work at listed temperatures as the gate direction according to the invention is that. that they need to be cleaned frequently.

In order to achieve the lowest possible temperature in the condenser, the best possible equipment is required to achieve this low temperature by increasing the vacuum. to be able to generate the condensation device to the highest possible value.

In this type of application, it is usual to use »high pressure V / asaerdampfdüsen to use to remove the air from the condensing device to remove. Mechanical vacuum pumps and jet pumps can also be used for this purpose. All these Pumps release the air separately into the atmosphere. previously it was considered impossible to take advantage of the general cheap normal liquid ring vacuum pump for this distance perceive the air from the condensation device. The main problem was that the amount of air which are removed from the condensation device. is sometimes so low that the vacuum pump is practically operating at Hull capacity. On this condition the normal liquid ring pump becomes "queer" or is exposed to and through cavitation symptoms

Cavitation phenomena that occur - as described above - *! if liquid is to be pumped without air, the pump is harms. The pump combination according to the invention, which

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contains atigen features of the liquid ring pump, also works on condition that the amount of air is practically gauze without being damaged.

Normal liquid ring pumps cannot match their usual Capacity work when the pump is used as a sealing medium supplied liquid approaches a temperature which The boiling point pressure of the liquid. Such pumps have to work at an absolute pressure which is significantly above the boiling point pressure, while it is possible with the pump construction according to the invention, at a high vacuum operate with the inlet seal temperatures practically corresponding to the boiling point temperature and the displacement capacity is normal for the respective air-steam mixture.

Another advantage of the device according to the invention is that it creates a higher vacuum than with one usual liquid ring vacuum pump 'is possible. Y / ie has already been carried out, must be on a conventional liquid ring pump There must be some gas or air in the suction inlet. With other * .7orten, There must be a certain partial air or gas pressure at the suction inlet insist «This makes it practical« eswesas & zle. Vacuum example7a.se limited to a one-step operation using a water seal at 15.6 ° C and approximately 63.5 cm of mercury. The pump can operate at a higher vacuum do not work safely, because then "dead end" processes and "strange" or cavitation phenomena occur. The pump according to the invention can, however, at the shut-off pressure

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or final pressure, which corresponds to the vapor pressure of its sealing 7 tion corresponds. Under this condition it needs to be satisfactory Operation, there is no air present, as is required with the usual liquid ring pump. Will 7 / water used as a sealant at 15 »6 C, the Pump can reach a vacuum of approximately 74.68 cm of mercury without cavitation damage, compared to 63.5 cm of a conventional one Pump.

The pump combination according to the invention contains a housing with a wing-having pump chamber or chambers and a liquid trace chamber ,, /./eiterhin it has a cylindrical Liquid ring rotor and a centrifugal liquid rotor which are connected to one another on a common drive shaft within the Punipenkammern. Of the Liquid ring pump part is arranged so that it comes straight out the device from which the boiling liquid, the vapors and the 3ase are to be removed, and this with a medium pressure su the inlet of the liquid runner promotes. The aUB runner and rotor existing unit is about a V / elle driven by a llabep.teil which has a disk on which the radially extending blades of a second stage centrifugal liquid rotor are mounted. On these blades are also the shell or walls and blades of the liquid ring rotor attached.

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H03578

According to the invention, the radially extending blades of the second liquid rotor are generally just as large or made larger than the blades of the liquid ring rotor and also larger than normally required would be to only pump liquid below the expected design operating pressure. The pump is still so con-

Structures that the channels of the representing the first stage Liquid ring are as large as possible in order to facilitate the conveyance of both liquid and gases if necessary.

The liquid ring rotor and the housing are designed in such a way that that they release a given displacement volume of gas via an inlet and outlet pressure gradient provided in the construction. In the case of a condenser, the inlet pressure is that of the condenser, i.e. e.g. a vacuum of the order of about 74 om Mercury j j

"■ '■." J

silver column, while the outlet pressure is slightly above atmospheric ^; '. Pressure, including friction loss, etc. * so possible. ||

has an overpressure of approximately 900 g to 1.56 kg * f " ^:

The design of the liquid ring pump also offers ί ^J

the possibility of not only gas but also the required liquid 4

ability to seal, cool and condense 'to promote. The degree | ^!

the absorption capacity for liquid is, however, in the ratio _f - \

to the total volume of gas which is supplied by the liquid ring part

promotes is still low. The diameter of the rotor. · ..; _

Piling up the liquid ring, the throughput or variance- ^ - *

power of these blades and the surrounding, with them * - *

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interacting elliptical housings are all designed in such a way that that they do the work described above at a normal motor drive speed Afford. The kinetic energy imparted to the ring of liquid by the blades or blades of the rotor just enough to get this level of work with an appropriate margin afford to. If the pump is only fed with liquid instead of gas at this point, it can use this liquid do not convey over the entire pressure difference, since the kinetic energy given to the liquid ring is insufficient. Huh In the invention, however, the liquid ring is only required to move the high density liquid mixture over a small pressure gradient to promote that corresponds to the kinetic energy given to the liquid ring or is comparable with it.

