CA2545949A1

CA2545949A1 - Cooling device, especially for chilling cooling chambers

Info

Publication number: CA2545949A1
Application number: CA002545949A
Authority: CA
Inventors: Juergen Lessing
Original assignee: Individual
Current assignee: Individual
Priority date: 2003-11-13
Filing date: 2004-10-13
Publication date: 2005-05-26
Also published as: EA200600948A1; ES2293326T3; EP1690044B1; EP1690044A1; PT1690044E; DE502004004772D1; DK1690044T3; DE10353046A1; MXPA06005316A; ATE371151T1; US20070289327A1; WO2005047778A1; EA010680B1; PL1690044T3

Abstract

Disclosed is a cooling device, especially for chilling cooling chambers, comprising two alternately activatable heat exchangers, particularly evaporators or coolers of a cooling circuit, and at least one fan for blowing gas, above all air, through the heat exchangers. In order to reduce production costs and space requirements, the two heat exchangers are disposed so as to be respectively penetrable by the entire gas flow of the fan at least when activated.

Description

A refri eratin~ apparatus, in particular for the cooling of refri eratin~ ss~aces The present invention relates to a refrigerating apparatus, in particular for the cooling of refrigerating spaces. comprising two alternately activatable heat exchangers, in particular evaporators or coolers of a coolant circuit, and at least one fan to blow gas, in particular air, through the heat exchanger.
A refrigerating apparatus of the initially named kind is known from DE
197 09 176 C2. With this refrigerating apparatus, the two alternately activatable heat exchangers made with lamellae are arranged next to one another or over one another and are flowed through by the same flow of the medium to be cooled. This means that the two heat exchangers are each only charged by half of the flow. To achieve a desired charge with a medium flow, the total flow must therefore be selected to be twice as large.
The fan must be made correspondingly large, whereby the costs and the space requirements are increased.
It is the underlying object of the invention to provide a refrigerating apparatus of the initially named kind which does not have these disadvantages. The refrigerating apparatus should in particular be cost favorable and space saving.
This object is satisfied in that the heat exchangers are arranged such that they can each be flowed through by the total gas flow of the fan at least on activation.
By the arrangement of the heat exchangers such that they can each be flowed through by the total gas flow of the fan, the required total gas flow

2 can be reduced to approximately half with respect to the known apparatus. The fan must accordingly be dimensioned smaller, whereby costs and space are saved.
A flowing through of both heat exchangers by the total gas flow can in particular be achieved in that the two heat exchangers are arranged behind one another in the direction of flow. In this process, both heat exchangers can be arranged on the same side of the fan. Both heat exchangers are thereby automatically charged with the total gas flow, irrespective of the direction in which the fan blows.
Another arrangement consists of a first heat exchanger being arranged before the fan or fans in the direction of flow and a second heat exchanger being arranged behind the fan or fans in the direction of flow. The two heat exchangers can thereby protect the fan from external influences.
A design is particularly cost favorable in which the heat exchangers are arranged freely in front of or behind the fan or fans. No additional components are thereby necessary and conventional heat exchangers can be used. Special products as with the initially named refrigerating apparatus are not necessary.
Gas conducting passages can, however, also be arranged between the fan or fans and the heat exchangers. A plurality of advantages hereby result.
The heat exchangers and the fan can inter alia be arranged spaced from one another. In addition, pressure measuring devices such as pressure gages, filters or attenuators can be arranged in the gas conducting passages.

3 In accordance with a further embodiment of the invention, the fan or fans and the heat exchangers are also arranged in closed gas conductors. The flow generated by the fan can thereby be fully utilized and a good flow guidance can be achieved.
It is particularly preferred for the fan or fans and the heat exchangers to be arranged in a common housing. This is space saving, on the one hand, and also effects a goad protection of the fan or fans by the heat exchangers exchanged in front and/or behind them:
Gas conducting passages can preferably be connectable to the housing at least at the gas outlet side. This advantageously permits the remote installation of the housing from the location to be cooled, for example in the false ceiling of a refrigerating space or completely outside a building surrounding the refrigerating space.
In accordance with a particular embodiment of the invention, a fan with a reversible blowing direction is provided. By reversing the blowing direction of the fan, the direction of flow of the gas through the heat exchangers arranged in front of or behind the fan can be reversed, in particular such that the gas is sucked in by the respectively non-active heat exchanger and blown out by the respectively active heat exchanger. The non-active heat exchanger is thus flowed through by the gas to be cooled and is heated by it, which can advantageously be used for defrosting with evaporators of a coolant circuit when the temperature of the gas to be cooled is above freezing point. Subsequently, the gas thereby already cooled passes through the activated second heat exchanger, with it being further cooled in the desired manner.

