The present invention relates to a refrigerating aggregate, especially designed for a refrigerating counter in which refrigerated articles such as bottles, cans and similar containers for drinks, tubes for caviar etc. are preferably continuously exposed to a cooling flow of cooled air, the evaporator of which cooling aggregate is located above a horizontal dividing plate, through which the hot-gas-tubes of the evaporator lead respectively to an underlying condenser and compressor underneath the dividing plate, which on its top side collects condensation water produced on the outside of the evaporator.

A refrigerating counter exhibiting these general constructional and functional features is, for example, described in NO patent No. 178.510, which at the outlet for the refrigerated articles has a supporting shelf, which radially, at its inner edge, has a possibly perforated supporting sidewall connected thereto, for the refrigerated articles. Components (evaporator, condenser, compressor) of the cooling aggregate are

located partly above, partly below a horizontal dividing plate. Above the horizontal dividing plate is an evaporator, whose hot-gas-tubes lead downwards through narrow holes in the horizontal dividing plate, underneath which, one of the hot-gas-tubes is connected to a compressor, while the other hot-gas-tube is connected to an air-cooled condenser.

Below the condenser and compressor which are located beside each other in the lower area of the refrigerating counter, below the horizontal dividing plate, is installed a horizontal hot plate, whereby a central, vertical through-tube with upwards and downwards open ends, extends through the horizontal dividing plate and ends by its lower free end slightly above the hot plate, the purpose of which is to evaporate condensation water supplied from above, coming from condensation on the outside of the evaporator.

This known refrigerating counter has functioned very satisfactorily in Nordic conditions as to ambient temperature and relative moisture.

By higher ambient temperatures and in particular higher relative moisture, the known refrigerating counter will have problems in handling the comparatively large amounts of condensation water produced on the outside of the evaporator. The hot plate will not be capable of evaporating more than part of the condensation water supplied from above. In a refrigerating aggregate the effect of the hot plate cannot be increased beyond a certain maximum value either. Heating the air-cooled condenser or compressor is not desirable. If not all of the condensation conveyed to the hot plate in the lower

area of the refrigerating counter is evaporated, through-holes must be formed in the lower portion of the base of the refrigerating counter to let out the excess water, so that it may be wiped off the floor of the shop, or maybe mount outlet piping for leading away the excess condensation water.

If said larger amounts of condensation can be dealt with, an increase in efficiency for the refrigerating counter may be counted on.

According to the present invention the purpose was to eliminate or substantially alleviate the above imperfections, drawbacks and limitations of application. A subordinate purpose which is integral with the purpose first mentioned, consists in reducing, at the same time, the temperature in the hot-gas-tubes from the evaporator to the compressor and condenser, respectively.

Said object has been realized by means of a device in a refrigerating counter, whose characteristic features will appear from the subsequent claims.

By heat exchange it is known in itself to provide helical tubes conveying a heat exchange fluid around another tube which conveys a second fluid, cf. DE 35 26 650, 30 15 905 and 25 14 342, and NO 139 455 and 89 592, which, however, do not concern the handling of large amounts of condensation water in connection with a refrigerating counter, in which the refrigerating aggregate comprises an evaporator arranged above a horizontal dividing plate, below which the condenser and compressor of the refrigerating aggregate are placed in mutual communication, each being connected to

the evaporator through hot-gas-tubes extending preferably without clearance through the horizontal dividing plate.

According to the invention condensation liquid is conveyed from above, it is temporarily being stopped and collected on top of the horizontal dividing plate formed with an upper surface sloping slightly downwards from a central point, and with at least one vertical through-hole for the inlet portion of a helical tube terminated level with the upper side of the dividing plate or somewhat below, whereby the dividing plate may have, in the area of the inlet portion of each helical tube, a recess into which condensation liquid may collect and run downwards into the respective helical tube. Each helical tube is wound around one of the hot- gas-tubes from the evaporator. The heat exchange thereby taking place, effects evaporation of at least part of the condensation water (any remainder may be evaporated at a lower level by means of a hot plate or the like) , at the same time less heat is generated in the hot-gas-tubes from the evaporator, which also is favourable. Further lower temperature is created in the lower area of the refrigerating counter, i.e. below the horizontal partition wall, where the air-cooled condenser and compressor possibly are located.

