DK172565B1

DK172565B1 - Heat treatment device for using steam at a reduced pressure

Info

Publication number: DK172565B1
Application number: DK568789A
Authority: DK
Inventors: Hideaki Yumoto; Takayuki Morii
Original assignee: Tlv Co Ltd
Priority date: 1989-11-14
Filing date: 1989-11-14
Publication date: 1999-01-18
Also published as: DK568789A; DK568789D0

Description

DK PR 172565 B1DK PR 172565 B1

Opfindelsen angår en varmebehandlingsindretning som angivet i krav 1's indledning.The invention relates to a heat treatment device as set forth in the preamble of claim 1.

Inden for den kemiske industri og levnedsmiddelindustrien behandles materialer ofte ved relativt lav temperatur, fx under 100aC, for at bevare produktets kvalitet og sikre driflsomstændig-5 heder. IJP patentskrift nr. 60-64108 beskrives en sådan varmebehandlingsindretning, hvor der anvendes damp af reduceret tryk som varmemedium. I denne Indretning ledes damp fra en dampkilde gennem en trykreduktionsventil til et varmevekslerkammer, hvis afgang er forbundet til en sædvanlig vakuumpumpe via en dampfælde, idet styring af strømningshastigheden for væskestrømmen etableres i et omløb til denne dampfælde. Imidlertid drives en sædvanlig 10 vakuumpumpe altid, så det højeste vakuum søges opnået, således at pumpen giver anledning til et for kraftigt sug på dampen, hvorved man får et uønsket højt vakuum i varmevekslerkammeret. For at forhindre dette kan strømningshastigheden i det før nævnte omløb forøges, så trykket i varmevekslerkammeret fastholdes. Som resultat heraf udblæses imidlertid en masse damp gennem omløbet, hvorved man ikke blot får et stort damptab, men også et ustabilt tryk i 15 varmevekslerkammeret.In the chemical and food industries, materials are often treated at relatively low temperatures, e.g., below 100 ° C, to maintain product quality and ensure operational conditions. IJP patent no. 60-64108 discloses such a heat treating device using reduced pressure steam as a heating medium. In this Device, steam from a steam source is passed through a pressure reducing valve to a heat exchanger chamber, the outlet of which is connected to a conventional vacuum pump via a steam trap, controlling the flow rate of the liquid flow in a circulation to this steam trap. However, a usual 10 vacuum pump is always operated so that the highest vacuum is sought, so that the pump gives rise to an excessive suction on the vapor, resulting in an undesirably high vacuum in the heat exchanger chamber. To prevent this, the flow rate in the aforementioned circulation can be increased so that the pressure in the heat exchanger chamber is maintained. As a result, however, a lot of steam is blown out through the circulation, thereby not only causing a large loss of steam, but also an unstable pressure in the heat exchanger chamber.

Det er i overensstemmelse hermed et formål med opfindelsen at tilvejebringe en forbedret varmebehandlingsindretning med anvendelse af damp af reduceret tryk, hvilken indretning har et stabilt tryk i varmevekslerkammeret og en høj termisk virkningsgrad.Accordingly, it is an object of the invention to provide an improved heat treating device using reduced pressure steam, which has a stable pressure in the heat exchanger chamber and a high thermal efficiency.

2020

Det er også et formål med opfindelsen at tilvejebringe en bekvem varmebehandlingsindretning, ved hjælp af hvilken man skiftevis kan opvarme og afkøle, som situationen nu kræver det.It is also an object of the invention to provide a convenient heat treatment device by means of which one can alternately heat and cool, as the situation now requires.

Ifølge opfindelsen tilvejebringes en varmebehandlingsindretning til anvendelse af damp af re-25 duceret tryk og omfattende en trykreduktionsventil med en tilgang, der er forbundet med en dampkilde, og en afgang, et varmevekslerkammer med en tilgang, der er forbundet med afgangen af trykreduktionsventilen, og en trykreduktionsindretning, der er forbundet med afgangen på varmevekslerkammeret, hvorhos trykreduktionsindretningen omfatter en ejektor med et sugekammer, der er forbundet med varmevekslerkammerets afgang, en indretning til at lede 30 driftsvæske til ejektoren og indretninger til at styre temperaturen på denne driftsvæske, hvorved en styring af ejektorens sugetryk bliver mulig ved styring af nævnte temperatur.According to the invention there is provided a heat treating device for use of reduced pressure steam and comprising a pressure reducing valve having an approach connected to a steam source and an outlet, a heat exchanger chamber having an approach connected to the outlet of the pressure reducing valve, and a a pressure reducing device associated with the outlet of the heat exchanger chamber, wherein the pressure reducing device comprises an ejector with a suction chamber connected to the outlet of the heat exchanger chamber, a device for conducting 30 operating fluid to the ejector, and devices for controlling the temperature of this operating fluid, thereby controlling a suction pressure becomes possible by controlling said temperature.