4 One heat exchanger can thus always be defrosted and one used for cooling by an alternate activation of the two heat exchangers and a corresponding reversal of the blowing direction of the fan. This also has the advantage that the blowing out direction of the unit changes cyclically, whereby a better distribution of the cooled gas in the refrigerating space can be achieved. If, in contrast, a blowing out should always only be desired in one direction, this can be achieved by a suitable arrangement of gas conducting passages and valves in front of the outlets or inlets of the refrigerating apparatus.
In accordance with another embodiment, the different throughflow direction of the heat exchangers is realized by valve-controlled fluid guides.
With this embodiment, the gas can also be alternately sucked in by the one heat exchanger and blown out by the other heat exchanger, with the one heat exchanger respectively being inactive and optionally defrosted, whereas the other heat exchanger is activated for cooling. A reversal of the blowing direction is not necessary with this arrangement. A further advantage consists of the fact that the fan power can be optimized for the only blowing direction of the fan.
In accordance with a special embodiment of the invention, a fan is provided whose blowing side can alternately be connected via switch-over valves and corresponding gas conducting passages to the first heat exchanger or the second heat exchanger and its suction side to the respectively other heat exchanger. With this variant, the fan is therefore arranged between the two heat exchangers.

In accordance with another special embodiment, a fan is provided whose suction side is connected to the entry opening of the apparatus and whose blowing side is alternately connected to the first heat exchanger or to the second heat exchanger, with the respectively other heat exchanger being

5 connected to the one heat exchanger, on the one hand, and to the outlet opening of the apparatus, on the other hand. In this variant, both heat exchangers are accordingly arranged in front of the fan or both heat exchangers are arranged behind the fan in the direction of flow.
In accordance with yet another special embodiment of the invention, two fans are provided which are arranged in opposite senses and parallel to one another and are each connected to the two heat exchangers via gas conducting passages and can be activated alternately. It can again also thereby be achieved that the gas to be cooled is alternately sucked in by the one heat exchanger and blown out by the other heat exchanger. In this process, one fan is active and the other fan is inactive respectively.
The advantage is also present here that the fan power can be optimized for the only direction of flow.
The respectively non-active branch of this arrangement can preferably be closed via a valve. A false flow through the non-active branch can thereby be avoided.
In accordance with a particularly preferred embodiment of the invention, the inlet opening and the outlet opening of the apparatus are formed in each case by the same opening irrespective of the throughflow direction of the heat exchangers. The advantage thereby results that a filter attached behind the inlet opening is always flowed through in the same direction.
No exchangeable filters therefore have to be provided, which permits a particularly good sealing of the filters. False air can hereby largely be

6 avoided so that a high filter performance up to clean room engineering can be ensured.
It is likewise preferred for the inlet opening and the outlet opening of the housing always to be arranged at the same side of the apparatus, in particular next to one another. A particularly compact design of the apparatus can thereby be achieved, whereby the space requirements can advantageously be reduced.
A further reduction in the space requirements can be achieved in that the fluid guides extend in different planes at least sectionally, in particular above one another and beneath one another, in accordance with a further embodiment of the invention. In addition, this variant is particularly advantageous when the inlet opening and the outlet opening are arranged on the same side of the apparatus.
It is furthermore advantageous for the diameter of the fluid guides to differ in different sections. The diameter can in particular be larger in the region of the heat exchangers than in front or behind them, for example in a ratio of approximately 2 : 1. The construction size can thus also be further reduced, without the performance capability of the apparatus being noticeably restricted since the cross-section can be kept advantageously large in the region of the heat exchangers and the reduced cross-section in another respect means hardly any impairment.
Axial fans can be used as fans in the refrigerating apparatus in accordance with the invention. However, radial fans can preferably also be used in the refrigerating apparatus in accordance with the invention. The latter have the advantage of a considerably higher pressing, which in particular comes into effect with the use of gas conducting passages.