The recesses of the horizontal dividing plate for the upper inlet end portion of the helical tubes are preferably located at the outer periphery of the dividing plate for rapid and efficient lead-away of cold condensation water through the helical tubes for heat exchange with hot-gas-tubes conveying hot gas from the interior of the evaporator. Since one hot-gas-tube leads to the condenser and another to the compressor it is the most practical to arrange an external helical

tube to each hot-gas-tube, the helical tube being wound around the hot-gas-tube and having an upper open inlet end and a lower, open drain or outlet end. The heat exchange will according to the climatic conditions ensure evaporation of a major, though varying part of the condensation water, while it is still passing in the helical tubes, at the same time as the temperature of the hot gas flowing downwards in the two downward tubes from the interior of the evaporator, is reduced.

The device according to the invention, which essentially consists in a heat exchange between helical tubes with cold condensation water, produced on the outside of the evaporator, and hot-gas-tubes with hot gas emitted by the evaporator in the interior thereof, may advantageously be used in connection with a refrigerating counter as disclosed in NO 178.510. However, the heat exchanging device according to the invention may be used with the same advantages in a great number of different types and embodiments of refrigerating counters of the initially mentioned and similar kinds.

The invention is described in the following with reference to the figure in the accompanying single drawing and a section thereof, in the main corresponding to the refrigerating counter according to NO 178.510, provided with a heat exchanging device according to the present invention.

The non-limiting example of a possible embodiment which is illustrated in the figure of the drawing, comprises a central, upright tube 10 having a lower conical end portion 10' widening downwards and additionally extending concavely in an upward sloping direction.

Such a conical tube-end-portion 10* forms a 360° circularly running, supporting sidewall portion for bottles 12, which are to be continuously refrigerated, and are displayed for sale in a 360° open outlet formed by the radially inner supporting sidewall portion 10' and a 360° circularly running conical supporting shelf 14 which through its radially inner circumferential edge may join the radially outer edge of the supporting sidewall portion 10' which may be formed with through perforations IO' ¹ .

Within the supporting sidewall portion 10' extends a concentric upright tube portion 16, supporting and shoring the refrigerating counter. The radially outer edge portion of the supporting shelf 14 is angled and supportingly grips an angled upper portion of an outer wall 18.

The concentric tube portion 16 widens 16• downwards in the area of a fan 20 which is arranged to draw cold, cooled air from the area around an evaporator 22 which is part of the refrigerating aggregate of the refrigerating counter. Other main components are a condenser 24 and a compressor 26, each having one of the hot-gas-tubes 30 and 30', respectively, from the interior of the evaporator 22, arranged thereto.

The reference numeral 36 designates a hot plate or similar for evaporating any condensation water reaching the bottom area of the base of the refrigerating counter, while 38 indicates a dividing plate.

In broad outline, the refrigerating counter works as follows: Cold cooling air from the area around the evaporator 22 of the refrigerating aggregate is brought

by the fan 20 to flow upwards in the central tube 10 to the upper area thereof, in which the air leaves the tube 10 via a number of upper holes 10 ^{, , ,} . As a consequence of the greater specific weight of the cold air than of the warmer air, the cold cooling air sinks along the outside of the tube 10, more specifically within an annular space defined between the outer mantle surface of the tube 10 and the inner mantle surface of a lower part 40' of a cap-shaped hood 40', 40" .

Like the circularly running supporting shelf 14 and the supporting sidewall 10' forming the bottle display and outlet of the refrigerating counter, the lower part 40* of the hood 40', 40" forms a storage for bottles 12. The upper part 40" of the hood 40', 40" is vertically displaceable along the tube 10; its lower edge is designated 40"'. The upper hood portion 40" being in the upper position (not shown) , the storage is replenished with bottles 12 or other containers with refrigerated articles by way of the upper end of the lower, fixed hood part 40'.

The invention essentially consists in the vertical portion of each hot-gas-tube 30, 30' from the interior of the evaporator 22, below the horizontal dividing plate 38, being surrounded by a helical tube 42, 42* each, whose upper inlet end is located within or immediately below a recess 44, 44' each, so that condensation water from the outside of the evaporator 22 drips down on the upper side of the horizontal dividing plate 38, which preferably slopes from an upper mid-portion outwards towards the periphery, where the two recesses 44, 44' are formed, diametrically opposite one another.

Thereby, a highly favourable heat exchange takes place between the hot hot-gas-tubes 30, 30' and the hot gas on the one side, and the cold helical tubes 42, 42* and the cold condensation water on the other side. This leads to the essential part of the condensation water evaporating in the helical tubes 42, 42' and leaving these through the upper end. A possible remainder of condensation water may be evaporated on the lower hot plate 36. Furthermore, less generation of heat in the hot-gas-tubes 30, 30' is ensured, and thereby lower temperature in the bottom area below the partition wall 38, so that i.a. overheating the compressor is avoided.