Cooling coil for cold air generation with de-icing device

Abstract

A refrigeration coil (1) has a plurality of refrigerant guide tubes (4) arranged at intervals and parallel to one another, as well as a mechanical de-icing device designed as a scraper for scraping off ice formed on the refrigerant guide tubes (4). The scraper comprises scraper sleeves (6) which surround the refrigerant guide tubes (4) and have an elongated shape with end sections (7) that are arranged on opposite sides of a coupling section (26) and project beyond the coupling section (26) in the longitudinal direction of the refrigerant guide tubes (4).

Description

[0001] The invention relates to a cooling register for generating cold air, in particular for snowmaking systems, according to the preamble of claim 1.

[0002] Snowmaking systems are commonly used to produce artificial snow, which can be used, for example, on ski slopes. Snowmaking systems work by spraying water into a cold air stream, which cools the water droplets and converts them into snow, snow crystals, or ice crystals.

[0003] For cooling an air stream, cooling registers (heat or cold exchangers) in the form of finned cooling registers are known. Such finned cooling registers have a very large number of fins, which are cooled significantly by a suitable refrigerant, creating a large cooling surface for the passing air stream.

[0004] Icing is a major problem with cooling registers. As icing increases, the efficiency of the register is significantly reduced. This can even lead to the register failing completely. One way to counteract this problem with finned cooling registers is to use two such registers, of which only one is used during normal operation. If one register is iced up, the second register is put into operation while the frozen register is defrosted. However, this principle is associated with high costs and requires a lot of space. This principle is not economical for applications where the air to be cooled has a high level of humidity, as the register would ice up too quickly. This is particularly true for snowmaking systems, where the humidity is often between 65% and 100%.

[0005] Furthermore, CN109141071 discloses a heat exchanger with retractable tube bundles for the chemical industry that can automatically defrost itself. CN104197749A relates to a device for recovering latent heat from the freezing of cold water, based on continuous mechanical ice removal from the outside of the tube.

[0006] The invention is based on the object of creating a cooling register for generating cold air, which is particularly suitable for cooling air with a high level of humidity and which enables particularly effective defrosting.

[0007] This object is achieved according to the invention by a cooling register having the features of claim 1. Advantageous embodiments of the invention are described in the further claims.

[0008] The cooling register according to the invention has the following features: The cooling register comprises a plurality of refrigerant guide tubes arranged at a distance from and parallel to one another, which are designed to be cooled by a refrigerant flowing within the refrigerant guide tubes and to be surrounded by an air flow to enable a heat exchange between the refrigerant guide tubes and the air flow, cooling the air flow. The cooling register comprises a mechanical defrosting device designed as a scraping device for scraping off ice formed on the refrigerant tubes. The scraping device comprises scraping sleeves which surround the refrigerant guide tubes and are movable back and forth along the refrigerant guide tubes by a drive device. The scraping sleeves have an elongated shape and have two sleeve-shaped end sections, on each of which at least one scraping edge is formed, and a coupling section arranged between the end sections.by means of which the scraping sleeves are drive-coupled to the drive device, wherein the end sections are arranged on opposite sides of the coupling section and project beyond the coupling section in the longitudinal direction of the refrigerant guide tubes, wherein the end sections have outer ends delimiting the scraping sleeves and taper conically towards the outer ends, so that the end sections are wedge-shaped in longitudinal section.

[0009] The term "ice" is used in the broadest sense within the scope of the invention and is intended to include all types of frozen substances that can deposit on the refrigerant guide pipes, in particular snow.

[0010] The cooling register according to the invention is a smooth-tube heat exchanger, i.e., a heat exchanger comprising a stack or bundle of parallel refrigerant guide tubes with a smooth surface and a constant outer diameter along their length. The scraping device enables highly effective, continuous scraping of ice forming on the refrigerant guide tubes during ongoing operation of the cooling register. The cooling register can thus be used particularly economically and effectively, particularly for generating cold air at high humidity, for example, at a humidity of 60% to 100%, and thus particularly in snow-making systems and for generating snow at relatively high temperatures.