7 The use of radial fans also permits the use of filters for the gas to be cooled. They can in particular be arranged in the gas conducting passages and jor in the fan housing. High hygiene demands can be satisfied by the use of filters.
In particular at least one rotary filter can be provided as the filter which is rotatable in dependence on the direction of flow of the gas. In this manner, the filter is always charged in the same direction by the gas flow. A
blowing out of filtered particles again can thereby be avoided.
In accordance with a further embodiment of the invention, at least one roll filter is provided. The latter can, for example, be made as a disposable filter and can be further rotated accordingly on every reversal of the direction of flow.
In accordance with another embodiment of the invention, the filter roll can, however, also be made to be movable to and fro in a cyclic manner in dependence on the direction of flow of the gas. A respective section of the filter roll is thereby always charged with the gas flow in the same direction so that the blowing out of particles again can also be avoided here. On the reaching of a specific degree of load of the filter, the roll can then be rotated further by twice the filter length so that two new sections of the roll filter can be used alternately.
At least one pressure measuring device, in particular a pressure gage, can be arranged in the gas conducting passages and/or in the fan housing. It can be used both for the determination of the degree of icing of the heat exchangers and for the determination of the necessity of a change of filter.

A change of filter or a further rotation of a roll filter can, however, also be triggered or indicated at the end of a predetermined or predeterminable time, for which purpose corresponding means are provided in accordance with a further embodiment of the invention. A pressure measuring device can thereby be saved. Good results can nevertheless be achieved on the basis of experience values.
The reversal of the direction of flow through the two heat exchangers can also take place in dependence on time, for which purpose suitable means are likewise preferably provided. Good results can also thereby be achieved on the basis of experience values and corresponding measuring devices such as pressure measuring devices for the detection of the degree of icing of the heat exchangers can be saved.
In accordance with a further embodiment of the invention, means for sterilization are provided in the gas conducting passages and/or in the fan housing, in particular in the region of the outlet opening. Hygienic demands can also thereby be satisfied, with the sterilization being particularly effective in the outlet region.
Means for LJV irradiation or ionization can preferably be provided for the sterilization. Alternatively or additionally, it is also possible to provide means for the injection of disinfectants, for example fruit acid. Both measures are well suited for sterilization.
The two heat exchangers are generally operated alternately. In accordance with an embodiment of the invention, however, an overlapping operation is also possible by a corresponding control for the activation of the heat exchangers. An increased refrigerating capacity can be made available in the short term by such a control. The air humidity can additionally thereby be regulated.
Furthermore, sound attenuation devices in the fan housing or in the gas guides are advantageous. The noise radiation of the apparatus can thereby be reduced.
The speed of rotation of the fan or fans can advantageously be regulated for the regulation of the capacity of the refrigerating apparatus in accordance with a further embodiment.
An advantageous design results when the housing has a plurality of chambers. It is advantageous for service and repair purposes in this process if the chambers are each accessible via their own access opening, in particular a door.
It is furthermore advantageous for each chamber to have its own condensate drain. Service and repair measures can also be simplified in that a lighting device is provided in the housing.
Non-restricting embodiments of the invention are shown in the drawing and will be described in the following. There are shown, schematically in each case:
Fig. 1 a block diagram of a first variant of the refrigerating apparatus in accordance with the invention;
Fig. 2 a representation in accordance with Fig. 1 of a second variant;
Fig. 3 a representation in accordance with Fig. 1 of a third variant;

Fig. 4 an upper view of a fourth variant of the refrigerating apparatus in accordance with the invention;
5 Fig. 5 a perspective view of the variant of Fig. 4 from a first direction of view; and Fig. 6 a perspective view of the same apparatus from a second direction of view.
Fig. 1 shows a fan 1, two heat exchangers 2 arranged at both sides of the fan 1 as well as two filters 3 arranged in each case on the side of the two heat exchangers 2 remote from the fan 1. Gas guides 4 are present between the fan 1 and the heat exchangers 2 and the filters 3> with these being able to consist of passages or lines. The fan 1 and the heat exchangers 2 as well as preferably also the filters 3 can, however, also be arranged in a common housing which then ensures the schematically shown gas guidance between the named components.
In addition, two pressure gages 5 are shown via which the pressure can be detected on both sides of the fan 1. A pressure gage 5 of this type can be arranged both in the region of the filters 3, as shown, to be able to draw a conclusion on the degree of load of the filters 3, and in the region of the heat exchangers 2 to be able to draw a conclusion on their degree of icing.
To be able to detect both, a plurality of pressure gages 5 can also be provided on each side.
The fan 1 is made as a radial blower whose direction of rotation can be reversed. In this manner, a gas flow can be generated both in the direction of the arrow 6 and in the reverse direction in accordance with arrow 7.

