• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
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    • 专利摘要:

    公开号:BE1020584A3
    申请号:E201200415
    申请日:2012-06-19
    公开日:2014-01-07
    发明作者:De Glind Marinus Willem Van
    申请人:De Glind Marinus Willem Van；
    IPC主号:
    专利说明:

    VENTILATION SYSTEM FOR A BUILDING
    TECHNICAL FIELD OF THE INVENTION
    The invention relates to a ventilation system for a building according to the preamble of claim 1. The building is in particular a residence for animals, for example a stable for cattle, pigs, goats or poultry. The invention further relates to a heat exchanger for use in a ventilation system.
    BACKGROUND OF THE INVENTION
    The use of a heat exchanger in a ventilation system for a chicken house is known. Fresh outside air is heated in the heat exchanger by the extracted room air. A centrifugal fan provided with a cochlea housing encloses fresh outside air and supplies it to an air inlet chamber. In the air inlet chamber, the air is distributed over thin-walled air ducts that extend through a heat exchanger chamber. The fresh outside air flows through the air ducts and is heated in counterflow or in crossflow through extracted warm, relatively humid stable air. Afterwards, the heated fresh outside air enters an air outlet chamber to be subsequently supplied to the chicken house. The result is a supply to the stable of relatively dry air that has a temperature that is close to the desired stable temperature. Because relatively moist stall air is continuously extracted and relatively dry air is supplied, an improved drying of the manure is achieved. Ventilation also reduces the CO2 concentration in the house.
    A characteristic of the existing heat exchangers with thin-walled ducts in ventilation systems is that it has at least one of the following shortcomings, namely: too low efficiency, too high air resistance in heat exchanger, too large or too bulky, insufficient flow for minimum required ventilation in the house, with a low outside air temperature (below zero), the temperature of the air at the outlet of the heat exchanger is too low to be fed to the shed, difficult or impossible to maintain and too expensive to manufacture. As a result, the concept of heat exchangers with thin-walled ducts has proved to be commercially not applicable.
    SUMMARY OF THE INVENTION
    An object of the invention is to provide an improved ventilation system that overcomes at least one of the aforementioned shortcoming, whereby a heat exchanger with thin-walled ducts does become commercially interesting for both manufacturer and user.
    According to the invention, the object is achieved with a ventilation system comprising the features of claim 1. Advantageous embodiments and further ways of implementing the invention can be achieved by the measures in the dependent claims.
    A ventilation system for supplying outside air into a building and extracting inside air from the building according to the invention comprises a heat exchanger unit for heat transfer between the discharged inside air and supplied outside air. The heat exchanger unit is provided with an elongated heat exchanger chamber through which a plurality of parallel running thin-walled hoses extend between a first wall located at a first end of the elongated heat exchanger chamber and a second wall opposite the first wall. The thin-walled hoses form a partition between a space for passage of discharged inside air and a space for passage of supplied outside air. In a cubic meter of the heat exchanger chamber, the partition wall formed by the thin-walled hoses has a surface in the range of 20-35 square meters.
    It has been found that the known heat exchangers have less than 20 square meters of partition wall in a cubic meter of the heat exchanger chamber. As a result, the heat exchange capacity per linear meter is too low or the heat exchange chamber becomes too long, so that application in a poultry house is not profitably applicable. With a low outside temperature, the heat exchanger cannot heat up the outside air sufficiently, which means that the supply air to the house has a temperature that is too low to be allowed to be introduced directly. The upper limit of the applicable area is determined by a number of factors. First of all, as the surface area increases per cubic meter, the air resistance in the heat exchanger also increases. To have sufficient air displacement, the fans will use more energy. This is an additional cost item when using the heat exchanger. The manufacturing costs of the heat exchanger unit also increase exponentially. With an upper limit of 35 square meters of interface in a cubic meter, it is possible to realize a heat exchanger with sufficiently low air resistance at acceptable manufacturing costs. The combination of air resistance, heat exchange capacity and manufacturing costs is even more favorable in an area of 21 - 31 square meters, and can be further improved by having a partition wall with an area of 22 - 27 square meters in a cubic meter.