The centrifugal liquid rotor is constructed according to the invention so that it operates at the same speed of rotation and conveys the required amount of liquid from the condensation device at a vacuum of about 74 cm of mercury to a higher superatmospheric pressure than is required for the liquid ring part. For this higher pressure, the runner is constructed in such a way that it conveys against atmospheric pressure when it conveys a dense mixture of air and water that contains about 20 percent air by volume.

The liquid ring part according to the invention promotes normal air or Gas quantities, he compresses them to a smaller volume and conveys them into the inlet of the centrifugal rotor.

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During this process, the liquid ring pump delivers the air and the non-condensable gases over the entire provided Pressure difference from the high vacuum to the superatmospheric pressure, as described above, because of the high The centrifugal rotor causes practically no additional gas pressure difference during this operation. In other words, the liquid ring pump drives the gas through the vane channels of the liquid centrifugal rotor. During this time, the load is removed from the liquid crystal centrifugal rotor however, the liquid ring part, in that the cooling and sealing liquid carried over the small pressure difference is pumped over the centrifugal liquid rotor, eliminating the need for the liquid ring portion of the pump to force this liquid through the channels by its pressure effect.

The circumferential channels or passages of the centrifugal rotor also have the advantage that they use centrifugal force to

Separate the liquid conveyed from the air-liquid mixture conveyed by the liquid ring part to its inlet. This separation of the liquid from the air creates a Better air flow is achieved as this separation reduces the friction loss that normally occurs with turbulent flow a mixture of gases and liquids is connected through a fixed channel;

During this work stage, the centrifugal liquid rotor cannot achieve a significantly increased pressure difference for the entire mixture flow, since the density of this mixture

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performance compared to the dimensions and speed of travel of the centrifugal rotor, which is only dimensioned for liquid ", is low iBt. This condition applies to a lion denial device, if the air is first removed from the device, '. Break the vacuum of the condensing device to the operating vacuum is brought, the amount of air or gas to be pumped gradually decreased. until only those left by leak damage in the condensation device and the air from the Air released from salt water are to be promoted. Is the condenser device particularly well built, the amount of air to be removed is very small and practically only consists of the ! .tight from the salt water flowing into the evaporator is released.

Yfenn at work on a pump constructed according to the invention Reduced the amount of air in a condensation device or the amount of liquid to be demanded by the liquid pump either through the condensate to be conveyed or through the returned amount of liquid is relatively increased, increased the density of the extinguishing at the outlet of the liquid ring pump, '«Tird the proportion of air in relation to the total amount the liquid to be pumped is further reduced, so approaches the mixture at the inlet of the centrifugal rotor a Tfert which the centrifugal liquid rotor can cause a significant pressure difference by its own action, and on At this stage the centrifugal liquid rotor begins to act as the second stage to the liquid ring pump «

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When evacuation of the condensing device progresses and the mixture is the described "dead center" position '. · (dead end position) when there is little or no air at the outlet of the liquid pump, the mixture is has become tight enough so that the centrifugal rotor pumps this liquid over the pressure difference normally provided for the rotor when the liquid is throughput. The constructive one Liquid pumping capacity for the centrifugal liquid rotor is intentionally kept greater than the pressure difference between the absolute pressure of the condensation device - ._ ·, · direction and the atmospheric pressure, so that both z, u the time at which dense liquid is pumped, as well as to that Intermediate point in time when there is still some air in the liquid-]

There is a large amount of room for maneuver. 'Λ

So if this condition occurs in the operation of the condensation device, the centrifugal liquid pump '\ _' acts. : '■■ as the second stage to the liquid ring pump, whereby the * i ·,' intermediate pressure 'which is also the outlet pressure of the liquid ring - ■ .. (

i "■ j is noticeably reduced. Under this condition, _t - :

the liquid ring part of the ko-abinatlon then only has one, ''. 'Pressure difference of about 2 to 5 cm of mercury to work, · instead of over full. 75 cm or more pressure height from the absolute ',, -, j pressure of the condensing device to the outer knee. "-. [.. '

With this greatly reduced pressure level, which is in the order of magnitude I. a pressure of about 1.27 to about 7.6 cm of mercury- «" \

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the liquid ring pump has its liquid ring enough kinetic energy is supplied that all of the incoming liquid is conveyed over this reduced pressure gradient without the liquid ring being slowed down or put in a stalled or queered position, as related to the "dead center" position in conventional liquid ring pumps described vrarde.

The pump of the invention is particularly advantageous for a new evaporator system and an evaporator device can be used, especially for vaporizers that are used to obtain drinking water or other than human food Serve liquid * The pump construction according to the invention uses the well-known properties of the liquid ring compressor and the liquid centrifugal pump, in which no internal Lubrication is required. Therefore, the liquid delivered by the pumps is not with lubricants or - as a result Frictional contact - metal particles diminished, as in general; commonly the case with other mechanical pumping equipment; is.

Another advantage of using the distillate obtained from an evaporator using this pumping equipment is the fact that the air coming out of the. Evaporator fed starting fluid is not removed _t,

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is lost, but rather during the compression and ragging in the device according to the invention with the distillate product obtained is united and given up. It is known that, for example, distilled water has a stale taste Has. With other ports, compared with normalia drinking water it is without taste. The reason for this is that if it comes out of the condenser, all of the air from the liquid has been removed, making it bad . will taste good. * .7 however, the air becomes during the compression and pumping are reunited with the distillate, so that is obtained Distillate product palatable again with its normal amount of air absorbed.