Opfindelsen skal i det følgende forklares nærmere i forbindelse med tegningen, hvor 35 fig. 1 skematisk viser en første udførelsesform for varmebehandlingsindretningen ifølge opfindelsen.BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be explained in more detail in connection with the drawing, in which FIG. 1 schematically shows a first embodiment of the heat treatment device according to the invention.

fig. 2 et blokdiagram over en variant af udførelsesformen ifølge fig. 1, fig. 3 et tværsnitsbillede af en vigtig del af et samlingsrør, der anvendes i varianten i fig. 2, 2 DK PR 172565 B1 fiog. 4 skematisk og delvis som blokdiagram en anden udførelsesform for varmebehandlingsindretningen ifølge opfindelsen, fig. 5 skematisk et tværsnitsbillede af en trykreduktionsventil, der anvendes i indretningen ifølge opfindelsen, og 5 fig. 6 et tværsnitsbillede, der viser en del af varmevekslerkammeret i den i fig. 4 viste udfø-relsesform.FIG. 2 is a block diagram of a variant of the embodiment of FIG. 1, FIG. 3 is a cross-sectional view of an important portion of a manifold used in the variant of FIG. 2, 2 DK PR 172565 B1 fiog. 4 is a schematic and partial block diagram of another embodiment of the heat treatment device according to the invention; FIG. 5 is a schematic cross-sectional view of a pressure reducing valve used in the device according to the invention; and FIG. 6 is a cross-sectional view showing a portion of the heat exchanger chamber of FIG. 4.

I fig. 1 ser man. at damp fra en passende dampgenerator (ikke vist) passerer en trykreduktionsventil 1 og ledes ind i et varmevekslerkammer 2, som beskrives nærmere i det følgende.In FIG. 1 you see. that steam from a suitable steam generator (not shown) passes through a pressure reduction valve 1 and is fed into a heat exchanger chamber 2, which is described in more detail below.

10 Varmevekslerkammeret 2 er forbundet med en ejektortndretning 3. Denne omfatter en ejektor 4 med et sugekammer, som står i forbindelse med varmevekslerkammeret 2, en lagertank 5 for ejektorvæsken i systemet (fx vand) og en sædvanlig snekkepumpe 6, som pumper væsken fra tanken til ejektorens 4 dyse og retur til tanken 5 fra ejektorens 4 afgangsrør (defuser).The heat exchanger chamber 2 is connected to an ejector device 3. This comprises an ejector 4 with a suction chamber which communicates with the heat exchanger chamber 2, a storage tank 5 for the ejector liquid in the system (e.g. water) and a conventional worm pump 6 which pumps the liquid from the tank to the the nozzle of the ejector 4 and return to the tank 5 from the ejector 4 (diffuser).

Tanken 5 er forsynet med et tilledningsrør 8 for vand og en på dette monteret elektrisk drevet 15 ventil 7 og en styringsenhed 9 for denne, som reagerer på et temperaturslgnai fra en temperaturføler 10, som er anbragt i røret mellem tanken 5 og pumpen 6. En anden elektrisk drevet ventil 11 med forbindelse til systemets ydre er anbragt mellem pumpen 6 og ejektoren 4, og der findes desuden for ventilen 11 en ventilstyreenhed 12. der reagerer på et signal fra en niveaumåler 13 i tanken 5.The tank 5 is provided with a supply pipe 8 for water and a valve 7 mounted on this electrically driven 15 and a control unit 9 for it, which responds to a temperature signal from a temperature sensor 10 arranged in the pipe between the tank 5 and the pump 6. another electrically driven valve 11 connected to the exterior of the system is disposed between the pump 6 and the ejector 4, and in addition there is a valve control unit 12 for the valve 11 which responds to a signal from a level meter 13 in the tank 5.