[0011] Because the scraper sleeves have two sleeve-shaped end sections protruding on opposite sides of the coupling section, the scraper sleeves are relatively thin-walled at their outer ends, meaning that the two end faces of the scraper sleeves are narrow or small in area. This means that the scraper sleeves push less ice in front of them during scraping. Ice accumulation is eliminated at the end of the scraper device's stroke. In particular, this prevents a large amount of scraped ice from being compressed and accumulating between the scraper sleeves and a strip or end plate located at the end of the stroke, through which the refrigerant guide tubes are routed.The fact that the sleeve-shaped end sections of the scraping sleeves protrude beyond the coupling section creates a large clearance between the ends and the coupling section of the scraping sleeves, which also prevents the accumulation of scraped ice there and promotes its entrainment by the airflow. Due to the arrangement of the end sections on both sides of the coupling section, these advantageous effects can be achieved equally in both directions of travel of the scraping sleeves.

[0012] In addition, the end sections have outer ends that delimit the scraping sleeves, with the end sections tapering conically toward the outer ends, so that the end sections have a wedge-shaped longitudinal section. The outer peripheral surface of the end sections preferably extends at an acute angle relative to the inner peripheral surface. This angle can be, for example, 2° to 20°, preferably 3° to 10°, particularly preferably 4° to 6°.

[0013] Preferably, the scraper sleeves have a stepped inner diameter, with the inner diameter being larger in the area between the end sections than in the area of ​​the end sections. This reduces friction between the scraper sleeves and the refrigerant guide tubes. The risk of jamming of the scraper sleeves and the required power of the drive device are reduced.

[0014] Preferably, the end sections each have a plurality of scraping edges, so that the scraping sleeves each have at least four scraping edges. This allows the ice to be scraped off particularly effectively.

[0015] It is particularly advantageous if the end sections comprise at least one peripheral scraping edge, preferably an inner and an outer peripheral scraping edge, and at least one further scraping edge arranged between the outer end and an inner peripheral edge of a contact surface of the end sections. This can further improve the scraping effect of the scraping sleeves.

[0016] Preferably, the further scraping edge is formed by a boundary wall of a groove that extends obliquely or arcuately from the outer end to the inner peripheral edge of the respective end section. This allows the ice scraped off by the further scraping edge to be removed from the space between the end section and the refrigerant guide tube via the groove.

[0017] The scraper sleeves preferably have an intermediate section arranged between the end section and the coupling section, with at least one wall opening adjacent to the end section. This allows ice scraped off by an inner peripheral scraping edge or another scraping edge of an end section to be discharged from the interior of the scraper sleeve to the outside through the wall opening.

[0018] Preferably, the scraper sleeves are engaged by means of a positive connection, rather than a rigid connection, with driver elements that can be moved back and forth by the drive device. This allows the scraper sleeves to align themselves simply and very precisely with the refrigerant guide tubes without becoming distorted or jammed by the driver elements. Furthermore, the driver elements and outer contours of the scraper sleeves can be manufactured with larger tolerances, thus making production simpler and more cost-effective.

[0019] Preferably, a gap-like space is provided between the scraper sleeves and the driver elements. This space allows the scraper sleeves and driver elements to expand and contract freely when temperatures change. This is particularly important when the scraper sleeves and driver elements are made of different materials with different expansion behaviors. For example, it is advantageous if the refrigerant guide tubes are made of stainless steel, the scraper sleeves are made of a softer material than the refrigerant guide tubes, particularly brass or a brass alloy, and the driver elements are made of a lightweight aluminum material.

[0020] Preferably, the driver elements consist of driver bars arranged between adjacent scraper sleeves. In particular, it is possible to provide horizontally arranged driver bars arranged between vertically adjacent rows of scraper sleeves. Alternatively, it is also possible to provide vertically arranged driver bars arranged between horizontally adjacent rows of scraper sleeves.

[0021] Preferably, the scraper sleeves on both sides of the carrier elements protrude beyond them in the longitudinal direction of the refrigerant guide tubes. This creates a gap or space between the ends of the scraper sleeves and the carrier elements, allowing the scraped ice to be carried along by the airflow without obstruction.

[0022] Preferably, the coupling section has a radially outwardly projecting coupling web that positively engages a groove in the driver elements. This allows a simple, positive connection to be created between the driver elements, in particular driver strips, and the scraper sleeves without rigidly connecting the scraper sleeves to the driver elements. Alternatively, it is also possible to provide the coupling web on the driver elements and the groove on the scraper sleeves.