Another advantage resulting from the use of the device according to the invention, which has already been indicated, is the fact that with this high vacuum ^{evaporator T} .7 heat sources of low temperature can be used. The cooling water, which is used to reduce the temperature of internal combustion engines, can be used as a Y / poor source for this evaporator unit. The temperature of the flowing around "Yasser that obtained from the normal internal combustion engine v / ill, is on the order of about 65 to 71 C. This temperature is quite sufficient for the inventive evaporator unit so that duijch use of these otherwise unused flowing \. ^R poor a relatively considerable amount of fresh "barrels can be produced,

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To show the fourth of this fact, it is roughly estimated that 3,780 liters of fresh drinking water distilled per day can be obtained with this device, which would otherwise not Utilized heat from the emitted cooling water of a 101 P.S. Motor is used. This shows that this type of device is particularly suitable for small boats, lonely islands, etc., where there is no fresh water supply.

The centrifugal liquid rotor has the design feature that it can operate at the flow rate of "liquids over its entire pressure range. Vifie all conventional centrifugal pumps, however, it does not have the ability to pump directly from the condensation supply line to the atmosphere when the absolute pressure of the condensation device In this case, the centrifugal rotor would require a positive net suction height in order to be able to work satisfactorily. In such an operation, the device according to the invention therefore creates the positive net suction height which is created by the action of the liquid ring of the device acting as the first stage erforderlieh is. this positive Kettosaughöhe, which is necessary for the centrifugal pump is compared with the normal constructively provided Druekge- \ falls of the liquid pump a small Jert * "Since this d for maintaining he suction head of the centrifugal rotor required pressure gradient is so small, the liquid ring can deliver this gradient, if practically all of the liquid

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is pumped without the liquid ring pump stalling or stalling or cavitation phenomena occurring. The liquid ring pump can continue to dispense liquid at the boiling point Pump over this low pressure gradient, which would not be possible if the liquid was pumped over a larger or a normal compressor pressure gradient would have to be pumped.

. It is known in the art that the present itself is smaller Amounts of steam at the inlet of a normal centrifugal pump Failure causes. The formation of steam at the inlet of the centrifugal pump is mostly caused by a reduction in the pressure of the Fluid, which in turn is caused by friction in the lines or at the inlet of the pump, whereby djaser Steam suddenly developed. The presence of steam reduces the overall density of the mixture in the centrifugal rotor "bis to a point at which the centrifugal pump part at this lighter mixing does not produce the required outlet pressure. As a result, the pump is shut down so that it only works wfenig P or nothing promotes.

A liquid ring pump, on the other hand, is primarily used for pumping of ufas, small amounts of steam and some liquid intended for cooling purposes · It is primarily a gas pump and can gas over its abnormal, constructively provided Promote pressure area. However, has the seal supplied to the PuMpe * liquid a temperature. That its evaporation pressure comes close to the inlet of the pump, the effect at the inlet of the -

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Additional pressure drop occurring an evaporation of the pump Sealing fluid. This vaporized liquid gradually fills the flow chambers of the liquid ring pump until this no longer has capacity for further gas throughput. The sudden development of the vapor at the inlet of the usual liquid pump occurs, as already stated an absolute pressure which is higher than the absolute evaporation pressure the sealing liquid used * This phenomenon occurs in all common liquid ring pumps and represents a generally recognized limitation. It thus shows that the usual liquid ring pump in this Trap can have air or gas at its inlet, but cannot get to this gas or it cannot suck in because Excessive vapor can quickly develop from the sealant at the pump inlet. This phenomenon approaches the bemts described "dead center" condition.

A pump according to the invention contains large channels leading to and from the liquid ring part of the combination, as well as the i as the second stage "acting centrifugal pump, which makes it possible that larger amounts of sealing and cooling liquid can be conveyed while with conventional liquid ring pumps, only limited amounts sealing By ensuring a greater flow of liquid through the pump, the same compression work results in a relatively low temperature reduction.

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909886/0313. !

increase in the liquid ring, and this fact itself is reduced the possibility of liquid evaporating at the inlet port. This danger of sudden evaporation continues reduced by the large channels, through which a lower pressure drop in the incoming gas and the incoming gas Liquid causes / ird.

A reduction in the formation of steam at the inlet is achieved by that the pressure gradient is reduced over which the liquid ring pump has to work in the first stage of the Zv / eistufeneinheit. This reduction in the pressure drop is reduced of course, the amount of work that the liquid ring part has to do has to perform, whereby the temperature rise in the large liquid flow through its channels is further kept low.

This effect is favored by another fact. the This lowers the temperature of the liquid ring somewhat, that steam develops at its outlet and as a result of the small temperature difference at which the seal works, this cooling effect is of better help than when there are large temperature differences, as is the case with a normal one Liquid pump is the case. This cooling effect and the evaporation of the sealing liquid change depending on the the thermal characteristics of the liquid passed through. This effect depends on the ratio of the latent heat of the liquid to the specific volume of its vapor at the respective Temperature and the respective steam.

