EP3073216B1 - Déshumidificateur d'air destiné à déshumidifier l'air pour le séchage du foin - Google Patents

Déshumidificateur d'air destiné à déshumidifier l'air pour le séchage du foin Download PDF

Info

Publication number
EP3073216B1
EP3073216B1 EP16163301.1A EP16163301A EP3073216B1 EP 3073216 B1 EP3073216 B1 EP 3073216B1 EP 16163301 A EP16163301 A EP 16163301A EP 3073216 B1 EP3073216 B1 EP 3073216B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
air
tubes
pipe
evaporator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16163301.1A
Other languages
German (de)
English (en)
Other versions
EP3073216A1 (fr
Inventor
Josef Reindl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Heutrocknung Sr GmbH
Original Assignee
Heutrocknung Sr GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Heutrocknung Sr GmbH filed Critical Heutrocknung Sr GmbH
Publication of EP3073216A1 publication Critical patent/EP3073216A1/fr
Application granted granted Critical
Publication of EP3073216B1 publication Critical patent/EP3073216B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B21/00—Arrangements or duct systems, e.g. in combination with pallet boxes, for supplying and controlling air or gases for drying solid materials or objects
    • F26B21/02—Circulating air or gases in closed cycles, e.g. wholly within the drying enclosure
    • F26B21/04—Circulating air or gases in closed cycles, e.g. wholly within the drying enclosure partly outside the drying enclosure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B21/00—Arrangements or duct systems, e.g. in combination with pallet boxes, for supplying and controlling air or gases for drying solid materials or objects
    • F26B21/06—Controlling, e.g. regulating, parameters of gas supply
    • F26B21/08—Humidity
    • F26B21/086—Humidity by condensing the moisture in the drying medium, which may be recycled, e.g. using a heat pump cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/1405—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit

Definitions

  • the present invention relates to a dehumidifier for dehumidifying air for drying hay, the dehumidifier comprising an evaporator and a condenser, wherein the condenser is arranged in a flow direction behind the evaporator and wherein the evaporator and the condenser to be dehumidified air in the flow direction can be flowed through.
  • the air used for drying can be heated. It is essential, however, that a sufficiently large amount of dehumidified air can be blown into the ventilation box or through the hay.
  • known dehumidifiers limit the air flow essential or offer at high air flow only unsatisfactory dehumidification.
  • a pressurized gas dryer with a container enclosing a part of a group of heat exchangers with a heat recovery device and an evaporator.
  • the dryer has a condensate drainage system, with a sensor provided to detect the level of condensate in the tank.
  • the evaporator is a gas-refrigerant heat exchanger with a refrigerant circuit.
  • the heat recovery device is a gas-gas heat exchanger having a pre-cooling section and a heating section, that is, the heat recovery device is not part of the coolant circuit. High flow velocities of the air are not treated.
  • a dehumidifier in connection with the drying of drying material is known, which has, inter alia, an evaporator and seen in the flow direction thereafter arranged condenser, wherein the flow direction extends from bottom to top.
  • the condenser has tubes which are arranged transversely to the flow direction and one above the other, wherein the tubes are subdivided into two superimposed packets.
  • the invention relates to a dehumidifier for dehumidifying air for drying hay according to claim 1 and a use of an air dehumidifier according to any one of claims 1 to 5 for drying food or hay.
  • a dehumidifier for dehumidifying sucked air has an evaporator in which refrigerant is vaporized by the heat of the sucked air flowing through the evaporator in a flow direction.
  • the sucked air is cooled below the dew point, and it comes to a condensation of water on the cold Surface of the evaporator.
  • the water trickles or drips in the sequence from the evaporator.
  • a drip tray is placed under the evaporator.
  • the dehumidifier has a condenser, which, viewed in the flow direction, is arranged behind the evaporator.
  • the flow velocity of the air must be increased while the flow cross-section of the dehumidifier or the evaporator remains the same.
  • this leads to the dripping water is increasingly transported by the air flowing through the dehumidifier in the flow direction. Accordingly, the dripping water no longer lands in the drip tray.
  • the shipment can even go so far that the water is blown up to the condenser, which acts as a barrier, and drips from there.
  • the water that does not drip into the drip tray can obviously cause great problems, especially if there is a risk that the water can subsequently reach electrical circuits.
  • a dehumidifier for dehumidifying air for drying hay comprising an evaporator and a condenser, wherein the condenser is arranged in a flow direction behind the evaporator and wherein the evaporator is to be dehumidified air in the flow direction
  • a drip tray is provided, over which both the evaporator and the capacitor are arranged.
  • the refrigerant condenses in the condenser, releasing latent heat. This can be used to warm the dehumidified air.
  • the condenser can also be flowed through by the dehumidified air. In this way, the dehumidified air can be warmed, which also contributes to a faster drying of the drying material.
  • the drip tray has a Staurau that divides the drip tray into a first collection section and a second collection section, wherein above the first collection section of the evaporator is arranged.
  • the water contained in the first collection section which makes up the majority of the drained water, is thus driven by the air flowing against the railing bar and can no longer spread over the entire drip tray.
  • water drops are still landing in the second collection area.
  • their amount in practice is not large enough to form a closed layer of water over the entire second collection area. An unwanted moistening of the air immediately after its dehumidification can thus be effectively prevented.
  • a drain opening of the drip tray is arranged between the first collecting portion and the second collecting portion.
  • either the entire drainage trough can be correspondingly inclined or the second collecting section can be designed with a corresponding inclination. Due to the air flow, the water located in the first collection section is in any case driven in the direction of the outflow opening.
  • the drain opening interrupts the dust bar.
  • the discharge opening can be arranged centrally in the longitudinal direction of the storage bar, which favors a particularly uniform drainage of the collected water.
  • the arrangement of the batten bar, the evaporator and the condenser is relative crucial to each other, as determined in experiments. Therefore, it is provided in a preferred embodiment of the dehumidifier according to the invention that the evaporator and the condenser have a distance from each other which is at least three times, preferably at least five times as large as a distance between the evaporator and the Staurau, the distances measured in the flow direction are.
  • the absolute air throughputs and / or flow velocities to be achieved must be taken into account.
  • m B 2 For the air throughputs of 200 m 3 / h per square meter of box area, m B 2 , to 600 m 3 / h / m B 2 , preferably 400 m 3 / h / m B 2 , which are usually to be achieved when drying hay, have become common in experiments
  • Distance between the evaporator and condenser of at least 50 cm and / or a distance between the evaporator and Stauolin of 7 cm to 15 cm, preferably 10 cm proved to be particularly favorable.
  • the term "box area” should be understood to mean the area of the ventilation box that can be flowed through, in which the hay is arranged for drying, the hay being arranged on the box area.
  • the hay is substantially loose in the aeration box, ie, especially not in the form of round bales.
  • the inflatable box area is limited to the area on which the round bale rests or rest. This can preferably be realized in such a way that in each case a round bale to be dried is arranged above an opening in an initial region of the ventilation box, wherein the air used for drying is blown through the opening into the ventilation box or directly onto the respective round bale.
  • the opening can be designed as a circular hole and is adapted to the diameter of the round bale, ie the diameter of the opening corresponds to Essentially the diameter of the round bale and is therefore for example between 1.2 m and 2 m. So that the round bale does not fall into the opening, the opening can be covered, for example, with a grid. Accordingly, in this case, air flow rates of 850 m 3 / h to 2000 m 3 / h per opening or per round bale arise.
  • the distance between the evaporator and condenser is at least 50 cm.
  • the said distance between evaporator and condenser also proves to be particularly advantageous insofar as it is sufficiently large to comfortably arrange an additional heat source between evaporator and condenser.
  • the additional heat source With the additional heat source, the dehumidified air can be additionally warmed in order to further promote or accelerate the drying process. Therefore, in a preferred embodiment of the dehumidifier according to the invention, provision is made for a heat source to be arranged between the evaporator and the condenser in order to additionally heat the air which has passed through the evaporator.
  • the dehumidifier includes a compressor to compress the refrigerant evaporated in the evaporator. Since the compressor emits heat in this case, so the compressor is suitable as an additional heat source, which can also be conveniently accommodated between evaporator and condenser, without the flow of air from the evaporator to the condenser substantially affect. Therefore, it is provided in a preferred embodiment of the dehumidifier according to the invention that the dehumidifier comprises a compressor which at least partially, preferably completely forms the heat source.
  • a bypass line and a changeover valve are provided to refrigerant, which has been heated in the evaporator and converted into the gaseous state, at least partially back to the evaporator - and not directly to the capacitor - supply.