    An embodiment of the invention is characterized in that grating-shaped positioning means are provided in the heat exchange chamber, wherein the thin-walled hoses run through openings of the grating-shaped positioning means and wherein successive grating-shaped positioning means along the thin-walled hoses in a horizontal direction and perpendicular to the longitudinal direction of the thin-walled hoses staggered position. An advantageous embodiment is characterized in that the thin-walled hoses have a diameter and wire elements of the grid-shaped positioning means have a thickness and the distance is determined by the diameter of the thin-walled hoses and optionally the thickness of the wire elements. The staggered position of the positioning means reduces the spread of the mutual distance between horizontally adjacent hoses. This improves the heat recovery capacity of the heat exchanger.
    An embodiment of the invention is characterized in that, in use in a cubic meter of the heat exchanger chamber, the space for passage of discharged inside air is 2 - 30% smaller than the space for passage of supplied outside air. This feature improves the heat recovery capacity of the heat exchanger with balanced air ventilation. With balanced air ventilation, the amount of air supplied and discharged through the heat exchanger is substantially the same. The stable can then be seen as a closed system so that optimum use is made of the heat recovery capacity of the heat exchanger.
    An embodiment of the invention is characterized in that the heat exchanger unit comprises conical tube elements for clamping the ends of the thin-walled hoses in openings of the first and the second wall. By making use of cone-shaped tubular elements, the thin-walled hoses can be easily installed and secured. The end of a hose runs through an opening in one of the two walls and lies outside the heat exchange chamber. The cone-shaped tubular member is then placed in the end of the hose and displaced in or with the end of the hose until it clamps into the opening of a wall. Due to the weight of the hose and any tensile stress on the hose, the cone-shaped tubular element is continuously pulled into the opening so that the hose cannot come loose. If a hose leaks, it can easily be replaced by pulling the cone-shaped tubular element loose from the opening, which releases the end of the hose.
    An embodiment of the invention is characterized in that the thin-walled hoses have a circumference between 180 and 340 mm. Hoses with this circumference have a sufficiently low air resistance per linear meter and can therefore be used with lengths of more than 20 meters.
    An embodiment of the invention is characterized in that a cross-section of the heat exchanger in a square meter comprises a number of thin-walled hoses in a range of 60-180.
    An embodiment of the invention is characterized in that the heat exchanger unit further comprises an air inlet chamber and a centrifugal fan, the first wall being located between the air inlet chamber and the heat exchanger chamber, characterized in that the centrifugal fan is positioned in the air inlet chamber for an air inlet opening in an inlet wall of the air inlet chamber. A further embodiment of the invention is characterized in that the centrifugal fan comprises an air inlet element, the air inlet element being coupled to the inlet wall of the air inlet chamber. In one embodiment, the air inlet element is flexibly coupled to the inlet wall of the air inlet chamber with a flexible coupling element. By not using a cochlea housing around the impeller or rotor of the centrifugal fan, the air drawn in around the rotor and along the inlet wall is distributed in the air inlet chamber. As a result, the air flow is better distributed over the air inlet chamber and the air speeds in the air inlet chamber are lower than when a centrifugal fan with cochlea housing is used outside the air inlet chamber. Less energy is also required for the same air displacement through the heat exchanger. A further advantage of placement in the air inlet chamber is that no shielding is required for driving the rotor.
    The thin-walled hoses have a longitudinal direction and the centrifugal fan has an axis of rotation. In an advantageous embodiment the axis of rotation is substantially parallel to the longitudinal direction of the thin-walled hoses. This results in an optimum air distribution of the air sucked in the air inlet chamber.
    A further embodiment of the invention is characterized in that an air deflecting element is provided along at least one wall of the air inlet chamber for reducing air flow rate differences through the thin-walled hoses. This prevents the air flow rate in the outer hoses of the heat exchanger from becoming too high in relation to the air flow rate of hoses located inwards. This measure increases the efficiency of the heat exchanger.
    An embodiment of the invention is characterized in that it comprises a control system which is adapted to reduce the amount of discharged indoor air if the temperature of the supplied outdoor air after the heat exchanger is higher than a set value. This measure has three effects. First, the amount of recovered heat decreases, so that the temperature of the supplied outside air does not increase further after the heat exchanger. In addition, less air is removed while the same amount is supplied. As a result, the warm air in the building on another road will leave the building and the temperature in the building will not rise or will rise less rapidly. Finally, because less air needs to be discharged, the power of the fan can be reduced exponentially, which greatly reduces the electrical consumption.