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As stated above, the vapor developed at the inlet to the liquid ring pump unit is less than the normal flow rate of the pump. As a result, the liquid ring part permeates or "swallows" its own vapor and still has a large capacity, in order to suck further amounts of liquid and vapor into its flow chambers, where they are compressed and conveyed to the intermediate point. When compressing to the middle point, its mean sealing temperature is low enough to condense the vapors during this compression stabilized liquid to your "Z \. ^is promoted, which at this point has such a large positive net suction height that it can be picked up by the centrifugal liquid running pump without the development of steam and brought to atmospheric or the desired higher pressure.

So it is sweek of the Urfiniunj to create an improved Purrpenconfjtr., Which permeates liquids at admission pressures that approaches the boiling point of the piunpten liquid ((.

3 another l'v.'eck of the iSrfinduns is to create a pump the? l "ll -sigkei-t at ei ^ esa! .lir.lest amount of positive ITettosaughhöhe pumps. '

Furthermore, the invention is intended to create a pump which contains a fluid pressure ring compressor part and a centrifugal fluid pump part which works in series, ■ _: · ■ - * ■■ · - *

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The invention is also intended to provide a pump that includes a liquid ring vacuum pump part with a Sealing fluid operates at a pressure equal to or approximated to the boiling point of the fluid at the pump inlet owns.

A v / Eiterer purpose of the invention is to provide a liquid ring vacuum pump unit, which can operate at a locked or _k covered suction inlet, occurs without damage from cavitation.

The invention is also intended to provide a liquid ring pump combination create that can convey liquid without causing cavitation « damage occurs.

Another purpose of the invention is to provide a combination of a liquid ring pump and a Zentrifugalflüssigkeitspumpe, in which the parts Bind arranged such that ψ can be satisfactory, vapors, liquids pumped gases or from these existing mixtures and a good service life and operation of secured are.

The invention is also intended to provide a liquid ring vacuum pump or create a compressor combination with improved efficiency. '■ ·' -

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In addition, the invention is intended to provide a combined pump unit create, which contains a liquid ring vacuum pump and a liquid centrifugal pump, so that liquid at the same time through which one inlet opening and air or gas can be conveyed through a second inlet opening.

The invention is also intended to provide an improved vaporizer system. This evaporator system should have a single pump unit which is arranged to remove air from the condenser system and which has a suction inlet, is pumped through the liquid distillate from the condenser, the pump having a first stage forming liquid ring compressor, which becomes a as Second stage acting centrifugal liquid pump part promotes and wherein the pump pumps liquid to boiling pressure can.

The invention also has the purpose of creating an evaporator system which contains a pump for the throughput of liquid, ⁼ "which is arranged at the same level as the evaporator and is able to dispense liquid from this at or near the boiling pressure with a positive one JÜTett ο pump suction head from Hull. ',

The purpose of the invention is also to provide an evaporator system create, in which a V / heat source with low temperature, for example, unused heat from the cooling wastewater Internal combustion engine, can be recycled.

909S8S / Q313 ".-.- ■

The invention is also intended to provide an effective vaporizer system, that "works at a low temperature, which avoids a troublesome precipitation of minerals and salts in the evaporator is.

Then the invention is to provide a vaporizer that is tasty distilled water results in which the normal absorbed Has air content and from contamination by Puapen lubricants free is.

Finally, the invention is intended to provide an improved liquid and create gas pumps that are simple in construction, stable in construction, economical to manufacture, and effective is in operation.

To better understand the invention, its operational advantages and the particular uses of the invention are as follows For example, explained in more detail with reference to the drawings, namely show:

Figure 1 is a schematic view of an evaporator system according to the invention,

) FIG. 2 shows, on a larger scale, a cross-section through the vacuum pump 14 shown in FIG.

FIG. 3 is a view of the pump shown in FIG. 2 from the seen from the left front side,

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FIG. 4 shows a section along line 4-4 of FIG. 2, FIG. 5 shows a section along line 5-5 of FIG. 2,

Figure 6 a pig. 2 similar Teilquersclmitt, the one shows another embodiment of the compressor inlet part for one of the pumps shown in Fig. 1, and

Figure 7 is a partial view in section along the line 7-7 of the Fig. 3.

In the drawings, an evaporator 10 is shown, which on has a condensation device 12 at the upper end of its one side. In the present embodiment of the invention the evaporator 10 is used to brine in the evaporator to evaporate arranged heating devices. The emerging Vapors go up and sideways into the condenser 12 headed. The condensation device 12 includes the usual cooling coils through which a liquid such as | Water, is directed and the resulting condensate .will be on the floor the condensation device collected. The condensate or Distillate is the fresh water which is produced by the system and which has the certificate of the evaporation process represents.

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In order for the vaporizer 10 to work as effectively as possible, it is important that the condensing device 12 ″ at a Temperature and a pressure works so low according to the available heats and the coolant supply as possible. In order to keep the temperature and the absolute pressure as low as possible, it is important that the condensation device constantly from accumulated gases and vapors freed and kept under vacuum. The absolute pressure in the condensation device is also reduced by entrained air, gases and non-condensable components her to be removed. Air remaining in the condensation device increases the total pressure prevailing in it.