[0023] Preferably, the coupling web is positioned centrally in the longitudinal direction of the scraper sleeve. This allows the driving force to be applied centrally and thus evenly to the scraper sleeve during both forward and reverse movements.

[0024] Preferably, the cooling register comprises several stacked rows of parallel refrigerant guide tubes, with a driver element arranged between each of two adjacent rows and engaging with the scraper sleeves of both rows. This allows the scraper sleeves to be coupled to driver elements on two opposite sides, thereby transferring the thrust forces evenly and without tilting moments to the scraper sleeves, and keeping the number of driver elements as low as possible.

[0025] Preferably, a heating device is provided on or in the drive elements to heat the drive elements. This allows ice that has accumulated in the space between the drive elements and the scraper sleeves to be quickly and easily melted away if necessary.

[0026] The heating device preferably comprises fluid guide lines for conducting a heated fluid, for example, hot water. This allows the defrosting process to be carried out in a simple and cost-effective manner. Other types of heating devices are readily possible, for example, an electric heating device.

[0027] Preferably, the cooling register has a holding element on each of two opposite sides, which can be moved back and forth by the drive device and to which the carrier elements are mounted in their end regions. This allows the carrier elements to be attached in a simple and space-saving manner and moved by means of the drive device. The holding elements are advantageously located at the outermost edge of the flow channel, thereby preventing or at least largely reducing turbulence in the air flowing through and impairing the cooling transfer.

[0028] Preferably, the refrigerant guide tubes are mounted with radial clearance, i.e., floating, in end plates designed as perforated plates. This allows the refrigerant guide tubes to expand and contract unhindered with temperature changes, thereby preventing material stresses and deformations of the refrigerant guide tubes and / or end plates. For this purpose, the refrigerant guide tubes can advantageously also be mounted in a floating manner in the longitudinal direction.

[0029] Preferably, the end plates are heated. This allows scraped ice, which has been pushed from the scraping sleeves to the end plates, to be easily melted and removed as needed.

[0030] The invention is explained in more detail below with reference to the drawings. They show: Figure 1: a spatial representation of a cooling register according to the invention; Figure 2: an enlarged view of the front lower corner area of Figure 1 ; Figure 3: a part of the cooling register with a representation of the carrier strips, whereby the refrigerant guide tubes and most of the scraper sleeves have been omitted for the sake of clarity; Figure 4: an enlarged lower section of Figure 3 ; Figure 5: a representation of the frame of the cooling register with the drive device for moving the scraping sleeves, whereby only three bottom-side, superimposed carrier strips are shown and the other carrier strips have been omitted; Figure 6: a lower part of Figure 5in an enlarged view, with some elements omitted; Figure 7: a longitudinal section through two superimposed refrigerant guide tubes with scraper sleeves and three driver strips, with the scraper sleeves shown in an end position; and Figure 8: a spatial representation of a second embodiment of a scraper sleeve.

[0031] Figure 1 shows an embodiment of a cooling register 1 for generating cold air in snowmaking systems.

[0032] The cooling coil 1 essentially has a cube-shaped or cuboid-shaped outer contour, which is defined by a housing frame 2. In the illustrated embodiment, the air inlet side is at the bottom and the air outlet side is at the top. The air to be cooled thus flows through the cooling coil 1 from bottom to top in the direction of arrows 3.

[0033] Another orientation of the cooling register 1, in which the air flow flows, for example, from top to bottom or in a horizontal direction through the cooling register 1, is also conceivable within the scope of the invention.

[0034] The cooling coil 1 comprises a plurality of straight refrigerant guide tubes 4 through which a refrigerant, for example, a glycol-water mixture, can be passed. The refrigerant guide tubes 4 are connected at one end to an external refrigeration machine (not shown), which cools the refrigerant to a low temperature of, for example, -30°C. The refrigerant cools the refrigerant guide tubes 4 accordingly, which then have a correspondingly cold surface.

[0035] In the illustrated embodiment, the refrigerant guide tubes 4 are arranged horizontally and parallel at a predetermined distance from one another such that they form a stack / bundle. A certain number of refrigerant guide tubes 4, for example, 10 to 100 refrigerant guide tubes 4, form a row 5 of refrigerant guide tubes 4 arranged horizontally next to one another, which lie in a certain horizontal plane. As can be seen from Figure 1 As can be seen, the cooling register 1 comprises a plurality, for example 20 to 100, of such superimposed rows 5 of refrigerant guide tubes 4.