    A further embodiment of the invention is characterized in that the control system is arranged to reduce the amount of supplied outside air if the temperature of the discharged inside air after the heat exchanger is lower than a set minimum value. Due to the temperature reduction of the indoor air, it can condense in the heat exchange chamber. As soon as the temperature is lower than 0 degrees Celsius, ice will form in the heat exchange chamber. The said measure prevents the temperature of the extracted indoor air from becoming lower than 0 degrees Celsius.
    An embodiment of the invention is characterized in that a spraying installation is provided in the heat exchanger chamber above the thin-walled hoses. In an advantageous embodiment, the spraying installation has two or more spraying sections, each spraying section being provided above a different part of the thin-walled hoses and each spraying section being separately controllable. The extracted indoor air contains dust particles that deposit as dirt on the outside of the hoses in the heat exchanger chamber. This reduces the efficiency of the heat exchanger. By regularly using the spraying installation, at least a part of the dirt is flushed from the hoses. The use of two or more spray sections has the advantage that the heat exchanger can also be used continuously during flushing because only in the section that is flushed, the heat recovery capacity is adversely affected. As a result, it can be prevented more often that the temperature of the heated fresh outside air is lower than the minimum desired temperature.
    It is a further aspect of the invention to provide an improved heat exchanger for use in a building ventilation system.
    It will be clear that the various aspects mentioned in this patent application can be combined and can each be considered separately for the split-off patent application. Other features and advantages of the invention will become apparent from the following detailed description, in conjunction with the accompanying drawings, which illustrate, by way of example, various functions of preferred embodiments of the invention.
    BRIEF DESCRIPTION OF THE FIGURES
    These and other aspects, features and advantages of the invention will be explained below on the basis of the following description with reference to the drawings, in which like reference numerals indicate like or comparable parts, and in which:
    FIG. 1 schematically shows a cross-sectional side view of an embodiment of a heat exchanger according to the invention;
    FIG. 2 schematically shows the coupling structure of a hose on the wall;
    FIG. 3 schematically shows a cross section of the hoses in the heat exchange chamber; and,
    FIG. 4 schematically shows a top view of the hoses and positioning means in the heat exchange chamber.
    DETAILED DESCRIPTION OF EMBODIMENTS
    FIG. 1 schematically shows a cross-sectional side view of an embodiment of a heat exchanger unit according to the invention. The heat exchanger unit comprises an air inlet chamber 2, an elongated heat exchanger chamber 4 and an air outlet chamber 6. A first wall 8 is provided between the air inlet chamber 2 and the heat exchanger chamber 4 and second wall 10 is provided between the air outlet chamber 6. Both the first wall 8 and the second wall 10 are provided with a plurality of openings through which plastic foil hoses 12 run. The plastic foil hoses 12 are a plurality of thin-walled air ducts that form an air connection between the air inlet chamber 2 and the air outlet chamber 6.
    Arranged in the air inlet chamber 2 is a centrifugal fan 14 for an air inlet opening in an air inlet wall 2A of the air inlet chamber 2. The fan 14 is placed between the air inlet wall 2A and the first wall 8. In an advantageous embodiment, the centrifugal fan 14 is with a flexible torque element 16 attached to the wall 2A. This dampens the vibrations of the fan. The fan comprises an air inlet element 14A, a blade or rotor 14C and a motor 14B. In FIG. 1, the centrifugal fan 14 is a direct driven fan. It is also possible to use an indirectly driven fan. The rotor 14C has an axis of rotation 14D which runs parallel to the longitudinal direction of the plastic foil hoses 12. The centrifugal fan has no housing. As a result, the fresh outside air 1 through the opening of the wall 2A is sucked in and spread around the rotor in the inlet chamber along the wall 2A. The air flow deflects along the side walls, floor and ceiling of the inlet chamber in the direction of the partition wall 8 and then flows through the thin-walled hoses 12 in the heat exchanger chamber to the air outlet chamber 6. From the air outlet chamber 6, the fresh outside air heated in the heat exchanger chamber is supplied. 1 ”supplied through a pipe system, not shown, from the ventilation system to rooms of the building to be ventilated. By heating up the fresh outside air 1 in the heat exchanger by the discharged inside air, the relative humidity has decreased.