According to the invention, a generally designated 14 is used Vacuum or compressor pump both to remove the air and "Jegpusipen the distillate as well as to maintain the Vacuum in the condensing device.

The pump 14, the particular construction of which is to be described in more detail below, contains a suction inlet which is connected by a line 16 to the upper part of the condensing device 12 or any other point of the condensing device at which it is possible to remove accumulated air to remove. Distillate, which is formed at the bottom or in the collecting vessel of the condenser 12, passes through a managerial '■ tung 18 to "the other of the pump suction inlet 14. The compressor pump 14 operates in a new manner to be described,

9 0 9885/0313 ■ - 29 -

BATH ORIGINAL

in order to direct the compressed air and the condensate into an outlet line 20 and from there into a container 22 situated higher up. The container 22 serves as a separator or separator and enables excess air to be discharged through an opening 24 into the open air. The excess liquid is brought via a line 26 to a collecting container or to the point of use for the evaporated water or distillate. Sin part of the guided to the vessel 22 liquid is recycled via a line 28 to a sealing shutter 29 and thus supplied to the pump to di "pump bearing with fluid seal and to promote the densification of the vapors * which are passed through the pump. Vapors further flow through the lines 16 and 18, since the steam is in the capacitor 12 at or near the pressure level at which the liquid; evaporates. ■

In accordance with the invention, the evaporator system includes another pump, indicated generally at 20, similar to pump 14 , and via line 32 with brine from the bottom of the pool can remove. Since the brine in the evaporator 10 is at or near the boiling point during the evaporation process, it has been shown that most pumps require a positive pressure head or a positive pressure gradient on the suction side is explained in more detail, does not require such a gradient and kanii on de »-; same Mveau as the Verdampf®? * be arranged * you

- 3ο -

the brine via an overboard or waste water pipe 36

According to the invention, the liquid and gas pump includes 14 a practically cylindrical, generally designated 38 Housing or housing part with an end wall 4o, the against the motor 34 and is bolted to this. The end wall 40 has an opening for a shaft 42 of the motor 34 on »At the opening of the wall 4o surrounding the shaft 42 is a mechanical shaft seal 44 intended*

At the opposite end of the housing part 38 is a generally designated 46 with this! The paddle housing accommodating the compressor and an inlet head are bolted. This wing housing and inlet head part 46 has an upper inlet channel 48 and a lower inlet channel 50 of. each of which opens into a separate inlet conduit 52a and 52b, respectively, which are formed within a cylindrical, apertured oven, generally designated 54, located in the center of the wing portion of the housing. The conduits 52a and 52b form separate inlets for each wing of the pump _t and in this way it is possible to obtain an independent pumping action on each of the separate files of the condenser connected to the lines 16 and 18.

- In the illustrated embodiment of the invention, the housing has. 46 practically elliptical inner walls 3B _t delimit the two wing parts.

According to the invention, a generally designated 58 is. '»Rotor provided, which is screwed to the Y / elle 42. and" is fastened and rotates with this. " The rotor has a hub 60, a disk 62 projecting radially outwardly from the hub, a blade assembly 64 extending axially outwardly from the disk 62, and a liquid ring rotor portion, generally designated 66, 7o and having eotor strips or blades 72. 'r ... ■ - · - .. Ä

According to the invention, the end jacket or V / andteil 7 o protrudes axially and radially beyond a liagerdiohtungteil 74 of the housing 46 and has an inner circumferential wall 7oa, which is arranged at a small distance from an inwardly protruding jacket or wall part 7ö of the housing 38, as well as a radially extending tip 7ob, so that a centrifugal fluid sealing chamber 79 is created between an annular pumping chamber and the fluid ring pump part 66 . The formed in the annular G-38 * ehause discharge chamber So is connected via an outlet conduit 82 having an outlet nozzle SA. - _; ..

During operation, .vierden liquid and Plussigkeits-Gas-ö-emisehe through the opening 5o from the Leiturg. 16 added, while by tiiiT l'ffnunj; 46 from the line 16 mainly <> as ιιηά -juamrf are taken on. To ensure,

909885/0313

BATH

that a certain amount of liquid is available for condensing and sealing, part of the liquid is returned from the container 22 via the line 28 to the sealing connection 29. It is directed to a sealing chamber 96 formed between the wall 68 and the housing 4-6, then passed through a precisely sized opening 98 and finally into the wing portion 56 (Fig. 7). Liquid that has entered the first compression stage of the pump is directed around the vanes by paddles 72, where the alternating inward and outward direction of the liquid ring causes the pumping action and the compression of the gases. Gas, liquid and vapor pass through an inlet opening 83a or 3b (Fig. 2) in the part 54 at the inner end of the blades 72 into the inlet channels 52a and 52b, while condensed vapors and compressed gases each pass through an outlet opening 86a and 86b in the cylindrical part 54 provided with openings. The part 54 provided with openings has an outlet channel 88 which is in communication with the inlet or inlet 9o of the liquid pump wheel 58. The pump delivers the liquid radially outwardly in the already described annular chamber ⁴ surrounded 8o.