[0036] The cooling register 1 can thus comprise a very large number, for example, from 100 to several thousand, of refrigerant guide tubes 4. The number is highly variable and is determined by the size of the cooling register 1 and the desired cooling capacity.

[0037] The refrigerant guide pipes 4 are preferably made of stainless steel pipes, which have a very precise, constant outer diameter with only very small tolerance deviations over their entire length.

[0038] The mutual spacing of the refrigerant guide pipes 4 in the vertical direction, ie the vertical spacing between the individual horizontal rows, is preferably the same and is advantageously 0.5 - 4 times, particularly preferably 0.8 - 2 times, in particular 0.9 - 1.2 times the outer diameter of the refrigerant guide pipes 4.

[0039] The mutual distance of the refrigerant guide pipes 4 in the horizontal direction can be the same or different from their vertical distance.

[0040] The cooling register 1 further comprises a mechanical defrosting device designed as a scraper for scraping off ice formed on the refrigerant guide tubes 4. This defrosting device is designed such that it can operate continuously and very effectively during ongoing operation of the cooling register 1, with the cooling and air flow through the cooling register 1 being impeded as little as possible.

[0041] Figure 7 shows two refrigerant guide pipes 4 and cooperating elements of the defrosting device, wherein a longitudinal section through the refrigerant guide pipes 4 is shown.

[0042] The defrosting device comprises, for each refrigerant guide pipe 4, a scraping sleeve 6 with opposite end sections 7 which tightly enclose the associated refrigerant guide pipe 4, a coupling section 26 which is arranged substantially in the middle of the scraping sleeve 6, and intermediate sections 9 arranged on both sides of the coupling section 26 which connect the end sections 7 to the coupling section 26.

[0043] The individual scraping sleeves 6 have no rigid connection relative to each other and can therefore align themselves solely on the refrigerant guide pipe 4.

[0044] The scraper sleeves 6 each have an elongated, tubular shape. The length of the scraper sleeves 6 can vary widely and can preferably be 2-8 times, particularly preferably 4-7 times, the outer diameter of the scraper sleeves 6 in their intermediate section 9. In the illustrated embodiment, the length of the scraper sleeves 6 is approximately 5 times the intermediate section outer diameter and approximately 6 times the outer diameter of the refrigerant guide tubes 4.

[0045] The wall thickness of the scraping sleeves 6 is small compared to their length, but can also vary widely. Preferably, the wall thickness in the intermediate sections 28 and end sections 7 is less than 10%, particularly preferably less than 5% of the total length of the scraping sleeve 6. In particular, the wall thickness in the sleeve sections 28, 7 can be approximately the same as the wall thickness of the refrigerant guide tubes 4.

[0046] As continues from Figure 7 As can be seen, the two opposite end sections 7 of each scraping sleeve 6 are sleeve-shaped and have frontal, outer ends 8 and a guide or contact surface 30 which bears against the refrigerant guide pipe 4 and encloses it tightly, i.e., without play or with only very slight play. The contact surface 30 is delimited on the one hand by an outer scraping edge 25a and on the other hand by an inner circumferential edge 31, which is formed by a diametrical step. The length of each contact surface 30 can be small compared to the total length of the scraping sleeve 6 and can be, for example, 1 to 20%, preferably 3 to 10%, particularly preferably 4 to 8% of the total length.

[0047] In the area of ​​the end sections 7, the outer diameter of the scraping sleeves 6 decreases continuously toward the ends 8, so that the end sections 7 have a conical shape. The end surfaces of the scraping sleeves 6 therefore have a smaller area than the cross-sectional area of ​​the coupling section 26. In particular, the wall thickness of the scraping sleeves 6 at the ends 8 can be smaller than or equal to the wall thickness of the refrigerant guide tubes 4. The end sections 7 are wedge-shaped in longitudinal section.

[0048] The circumferential scraping edge 25a of the scraping sleeves 6, provided at the front ends 8, is designed as a sharp-edged scraping edge that surrounds the associated refrigerant guide tube 4 with minimal or no play. When the scraping sleeves 6 are moved along the refrigerant guide tubes 4, the scraping edge 25a scrapes off the ice formed or deposited on the associated refrigerant guide tube 4.