    A plurality of thin-walled hoses 12 are arranged in the elongated heat exchanger chamber 4 between the first wall 8 and the second wall 10. The space in the thin-walled hoses 12 forms a space for passage of the outside air from the inlet chamber 2 to the outlet chamber 6. The space around the hoses 12 forms a space for passage of extracted indoor air 3. The airflow, not shown in Fig. 1 the extracted indoor air 3 is introduced into the heat exchanger chamber via an inlet opening 4A. The inside air then flows into the heat exchanger chamber along the outside of the thin-walled hoses 12 to leave the heat exchanger chamber 4 via an outlet opening 4B to discharge into the outside air via an air channel (not shown). The inlet opening 4A is on the side of the air outlet chamber 6. The outlet opening 4B is on the side of the air inlet chamber 2. The fan for extracting the inner air 3 can be fitted both before and after the heat exchange chamber 4. In an advantageous embodiment, the area of a cross-section of the heat exchanger chamber at the level of the inlet opening 4A and / or the outlet opening 4B is larger than a cross-section of the heat exchange chamber between the inlet opening 4A and / or the outlet opening 4B. As a result, the air flow can distribute more evenly over space between the hoses 12. In one embodiment, there is extra space at the height of the inlet opening 4A and the outlet opening 4B between the hoses and the ceiling, one or two side walls or the floor of the heat exchanger chamber. This allows the air to come between the hoses from multiple sides. This improves the heat recovery properties of the heat exchanger and lowers the air resistance of the heat exchanger.
    The air flow of discharged inner air 3 moves substantially from the second wall 10 to the first wall 8 of the heat exchanger chamber 4. The air flow from outside air 1 moves substantially from the first wall 8 to the second wall 10 of the heat exchanger chamber 4. The air flows are separated from each other by the thin wall of the hoses 12 forming a partition wall. The two air flows do not mix as a result. The heat from the extracted indoor air 3 is transferred in the heat exchange chamber 4 through the wall of the hoses 12 to the supplied outdoor air 1.
    In order to realize sufficient heat transfer from air flow to air flow with sufficient efficiency, it has been found that in a cubic meter of the heat exchange chamber there must be at least 20 square meters of partition wall between the air flows. In the context of the present application, efficiency of a heat exchanger is understood to mean the number of degrees by which the outside air is heated relative to the difference in temperature of the discharged inside air and the supplied outside air for the heat exchanger unit. The upper limit on the number of square meters is determined by a number of factors such as air resistance, production costs and the risk of clogging due to pollution. As the separation surface increases, the number of hoses will increase by one cubic meter and the diameter of the hoses will decrease. If the diameter decreases, the air resistance of the hoses per linear meter will increase and more energy will be needed to move the air. The production costs are determined by the number of hoses that must be attached. The distance between the hoses will decrease as the separation surface increases and this increases the chance of clogging due to contamination. An upper limit of 35 square meters of dividing wall in a cubic meter is seen as an upper limit. A surface in the area of 21 - 31 square meters in a cubic meter will prove to be more useful. In an area of 22 - 27 square meters of separation surface or hose surface in a cubic meter, on average, it will be most often usable where the least number of concessions need be made.
    Positioning means in the form of, for example, mesh are arranged at a regular distance in the longitudinal direction of the heat exchange chamber 4 in order to keep the thin-walled hoses 12 in place and to prevent the hoses from sinking too far due to their own weight. The distance between the positioning means can vary between 1 and 3 meters. A distance of approximately 1.7 meters appears to be satisfactory in practice. The positioning means furthermore cause additional swirls in the air flow outside the hoses. This improves the heat transfer from the air flow to the wall of the hoses.
    FIG. 3 shows a cross-section of a portion of the thin-walled hoses in the heat exchange chamber. Shown are the thin-walled hoses 12 and a positioning means 16. The positioning means 16 can be made of metal or plastic and has a mesh size that is larger than a cross-section of the thin-walled hoses 12. The space in the hoses is indicated by reference numeral 4D. The space around the hoses 12 is indicated with reference number 4C. It is preferred that the space for passage of discharged indoor air, i.e. the space around or between the hoses 12, is 2 - 30% larger than the space for passage of the supplied outside air, i.e. the space in the hoses 12. The structure of the space around the hoses 12 is such that the air flow is less likely to flow into the space located between the shortest distance between hoses than the space located between the largest distance between the hoses. By making the space between the hoses larger than the space in the hoses, the air flow around the hoses is improved. Furthermore, this reduces the air resistance of the space between the hoses, as a result of which a fan requires less power to discharge the air from the shed.