The dimensions of the liquid ring compressor part 66 and the blades 72 of the Botor, as well as the size of the Ge ·· "·" housing 46 are chosen so that a certain delivery volume of gas, based on a given suction pressure in millimeters Mercury column, is promoted. This volume then becomes

9 Q-98 8: 5/03 13

compressed while part of the the gas and the Liquid moisture-moving vapor condenses and at practical atmospheric pressure in the inlet 9o (! "Fig. 2) promoted ' will. The compressor 66 can not only deliver the gas volume, that he compresses, but ey can also do the necessary amount of liquid for sealing, cooling and condensing promote »the ratio of this fluid capacity to the gas displacement of the pump is, however, very small »

When the ring rotor 66 primarily promotes gas, such as in the initial release process of a condenser, this gas becomes in the Sotor compressed to the required atmospheric or superatmospheric pressure and through its opening passed into the inlet 9o of the centrifugal rotor, like this Common in hanging pumps is · This dispensed mixture of gas and liquid contains less gas per volume than am! in *

. outlet channel 52, namely as a result of the compression ratio between the absolute inlet and outlet pressure, pus any condensation phenomena that may occur within the ring pump of the centrifugal ^{rotor 58 l} (FIG. 5), through the collecting chamber 8o and then through the outlet line 84, the centrifugal rotor calls out:, -

^ bei.dem at this % dusohströmendeÄ% sa &# i »ö» ro # iÄiohtjac

00988t / 01 * 3

Pressure difference, but acts heim pumping the Liquid that is discharged from the ring rotor together with the gas. The centrifugal rotor also separates by power the centrifugal force removes the liquid from the gas while this flows through him, so that a clean passage gang for the gas on its way through the runner's license is guaranteed. This reduces friction losses that would otherwise occur with turbulent mixtures of gas and Liquid are extraordinarily large.

According to the invention, the size and shape of the blades 72 taking into account the displacement provided for the liquid ring, which is caused by the wing part of the housing is determined, chosen so that the required amount of G-as and liquid at a nominal drive speed of the Motor is pumped or dilrchleitung. The one from the engine Kinetic energy transmitted via the blades is just enough to carry out this work within reasonable limits *

During normal operation of a condensing device and after the condensation device has been freed from the initially available air volume is little or no air from the liquid ring pump so that it tries to only pump liquid. The dimensions of the liquid ring pump are chosen so that they are not kinetic enough Energy possesses to liquid only over the same pressure gradient; au pumps through which it normally delivers air,

9Q9885 / & 313

In this embodiment of the invention there is therefore precaution. taken that the pressure drop across the liquid ■ pump is reduced if this is only intended to pump liquid. This is done by combining it with the rotor blades 64 of the second stage. This second runner has a additional peak capacity that is above and above the Peak conditions of the pressure between the condensing device and the final exit point, the pressure head of which is slightly above atmospheric pressure.

The rotor blades 64 are dimensioned so that they have a tight Liquid-air mixture from the absolute pressure of the condensing device 12 convey to the separation container 22. During the preparatory work step, in which the mixture has a has a lower density and the liquid ring pump is air the centrifugal rotor adds practically no pressure difference the pumped gas. However, once this density is reduced by the liquid ring pump When the conveyed air is increased, the blades 64 act the centrifugal rotor as a second stage of the ring rotor, whereby the intermediate pressure at the outlet ports 86a of the Mngrotors is degraded to the point where the pressure drop across the King rotor is so low that the liquid ring only has to face this pressure gradient Fluid promotes, and without harm and without the existing kinetic energy to exceed that of

909885/0313

Motor 34 is transferred to the liquid ring · The Blades 64 of the centrifugal rotor convey the diohte air-liquid mixture into channel 8o, from which it is discharged via line 82 with a prescribed pressure gradient to outlet line 84 »

The pump shown at 3o in FIG. 1 is the pump 14 similar, but contains only a single inlet 92 (Fig. 6), which is used for both pump blades and the one with the line connected is. The inlet 92 is formed in an end housing part generally designated 94 (see Fig. 6). By, liquid, gas and vapor drawn in through inlet 92 into a single channel 52 of the cylindrical, with openings provided part 54 passed. This channel 52 is for both of them Inlet ports 83a and 83b are provided. The pump is used to remove brine at the boiling point from the evaporator 1 ο to pump. The same single inlet pump 92 can be used to remove material from the conditioning device 12, the inlet of both the distillate and the air from the condenser records. Some capacitor designs are advantageous connected in this way.

It should also be noted that each of the pumps with two Wing parts 56 is shown provided. However, it can also have "a single eccentric housing as a single wing

909885/0313

a single inlet connection and a single outlet port which communicates with the inlet 9o of the second stage rotor, or a "can be used by a number of blades in excess of two. where a single inlet 92 and outlet 86 are shown which in turn communicates with the inlet 9o of the second stage rotor.

^; '■ "■■■

It should be noted that the improved pump construction according to the invention has many other uses in addition to the evaporation system described Boiler traced back. In such cases, it has so far been customary to use a pump ^s system containing a jet pump or jet pump and a centrifugal pump in a combined arrangement of "The centrifugal pump withdraws a heat spreading, Anfüllumfuhrung provided with fins. Water and conveys it through the nozzle pump, which causes a positive flow of condensate, grass and air from the outlet line of the system for this process and feeds the condensate directly into the boiler. In such systems, entrained »non-condensable gas and / or air is removed by means of a ■ ₍

Irennkammeranlage removed from the process stream. - ·

ÖÖ98SS / Q313

■ The pump according to the invention can be the combination of a nozzle and replace centrifugal pump and when pumping liquids, Gases and vapors or mixtures work effectively.