  • the switching valve is arranged after the compressor and preferably operates automatically, for example as a thermostat-controlled solenoid valve.
  • hot gaseous refrigerant which has been converted in the evaporator in the gaseous state, is returned from the compressor to the evaporator via the bypass line, excessive cooling of the evaporator and thus ice formation on the evaporator is prevented. If ice formation has already started at the evaporator, defrosting of the evaporator by means of the hot gaseous refrigerant is made possible by the bypass line.
  • the switching valve switches back, and the hot gaseous refrigerant is again fed directly from the compressor to the condenser.
  • the bypass line and the switching valve allow the compressor can be operated with very high power, so that a high performance of the dehumidifier is made possible and at the same time the compressor can be used as a particularly good heat source for heating the dried air without the evaporator iced.
  • the evaporator consists of lamellae, in which the coolant is guided, or the coolant is guided in pipes, between which the lamellae are arranged and with which the lamellae are thermally conductively connected (eg by soldering or by a mechanical pressing or pressing on the tubes are widened) to increase the performance of the evaporator.
  • the lamellae have a lamellar spacing in a direction normal to the direction of flow, which allows the air to be dehumidified to flow through the evaporator or between the lamellae. Experiments have shown that the lamellar spacing can be adapted to the air flow rates usually achieved when drying hay in order to allow a further increase or optimization of the air dehumidification performance.
  • the evaporator has lamellae, which are spaced from one another in a direction normal to the flow direction with a fin spacing of 1.5 mm to 2 mm, preferably of 1.8 mm.
  • the lamellae have a non-stick coating in order to promote a drainage of condensed water from the lamellae.
  • this is a variety of known non-stick coatings that allow faster drainage, such as Teflon or paints.
  • a non-stick coating is advantageous if the blades are made of aluminum.
  • Aluminum basically forms on its surface an oxide layer, which brings a certain roughness and thus a large surface with it. This, in turn, causes the water to adhere more strongly to the lamellae via capillary action.
  • the coating of the lamellae with a non-stick coating causes a reduction in the roughness of the lamellar surface and thus a reduction in capillary action, so that the water can drain better.
  • a grid is arranged whose mesh size is smaller than that Slat spacing is. This is particularly important in the mentioned, relatively small fin spacing, since this relatively small fin spacing can be relatively easily clogged by dirt / dust / insects or the like, which in turn would have a negative effect on the air flow.
  • the refrigerant in the evaporator is passed through tubes which are connected in a heat-conducting manner with the lamellae.
  • the evaporator at least one row of tubes, preferably several Tube rows, particularly preferably four rows of tubes, that the at least one row of tubes comprises a plurality of tubes for refrigerants, wherein the tubes are arranged transversely to the flow direction and one above the other, and that the tubes are divided into a plurality of superimposed packets, each package has its own Distributor head is provided, via which the respective package refrigerant can be supplied. This ensures that the refrigerant is evenly distributed over the tubes of at least one row of tubes. Or. the refrigerant is evenly distributed to the tubes of the first row of tubes seen in a refrigerant flow direction, and thus evenly to the tubes of each subsequent tube row.
  • the even distribution on the tubes of one row of tubes, especially on all tubes, of one row of tubes ensures that the refrigerant in the entire tube row has essentially the same temperature. This ensures that there is a condensation of air moisture in the air flowing evenly across the surface of the row of tubes. In particular, it is thereby avoided that pipes arranged further down in the row of pipes are substantially warmer than pipes arranged above them. If this were the case, there would be a risk that condensed water on the upper tubes or fins drips on warmer underlying tubes or fins or run and evaporated there due to the higher temperature, so that the humidity of the air flowing through again increases.
  • the use of multiple distribution heads has the further advantage that the individual distribution heads can be made relatively small. Due to the number of pipes to be fed with refrigerant piping a single distributor head would have a very large diameter need. The arrangement of supply lines from the distributor head to the tubes of the tube row would be correspondingly complicated. In contrast, the arrangement of the leads of multiple headers designed easier because much fewer leads are to provide per header, as would be the case with a single large distribution head.
  • the plurality of distribution heads in turn, depending on the size of the dehumidifier can be supplied via a line with its own expansion valve with refrigerant or via a line with an expansion valve, as seen in the refrigerant flow direction after the expansion valve is divided into the plurality of distribution heads.
  • the latter is particularly suitable for smaller dehumidifiers, wherein the distribution to the plurality of distribution heads, e.g. can be done with a T or U-shaped piece of pipe.
  • the use of multiple expansion valves is advantageous.
  • the provision of several, preferably four rows of tubes has the advantage that the air to be dried must pass through all the rows of tubes one after the other. Although, when passing through the first row of tubes seen in the direction of flow, cooling of the air does occur but not yet condensation of the moisture, there are still one or more rows of tubes available where the condensation can take place. In other words, the probability that the dew point falls below this level is dramatically increased or practically ensured by the provision of several rows of pipes.
  • the rows of tubes are preferably arranged such that the first row of tubes, viewed in the direction of refrigerant flow, is the one which, as seen in the direction of flow, is the last to be flowed through by the air to be dried. Conversely, the last row of pipes, as seen in the direction of flow of the refrigerant flow, is the one which, as seen in the flow direction, flows through the air to be dried first.
  • This arrangement has the advantage that the temperature of the rows of tubes decreases in the direction of flow, since the first row of tubes seen in the direction of refrigerant flow is the coldest row of tubes.
  • the probability of the dew point falling below the dew point in a row of tubes following in the flow direction is increased by the arrangement of the rows of tubes.
  • the moisture of the air to be dried will condense on all rows of tubes, providing a maximum dehumidifying effect.
  • Each tube of the last row of tubes discharges into a collecting tube, via which the refrigerant is subsequently removed in the direction of the condenser.
  • a separate collecting pipe is provided for each package, via which refrigerant can be discharged from the respective package. On the one hand, this allows the refrigerant to be very quickly derived from the evaporator.
  • each of these packages is supplied via its own manifold refrigerant. It can then be provided for each of these manifolds a corresponding manifold, which ensures a particularly effective supply of the refrigerant to the condenser.
  • the condenser comprises at least one row of tubes, preferably several rows of tubes, more preferably four rows of tubes, that the at least one row of tubes comprises a plurality of tubes for refrigerant, wherein the tubes transverse to the flow direction and one above the other are arranged, and that the tubes are divided into a plurality of superimposed packages, wherein for each package a separate manifold is provided, through which the respective package refrigerant can be supplied.
  • each manifold connects to its own feed section for feeding the respective manifold with refrigerant, wherein the respective feed section opens in the region of one of the bottom three tubes of the respective package in the respective manifold.