2020

Under drift tvinges vandet i tanken 5 af pumpen 6 til ejektoren 4, og det recirkuleres til tanken 5. Herved opstår der i ejektoren et mætningstryk svarende til den øjeblikkelige vandtemperatur, og trykket i varmeveksleren 2 reduceres herved. Vandtemperaturen overvåges konstant af temperaturføleren 10, og hvis den overstiger en forudbestemt værdi, åbnes den elektrisk 25 drevne ventil 7 af ventilkontrolenheden 9, og der ledes koldt vand fra tilgangsrøret 8 ind i tanken, hvorved vandtemperaturen falder. I overensstemmelse hermed holdes trykket i varmevekslerkammeret 2 automatisk på en forudbestemt værdi, idet man på passende måde sætter ventilkontrolenhedens 9 aktiveringstemperatur. Vandniveauet i tanken 5 øges, når der tilledes vand, men det overvåges konstant af niveaumåleren 13, og hvis det overstiger en forudbe-30 stemt øvre grænse, åbnes den elektrisk drevne ventil 11 af ventilkontrolenheden 12. hvorved det overskydende vand lukkes ud af systemet. Når niveauet når en forudbestemt nedre grænse, lukkes ventilen 11. I indretningen ifølge opfindelsen fastholdes altså damptrykket i varmevekslerkammeret 2 på et forudbestemt, reduceret tryk, og der opstår aldrig et for stort vakuum, som det er tilfældet i indretninger ifølge den kendte teknik.In operation, the water in the tank 5 is forced by the pump 6 to the ejector 4 and it is recirculated to the tank 5. This results in a saturation pressure corresponding to the instantaneous water temperature in the ejector and the pressure in the heat exchanger 2 is thereby reduced. The water temperature is constantly monitored by the temperature sensor 10 and if it exceeds a predetermined value, the electrically driven valve 7 is opened by the valve control unit 9 and cold water is fed from the supply pipe 8 into the tank, whereby the water temperature drops. Accordingly, the pressure in the heat exchanger chamber 2 is automatically maintained at a predetermined value, appropriately setting the actuation temperature of the valve control unit 9. The water level in the tank 5 increases as water is fed, but it is constantly monitored by the level gauge 13, and if it exceeds a predetermined upper limit, the electrically driven valve 11 is opened by the valve control unit 12. thereby leaving the excess water out of the system. Thus, when the level reaches a predetermined lower limit, valve 11. In the device according to the invention, the vapor pressure in the heat exchanger chamber 2 is maintained at a predetermined reduced pressure, and no excessive vacuum, as is the case in devices of the prior art, never arises.

3535

Som beskrevet ovenfor forventes trykket I varmevekslerkammeret 2 at blive lig mætningsdamptrykket for systemets væske, og temperaturen for opvarmningsdampen, som ledes gennem trykreduktionsventilen 1, forventes at blive den til dette tryk svarende mætningstempera- 3 DK PR 172565 B1 tur. Imidlertid har damp af højt tryk en tendens til at blive overhedet, når trykket reduceres i en trykreduktionsventil, og temperaturen i varmevekslerkammeret 2 kan derfor blive højere end forventet. For at undertrykke en sådan overhedning kan man, som vist i fig. 2. anbringe et samlekammer 14 mellem trykreduktionsventilen 1 og varmevekslerkammeret 2, idet samle· 5 kammerets 14 bund via en dampfælde 15 er forbundet med ejektorens 4 sugekammer, og idet den elektrisk drevne ventils 11 tilgangsside via en ventil 16 er forbundet med en temperaturregulator 17, som sidder på samlekammerets 14 sidevæg. Som det fremgår af Tig. 3, omfatter temperaturregulatoren 17 en hul frontdel 18, som er skruet ind i sidevæggen på samlekamme-ret 14, og en dertil koblet rørforbindelse 19, idet frontdelen 18 har en gennemboring 20, som 10 danner en åbning ind til samlekammerets 14 øvige del, og en bageste del, som er forbundet med det indre af rørforbindelsen 19 gennem sideåbninger 21 og en afskærmning 22. Ved hjælp af denne indretning opsuges drænvand, som af dampfælden 15 er opsamlet fra samle-kammeret, af ejektorlndretningen 3, og når ventilen 16 er åben, ledes vand af mætningstemperaturen ved hjælp af pumpen 6 til temperaturregulatoren 17. hvor det forstøves ind i samle-15 kammeret 14 gennem gennemboringen 20. Herved reduceres temperaturen på den overhedede damp, og det forstøvede vand bliver til mættet vanddamp. Damptrykket i varmevekslerkammeret 2 kan holdes konstant på et tryk svarende til mættet vanddamps tryk ved at styre ventilen 16, hvorved mængden af forstøvet vand justeres.As described above, the pressure in the heat exchanger chamber 2 is expected to be equal to the saturation vapor pressure of the system fluid, and the temperature of the heating vapor passed through the pressure reducing valve 1 is expected to be the saturation temperature corresponding to this pressure. However, high pressure steam tends to overheat when the pressure is reduced in a pressure reducing valve and the temperature in the heat exchanger chamber 2 may therefore be higher than expected. To suppress such superheating, as shown in FIG. 2. placing a collecting chamber 14 between the pressure reducing valve 1 and the heat exchanger chamber 2, the bottom of the chamber 5 being connected via a steam trap 15 to the suction chamber of the ejector 4 and the access side of the electrically driven valve 11 connected to a temperature controller 17 by means of a valve 16; which sits on the side wall of the assembly chamber 14. As shown by Tig. 3, the temperature controller 17 comprises a hollow front portion 18 screwed into the sidewall of the assembly chamber 14 and a tubular connection 19 connected thereto, the front portion 18 having a bore 20 which forms an opening into the other portion of the assembly chamber 14, and a rear portion which is connected to the interior of the pipe connection 19 through side openings 21 and a shield 22. By means of this device, drainage water which is collected by the steam trap 15 from the collecting chamber by the ejector device 3 and when the valve 16 is open , water is fed from the saturation temperature by means of the pump 6 to the temperature regulator 17. where it is atomized into the collecting chamber 14 through the bore 20. This reduces the temperature of the superheated steam and the atomized water becomes saturated water vapor. The vapor pressure in the heat exchanger chamber 2 can be kept constant at a pressure corresponding to saturated water vapor pressure by controlling the valve 16, thereby adjusting the amount of atomized water.