Of course, the invention is not limited to the ones described and illustrated embodiments, but rather there are modifications within the scope of the inventive concept. and changes are possible. "

- Expectations -

909385/0313

Claims (1)

1. Zentrifugalverdrängerpumpe, characterized by a housing having an interior at least one vane having compressor part and an inner compressor part notify a disclosed liquid pump portion, further characterized by inlet means for connection which protrude aufcen from the liquid pump portion to this Kompresaorteiles, outlet means, a symmetrical, rotatable Kompres ^ orrotor in the Kotorteil with symmetrically radially extending compressor blades, a liquid rotor adjacent to the KomnresBorrotor with blades that are shaped so that they create a central MnlaiS co..ie a radial outlet, which is directed towards the Auslaßeinrichtur \ - in such a way, that ledia are taken up in the middle part and conveyed to the outlet device, and the compressor outlet device is connected to the middle liotoi-fin outlet, and furthermore characterized by devices for rotating the Iiotor and the runner, the iiom ^ resEOrteil and de r compressor rotor such a ^ mes. U2i ^ cn have that they practically fully-ί the steam delivered to the inlet within predetermined pressure limits. i .; compress and the compressed vapors and gases ^ u Gf-:;. I encourage runners and the runners are measured and 909385/0313 is shaped so that it pumps practically all of the liquid up to a predetermined pressure and the pressure at the outlet of the compressor is reduced, which means that this compressor practically all of the liquid over a smaller pressure drop can promote. 2. centrifugal displacement pump according to claim 1, characterized in that that the compressor inlet has a central channel with the inner ends of the Hotor blades adjacent peripheral openings having. 3. centrifugal displacement pump according to claim 2, characterized in that that the compressor outlet opposite the central inlet channel has a central channel which is connected to the runner inlet connected eats and has openings with the: Komprer.porpumpteil on the inner circumference of the blades in connection stand. 4. Zientrifugalverdrf-n ^ er pump according to claim 1, characterized in that the housing has a wall spaced from the de: r. ilompressorrotor is adjacent end of the rotor, and that the compressor rotor has a V / andteil, _x which is arranged so that it rotates with its circumference at a small distance νυπ the wall, the rotor and the housing eir.nn sealing channel between the runner and the Xompressor rotor. 909885/0313 6AD OHiGlMAU 5 centrifugal displacement pump according to claim 1, characterized shows that the inlet device connected to the compressor rotor has a central opening part around which the compressor rotor blades are rotatably arranged, the opening portion being one adjacent to the interior of the blades Has control opening. 6. centrifugal displacement pump according to claim 5, characterized in that that the opening part has a second control opening which is practically diametrically opposite the first opening, and that the compressor pump part has at least two wing parts, to which corresponding openings are assigned are, with at least two inlet channels connecting the inlets of the opening parts. 7. Centrifugal displacement pump for pumping liquid or gas or a combination of (Jas and liquid, characterized by a housing with an inner, at least one wing-forming compressor part and an adjacent to the compressor part arranged liquid pump part with an annular outlet formed in it, through a One-piece rotor part with a centrifugal vane part, which is arranged in the liquid pump part of the housing, and a compressor rotor part connected to this, which has a number of symmetrical radially extending blades which protrude into the compressor part, further through an inlet channel arranged in the housing , the ■ Q09885 / 0313 Compressor part in radially outwards into the rotor blades' running directions medium, through an outlet channel formed in the housing, from the central part of the compressor rotor blades to the central area of the rotor blades leads and medium from the compressor part leads to the liquid pump part, the housing, the rotor blades, the rotor blades and the inlet and the outlet channel are dimensioned so that only gases over a predetermined pressure range from the compressor part ™ are conveyed and only conveyed liquid from the compressor part over a smaller pressure range while combined gas and liquid components are conveyed within set operating pressures. 8. Centrifugal positive displacement pump for pumping liquids at their boiling point and for pumping liquid, exclusively Gas or a mixture of these, characterized by a housing with an inner, at least one wing fc forming compressor part and one adjacent to the compressor part arranged inner liquid pump part, as well as a rotatable rotor device in the housing, this device a compressor part for compressing gases from a low pressure to a specified higher pressure and for the passage of liquid alone or liquid and gas in any proportions over a smaller pressure range has, as well as by a liquid rotor that so is arranged that he discharged from the compressor 909885/0313 Receiving media and at an elevated, over the high initial, laßdruck the compressor past print promotes and reduces the pressure at the outlet of the compressor when substantially only liquid is discharged from the pump. 9. Zentriiugalverdrängerpunrpe according to claim 8, characterized in that that they have a backshell part with two separate inlets which are connected to the compressor part, and that the Kompres sort eil at least zv / ei. Has wings that A separate inlet is assigned to each. 1o. "Plant for the evaporation of oil with devices for the continuous stranding and for the evaporation of the liquid and devices for the condensation of the evaporated liquid, characterized in that there !. ^J is a single iumpe castle to the condenser: i is that a rotating KomrrfSi ortßil pufv / f int, the continuously üase and vapors i'us the condensate: * iervtrrichlung tntfernt to the vapors and IASE a ^ n v. 