  • the compressor of the dehumidifier has an oil lubrication. Due to the design, a part of this oil of the compressor passes into the refrigerant circuit and is carried there by the refrigerant.
  • hose-like or tubular connection means come into consideration as connecting means, eg substantially U-shaped connecting pipe bends.
  • the tubes of the tube lines are usually even horizontally, with a slightly inclined, in the direction of coolant flow from the top to inclined downward arrangement would be conceivable. Overall, this results in that the condenser and / or the evaporator have a predominantly falling arrangement of the rows of tubes or rows of tubes.
  • the oil in the refrigerant circuit is led away from the compressor to the manifolds of the condenser, the oil flows due to gravity - and to some extent also due to the prevailing pressure in the tubes - virtually lossless through the tubes of the rows of tubes of the capacitor or through the pipe lines of the condenser into a manifold of the condenser.
  • the pressure in the coolant lines is conveyed by the pressure in the coolant lines to the expansion valve or to the expansion valves and pressed through the distribution heads of the evaporator and supply lines in the tubes of the rows of tubes or pipe lines.
  • the falling arrangement of the rows of tubes or rows of pipes causes no or only a negligible siphon or no or only a negligible low point in the pipe guide or in the pipe lines is formed, where the oil can remain. That
  • the oil like the refrigerant, can flow substantially continuously through the tube lines of the evaporator, from the supply lines to the collector pipe or to the collector pipes. About the manifold or the manifolds of the evaporator, the oil is transported back into the compressor.
  • the arrangement of the rows of tubes and in particular the arrangement of the connecting elements of the tubes of the rows of tubes or the pipe lines formed in this way are also of great importance, since the refrigerant partially circulates in the gaseous state in the refrigerant circuit and the gaseous refrigerant takes the liquid oil only bad.
  • the inventive design of the pipe lines with appropriately trained and arranged fasteners this problem is solved, since the oil substantially in each row of pipes by gravity from a row of pipes for Next down and there are no or only negligible places where the oil must be pushed up. Losses of oil in the pipe lines can thus be virtually completely avoided.
  • At least one distributor tube of the condenser is preferably provided with a downward bulge, particularly preferably all distributor tubes of the condenser.
  • the bulge is arranged in the region of the confluence of the respective feed section and extends downwardly - deeper than the feed section or as its confluence with the respective distributor tube.
  • the bulge, in conjunction with a relatively small diameter of the respective manifold ensures that a particularly good mixing of refrigerant and oil in the region of the mouth of the feed section takes place in the respective manifold. Due to this good mixing of refrigerant and oil, the oil is carried better in the refrigerant circuit. Oil losses or the stagnation of oil are thus minimized.
  • the oil separator would have the function of filtering the oil after the compressor from the refrigerant and returning it to the compressor.
  • dehumidifiers would be conceivable, although not drip tray according to the invention with Stauil, but may have evaporators and / or capacitors with the described rows of tubes.
  • the dehumidifier comprising an evaporator and a condenser, wherein the condenser in a Seen through the direction of flow behind the evaporator is arranged and wherein the evaporator to be dehumidified air in the flow direction
  • the evaporator at least one row of tubes, preferably several rows of tubes, more preferably four rows of tubes, that the at least one row of tubes a plurality of tubes for refrigerants, wherein the tubes are arranged transversely to the flow direction and one above the other, and that the tubes are divided into a plurality of superimposed packages, wherein for each package a separate distributor head is provided, via which the respective package refrig
  • the dehumidifier for dehumidifying air for drying hay
  • the dehumidifier comprising an evaporator and a condenser, wherein the condenser is arranged in a flow direction behind the evaporator and wherein the evaporator to be dehumidified by air to be dehumidified in the flow direction
  • the condenser at least one row of tubes, preferably a plurality of rows of tubes, more preferably four rows of tubes, that the at least one row of tubes comprises a plurality of tubes for refrigerants, wherein the tubes are arranged transversely to the flow direction and one above the other, and that the tubes are divided into a plurality of stacked packages, each package having its own distribution pipe is provided, via which the respective package refrigerant can be supplied.
  • each distributor pipe connects to its own feed section for feeding the respective distributor pipe with refrigerant, wherein the Feeding section in the region of one of the bottom
  • each tube of a row of tubes is connected to a tube of at least one other row of tubes via at least one connecting element for the refrigerant to form one row of tubes, wherein at least 80%, preferably at least 90%, more preferably at least 95% of all pipe lines, the connecting elements are formed and / or arranged so that the refrigerant in these connecting elements can flow continuously from top to bottom.
  • the dehumidifier according to the invention can be achieved not only when drying hay but also when drying food, or the use of the dehumidifier according to the invention also has a positive effect on the achievable air flow rates and drying capacities in these cases ,
  • the aroma of the food can be maximally obtained by the rapid drying achievable by means of the dehumidifier according to the invention.
  • the invention provides the use of an inventive dehumidifier for dehumidifying air for drying food.
  • an inventive dehumidifier for drying hops provided.
  • the achievable, rapid drying also allows in the case of hops maximum preservation of the aroma.
  • Fig. 1 is a schematic plan view of a dehumidifier 5 according to the invention shown, for the dehumidification of air in the drying of Trocknungsgut, in particular of hay 1 (see FIG. Fig. 4 ), can be used.
  • the dehumidifier 5 comprises an evaporator 11 in which refrigerant (not shown) by the heat of air, in a flow direction 22 through the evaporator 11 and between fins 27 (see. Fig. 2 ) of the evaporator 11 passes through, is evaporated.
  • the air is cooled below the dew point, and there is a condensation of water on the cold surface of the evaporator 11.
  • the water trickles or drips in the sequence of the evaporator 11 in a drip tray 18 from.
  • the air flowing through is thereby dehumidified and can subsequently be used to dry the material to be dried or the hay 1.
  • the gaseous refrigerant passes via a coolant line 32 (arrowheads indicate the direction of flow) from the evaporator 11 in a compressor 13 of the dehumidifier 5, where it is further compressed. Subsequently, the hot gaseous coolant is passed from the compressor 13 via a further coolant line 32 in a condenser 12 of the dehumidifier 5, which is arranged behind the evaporator 11 seen in the flow direction 22. In the condenser 12, the refrigerant condenses and releases latent heat. This can be used to heat the dehumidified air by also the condenser 12 can be traversed by the air, which also contributes to a faster drying of the drying material. Finally, the liquid refrigerant is supplied via a further coolant line 32 from the condenser 12 back to the evaporator 11, where the cycle begins again.
  • the dehumidifier 5 In order to prevent icing of the evaporator 11, which is e.g. could occur at low ambient temperatures and high relative humidity, and / or to be able to defrost the evaporator 11 if necessary, the dehumidifier 5 according to the invention also has a bypass line 31 and a switching valve 30.
  • a switching valve 30 To heat the evaporator 11 and possibly defrost, 30 hot gaseous refrigerant from the compressor 13 instead of directly into the condenser 12 back into the evaporator 11 can be passed by means of the switching valve.