20 I fig. 4 ses, at ejektorlndretningen i denne udførelsesform også omfatter en ejektor 4, en tank 5, en pumpe 6, en tilgangsventil 7, et tilgangsrør 8 og en afgangsventil 11. og tanken er forsynet med en temperaturføler 10 og en niveaumåler 13, ligesom I den i fig. 1 viste udførelsesform. I den i fig. 4 viste udførelsesform er der imidlertid anbragt en elektrisk drevet ventil 23 før trykreduktionsventilen 1, og pumpens afgangsside er via en elektrisk drevet ventil 24 forbundet 25 med trykreduktionsventllens 1 afgangsside, nemlig til varmevekslerkammerets 2 tilgang. Motorer eller elektromagneter 25,26 til drift af ventilerne 23 henholdsvis 24 står i forbindelse med en central kontrolenhed 27, som kontrollerer åbningen og lukningen af ventilerne 23 og 24. idet den ene er lukket, når den anden er åben og vice versa. Motorer eller elektromagneter 28,29 til drift af ventilerne 7 henholdsvis 11 står også i forbindelse med den centrale kontrolenhed 27, 30 og ventilerne er beregnet på at reagere på samme måde som i den i fig. 1 viste udførelsesform på basis af signalerne fra temperaturføleren 10 og niveaumåleren 13. Varmevekslerkammeret 2 hari denne udførelsesform, som det fremgår af figuren, U-formet lodret tværsnit, og det bringes i kontakt med et cylindrisk reaktionskammer 30, som har en materialetilgang 31. en produktafgang 32 og en omrører 33. En kondensator 34 er indsat mellem varmevekslerkamme-35 rets 2 afgang og ejektoren 4, og kølevandet til kondensatoren 34 ledes fra tilgangsrøret 8 gennem en elektrisk drevet ventil 35 og ledes efter passage af kondensatoren ud af systemet. En drivmotor eller elektromagnet 36 for denne ventil står også i forbindelse med den centrale kontrolenhed 27.In FIG. 4, the ejector device in this embodiment also comprises an ejector 4, a tank 5, a pump 6, an inlet valve 7, an inlet pipe 8 and an outlet valve 11. and the tank is provided with a temperature sensor 10 and a level meter 13, just as in the in FIG. 1. In the embodiment shown in FIG. 4, however, an electrically driven valve 23 is arranged before the pressure reducing valve 1 and the discharge side of the pump is connected via an electrically driven valve 24 to the outlet side of the pressure reducing valve 1, namely to the approach of the heat exchanger chamber 2. Motors or electromagnets 25, 26 for operating valves 23 and 24, respectively, are connected to a central control unit 27 which controls the opening and closing of valves 23 and 24. one being closed when the other is open and vice versa. Motors or electromagnets 28,29 for operating the valves 7 and 11 are also connected to the central control unit 27, 30 and the valves are intended to react in the same manner as in the one shown in FIG. 1, on the basis of the signals from the temperature sensor 10 and the level meter 13. In this embodiment, as shown in the figure, the heat exchanger chamber 2 has a U-shaped vertical cross-section and is contacted with a cylindrical reaction chamber 30 having a material access 31. product outlet 32 and an agitator 33. A capacitor 34 is inserted between the outlet of the heat exchanger chamber 35 and the ejector 4, and the cooling water of the capacitor 34 is passed from the inlet pipe 8 through an electrically driven valve 35 and is passed out of the system after passage of the capacitor. A drive motor or electromagnet 36 for this valve is also connected to the central control unit 27.