The switch-over can take place in dependence on the degree of icing of the heat exchangers 2 or in dependence on time. A corresponding control is provided, but not shown.
The filters 3 can be made as rotary filters, in particular as bag filters rotatable around 180°. The rotary position can be set according to the blowing direction of the fan 1 via a suitable control so that the filters are always charged by the gas flow 6 or 7 in the same direction and the particles absorbed by the filters 3 are not blown out again when the direction of rotation of the fan 1 reverses. The filter 3 on the outflow side could, however, also simply be moved out of the flow since it is often sufficient for the filter 3 on the suction side to be active.
Roll filters with which filter material can be wound off a roll can also be used instead of bag filters. If the roll filter is made as a disposable filter, it is respectively wound off the roll by a corresponding length on the reversal of direction of the fan 1. However, a multifilter can also be used with which the control winds the filter on and off cyclically so that always the same section of the filter is active in the one and the other blowing direction 6, 7 of the fan 1. The control can furthermore be made such that on a specific degree of loading of the filter the roll is further rotated so far that two new sections are available for the rolling onto and off the roll.
The necessity of a change of filter or of a further rotation of a roll filter can be detected via a suitable control in dependence on the pressure. The control can indicated this and/or initiate an automatic change or an automatic further rotation of the filter.
The necessity of a filter change can, however, also be detected by the passing of time instead of via the pressure. The time span in particular results from experience values and can be preset. The time span can, however, also be changeable and be predetermined by the user.
The heat exchangers 2 can be made with lamellae as is described, for example, in DE 19709 176 C2. In another respect, conventional heat exchangers can, however, also be used such as are also used for simple fans blowing only in one direction. Conventional fans of this type can also be used for the fan 1.
In the variant shown in Fig. 2, the direction of rotation of the fan 1 is not reversible. Instead, the fan 1 is respectively connected to the two heat exchangers 2 via two alternative paths 4a, 4b and 4c, 4d. In each of these four sections 4a, 4b, 4c, 4d, a closing valve 8 is arranged which is opened or closed depending on the desired direction of flow of the gas flow 6 or 7.
To effect a flow in accordance with the arrows 6, the valves 8 in the sections 4a and 4d are open and those in sections 4b and 4c are closed.
Accordingly, to effect a flow in accordance with the arrows 7, the valves 8 in the sections 4b and 4c are open and those in sections 4a and 4d are closed. The fan 1 is here also preferably made as a radial blower, with it now, however, being able to be optimized better due to the single direction of rotation. In other respects, the design of this variant can be identical to the one previously described. The mode of operation is also identical with the exception of the switching over of the valves 8.
In the variant shown in Fig. 3, two fans la and lb are provided which are arranged parallel to one another and with opposite directions of rotation in a respective part section 4e, 4f of the gas guide 4. The one fan la or the other fan lb is switched on in dependence on the desired direction of flow 6 or 7. A flow is in particular generated in the direction of arrow 6 by switching on the fan 1 a and closing the section 4f and a flow in the direction of arrow 7 by switching on the fan lb and closing the section 4e.
The respective section 4e or 4f with the non-active fan la or lb is closed via closing valves 9 in the two sections 4e and 4f to avoid a false flow.
The two fans la and lb are in turn preferably made as radial fans and are optimized for their respective direction of flow. In other respects, the apparatus can also be made in the same manner as with variant 1 here.
The operating mode is also identical to that of variant 1 with the exception of the alternate activation of the two fans la and lb and the closing of the respectively other section 4f or 4e.
The variant shown in Figs. 4 to 6 includes a housing 10 with an inlet opening 11 and an outlet opening 12. A filter 3 is arranged behind the inlet opening 11 and behind it a fan 1 not reversible in its direction of rotation. The suction side of the fan 1 faces the inlet opening 11 of the housing 10. The blowing side of the housing 1 is adjoined by a valve 13 and behind this the two heat exchangers 2.
The housing 10 is divided by a partition wall 14 into two regions 15 and 16 which are in turn divided into a plurality of chambers 18 by partition walls 17. The filter 3 is arranged in a first chamber 18' behind the inlet opening 11 of the housing 10. It is followed by a chamber 182 which is separated from the first chamber by a partition wall 17'. The partition wall 17' has a passage opening 19 to which the suction side of the fan 1 is connected.
The chamber 18z with the fan 1 is bounded on the other side by a partition wall 172 in which the valve 13 is provided. As can in particular be recognized in Fig. 5, the height of the valve 13 amounts approximately to half the height of the partition wall 17z.
The partition wall 172 bounds a further chamber 183 with the first heat exchanger 2'; the first heat exchanger 2' a chamber 184 with the second heat exchanger 22; and the second heat exchanger 22 a further chamber 185 with the housing 10. All chambers 18' to 185 are located in the first housing section 15.
As can in particular be recognized in Fig. 6, a chamber 186 and a chamber 18' are formed in the second housing section 16 by a two-fold angled partition wall 173. The chamber 186 is connected to the chamber 185 via an opening 20. A further connection of the chamber 186 is present via a valve 21 to the chamber 182 in which the fan 1 is located. The chamber 18' is connected to the chamber 183 via a further valve 22 and to the chamber 186 via a further valve 26.