[0049] The intermediate sections 9 preferably have a constant outer diameter at least over the major part of their length.

[0050] The coupling section 26 is formed by a coupling web 10, which protrudes radially beyond the outer contour of the intermediate sections 9 and end sections 7. The coupling web 10 can be a web that extends continuously around the circumference of the scraping sleeves 6. It is also possible for the coupling web 10 to consist of two partial webs or projections that protrude diametrically opposite one another upwards and downwards beyond the outer contour of the intermediate sections 9.

[0051] The coupling webs 10 serve to positively connect the scraper sleeves 6 to driver elements 11, which in the illustrated embodiment are designed as elongated driver bars 12 and extend transversely to the refrigerant guide tubes 4. The driver bars 12 serve to move the scraper sleeves 6 back and forth along the refrigerant guide tubes 4.

[0052] For this purpose, each row of scraper sleeves 6 arranged next to one another in a horizontal plane is positively coupled to two driver bars 12, with one driver bar 12 being arranged below a specific row of scraper sleeves 6 and another driver bar 12 being arranged above this row of scraper sleeves 6. With the exception of the bottom and top rows of scraper sleeves 6, one driver bar 12 is provided in the space between two vertically spaced rows of scraper sleeves 6, which interacts with both a lower row and an upper row of scraper sleeves 6.

[0053] The carrier strips 12 form a vertical stack, wherein a horizontal row 5 of refrigerant guide tubes 4 or scraper sleeves 6 is arranged in the space between each two vertically adjacent carrier strips 12.

[0054] The Figures 3 and 4show the stack of carrier strips 12, with a few scraper sleeves 6 shown between the three lowest carrier strips 12. In the Figures 3 and 4 the carrier strips 12 are in an end position of the displacement path.

[0055] As is particularly evident from Figure 7 As can be seen, the driver bars 12 are flat bar elements with a relatively low height. The height of the driver bars 12 is less than the vertical distance between vertically adjacent scraper sleeves 6. This creates a gap or space 13 between the driver bars 12 and the adjacent scraper sleeves 6, which allows the driver bars 12 and scraper sleeves 6 to freely expand in the event of temperature fluctuations, even in the vertical direction.

[0056] The driver strips 12 are in exclusively positive engagement with the scraper sleeves 6 such that, upon movement in the longitudinal direction of the refrigerant guide pipes 4, they move the scraper sleeves 6 accordingly, i.e., they slide on the refrigerant guide pipes 4. For this purpose, the driver strips 12 have grooves 14 which extend in the longitudinal direction of the driver strips 12, i.e., transversely to the longitudinal direction of the refrigerant guide pipes 4, and are designed such that the coupling webs 10 of the scraper sleeves 6 can engage in the grooves 14.

[0057] As from Figure 7As can also be seen, at least those carrier strips 12 arranged between vertically spaced rows of refrigerant guide tubes 4 or scraper sleeves 6 have a groove 14 on both their underside and their upper side. The lower and upper grooves 14 are preferably of identical design but open on opposite sides. This allows a carrier strip 12 to be positively coupled to both the scraper sleeves 6 located below and above.

[0058] The width of the carrier strips 12 is less than the length of the scraping sleeves 6. Preferably, the width of the carrier strips 12 is dimensioned such that the end sections 7 of the scraping sleeves 6 protrude beyond the carrier strips 12. This creates a distance or free space between the ends 8 of the scraping sleeves 6 and the carrier strips 12 for receiving scraped ice, over which the scraped ice can be carried along by the air flow without being obstructed by the carrier strips 12.

[0059] A heating device is provided within the drive rails 12 for heating the drive rails 12 in the event that defrosting is required. In the present embodiment, the heating device comprises a fluid guide line 15, which is arranged inside or at the edge of each drive rail 12. The fluid guide lines 15 preferably extend over the entire length of the drive rails 12. If necessary, a heated fluid, in particular hot water, can be conducted within the fluid guide lines 15, which transfers the heat to the drive rails 12. This allows ice that has accumulated on or near the drive rails 12, in particular in the gap 13, to be easily defrosted.