4 DK PR 172565 B1 Når i denne indretning ventilen 24 er lukket, og ventilen 23 er åben, trænger damp fra en dampkilde (ikke vist) ind i varmevekslerkammeret 2 gennem trykreduktionsventilen 1, og efter opvarmning af reaktionskammeret 30, som er i kontakt med varmevekslerkammeret 2, og efter således måske at have fået en ønsket reaktion til at forløbe, som I den i fig. 1 viste udførelses· 5 form, kondenseres dampen I kondensatoren 34 og suges af ejektoren 4 over i tanken 5, hvorved vandtemperaturen heri stiger. Kondensatoren 34 behøver dog ikke anvendes I en sådan varmeoperation, hvilket heller ikke er tilfældet i den i fig. 1 viste udførelsesform.4 EN PR 172565 B1 When in this device valve 24 is closed and valve 23 is open, steam from a steam source (not shown) enters the heat exchanger chamber 2 through the pressure reduction valve 1, and after heating the reaction chamber 30 which is in contact with the heat exchanger chamber 2, and after thus perhaps having caused a desired reaction to proceed, as in the embodiment shown in FIG. 1, the steam in the capacitor 34 is condensed and sucked by the ejector 4 into the tank 5, thereby raising the water temperature therein. However, the capacitor 34 need not be used in such a heating operation, which is not the case in the FIG. 1.

Hvis ventilen 23 så lukkes, og ventilen 24 åbnes, stopper damptilledningen til varmeveksler-10 kammeret 2, og samtidig leder pumpen 6 det varme vand i tanken 5 til varmevekslerkammeret 2. Dette vand og den resterende damp suges af ejektoren 4 retur til tanken 5. Samtidig åbnes tiigangsventilen 7, så tanken 5 igen fyldes op med vand, hvorved temperaturen på vandet i tanken 5 gradvis falder. Medens det vand, som ledes ind i varmevekslerkammeret 2 fordamper på grund af varmen fra reaktionskammeret 30, som derved afkøles på grund af fordamp-15 ningsvarmen, kondenseres en masse damp. som så dannes, I kondensatoren 34, hvorfra det opsuges af ejektoren 4. Kondensatoren 34 tjener altså til at undertrykke overbelastningen af ejektorens 4 sugeoperation. Hvis kølevand ledes ind i varmevekslerkammeret 2 som I indretninger ifølge den kendte teknik, kondenseres den resterende damp heri hurtigt, så der opstår en pludselig trykændring, en såkaldt hammereffekt, som kan fremkalde vibrationer I indretnin-20 gen og ødelæggelse heraf. I indretningen ifølge opfindelsen er der imidlertid ingen hurtig kondensation af den resterende damp, og derfor forekommer der ingen hammereffekt, da temperaturen på vandet i tanken 5 lige efter varmeoperationen er temmelig høj. Temperaturen i varmevekslerkammeret 2 falder gradvis med den faldende vandtemperatur j tanken 5. Hvis man har sat et passende sætpunkt for temperaturen i kontrolenheden 27, styres ejektorens 4 25 negative tryk i overensstemmelse hermed, og afkølingshastigheden styres derved, så man opnår den ønskede afkølingsbehandling.If the valve 23 is then closed and the valve 24 is opened, the steam supply to the heat exchanger-10 chamber 2 stops, and at the same time the pump 6 conducts the hot water in the tank 5 to the heat exchanger chamber 2. This water and the remaining steam are sucked back by the ejector 4 to the tank 5. At the same time, the ten-valve 7 is opened so that the tank 5 is again filled with water, which gradually decreases the temperature of the water in the tank 5. While the water which enters the heat exchanger chamber 2 evaporates due to the heat of the reaction chamber 30, which is thereby cooled by the heat of evaporation, a lot of steam is condensed. which is then formed, in the capacitor 34, from which it is absorbed by the ejector 4. The capacitor 34 thus serves to suppress the overload of the suction operation of the ejector 4. If cooling water is fed into the heat exchanger chamber 2 as in prior art devices, the residual vapor therein is rapidly condensed to produce a sudden pressure change, a so-called hammer effect, which can cause vibration in the device and its destruction. In the device according to the invention, however, there is no rapid condensation of the residual vapor, and therefore no hammering effect occurs, since the temperature of the water in the tank 5 just after the heating operation is rather high. The temperature in the heat exchanger chamber 2 gradually decreases with the decreasing water temperature in the tank 5. If an appropriate set point for the temperature of the control unit 27 is set, the negative pressure of the ejector 4 is controlled accordingly and the cooling rate is thereby controlled to obtain the desired cooling treatment.