    The positioning means 16 increase the air resistance of the space between the hoses. But because the positioning means 16 cause additional air turbulence in the air flow, the air flow is continuously mixed and thereby the heat transfer to the air flow in the hoses is improved. With balanced ventilation, that is to say that the amount of discharged air per unit of time is approximately equal to the amount of supplied air, the average velocity of the air flow outside or between the hoses will be lower than the average velocity of the air in the hoses. The advantage of balanced ventilation is that all air enters the building via the heat exchanger and goes out via the heat exchanger. Balanced ventilation is particularly important in cold outdoor temperatures. There is no airflow of cold outside air into the house and therefore no fall of cold air in the room. This cold air considerably worsens the climate of the animals in the house. This balanced air flow is considerably reduced with balanced air ventilation.
    In one embodiment of the invention, film hoses of LDPE (Low Density Polyethylene) with a thickness of 150 µm and a hose diameter of 7 to 8 cm have been used. Depending on the specifications of the heat exchanger, the film thickness can be in the range of 50 - 250 pm. In this embodiment, a positioning means is used with a mesh size of 10 x 10 cm. The number of hoses through a cross-section with an area of one square meter is 100 hoses. With hoses that have a diameter of 7 to 8 cm, the interface between the air flow is fresh outside air and warm inside air between 22 and 25 square meters per cubic meter. The ratio between the space in the hoses and outside the hoses is 1: 1 for a hose diameter of 8 cm and 0.63: 1 for a hose diameter of 7 cm. The heat exchanger chamber 4 has a height and width of approximately 2 meters and a length of approximately 30 meters, so that approximately 400 thin-walled hoses 12 with a diameter of 7 to 8 cm extend through the heat exchange chamber between the first wall 8 and the second wall 10. The length of the heat exchanger chamber can have any length and can for instance be determined by the dimensions of the building or the space in which the heat exchanger is placed.
    To obtain a ratio of 1: 1 with a hose diameter of 7 cm, a mesh size of 8.8 x 8.8 cm will have to be used. The separation area formed by the hoses in a cubic meter is then 28.5 square meters and the number of hoses through a cross-section of one square meter is then 130.
    Because the centrifugal fan causes the sucked air to flow along the walls, the air flow through the hoses which have their opening near the side walls, ceiling or floor of the inlet chamber 2 can have a higher speed than the air flow through the hoses in the middle. To counteract this effect, one or more air deflecting elements 2B are placed where necessary along the side walls, floor and ceiling of the inlet chamber for the hose openings located on the outside. As a result, the rapid air flow along the walls cannot flow directly into hoses located near the side walls of the heat exchanger chamber and the variation in air speed will decrease.
    In FIG. 2 schematically shows a cross-section of the coupling of the thin-walled hoses 16 in an opening of a wall 20. The wall 20 can be both the partition between the air inlet chamber and the heat exchanger chamber and the partition between the heat exchanger chamber and the air outlet chamber. The space in the heat exchanger chamber is indicated by reference numeral 22. The space in the air inlet chamber or air outlet chamber is indicated by reference numeral 24. The thin-walled hose 12 which runs through the heat exchanger chamber passes through an opening in the wall 20. A coupling element 18 in the form of a tubular element with a conical exterior is placed in the air inlet chamber or the air outlet chamber 24 in the end 12A of the thin-walled hose 12. Because the material of the hoses is to a certain extent elastic, the hoses do not tear as a result. The cone shape is chosen such that the smallest outer diameter is smaller than the opening in the wall and the largest outer diameter of the coupling element is larger than the opening. By pushing the coupling element 18 into the opening or by pulling tensile stress from the hoses in the heat exchanger chamber into the opening, the hose gets stuck between the wall of the opening and the outside of the coupling element 18. This also makes a practical view airtight seal realized between the supplied outside air flow and the discharged inside air flow. This coupling also has the advantage that a defective hose can easily be replaced by the following steps in succession: 1) releasing coupling element 18 from opening in wall 20; 2) removing coupling element 18 from end 12A of the defective hose; 3) attaching end of defective hose to end of new hose; 4) releasing coupling element 18 from opening in other wall; 5) removing coupling element 18 from other end 12A of the defective hose; 6) pulling out the defective stroke and simultaneously applying new hose to the heat exchanger chamber; 7) securing both ends in the manner described above.