[0060] The Figures 5 and 6show the drive device for moving the scraping sleeves 6 and the holding structure for holding the driving strips 12, wherein for the sake of clarity the majority of the refrigerant guide tubes 4, scraping sleeves 6 and driving strips 12 are omitted.

[0061] As can be seen, the cooling register 1 has a holding element 16 on each of two opposite sides, which can be moved back and forth by the drive device, i.e., displaced in the longitudinal direction of the refrigerant guide pipes 4, and on which the carrier strips 12 are held by their opposite end regions. The two holding elements 16 extend vertically and over the entire height of the stack of carrier strips 12 and are located at the outermost edge of the air duct. The holding elements 16 are displaceable at their lower and upper ends on a sliding guide (not shown) of the housing frame 2 in the longitudinal direction of the refrigerant guide pipes 4.

[0062] The holding elements 16 comprise rake-like slotted strips 17 with horizontal slots arranged one above the other, wherein the end region of each carrier strip 12 engages in an associated horizontal slot and is thereby positioned. Figures 5 and 6 only the slit strip 17 assigned to the rear holding element 16 is shown, while the slit strip 17 assigned to the front holding element 16 is omitted for the sake of clarity.

[0063] The movement of the holding elements 16 and thus of the drive strips 12 is effected by a drive device 18 comprising two motors 19 arranged on either side of the cooling register 1. The motors 19 are fixedly mounted outside the housing frame 2 to a stationary support structure (not shown). The motors 19 rotate vertical shafts 20, which carry a stationary drive pinion 21 at their ends.

[0064] The drive pinions 21 mesh with horizontally guided racks 22, which are displaced in their longitudinal direction by the rotational movement of the drive pinions 21 relative to the housing frame 2. The racks 22 are connected to the holding elements 16 for the drive rails 12, so that the holding elements 16 are moved accordingly.

[0065] As can be seen from the Figures 6 and 7 As can be seen, the end regions of the refrigerant guide tubes 4 are guided through bores 24 arranged in end plates 23, whereby the refrigerant guide tubes 4 are radially positioned. The end plates 23 are thus designed as perforated plates and also form the end of the displacement path for the scraper sleeves 6.

[0066] In order to allow radial expansion of the refrigerant guide tubes 4 in the event of temperature fluctuations, the refrigerant guide tubes 4 are mounted in a floating manner in the end plates 23, preferably by means of an elastic O-ring 39, wherein the diameter of the bores 24 is larger than the outer diameter of the refrigerant guide tubes 4.

[0067] An axial expansion possibility of the refrigerant guide pipes 4 is achieved in that the refrigerant guide pipes 4 are loosely fixed to the outside of the end plates 23 by means of a washer 28 and two mutually counter-locked nuts 32, 33 which are thereby fixed to the refrigerant guide pipes 4 and which are screwed onto an end thread 34 of the refrigerant guide pipes 4.

[0068] Figure 7also shows fittings 35 and intermediate pieces 36, 37 for connecting the refrigerant guide pipes 4 to lines with which the refrigerant is supplied to or discharged from the refrigerant guide pipes 4.

[0069] Figure 8 shows a second embodiment of a scraping sleeve 6' according to the invention. The arrangement of this second embodiment within the cooling register 1 and the elements surrounding the scraping sleeve 6' are the same as described in connection with the first embodiment, which is shown in particular in Figure 7is shown. Furthermore, the basic structure and operation of the scraping sleeve 6' is very similar to that of the scraping sleeve 6, so that, unless otherwise described below, reference is made to the description of the first embodiment. Identical elements are provided with the same reference numerals. Corresponding, but modified elements are designated by the same reference numerals, but with an additional prime.

[0070] In this second embodiment, the intermediate sections 9' of the scraping sleeve 6' each have two diametrically opposed wall openings 29, which adjoin the sleeve-shaped end sections 7'. The wall openings 29 serve to allow scraped ice located within the scraping sleeve 6' to escape to the outside to be carried away by the air flow.

[0071] The wall openings 29 extend in the longitudinal direction of the scraping sleeve 6', preferably at least over the majority of the length of the intermediate sections 9'. In the circumferential direction of the scraping sleeve 6', each wall opening 29 extends over a circular arc of, for example, 90° to 120°. This results in the end sections 7' being connected to the coupling section 26 or a section 41 of the intermediate sections 9' adjacent to the coupling section 26 only by relatively narrow retaining strips 40, which extend in the longitudinal direction of the scraping sleeve 6' and form the intermediate sections 9' or a part thereof.