Når man efter afkølingsoperationen genoptager varmeoperationen, lukkes først tilgangsventilen 7. Så cirkulerer vandet i tanken 5 gennem pumpen 6, ventilen 24, varmevekslerkammeret 30 2, kondensatoren 34 og ejektoren 4 og absorberer varme fra reaktionskammeret 30, hvorved vandets temperatur gradvis stiger. Når temperaturen er passende, lukkes ventilen 24, og ventilen 23 åbnes samtidig, så der indføres damp. På denne måde kan varmeoperationen genoptages uden den hammereffekt, som skyldes en pludselig temperaturændring.When the heating operation is resumed after the cooling operation, the inlet valve 7. First, the water in the tank 5 is circulated through the pump 6, the valve 24, the heat exchanger chamber 30 2, the capacitor 34 and the ejector 4 and absorbs heat from the reaction chamber 30, thereby gradually increasing the temperature of the water. When the temperature is appropriate, the valve 24 is closed and the valve 23 is simultaneously opened to introduce steam. In this way, the heating operation can be resumed without the hammer effect caused by a sudden change in temperature.

35 Ovennævnte justering af vandtemperaturen og styringen af ventilerne kan lagres på forhånd som et program i kontrolenheden 27, hvorved varme- og køleoperationeme kan automatiseres fuldstændigt.The aforementioned adjustment of the water temperature and the control of the valves can be stored in advance as a program in the control unit 27, whereby the heating and cooling operations can be fully automated.

5 DK PR 172565 B15 DK PR 172565 B1

Varmebehandlingsindretningen ifølge opfindelsen er særligt effektiv, når den anvendes til varmebehandlinger, hvor temperaturen er under 100°C, fx i diverse reaktionskamre og i destillations-, kondensations- og sterilisationsapparatur til fødevarer, og en i disse tilfælde anvendt trykreduktionsventil 1 er vist skematisk i fig. 5. Trykreduktionsventilen 1 har en damptilgang 37 5 og en dampafgang 38 og omfatter et ventilhoved 39 imellem disse. Ventilhovedet 39 er koblet til en trykfølsom membran 41 via en forbindelsesstang 40, og det trækkes opad sammen med membranen 41 ved hjælp af en fjeder 42, hvorved der lukkes for passage af damp; omvendt i forhold til sædvanlige trykreduktionsventiler. Den nedre del af membranen 41 står i forbindelse med afgangssiden via en åbning 43, så det sekundære tryk registreres. Når dette sekundære 10 tryk, nemlig trykket i varmevekslerkammeret 2, falder til et vist niveau, trækkes membranen 41 altså nedad imod fjederens 42 virkning, hvorved ventilhovedet 39 åbner, så der ledes damp til varmevekslerkammeret 2. Når det sekundære tryk er genetableret, trækkes membranen 41 op, så ventilhovedet 39 lukker. Fjederens 42 spænding kan justeres ved hjælp af en styreenhed 44 herfor. Denne styreenhed 44 kan fx omfatte en justeringsmotor, og den kan reagere på 1S et signal fra kontrolenheden 27, der er vist i fig. 4. Når varmebehandlingstemperaturen er over 100'C, anvendes en trykreduktionsventil af sædvanlig opbygning, da i dette tilfælde det sekundære mættede damptryk bliver højere end atmosfæretryk. I dette tilfælde skubbes ventilhovedet 39 ned af fjederen 42 og åbner normalt, medens det er lukket, når det sekundære tryk bliver højere end en forudbestemt værdi.The heat treatment device according to the invention is particularly effective when used for heat treatments where the temperature is below 100 ° C, for example in various reaction chambers and in food distillation, condensation and sterilization apparatus, and a pressure reduction valve 1 used in these cases is shown schematically in FIG. . 5. The pressure reducing valve 1 has a steam inlet 37 5 and a steam outlet 38 and includes a valve head 39 therebetween. The valve head 39 is coupled to a pressure-sensitive membrane 41 via a connecting rod 40 and it is pulled upwardly with the membrane 41 by means of a spring 42, thereby closing off the passage of steam; vice versa compared to usual pressure reduction valves. The lower part of the membrane 41 communicates with the outlet side via an opening 43 so that the secondary pressure is recorded. Thus, when this secondary pressure, that is, the pressure in the heat exchanger chamber 2, drops to a certain level, the diaphragm 41 is pulled downwardly against the action of the spring 42, thereby opening the valve head 39 to supply steam to the heat exchanger chamber 2. When the secondary pressure is restored, the diaphragm is drawn. 41 up so that the valve head 39 closes. The tension of the spring 42 can be adjusted by means of a control unit 44 therefor. This control unit 44 may comprise, for example, an adjustment motor, and it may respond to 1S a signal from the control unit 27 shown in FIG. 4. When the heat treatment temperature is above 100 ° C, a pressure relief valve of conventional design is used, since in this case the secondary saturated vapor pressure becomes higher than atmospheric pressure. In this case, the valve head 39 is pushed down by the spring 42 and normally opens while closed when the secondary pressure becomes higher than a predetermined value.