The angled partition wall 173 has a first vertical section 23 which is connected to the upper side of the housing 10, a horizontal section 24 adjoining it and a second vertical section 25 which adjoins the latter and is connected to the base of the housing 10. The height h, of the second vertical section is approximately half the size of the height hz of the first vertical section. In addition, the further valve 26 is provided in the second vertical section 25.
All the chambers 18 of the housing 10 are provided with their own condensate drain as is indicated by jagged arrows 27. In addition, the chambers are accessible, in particular for maintenance and repair work, via doors 28. Furthermore a LJV radiation device 29 is provided in the chamber 186 and the medium guided through the apparatus can be sterilized by it. Finally, a lighting can be provided in the housing 10.
In the variant shown in Figs. 4 to 6, the inlet opening is always formed independently of the throughflow direction of the two heat exchangers 2' 5 and 2~ by the opening 11 and the outlet opening is always formed by the opening 12 of the housing 10. To nevertheless permit a changing throughflow of the two heat exchangers 21 and 22, the valves 17, 21, 22 and 26 are provided. The valves 17 and 26 are open, the valves 21 and 22 closed, in contrast, for the throughflow of the apparatus in the first 10 direction marked by the arrow 6. The gas flow sucked in through the fan 1 moves from the inlet opening 11 via the filter 3 into the chamber 18' and from there into the chamber 182. Then the gas flow moves through the valve 13 into the chamber 183, flows through the first heat exchanger 2', which is inactive in this case and is defrosted by the warm gas flow, then 15 into the chamber 185, then through the active heat exchanger 22 by which the gas flow is cooled and then into the chamber 185. From there, the gas flow moves via the opening 20 in the wall 14 into the chamber 186 in which the gas flow is sterilized by the LJV radiation device 29. The gas flow then flows through the valve 26> moves into the chamber 18' and moves from there via the outlet opening 12 out of the housing 10 of the apparatus.
On the reverse operation of the apparatus in accordance with arrow 7, the valves 17 and 26 are closed, whereas the valves 21 and 22 are open. The gas flow sucked in by the fan 1 now no longer moves from the chamber 182 into the chamber 183 since the valve 13 is closed, but rather via the valve 21 into the chamber 186. From there, the gas flows on through the opening 20 in the wall 14 into the chamber 185, flows through the second, now inactive heat exchanger 22, with this being defrosted, further into the chamber 184, then through the first, now active heat exchanger 2' which cools the gas flow and then into the chamber 183. Since the valve 13 is closed, the gas flow moves from the chamber 183 via the valve 22 into the chamber 18' and flows out from there via the outlet opening 12 of the housing 10. The gas is also sterilized by the UV radiation device 29 in the chamber 186 in this operating direction. Instead of the arrangement of the radiation device in chamber 186, it can also be arranged in chamber 18', that is in the region of the outlet opening 12.
As can be recognized, the two heat exchangers 21 and 22 can selectively be flowed through in the one or the other direction 6, 7 in accordance with the operating mode described. A large cross-section of the heat exchangers and, on the other hand, a relatively low housing size overall is realized by the ratio of the housing section 15 to the housing section 16 of approximately 2 : 1. The cross-section changes thereby occurnng have no disadvantageous influence on the flow.
In all the variants shown, both heat exchangers 2, which can in particular be the evaporator or cooler of a coolant circuit, are flowed through by the total gas flow of the fan 1 or of the fans la, lb. This means that gas is sucked in by the one heat exchanger 2, which is then not activated, and is blown out by the other heat exchanger 2, which is activated. If the first heat exchanger 2 is iced, the sucked in gas is already cooled. With gas having a temperature above freezing point, the first heat exchanger 2 is thereby defrosted without any electrical or other defrosting equipment being necessary. The gas is further cooled in the desired manner in the active, second heat exchanger.
After reaching a specific degree of icing of the second heat exchanger 2 or after a predetermined extent of time, the flow direction is switched over in that, in the case of the variant of Fig. 1, the direction of rotation of the fan 1 is switched over. In the case of the variant of Fig. 2, the valves 8 are switched over for this purpose from their open position into their closed position and from their closed position into their open position. And in the case of the variant of Fig. 3, when the fan la was first switched on, it is switched off and the other fan lb is switched on and the closed valve 9 is opened and the open valve 9 is closed. If, on the other hand, the fan lb was switched on, the switch-over takes place in reverse accordingly. The switching over in the variant of Figs. 4 to 6 has already been described above.
In all cases, an overlapping operation is also possible in which both heat exchangers 2 are active for a specific period of time. The refrigerating capacity can thereby be increased in the short term, on the one hand, and the humidity content of the gas can thereby be regulated, on the other hand.
Filters 3, gas conducting passages 4 and also noise attenuation devices can be used due to the use of a radial fan with which a much higher pressing can be realized than with an axial fan. The noise of the refrigerating device can thereby be advantageously reduced.
In addition, means can be provided in the fan housing for sterilization, such as LJV radiation, and means for the injection of disinfectant, such as fruit acid.