  • the switching valve 30 switches again, and the refrigerant is again supplied directly from the compressor 13 to the condenser 12.
  • the switching of the switching valve 30 can be automated, for example, by the switching valve 30 is designed as thermostat-controlled solenoid valve.
  • the flow rate of the air must be correspondingly high.
  • the drip tray 18 is designed so that both evaporator 11 and capacitor 12 can be arranged above the drip tray 18.
  • a storage bar 19 is provided. This divides the drip tray 18 into a first collecting section 25 and a second collecting section 26, wherein the evaporator 11 is disposed above the first collecting section 25. That in the first Collection section 25 collecting water can be driven by the air flowing through only to the bar 19, whereby the formation of a large-scale water layer is prevented. This ensures that the already dehumidified air on its way from the evaporator 11 to the capacitor 12 can not absorb moisture again.
  • a drain opening 20 is provided in the drip tray 18.
  • the drainage port 20 is arranged to interrupt the railing bar 19 so that water can flow out of both the first header section 25 and the second header section 26.
  • the jam bar 19 is interrupted by the discharge opening 20 in the middle, which favors a particularly uniform churning of the collected water.
  • the longitudinal direction 29 is substantially normal to the flow direction 22.
  • the Stauring 19 is conceivable, the oblique-angled configurations of the longitudinal direction 29 to the flow direction 22 result.
  • the arrangement of the Staurau 19 relative to the position of the evaporator 11 and the condenser 12 is selected so that in the first collection section 25, the bulk of the dripping water is collected.
  • a distance 23 between evaporator 11 and condenser 12 is at least 50 cm and a distance 24 between evaporator 11 and stowage bar 19 is 7 cm to 15 cm, preferably 10 cm, wherein the distances 23, 24 are measured in the direction of flow 22.
  • These distances 23, 24 are in the schematic side view of Fig. 3 particularly clearly recognizable, wherein the representation of coolant lines 32, the bypass line 30th and the switching valve 31 has been omitted for the sake of clarity.
  • the dehumidifying performance of the dehumidifier 5 can be further increased by optimizing the distance of the fins 27 of the evaporator 11 in view of the air flow to be handled.
  • Fig. 2 shows an enlarged view of the evaporator 11, in which the fins 27 are clearly visible. These are mutually spaced in a direction normal to the flow direction 22 with a fin spacing 28 of 1.5 mm to 2 mm, preferably of 1.8 mm, which is shown in experiments to be optimal for the to be handled in the drying of hay 1 air flow rates Has.
  • the surface of the fins 27 is also provided with a non-stick coating (not shown) to allow rapid draining of the condensed on the fins 27 water.
  • a fly screen 21 is provided.
  • the fly screen 21 is arranged in the flow direction 22 before the evaporator 11 and has a mesh size which is smaller than the fin spacing 28.
  • FIG. 1 shows a schematic representation of a use of the dehumidifier 5 for dehumidifying air during the drying of hay 1.
  • the hay 1 is arranged in a ventilation box 2 between an initial region 15 and an end region 16.
  • the ventilation box 2 is roofed with a roof 3, so that the hay 1 is protected from the weather.
  • the hay 1 rests on a box surface 33.
  • the box surface 33 can be flowed in with air by the box surface 33 being realized, for example, by a reinforcing steel grid, which rests on grate carriers (not shown) and is arranged above a base 34 at a certain distance, for example 40 cm.
  • an air channel 17 is formed in the initial region 15, through which air can be blown onto the box surface 33 or into the ventilation box 2.
  • the in Fig. 4 shown device for hay drying a fan 4, wherein the arrows in Fig. 4 symbolize possible air flows.
  • the air to be injected into the ventilation box 2 is first sucked in by means of the fan 4, wherein preferably the entire sucked-in air is sucked through the dehumidifier 5, in which dehumidifier 5 the air is dehumidified.
  • the air flow rate can be influenced by a control of the fan 4, ie the amount of air sucked in and thus the amount of air blown into the ventilation box 2 can be regulated.
  • air flow rates or amounts of intake air of 200 m 3 / h per square meter of pit area 22, m B 2 , to 600 m 3 / h / m B 2 , preferably 400 m 3 / h / m B 2 are set to a rapid drying of the hay 1 to allow.
  • the density of hay 1 can vary - typically between 100 kg / m 3 to 250 kg / m 3 -, whereby a different resistance for the blown into the aeration box 2 air is accompanied. Accordingly, the power or the rotational speed of the fan 4 must be controllable, frequency converters being provided for this purpose (not shown). Frequency converters are also preferably used to control the power of the dehumidifier 5 or the compressor 13 of the dehumidifier 5.
  • the compressor 13 can be operated by means of frequency typically with up to 50% more power than usual. This makes it possible, on the one hand to achieve a high drying performance of the dehumidifier 5, on the other hand, the associated increased waste heat of the compressor 13 can be used specifically for heating the dried air, which is blown into the ventilation box 2. Additional means for warming the air can therefore typically be completely eliminated, and yet an internal temperature inside the ventilation box 2 can be increased and thus the hay drying performance can be increased.
  • the bypass line 30 and the changeover valve 31 have a positive effect, in particular in this operation of the high-power compressor 13, or allow this operation only since, despite the high performance of the compressor 13, icing of the evaporator 11 is prevented.
  • a change-over flap 6 is provided, which is arranged in the end region 16 and can be moved back and forth by means of an electric cylinder 10 between a first position 7 and a second position 8.
  • first position 7 causes the changeover 6, that air can be sucked only from the ventilation box 2. This air is subsequently fed to the dehumidifier 5 and blown back into the ventilation box 2. This means that in this case there is a closed air circulation in the device for hay drying.
  • the air is preferably sucked completely from the outside or from outside the ventilation box 2.
  • this is an air duct 9 formed under the roof 3.
  • a heat transfer between this air and the roof 3 is favored. If the roof 3 is warm due to the sunlight, in this way the air drawn in from outside - ultimately by solar energy - can be warmed up.
  • the switching flap 6 thus makes it possible to use air which can be sucked in from the outside in a targeted manner in order to contribute to achieving a desired temperature of the air in the ventilation box 2 or in its starting area 15 and / or end area 16, ie to achieve a desired internal temperature.
  • a control unit 14 is provided, which is preferably designed as a programmable logic controller.
  • the control unit 14 processes signals or data from sensors (not shown) on the air temperature and relative humidity in the ventilation box 2 and outside the ventilation box 2.
  • the execution of the control unit 14 as a programmable logic controller also allows the current amount of to be dried hay 1 to be considered and thresholds for the indoor temperature, the temperature outside the aeration box 2, the humidity and the air flow rate to specify or adapt. Based on these data or information, the control unit 14 controls the change-over flap 6 or the electric cylinder 10 and regulates the power of the fan 4 and of the ventilator 5 or of the compressor 13.
  • FIG. 2 shows a schematic side view of evaporator 11 and condenser 12 of a variant embodiment of the dehumidifier 5 according to the invention.
  • the evaporator 11 has tubes 42 for the coolant, which extend transversely to the flow direction 22.
  • the tubes 42 form four tube rows 43a, 43b, 43c, 43d extending from top to bottom, cf. also Fig. 6 ,
  • the tubes 42 are divided into two stacked packages 50, wherein for each package 50 a separate header 40 is provided, through which the respective package 50 refrigerant is supplied.
  • the tubes 42 of the first tube row 43a which are seen in a refrigerant flow direction 48, are supplied with refrigerant via the two distributor heads 40.