    In the heat exchanger chamber 4, a spraying installation can optionally be arranged above the package with thin-walled hoses. With the spraying installation, the hoses can be sprayed with water and dirt or dust can be removed from the air of the stable deposited on the outside of the hoses by the heat exchange chamber and the heat exchanger retains its efficiency. To reduce air flow through the space above the hoses for the spraying installation, partitions have been placed at regular intervals across the width of the heat exchange chamber. These baffles run from the top of the heat exchange chamber to at least the top of the upper hoses in the heat exchange chamber.
    In an advantageous embodiment, the spraying installation comprises two or more spray sections located next to or behind one another, viewed in the longitudinal direction of the heat exchange chamber. Each spray section can be controlled separately. This makes it possible to spray only a portion of the amount of hoses in the heat exchange chamber. Because only a portion of the hoses is sprayed with relatively cold ground water, the heat exchanger only partially loses its heat recovery capacity during the spraying or rinsing of the hoses. As each spray section extends the entire length of the heat exchanger chamber, the portion being flushed loses its heat recovery capacity and the adjacent sections retain their heat recovery capacity. In the air outlet room, the air flows are mixed with different temperatures and then supplied to the space in the building.
    A ventilation system comprising the above-described heat exchanger unit is also provided with a control system and temperature sensors. A ventilation system for a stable has a temperature sensor at the place where the air is blown into the room in the building. In a chicken house, the heated and dry outside air is preferably supplied just above the manure. For an optimal climate, the temperature around the living things must not exceed a certain value. The control system is arranged to reduce the amount of discharged indoor air if the temperature of the supplied outdoor air after the heat exchanger is higher than a set value. As a result, the ventilation system is no longer balanced and more air is supplied than discharged by the ventilation system. This has two effects. First, the heat recovery capacity of the heat exchanger decreases. Secondly, warm air will leave the building through other openings, causing heat to disappear from the building.
    In one embodiment the ventilation system comprises a temperature sensor for measuring the air temperature of the discharged indoor air at the outlet 4B of the heat exchanger. In winter periods when the temperature falls below zero, the moisture in the extracted indoor air in the heat exchanger chamber can lead to ice formation on the hoses 12. To prevent this, the control system is designed to reduce the amount of supplied outside air as the temperature of the extracted indoor air after the heat exchange chamber is lower than a set minimum value. The set minimum value will be slightly above zero, for example in the range of 0.6-1 ° C.
    In one embodiment the ventilation system comprises a temperature sensor for measuring the outside air and the control system is adapted to activate and deactivate the spraying installation above the thin-walled hoses with a predetermined cycle when the measured outside temperature is higher than a set minimum temperature value . If the measured outside temperature is lower than the set minimum temperature value, the spraying installation will not be activated. The spraying installation is therefore not activated if the value of the outside temperature is smaller than an adjustable minimum temperature value. In one embodiment, the minimum temperature value corresponds to an outside temperature of 6 ° C. This prevents too cold air from being supplied to the shed during the flushing of the hoses in the heat exchange chamber.