't / Ptntiich above the working pressure of the condensing device α :: .- lie.;. The pressure to cone ^ ren or to coni'rimit-rer., whereby the pump v.eitt: xin i. ittel has to ..onieiiniri ·· t-? 1 ipi ^! i _f ; kf-it from the - ^ cndeiifiervcrrichtung to remove * ii uno Pie with Jämvien z \ i unite the removed v.-eruvn, -.v ⁱ : u this grain; riroi · ri xi-d condensed -.vird, L'O '.: ie eiiiMi ^ -1 ·!; ε ^ i rkeitsrotcr benrciib ^ rt new. Compressor, ■ 1fr is arranged in such a way that it conveys liquid and combines Jase from the Komrrtesor with servant again at increased pressures « 909885 / Ο 313 _eA D 11.Verdampferanlage according to claim 1o, characterized! that the single pump has a housing which is adjacent to an inner compressor blade part and a fluid pump part surrounds the compressor blade part with an annular outlet. 12.Verdampferanlage according to claim 1o, characterized gekennzelehnet that the pump has separate inlet channels, of which the one with the upper part of the condensing device and de? other is connected to the lower part of the condensing device. 13 "Evaporator system with an elongated container with" Equipment for the continuous heating of BoIe in order to " to evaporate their liquid, and one with the Ifcngge «- stretched container connected condensing device with a cooling device for condensing the vapors, dmdureh characterized in that a centrifugal displacement pump «in the dl · Condensing device is connected and a liquid ring compressor cell with an outlet and a centolfttgftl fluid pump part has, behind defl Auelafl dee Kompreesorteiles is switched, which serves to Äin Äirehsatz convey into the centrifugal liquid pump part BU, ■ and that in the compressor and in the liquid pump part Itotor devices are provided to glasses from the condensing device to a considerable extent above the ' Pressure of the condensing device to condense lying pressure and to promote liquid from the condensing device to the liquid overflow with a pressure that is only slightly higher 9098 85/0313 ßAD ORIGINAL is than the pressure in the condensing device, where the • liquid runner part is the outlet pressure of the compressor part reduced when this essentially only penetrates liquid. 14.Verdampferanlage according to claim 13, characterized in that the compressor part has a central, provided with openings part which has practically diametrically opposed openings, wherein the housing part has at least two blades and the Hotor has radially extending blades which are rotatable about the opening part and have a separate inlet which connects the bottom of the condensing device at the point where the condensed liquid is located therein, and an inlet opening which connects to the upper part of the condensing device at the point where Vapors and gases are formed. 15. Pump device for use in an industrial process for pumping liquids below the boiling point obvious conditions of the fluid, characterized by a G housing with a fluid trace part a compressor section adjacent the liquid pump section including at least one vane by inlet means for connecting the compressor part and an outlet device for connecting the liquid pump table, wherein. the liquid pump part has a central opening on the side opposite the compressor, a rotatable one 909885/0313 . Shaft protrudes into this opening and a one-piece rotor is attached to the rotatable shaft, this rotor part being a centrifugal rotor with blades which are bent around a central inlet and an outlet directed towards the outlet means forms, while a compressor rotor part has symmetrical, radially extending blades in the wing of the compressor part are arranged, and a central inlet channel, the inlet device and the central part of the Compressor rotor connects and a central outlet channel, which the central part of the compressor rotor and the liquid runner part connects with each other. 16. Industrial process in which liquids under the Boiling point of the liquid, pressure and temperature conditions are processed, characterized in that a? Pump is used to pump the fluids that a housing having a liquid pump part and a compressor part adjacent to the liquid pump part contains at least one wing, furthermore an inlet device for connecting the compressor part and an outlet device for connecting the liquid pump part, the liquid pump part having a central opening has a side opposite the compressor part, a rotatable shaft protrudes into this »opening and a one-piece rotor part attached to the rotatable shaft is, this Hotorteil a centrifugal rotor part 909885/0313 with blades that are curved and a central one Form inlet and a radial outlet directed towards the outlet device, while the ICompresaorrotorteil symmetrical, having radially extending blades or scoop parts, the are arranged in the compressor part and middle inlet and outlet passages connect the inlet means and the central portion of the compressor rotor to the liquid runner portion. Method for operating an evaporator for the distillation of water from salt water or brine, in which the distillate is collected in a condensing device and the brine is subjected to high temperatures and a vacuum, characterized in that vapors and gases are continuously sucked out of the condensing device , will be the .Destillat and the vapors and Jase combined and subjected dannDruck to condense the vapors and to compress the gases, and that subsequently the pressure of the combined g distillate, the compressed oasis and the condensed vapors increases this ur.dT be promoted at such increased pressure. « 1ö. Method according to claim 17, characterized in that the concentrated brine is continuously removed from the lower part of the evaporator lY-rs while the evaporator is below high tensile and vacuum pressure works. 0 9 8 6 5/0313