  • the refrigerant in turn is the distributor heads 40 via an expansion valve 35, a manifold 38 and a subsequent to the manifold 38 U-tube 39 is supplied.
  • the subdivision into packets 50, to which refrigerant is supplied separately, or the two distributor heads 40 allow a uniform supply of the refrigerant to the tubes 42 of the first tube row 43a, so that the tubes 42 of the first tube row 43a and with these tubes thermally conductively connected blades (in Fig. 5 not shown) on the surface substantially all the same temperature.
  • feed lines 41 with all tubes 42 of the first row of tubes 43a in a package 50, ie with all tubes 42 in the upper half of the first row of tubes 43a, and the other header 40 is with all tubes 42 of the first row of tubes 43a in the other package 50, ie with all the tubes 42 in the lower half of the first row of tubes 43a.
  • a feed line 41 is provided for each tube 42 of the first tube row 43a (for reasons of clarity, FIGS Fig. 5 not all leads 41 are shown).
  • the refrigerant flows in each line 52 of a pipe 41 in a manifold 36: first from the distributor head 40 via the feed line 41 in a tube 42 of the first row of tubes 43a, then into a tube 42 of the second row of tubes 43b, then into a tube 42 of the third row of tubes 43c, then into a tube 42 of the fourth row of tubes 43d and finally into the collecting tube 36, which discharges the refrigerant in the direction of the compressor 13 and subsequently in the direction of the condenser 12.
  • the connecting pipe bends 47a, 47b are formed and arranged so that the refrigerant in the connecting pipe bends 47a, 47b in the refrigerant flow direction 48 continuously from top to bottom flowing down.
  • the tubes 42 of the tube lines 52 are usually arranged horizontally, but would also be conceivable a slightly inclined arrangement, preferably in the direction of refrigerant flow 48 from top to bottom.
  • the falling arrangement of the tube lines 52 causes the refrigerant - from the entry into the respective tube 42 of the first row of tubes 43a to the exit from the respective tube 42 of the fourth row of tubes 43d into the collecting tube 36 - flow through these tube lines 52 basically alone due to gravity can.
  • a pressure in the pipes 42 promotes the flow of the refrigerant in the refrigerant flow direction 48 and ensures that the refrigerant flows without any problem through those pipe lines 52 having connecting pipe bends 47 a, 47 b, through which the refrigerant is not continuously in the refrigerant flow direction 48 from top to bottom can flow.
  • the falling arrangement of the pipe lines 52 is of great advantage, as well as oil, which is used for lubrication of the compressor 13, inevitably passes into the coolant circuit due to the design.
  • This oil can now not settle in the arrangement of tubes 42 and in the tube lines 52, since it also already due to gravity tends to flow through all falling arranged tube lines 52 therethrough.
  • the pressure in the tubes 42 promotes the flow of the oil in the refrigerant flow direction 48 and ensures that the oil flows without any problems through those tube lines 52 that are not arranged falling or the connecting tube arches 47a, 47b, through which the oil is not continuous in the refrigerant flow direction 48 can flow from top to bottom.
  • the air to be dried must flow through four consecutive rows of tubes 43d, 43c, 43b, 43a as viewed in the direction of flow 22. If it comes to the passage through the tube 43d, although to a cooling of the air, but not yet to the condensation of moisture, are still rows of tubes 43c, 43b, 43a are available where the condensation can take place. In other words, the probability that the dew point falls below this level is dramatically increased by the provision of the four rows of pipes 43d, 43c, 43b, 43a or it can practically be ensured that the dew point is not reached.
  • the condensation due to the uniform temperature distribution of the coolant over each of the rows of tubes 43d, 43c, 43b, 43a takes place uniformly over this row of tubes 43d, 43c, 43b, 43a. That is, the condensation takes place uniformly over the entire register surface of the respective rows of pipes 43d, 43c, 43b, 43a.
  • the falling arrangement of the tube lines 42 of the tube rows 43d, 43c, 43b, 43a has a favorable effect. Due to the uniformly falling arrangement of the tube rows 43d, 43c, 43b, 43a and the tube lines 52 against the flow direction 22 of the air, the air can easily cover the entire surface of each of the successive rows of tubes 43d, 43c, 43b, 43a, and it can Comparatively larger temperature range over the entire register surface of the respective tube rows 43d, 43c, 43b, 43a are covered with the same compressor performance.
  • the condenser 12 has tubes 45 for the coolant, which extend transversely to the flow direction 22.
  • the tubes 45 form four tube rows 46a, 46b, 46c, 46d extending from top to bottom, cf. also Fig. 6 ,
  • the tubes 45 are divided into two stacked packages 49, wherein for each package 49 a separate manifold 44 is provided, via which the respective package 49, the refrigerant is supplied.
  • Each distributor tube 44 receives the refrigerant from its own feed section 51, which opens into the respective distributor tube 44 in the area of one of the three lowermost tubes 45 of the respective package 49.
  • By feeding the distributor tubes 44 from below in each case improved mixing of the refrigerant, in particular of liquid and gaseous parts of the refrigerant, can be guaranteed before the refrigerant is supplied to the tubes 45.
  • each of the rows of tubes 46a-d is charged almost evenly with the same warm refrigerant. For the air flowing through, therefore, only very slight deviations of the temperature result - both above each individual row of tubes 46a-d and between the rows of tubes 46d, 46c, 46b, 46a seen in the flow direction 22.
  • the refrigerant in each tube line 53 flows from the distributor tubes 44 into a collecting tube 37: first from the respective distributor tube 44 into a tube 45 of the first tube row 46a, then into a tube 45 of the second tube row 46b, then into a tube 45 of the third Tube row 46c, then into a tube 45 of the fourth row of tubes 46d and finally into the collecting tube 37, which discharges the refrigerant in the direction of expansion valve 35.
  • the connecting pipe bends 47a, 47b are formed and arranged so that the refrigerant in the connecting pipe bends 47a, 47b in the refrigerant flow direction 48 continuously from above flows down.
  • the pipes 45 of the Tube lines 53 are usually arranged horizontally, but would also be conceivable a slightly inclined arrangement, preferably in the direction of refrigerant flow 48 from top to bottom.
  • the falling arrangement of the tube lines 53 causes the refrigerant - from the entry into the respective tube 45 of the first row of tubes 46a to the exit from the respective tube 45 of the fourth row of tubes 46d into the collecting tube 37 - these tube lines 53 can flow through solely by gravity , A pressure in the pipes 45 promotes the flow of the refrigerant in the refrigerant flow direction 48 and ensures that the refrigerant flows without any problem through those pipe lines 53, the connecting pipe bends 47 a, 47 b, through which the refrigerant is not continuously in the refrigerant flow direction 48 from top to bottom can flow.
  • the falling arrangement of the tube lines 53 is of great advantage, since the oil of the compressor 13 can not settle in the arrangement of tubes 45 and in the tube lines 53, since it also tends already by gravity through all falling arranged tube lines 53rd to flow through.
  • the pressure in the tubes 45 promotes the flow of the oil in the refrigerant flow direction 48 and ensures that the oil flows without any problems through those tube lines 53 that are not arranged falling or have the connecting pipe bends 47a, 47b, through which the oil is not continuous in the refrigerant flow direction 48 can flow from top to bottom.
  • Fig. 8 shows a further embodiment of the dehumidifier 5 according to the invention, in which for each package 50 a separate manifold 36 is provided, via which refrigerant is discharged after it has leaked from the tubes 42 of the fourth tube row 43d. Furthermore, a distributor head 40 is provided for each package 50, which in turn is supplied in each case via its own expansion valve 35 and a separate manifold 38 with refrigerant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Drying Of Gases (AREA)