2020

Varmevekslerkammeret 2 i den i fig. 4 viste udførelsesform lider af den mangel, at kølevandet, når det indføres deri fra ventilen 24 ved den proces, som er beskrevet ovenfor, og som almindeligvis foretages på dampen efter varmeoperationen, ikke kommer ordentligt i kontakt med reaktionskammerets 30 overflade og suges væk af ejektoren 4 før fordampningen, hvilket re-25 suiterer i en lav afkølingseffektivitet. I fig. 6 er vist en særlig konstruktiv detalje, som retter op på denne mangel. Som man ser, er reaktionskammeret 30 omgivet af varmevekslerkammeret med en ydre væg 45. Varmevekslerkammeret 2 bærer et ringformet låg 46. som er fastgjort med bolte 48, idet der er anbragt en ringformet gummiplade 47 mellem kammer og låg.The heat exchanger chamber 2 in the embodiment of FIG. 4, suffers from the lack of cooling water when introduced therein from the valve 24 by the process described above, and which is usually carried out on the steam after the heating operation, does not come into proper contact with the surface of the reaction chamber 30 and is sucked away by the ejector. 4 before evaporation, which recites in a low cooling efficiency. In FIG. 6 is a particularly constructive detail which corrects this defect. As can be seen, the reaction chamber 30 is surrounded by the heat exchanger chamber with an outer wall 45. The heat exchanger chamber 2 carries an annular lid 46. which is secured with bolts 48, with an annular rubber plate 47 arranged between the chamber and the lid.

Gummipladens 47 indre diameter er lidt mindre end reaktionskammerets 30 ydre diameter, og 30 derfor bøjer den indre, periferale del nedad langs reaktionskammerets 30 ydervæg, som vist i fig. 8. Når kølevandet indføres fra ventilen 24 i hulheden over gummipladen 47, som vist skematisk med en pil 49, deformerer det gummipladen 47 på grund af dets tryk, og det flyder ned gennem spalten mellem reaktionskammerets 30 ydervæg og gummipladen 47 langs denne ydervæg, og til slut suges det ud gennem den nedre afgang 50. Det tilledte kølevand fordam-35 pes på denne måde effektivt af varmen fra reaktionskammeret 30, og reaktionskammeret 30 kan køles effektivt af den resulterende fordampningsvarme. Med denne konstruktion kan den opvarmende damp indføres fra trykreduktionsventilen 1 gennem et andet rør, adskilt fra køle- 6 DK PR 172565 B1 vandet, ind under gummipladen 47, som det skematisk er vist med en pil 51. Gummipladen 47 kan fremstilles af andet elastisk materiale end gummi.The inner diameter of the rubber plate 47 is slightly smaller than the outer diameter of the reaction chamber 30, and therefore the inner peripheral portion bends downward along the outer wall of the reaction chamber 30, as shown in FIG. 8. When the cooling water is introduced from the valve 24 into the cavity over the rubber plate 47, as shown schematically by an arrow 49, it deforms the rubber plate 47 due to its pressure and flows down the gap between the outer wall of the reaction chamber 30 and the rubber plate 47 along this outer wall, and finally, it is sucked out through the lower outlet 50. The entrained cooling water is thus effectively evaporated by the heat from the reaction chamber 30 and the reaction chamber 30 can be effectively cooled by the resulting evaporation heat. With this construction, the heating steam can be introduced from the pressure reducing valve 1 through another pipe, separated from the cooling water, under the rubber plate 47, as shown schematically by an arrow 51. The rubber plate 47 can be made of other elastic material than rubber.