Reference numeral list 1 fan la, lb fan 2, 2', Z heat exchangers 3 filter 4 gas guide 4a - 4f section of 4 5 pressure gage 6 direction of flow 7 direction of flow

8 valve

9 valve

10 housing

11 inlet opening

12 outlet opening

13 valve

14 wall

15 housing section

16 housing section

17' - 173 partition wall

18' - 18' chamber

19 opening

20 opening

21 valve

22 valve

23 vertical section

24 horizontal section

25 vertical section

26 valve 2~ condensate drain 28 door h, height of 25 h2 height of 23

Claims

1. A refrigerating apparatus, in particular for the cooling of refrigerating spaces, comprising two alternately activatable heat exchangers (2), in particular evaporators or coolers of a coolant circuit, and at least one fan (1) for the blowing of gas, in particular air, through the heat exchangers (2), characterized in that the heat exchangers (2) are arranged such that they can each be flowed through by the total gas flow of the fan (1) at least on activation.

2. A refrigerating apparatus in accordance with claim 1, characterized in that the two heat exchangers (2) are arranged behind one another in the direction of flow (6, 7).

3. A refrigerating apparatus in accordance with claim 2, characterized in that a first heat exchanger (2) is arranged in front of the fan or fans (1) in the direction of flow (6, 7) and a second heat exchanger (2) is arranged behind the fan or fans (1) in the direction of flow (6, 7).

4. A refrigerating apparatus in accordance with claim 1 or claim 2, characterized in that both heat exchangers (2) are arranged in front of the fan or fans (1) in the direction of flow (6, 7) or both heat exchangers (2) are arranged behind the fan or fans (1) in the direction of flow (6, 7).

5. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the heat exchangers (2) are arranged freely in front of or behind the fan or fans (1).

6. A refrigerating apparatus in accordance with any one of the claims 1 to 4, characterized in that gas conducting passages (4) are arranged between the fan or fans (1) and the heat exchangers (2).

7. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the fan or fans (1) and the heat exchangers (2) are arranged inside gas conducting passages.

8. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the fan or fans (1) and the heat exchangers (2) are arranged in a common housing.

9. A refrigerating apparatus in accordance with claim 8, characterized in that gas conducting passages can be connected to the housing at least at the gas outlet side.

10. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that a fan (1) with a reversible blowing direction is provided.

11. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the different directions of throughflow of the heat exchangers is realized by valve-controlled fluid guides.

12. A refrigerating apparatus in accordance with claim 11, characterized in that a fan (1) is provided whose blow side can be alternately connected to the first or second heat exchangers (2) via switchover valves (8) and corresponding gas conducting passages (4, 4a, 4b, 4c, 4d) and whose suction side can be connected to the respectively other heat exchanger (2).