Claims (7)

  1. Déshumidificateur d'air (5) pour déshumidifier de l'air destiné à sécher du foin, le déshumidificateur d'air comprenant un évaporateur (11) et un condenseur (12), dans lequel le condenseur (12) est disposé derrière l'évaporateur (11) dans une direction d'écoulement (22) et dans lequel l'évaporateur (11) et le condenseur (12) peuvent être traversés par un flux d'air à déshumidifier dans la direction d'écoulement (22), dans lequel l'évaporateur (11) comprend plusieurs rangées de tubes, particulièrement de préférence quatre rangées de tubes (43a-d), les rangées de tubes (43a-d) comprenant une pluralité de tubes (42) pour un réfrigérant, dans lequel les tubes (42) sont disposés transversalement à la direction d'écoulement (22) et les uns au-dessus des autres, et dans lequel les tubes (42) sont divisés en plusieurs paquets (50) disposés les uns au-dessus des autres, une tête distributrice séparée (40) étant prévue pour chaque paquet, par laquelle le réfrigérant peut être amené au paquet respectif (50) pour s'assurer que le réfrigérant soit sensiblement à la même température dans toute la rangée de tubes respective (43a-d) et qu'une condensation de l'humidité de l'air qui s'écoule puisse être uniformément répartie sur la surface de la rangée de tubes respective (43a-d), dans lequel des lamelles (27) sont disposées entre les tubes (42) et reliées de manière thermoconductrice aux tubes (42), et dans lequel les lamelles (27) présentent entre elles, dans une direction normale à la direction d'écoulement (22), un espacement de lamelles (28) qui permet à l'air à déshumidifier de s'écouler à travers l'évaporateur (11), respectivement entre les lamelles (27).
  2. Déshumidificateur d'air (5) selon la revendication 1, caractérisé en ce que le condenseur (12) comprend au moins une rangée de tubes, de préférence plusieurs rangées de tubes, particulièrement de préférence quatre rangées de tubes (46a-d), que ladite au moins une rangée de tubes (46a-d) comprend une pluralité de tubes (45) pour un réfrigérant, les tubes (45) étant disposés transversalement à la direction d'écoulement (22) et les uns au-dessus des autres, et que les tubes (45) sont divisés en plusieurs paquets (49) disposés les uns au-dessus des autres, un tube distributeur séparé (44) étant prévu pour chaque paquet, par lequel le réfrigérant peut être amené au paquet respectif (49).
  3. Déshumidificateur d'air (5) selon l'une des revendications 1 à 2, caractérisé en ce qu'un tube collecteur séparé (36) est prévu pour chaque paquet (50) de l'évaporateur (11), par lequel le réfrigérant peut être évacué du paquet respectif (50).
  4. Déshumidificateur d'air (5) selon l'une des revendications 1 à 3, caractérisé en ce que chaque tube distributeur (44) est relié à sa propre section d'alimentation (51) pour alimenter en réfrigérant le tube distributeur respectif (44), la section d'alimentation respective (51) débouchant dans le tube distributeur respectif (44) dans la zone de l'un des trois tubes inférieurs (45) du paquet respectif (49).
  5. Déshumidificateur d'air (5) selon l'une des revendications 1 à 4, caractérisé en ce que plusieurs rangées de tubes (43a-d, 46a-d) sont prévues et que chaque tube (42, 45) d'une rangée de tubes (43a-d, 46a-d) est relié à un tube (42, 45) d'au moins une autre rangée de tubes (43a-d, 46a-d) par au moins un élément de liaison (47a, 47b) pour le réfrigérant, pour former dans chaque cas une ligne de tubes (52, 53), les éléments de liaison (47a, 47b) étant conçus dans au moins 80 %, de préférence dans au moins 90 %, particulièrement de préférence dans au moins 95 % de toutes les lignes de tubes (52, 53) de telle sorte que le réfrigérant puisse circuler continuellement de haut en bas dans ces éléments de liaison (47a, 47b).
  6. Utilisation d'un déshumidificateur d'air (5) selon l'une des revendications 1 à 5 pour sécher des produits alimentaires ou du foin.
  7. Utilisation selon la revendication 6, dans laquelle les produits alimentaires sont du houblon.
EP16163301.1A 2013-11-22 2014-11-24 Déshumidificateur d'air destiné à déshumidifier l'air pour le séchage du foin Active EP3073216B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT3922013 2013-11-22
EP14194496.7A EP2876397A3 (fr) 2013-11-22 2014-11-24 Dés-humidificateur d'air destiné à déshumidifier l'air pour le séchage du foin