Ved opfindelsen tilvejebringes der altså en forbedret varmebehandlingsindretning til damp af 5 reduceret tryk, hvilken indretning har en høj stabilitet og en høj termisk virkningsgrad. De beskrevne udførelsesformer illustrerer kun opfindelsen og må ikke begrænse denne, da man kan foretage diverse modifikationer og ændringer heraf, uden at opfindelsens idé og formål, som det fremgår af kravene, ændres. Fx kan varmevekslerkammerets 2 struktur og form frit ændres. selv om der i beskrivelsen af udførelsesformeme omtales et U-formet tværsnit af varme-10 vekslerkammeret 2, der omgiver reaktionskammeret 30, og om nødvendigt kan materialet, som skal behandles, indføres direkte i varmevekslerkammeret 2. Ligeledes står det en frit for at styre en eller flere af ventilerne manuelt, skønt det af fig. 4 fremgår, at alle ventiler styres automatisk. Hvis trykreduktionsventilen 1 i fig. 4 bringes til at kunne lukke fuldstændigt, kan den foregående ventil 23 fjernes. Desuden kan andre komponenter end trykreduktionsventilen, 15 varmevekslerkammeret og ejektorindretningen eventuelt fjernes i overensstemmelse med anvendelsen og driftsbetingelserne for indretningen ifølge opfindelsen.Thus, the invention provides an improved steam pressure heat treatment device of 5 which has a high stability and a high thermal efficiency. The embodiments described illustrate the invention only and are not intended to limit it, since various modifications and modifications thereof may be made without changing the idea and purpose of the invention as set forth in the claims. For example, the structure and shape of the heat exchanger chamber 2 can be freely changed. although in the description of the embodiments, a U-shaped cross section of the heat exchanger chamber 2 surrounding the reaction chamber 30 is mentioned and, if necessary, the material to be treated can be introduced directly into the heat exchanger chamber 2. It is also free to control a or more of the valves manually, although in FIG. 4 shows that all valves are controlled automatically. If the pressure reducing valve 1 in FIG. 4 can be completely closed, the previous valve 23 can be removed. In addition, components other than the pressure reducing valve, the heat exchanger chamber and the ejector device may optionally be removed in accordance with the use and operating conditions of the device according to the invention.

Claims

A heat treating device for use of reduced pressure steam and comprising a pressure reducing valve (1) having an inlet connected to a steam source and an outlet, a heat exchanger chamber (2) having an inlet connected to the outlet of the pressure reducing valve ( 1) and a pressure reducing device (3). connected to the outlet of the heat exchanger chamber (2). characterized in that the pressure reducing device comprises an ejector (4) having a suction chamber connected to the outlet of the heat exchanger chamber, a device (5,6) for directing operating fluid to the ejector and devices (9,10) for controlling the temperature 10 at this operating fluid, whereby a control of the ejector suction pressure becomes possible by controlling said temperature.

Device according to claim 1, characterized in that it further comprises a device for introducing the operating fluid into the heat exchanger chamber's approach and means (23, 24) for switching 15 between supply of steam and operating fluid to the heat exchanger chamber (2).

Device according to claim 1 or 2, characterized in that the device for directing the operating fluid to the ejector comprises a liquid storage tank (5), a pump device (6) for forcing the operating liquid from the storage tank into a jet nozzle in the ejector (4), devices for returning the operating fluid from the ejector to the storage tank and devices (7,8) to replenish the storage tank with operating fluid of relatively low temperature.

Device according to claim 3, characterized in that the devices for controlling the temperature of the operating fluid comprise a temperature sensor (10) for measuring the temperature of the operating fluid and for providing a measuring signal and a venial control unit (9) responding to the measuring signal, and a control valve (7) responsive to this measurement signal for controlling the amount of additive to the operating fluid.

Device according to claim 3, characterized in that it further comprises a device 30 (13) for measuring the level of the liquid storage leach (5) and for providing a measuring signal and a device (11) capable of responding to this measuring signal and emptying. operating fluid out of the system.

Device according to claim 1, characterized in that it further comprises a device (14,17) for saturating superheated steam, which is inserted between the pressure reducing valve (1) and the heat exchanger chamber (2) and comprises a tightly closed cavity. and a means (17) for atomizing operating fluid into the cavity. DK PR 172565 B1

Device according to claims 2-5, characterized in that it comprises a capacitor (34) in the piping between the heat exchanger chamber (2) and the ejector (4).

Device according to claim 2,3,4,5 or 7. characterized in that the heat exchanger chamber 5 (2) has a U-shaped cross section and surrounds a cylindrical reaction chamber (30), has an inner cavity which is divided by an annular dividing plate ( 47) in an upper cavity having a relatively small volume and a lower cavity having a relatively large volume, said dividing plate (47) consisting of an elastic material having an inner diameter smaller than the outer diameter of the reaction chamber (30), such that the inner peripheral portion of this dividing plate bends down the outer wall of the reaction chamber, and the upper cavity has an operating fluid (49) and the lower cavity has a steam (51) and a discharge (50) ) for both steam and liquid.