[0072] The number, size and arrangement of the wall openings 29 can be varied to a large extent.

[0073] The inner peripheral edge 31 of the contact surface 30' of the sleeve-like end sections 7', i.e., the edge closest to the coupling section 26, is formed as a circumferential scraping edge 25b in the same way as the peripheral scraping edge 25a. The contact surfaces 30' are therefore each delimited by two peripheral scraping edges 25a, 25b extending in the circumferential direction of the end sections 7', which are referred to here as outer scraping edges 25a and inner scraping edges 25b.

[0074] This allows each end section 7' ​​to scrape ice in both directions of movement of the scraper sleeves 6'. If the scraper sleeve 6' is Figure 8 shifted to the right, the outer scraping edge 25a of the right end section 7' ​​and simultaneously the inner scraping edge 25b of the left end section 7' ​​scrape off the ice. If the scraping sleeve 6' is Figure 8shifted to the left, the outer scraping edge 25a of the left end section 7' ​​and at the same time the inner scraping edge 25b of the right end section 7' ​​scrape off the ice.

[0075] A further improvement in the scraping effect can be achieved by additional scraping edges 38a, 38b, which are arranged in the region of the contact surface 30' and extend from the outer end 8 of the scraping sleeve 6' to the inner peripheral edge 31 of the contact surface 30'.

[0076] These additional scraping edges 38a, 38b are formed by the boundary edges of a groove 27, which runs obliquely or arcuately along the contact surface 30' and opens into both the outer end 8 and the inner peripheral edge 31. Ice scraped off by the scraping edges 38a, 38b can be discharged into the environment through the groove 27, either via the end face of the scraping sleeve 6' or via the wall openings 29.

[0077] Each end section 7' ​​preferably has a plurality of grooves 27 arranged over the circumference of the contact surface 30' such that the outer end of a groove 27 or scraping edge 38a, 38b overlaps with the inner end of an adjacent groove 27 or scraping edge 38a, 38b in the circumferential direction of the contact surface 30'. This allows the entire circumference of a refrigerant pipe 4 to be subjected to the scraping edges 38a, 38b when the scraping sleeves 6' are moved back and forth.

[0078] For all embodiments, the drive device 18 is controlled by means of a precise control system such that the scraping sleeves 6, 6' are moved in one direction until one end 8 of them strikes one of the end plates 23. Once this end position is reached, the drive device 18 is switched to move the scraping sleeves 6, 6' in the opposite direction until the opposite end position is reached.

[0079] By the scraper sleeves 6, 6' striking the end plates 23 and the thin-walled design of the ends 8, ice accumulations at the end plates 23 are squeezed off, so that ice accumulations can also be prevented in the area of ​​the end plates 23.

[0080] The end plates 23 can also be heated by means of a heater (not shown in detail) in such a way that scraped ice on or in the vicinity of the end plates 23 can be melted away.

[0081] It can be seen that for the cooling register 1 according to the invention, it is sufficient to provide only a single scraper sleeve 6, 6' for the entire effective length of each refrigerant guide tube 4. All scraper sleeves 6, 6' and carrier strips 12 form a single stack. Turbulence in the air flow through the cooling register 1 and the resulting heat transfer losses can thus be minimized. The cooling register 1 according to the invention operates with high efficiency and can be operated for extended periods without icing, especially at high humidity.

Claims

1. Refrigeration register (1) for cold air production, having the following features: - the refrigeration register (1) has a plurality of refrigerant supply pipes (4) arranged in a distance from and parallel to one another, which are designed to be cooled by means of a refrigerant flowing inside the refrigerant supply pipes (4) and to be flowed around by an air flow, in order to enable a heat exchange that cools the air flow between the refrigerant supply pipes (4) and the air flow, - the refrigeration register has a mechanical de-icing device designed as a scraping device for scraping ice formed on the refrigerant supply pipes (4), - the scraping device comprises scraping sleeves (6, 6') which surround the refrigerant supply pipes (4) and can be moved back and forth by a drive device (18) along the refrigerant supply pipes (4), - the scraping sleeves (6, 6') have a longitudinal form and have two sleeve-shaped end sections (7, 7') on which in each case at least one scraping edge (25a, 25b, 38a, 38b) is designed, and a coupling section (26) arranged between the end sections (7, 7'), by which the scraping sleeves (6, 6') are coupled in a driving manner to the drive device, - wherein the two end sections (7, 7') are arranged on opposite sides of the coupling section (26) and project over the coupling section (26) in the longitudinal section of the refrigerant supply pipes (4), characterised in that the end sections (7, 7') have outer ends (8) delimiting scraping sleeves (6, 6') and taper conically to the outer ends (8), such that the end sections (7, 7') are designed wedge-shaped in the longitudinal section.