13. A refrigerating apparatus in accordance with claim 11, characterized in that a fan (1) is provided whose suction side is connected to the inlet opening (11 and whose blowing side is alternately connected to the first or the second heat exchangers (2 1, 2 2); and in that the respectively other heat exchanger (21, 2 2) is connected to the one heat exchanger (2 1, 2 2), on the one hand, and to the outlet opening (12), on the other hand.

14. A refrigerating apparatus in accordance with claim 11, characterized in that two fans (1a, 1b) are provided which are arranged in opposite senses and parallel to one another and which are each connected to the two heat exchangers (2) via gas conducting passages (4a, 4e, 4f) and which are alternately activatable.

15. A refrigerating apparatus in accordance with claim 14, characterized in that the respectively non-active branch (4e, 4f) can be closed via a valve (9).

16. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the inlet opening (1) and the outlet opening (12) of the apparatus are each formed by the same opening (11, 12) irrespective of the throughflow direction (6, 7) of the heat exchangers (2 1, 2 2).

17. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the inlet opening (11) and the outlet opening (12) are always arranged on the same side of the apparatus, in particular next to one another.

18. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the fluid guides (18) extend in different planes at least sectionally.

19. A refrigerating apparatus in accordance with claim 18, characterized in that the fluid guides (18) extend over and beneath one another and/or next to one another.

20. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the cross-section of the fluid guides (18) is different in different sections (15, 16).

21. A refrigerating apparatus in accordance with claim 20, characterized in that the cross-section of the fluid guides (18) in the region of the heat exchangers (2 1, 2 2) is larger, in particular in a ratio of approximately 2 : 1, than before or behind them.

22. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that at least one radial fan is provided as the fan (1).

23. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that at least one filter (3) is provided in the gas conducting passages (4) andjor in the fan housing.

24. A refrigerating apparatus in accordance with claim 23, characterized in that at least one rotary filter is provided which can be rotated in dependence on the gas flow direction (6, 7).

25. A refrigerating apparatus in accordance with claim 23 or claim 24, characterized in that at least one roll filter is provided.

26. A refrigerating apparatus in accordance with claim 25, characterized in that the roll filter is made as a disposable filter.

27. A refrigerating apparatus in accordance with claim 25, characterized in that the filter roll can be wound on and off cyclically in dependence on the gas flow direction (6, 7).

28. A refrigerating apparatus in accordance with claim 27, characterized in that the filter can be further rotated by at least twice the filter length if required.

29. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that at least one pressure measuring device (5), in particular a pressure gage, is arranged in the gas conducting passages (4) and/or in the fan housing.

30. A refrigerating apparatus in accordance with claim 29, characterized in that a pressure measuring device (5) serves for the determination of the degree of icing of a heat exchanger (2).

31. A refrigerating apparatus in accordance with claim 29 or claim 30, characterized in that a pressure measuring device (5) serves for the determination of the necessity of a filter change.

32. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that means are provided which trigger a filter change or a further rotation of a roll filter after the end of a predetermined or predeterminable time and/or indicate the necessity of such a measure.

33. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that means are provided by which a reversal of the direction of flow (6, 7) of the gas through the heat exchangers (2) is triggered in dependence on a predetermined or predeterminable time.

34. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that means (29) for sterilization are provided in the gas conducting passages (4) and/or in the fan housing, in particular in the region of the outlet opening (12).

35. A refrigerating apparatus in accordance with claim 34, characterized in that means for sterilization by means of UV rays or ionization are provided.

36. A refrigerating apparatus in accordance with claim 34 or claim 35, characterized in that means are provided for the injection of disinfectant such as fruit acid.

37. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that a control for the activation of the heat exchangers (2) is provided which permits an overlapping operation.

38. A refrigerating apparatus in accordance with claim 37, characterized in that the control permits a regulation of the gas humidity.

39. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that noise attenuation devices are arranged in the fan housing and/or in the gas guides (4).

40. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the speed of rotation of the fan or fans (1) can be regulated.

41. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that the housing (10) has a plurality of chambers (18' to 18') which are each accessible via their own access opening, in particular a door (28).

42. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that each chamber (18' to 18') has its own condensate drain (27).

43. A refrigerating apparatus in accordance with any one of the preceding claims, characterized in that a lighting device is provided in the housing (10).