    FIG. 4 schematically shows a plan view of an arrangement of grid-shaped positioning means 16, with hoses 12 running through the grid openings. The positioning means are composed of bars running vertically and horizontally. The grid openings are square and have a width W. Hoses 12 with a diameter D run through the grid openings. The positioning means 16 have a mutual distance A viewed in the longitudinal direction of the hoses 12. Stand in a direction perpendicular to the longitudinal direction of the hoses the positioning means 16 in the horizontal direction are alternately staggered with respect to each other over a distance V. The distance V depends on the grid width W and the diameter D of the hoses 12. Hoses with a length of at least 10 meters could be virtually opposed without staggering positioning means come to lie. Where they are in practical opposition, there will be virtually no air flow along the hose and therefore no heat exchange at those places. By allowing the positioning means 16 to stagger relative to each other over a distance V, the space of movement of the hoses is limited. Viewed along the hoses, the hose will alternately lie with its left side and right side against a vertically running post of the positioning means 16. A minimum mutual distance of adjacent hoses is hereby obtained which approximately corresponds to the distance V. This measure improves the air flow along the outer surface of the hoses and thus the heat exchange properties of the heat exchanger. In one embodiment, the distance A between positioning means is 170 cm, V is approximately 2.3 cm, W is 10 cm and D is approximately 7.7 cm
    The positioning means can be made of galvanized steel grid. However, due to the galvanizing process, there may be sharp points on the steel grid. These can puncture the thin-walled snakes. In an advantageous embodiment, the positioning means are made of horizontally and vertically running LDPE bars which are welded together at the crossings. A first advantage is that the positioning means can be assembled on site in the heat exchanger chamber from LDPE rod-shaped elements which are subsequently fused together at the intersections. LDPE is a corrosion-resistant material and when fused together it remains corrosion-resistant. If steel rod-shaped elements were to be used on site for assembling the positioning means, the weld points would be susceptible to corrosion. Due to the condensation that occurs in the heat exchange chamber, this would considerably shorten the service life of the positioning means assembled on site compared to the use of pre-assembled and galvanized steel gratings.
    It is to be understood that the above description is included to illustrate the operation of preferred embodiments of the invention, and not to limit the scope of the invention. The measures as described above for carrying out the invention can of course be carried out separately, in parallel or in another combination. If possible, the invention can be supplemented with further measures. Changes can be made without departing from the idea of the invention.
    权利要求:
    Claims (19)
    [1]
    A ventilation system for supplying outside air into a building and extracting inside air from the building, wherein the ventilation system comprises a heat exchanger unit for heat transfer between the discharged inside air and supplied outside air, the heat exchanger unit comprising an elongated heat exchanger chamber whereby a plurality of parallel running thin-walled hoses extending between a first wall located at a first end of the elongated heat exchanger chamber and a second wall located opposite the first wall, wherein the thin-walled hoses form a partition between a space for passage of discharged inside air and a space for passage of supplied outside air, with the characterized in that in a cubic meter of the heat exchanger chamber the partition wall formed by the thin-walled hoses has a surface in the range of 20 - 35 square meters, in particular in the range of 21-31 square meters, more in particular 22 - 27 square meters.
    [2]
    Ventilation system as claimed in claim 1, characterized in that grating-shaped positioning means are provided in the heat exchange chamber, wherein the thin-walled hoses run through openings of the grating-shaped positioning means and wherein successive grating-shaped positioning means along the thin-walled hoses in horizontal direction and perpendicular to the longitudinal direction of the thin-walled positioning hoses have a staggered position over a distance.
    [3]
    Ventilation system according to claim 2, characterized in that the thin-walled hoses have a diameter and wire elements of the grid-shaped positioning means have a thickness and the distance is determined by the diameter of the thin-walled hoses and optionally the thickness of the wire elements.
    [4]
    Ventilation system according to any of the preceding claims, characterized in that That when used in a cubic meter of the heat exchanger chamber, the space for passing through exhausted indoor air is 2 - 30% larger than the room for passing through supplied outside air.
    [5]
    Ventilation system according to any of the preceding claims, characterized in that the heat exchanger unit comprises cone-shaped tubular elements for clamping the ends of the thin-walled hoses in openings of the first and the second wall.
    [6]
    Ventilation system according to any of the preceding claims, characterized in that the thin-walled hoses have a circumference between 180 and 340 mm.
    [7]
    Ventilation system according to any of the preceding claims, characterized in that a cross-section of the heat exchanger in a square meter comprises a number of thin-walled hoses in a range of 60-180.
    [8]
    A ventilation system according to any one of the preceding claims, wherein the heat exchanger unit further comprises an air inlet chamber and a centrifugal fan, the first wall being located between the air inlet chamber and the heat exchanger chamber, characterized in that the centrifugal fan is positioned in the air inlet chamber for a air inlet opening in an inlet wall of the air inlet chamber.
    [9]
    Ventilation system according to claim 8, characterized in that the centrifugal fan comprises an air inlet element, the air inlet element being coupled to the inlet wall of the air inlet chamber.