2. Refrigeration register according to claim 1, characterised in that the scraping sleeves (6, 6') have a stepped inner diameter, wherein the inner diameter is greater in the region between the end sections (7, 7') than in the region of the end sections (7, 7').

3. Refrigeration register according to one of the preceding claims, characterised in that the end sections (7, 7') have several scraping edges (25a, 25b, 38a, 38b), such that the scraping sleeves (6, 6') each have at least four scraping edges (25a, 25b, 38a, 38b).

4. Refrigeration register according to claim 3, characterised in that the end sections (7') comprise at least one edge-side scraping edge (25a, 25b) and at least one further scraping edge (38a, 38b), which is arranged between the outer ends (8) and an inner circumferential edge (31) of a contact surface (30) of the end section (7').

5. Refrigeration register according to claim 4, characterised in that the further scraping edge (38a, 38b) is formed by a delimiting wall of a groove (27) that extends in an oblique or curved manner from the outer end (8) to the inner circumferential edge (31) of the respective end section (7').

6. Refrigeration register according to one of the preceding claims, characterised in that the scraping sleeves (6, 6') have an intermediate section (9, 9') arranged between the end section (7, 7') and the coupling section (26), having at least one wall opening (29) which borders the end section (7, 7').

7. Refrigeration register according to one of the preceding claims, characterised in that the scraping sleeves (6, 6') are in driving engagement by means of a positive locking connection and without a rigid connection to driver elements (11), which can be moved back and forth by the drive device (18).

8. Refrigeration register according to claim 7, characterised in that a gap-like intermediate space (13) is provided between the scraping sleeves (6, 6') and the driver elements (11).

9. Refrigeration register according to claim 7 or 8, characterised in that the driver elements (11) consist of driving strips (12) which are arranged between neighbouring scraping sleeves (6, 6').

10. Refrigeration register according to one of claims 7 to 9, characterised in that the scraping sleeves (6, 6') on both sides of the driver elements (11) project over these in the longitudinal direction of the refrigerant supply pipes (4).

11. Refrigeration register according to one of the preceding claims, characterised in that the coupling section (26) has a coupling web (10) projecting radially outwards, which engages with a groove (14) of the driver elements (11) in a positive locking manner.

12. Refrigeration register according to claim 11, characterised in that the coupling web (10) is arranged centrally when viewed in the longitudinal direction of the scraping sleeve (6, 6').

13. Refrigeration register according to one of claims 7 to 12, characterised in that the refrigeration register (1) has several rows (5), arranged one above the other, of refrigerant supply pipes (4) arranged parallel one alongside the other, wherein in each case a driver element (11) is arranged between two neighbouring rows (5) and is in driving engagement with the scraping sleeves (6, 6') of both rows (5).

14. Refrigeration register according to one of claims 7 to 13, characterised in that the driver elements (11) are each arranged in horizontal planes and between vertically adjacent scraping sleeves (6, 6').

15. Refrigeration register according to one of claims 7 to 14, characterised in that a heating device is provided on or in the driver elements (11) for warming the driver elements (11).

16. Refrigeration register according to claim 15, characterised in that the heating device comprises fluid supply lines (15) for supplying a warmed fluid.

17. Refrigeration register according to one of claims 7 to 16, characterised in that the refrigeration register (1) in each case has a retaining element (16) that can be moved back and forth by the drive device (18) on two opposing sides, on which the driver elements (11) are held in their end regions.

18. Refrigeration register according to one of the preceding claims, characterised in that the refrigerant supply pipes (4) are mounted with radial play in end plates (23) which are designed as perforated plates.

19. Refrigeration register according to one of the preceding claims, characterised in that the end plates (23) are heated.

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