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP14194496.7A Division EP2876397A3 (fr) 2013-11-22 2014-11-24 Dés-humidificateur d'air destiné à déshumidifier l'air pour le séchage du foin

Publications (2)

Publication Number Publication Date
EP3073216A1 EP3073216A1 (fr) 2016-09-28
EP3073216B1 true EP3073216B1 (fr) 2019-09-04

Family

ID=52015837

Family Applications (2)

Application Number Title Priority Date Filing Date
EP14194496.7A Withdrawn EP2876397A3 (fr) 2013-11-22 2014-11-24 Dés-humidificateur d'air destiné à déshumidifier l'air pour le séchage du foin
EP16163301.1A Active EP3073216B1 (fr) 2013-11-22 2014-11-24 Déshumidificateur d'air destiné à déshumidifier l'air pour le séchage du foin

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP14194496.7A Withdrawn EP2876397A3 (fr) 2013-11-22 2014-11-24 Dés-humidificateur d'air destiné à déshumidifier l'air pour le séchage du foin

Country Status (1)

Country Link
EP (2) EP2876397A3 (fr)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2261490A1 (en) * 1974-02-18 1975-09-12 Madre Marc Air conditioning equipment for product drying - sucks in humid air in housing via products before evaporation
NZ246813A (en) * 1992-01-08 1996-03-26 Ebco Manufacturing Co Portable electric dehumidifier structure
US6209223B1 (en) * 1998-12-08 2001-04-03 Advanced Dryer Systems, Inc. Grain drying system with high efficiency dehumidifier and modular drying bin
US6471739B2 (en) * 1999-12-02 2002-10-29 Lg Electronics Inc. Dehumidifier housing
ITMI20040141A1 (it) 2004-01-30 2004-04-30 Domnick Hunter Hiross S P A Essicatore di gas compresso a refrigerazione
US7845185B2 (en) * 2004-12-29 2010-12-07 York International Corporation Method and apparatus for dehumidification
EP1941214B1 (fr) * 2005-10-24 2013-12-04 LG Electronics, Inc. Deshumidificateur
JP2007240059A (ja) * 2006-03-08 2007-09-20 Daikin Ind Ltd 冷凍装置用熱交換器の冷媒分流装置
KR101542389B1 (ko) * 2009-02-05 2015-08-06 엘지전자 주식회사 히트펌프모듈 및 히트펌프모듈을 이용한 건조장치
KR101077183B1 (ko) * 2009-03-09 2011-10-27 김봉석 냉동장치를 이용한 건조기
US20100269521A1 (en) * 2009-04-28 2010-10-28 Steven Clay Moore Air-conditioning with dehumidification
WO2011079071A2 (fr) * 2009-12-23 2011-06-30 Thermo King Corporation Appareil destiné à réguler l'humidité relative dans un récipient

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2876397A3 (fr) 2015-10-07
EP3073216A1 (fr) 2016-09-28
EP2876397A2 (fr) 2015-05-27

Similar Documents

Publication Publication Date Title
DE60309217T2 (de) Kombinierter kondensator mit luftkühlung
DE69432612T2 (de) Verdampfungswärmetauscher mit geschlossenem direktem und indirektem Kreislauf in Kombination
DE3122197C2 (de) Kondensator
DE4439801C2 (de) Luftbeaufschlagter Trockenkühler
EP3728975B1 (fr) Installation de condenseur à refroidissement par air
EP2660084A1 (fr) Réservoir d'eau pour un véhicule automobile
EP3187807A1 (fr) Dispositif de séchage de matières à sécher
EP2696159B1 (fr) Échangeur thermique et procédé de mise en réseau d'échangeurs thermiques
CH652276A5 (de) Verfahren und anlage zum trocknen eines feuchten gutes, insbesondere von landwirtschaftlichen produkten.
DE1601870B2 (de) Gefrierbehaelter mit kuehlluftumwaelzung
WO1990015299A1 (fr) Installation refrigerante de type hybride
DE69802353T2 (de) Luftgekühlter kondensator
EP3073216B1 (fr) Déshumidificateur d'air destiné à déshumidifier l'air pour le séchage du foin
WO2008025630A1 (fr) Dispositif pour faire évaporer l'eau de dégivrage récoltée dans une coupelle collectrice d'un appareil de réfrigération et appareil de réfrigération avec un dispositif de ce type
DE69727197T2 (de) Absorptionskühlapparat
EP2546595A1 (fr) Dispositif et procédé de refroidissement
DE3519694A1 (de) Taupunktkuehler
EP0632240A1 (fr) Dispositif de refroidissement et d'humidification pour des chambres froides
AT514802B1 (de) Luftentfeuchter zum Entfeuchten von Luft zur Trocknung von Heu
DE4024276C2 (de) Kuehl- und befeuchtungsvorrichtung fuer waren, wie blumen, gemuese, obst, kaese
DE3216948A1 (de) Aussenwaermeaustauscher und -waermeaustauschvorrichtung
WO2016074893A1 (fr) Appareil de réfrigération sans givre
DE3327932C2 (de) Kühlturm zur Wasserrückkühlung
EP1600711A2 (fr) Usine à neige intérieure
DE102015014596B3 (de) Verbesserter Tropfenabscheider und verbesserte Klimaanlage

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AC Divisional application: reference to earlier application

Ref document number: 2876397

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170322

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20180220

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20190322

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AC Divisional application: reference to earlier application

Ref document number: 2876397

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1175956

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190915

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502014012595

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190904

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191204

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191204

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20191205

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200106

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200224

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502014012595

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG2D Information on lapse in contracting state deleted

Ref country code: IS

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191130

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191124

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191130

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200105

26N No opposition filed

Effective date: 20200605

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20191130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191124

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20141124

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190904

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20240502

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240502

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20240506

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20240515

Year of fee payment: 10