    [10]
    10. Ventilation system as claimed in claim 9, characterized in that the air inlet element is flexibly coupled to the inlet wall of the air inlet chamber with a flexible coupling element.
    [11]
    A ventilation system according to any one of claims 8-10, wherein the thin-walled hoses have a longitudinal direction and the centrifugal fan has a rotation axis, characterized in that the rotation axis is substantially parallel to the longitudinal direction of the thin-walled hoses.
    [12]
    Ventilation system according to claim 11, characterized in that an air deflecting element is provided along at least one wall of the air inlet chamber for reducing air flow rate differences through the thin-walled hoses.
    [13]
    12. Ventilation system as claimed in any of the foregoing claims, further comprising a control system with temperature sensors, characterized in that the control system is adapted to reduce the amount of discharged indoor air if the temperature of the supplied outdoor air after the heat exchanger is higher than a set value.
    [14]
    A ventilation system according to claim 13, characterized in that the control system is adapted to reduce the amount of supplied outside air if the temperature of the discharged inside air after the heat exchanger is lower than a set minimum value.
    [15]
    A ventilation system according to any of the preceding claims, characterized in that a spraying installation is provided in the heat exchanger chamber above the thin-walled hoses.
    [16]
    A ventilation system according to claim 15, characterized in that the spraying installation comprises two or more spraying sections, wherein each spraying section is provided above a different part of the thin-walled hoses and each spraying section can be controlled separately.
    [17]
    17. Ventilation system as claimed in claim 15 or 16, characterized in that the system further comprises a control system provided with a temperature sensor for measuring the outside air temperature, wherein the control system is adapted not to activate the spraying installation if the outside temperature is smaller than a adjustable minimum temperature value.
    [18]
    A ventilation system according to any of the preceding claims, characterized in that the building is a shed for poultry, pigs, goats or cattle.
    [19]
    A heat exchanger for use in a ventilation system, wherein the heat exchanger comprises all technical elements of a heat exchanger unit according to any of claims 1-16.
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    同族专利:
    公开号 | 公开日
    NL2006986C2|2013-01-02|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    NL62676C|
    DE3405124A1|1984-02-14|1985-08-22|HLK-Luft- und Klimatechnik GmbH, 7118 Künzelsau|Heat exchanger for cowsheds|
    DE8505174U1|1985-02-23|1985-07-18|SCHÖKO Gerätebau, 8317 Mengkofen|Transportable heat exchanger device for stalls with animals kept in batteries|
    FI942068A|1994-05-05|1995-11-06|Shippax Ltd Oy|Heat|
    DE19911177A1|1999-03-12|1999-08-19|Prostadt Ingenieurgesellschaft|Heat exchanger for exchange of heat between gases|
    DE10159891A1|2001-12-06|2003-06-18|Kermi Gmbh|Counterflow heat exchanger producing process involves joining two endface plates, one with tubes, other with apertures and then drawing tubes out to thin-walled tubes|
    DE102006038391A1|2006-08-15|2008-02-21|Thomas Pollmeier|Exhaust duct for e.g. animal house, has wall parts connected with building opening, where duct is designed as heat exchanger, which is integrated into guide such that entire exhaust air supplied over exhaust inlet flows through exchanger|
    GB2463004A|2008-08-26|2010-03-03|Daniel Carl Lane|Heat exchanger in a heat recovery ventilation system|
    KR101572889B1|2009-05-15|2015-11-30|엘지전자 주식회사|Ventilation System and Controlling Method of the Same|
    FR2953002B1|2009-11-23|2012-09-28|France Air|VENTILATION INSTALLATION WITH MEANS FOR CLEANING A DUAL FLOW THERMAL RECUPERATOR, THERMAL RECUPERATOR, AND VENTILATION METHOD|
    DE202010000189U1|2010-02-15|2010-04-22|Polytetra Gmbh|Tube bundle heat exchanger made of plastic|
    法律状态:
    2019-08-19| PD| Change of ownership|Owner name: BEEKAMP B.V.; NL Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), CESSION; FORMER OWNER NAME: VAN DE GLIND MARINUS WILLEM Effective date: 20190617 |
    优先权:
    申请号 | 申请日 | 专利标题
    NL2006986|2011-06-22|
    NL2006986A|NL2006986C2|2011-06-22|2011-06-22|VENTILATION SYSTEM FOR A BUILDING.|
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