Reversible cycle cooling unit

Description

[0001] The field of this invention is reversible cycle cooling unit.

[0002] In particular, this invention is used on a reversible cycle cooling unit for centralised air-conditioning systems, to which this text will explicitly refer without loss in generality.

[0003] As known from GB-A-2130747, which reveals a cooling unit according to the preamble of claim 1, centralised air-conditioning systems normally comprise of a cooling unit that cools the liquid circulating in the radiators and/or fan-coils that belong to the system, so as they subtract heat from the inside environment in order to lower the air temperature inside the different rooms of the building where they are placed.

[0004] In air conditioning systems of larger dimension, the cooling unit/s work/s according to the heat pump principle and can cool or heat the liquid circulating inside the hydraulic circuit of the air-conditioning system, so as the radiators and/or the fan-coils, selectively and according to the season, subtract or give heat to the ambient without using a boiler.

[0005] On request, said cooling units can change over from one working modality to the other one and, therefore, comprises of two different refrigerant circuits, so as the refrigerant can flow in proper sequence to said two heat exchangers belonging to the unit, so as the unit can selectively work in one of the two possible operation modalities.

[0006] Unfortunately, in reversible cycle cooling unit known at present, cooling circuits normally used cause a lot of problems: first of all, after the change over from one operation modality to the other, it's particularly difficult to empty the components of the circuit in which the refrigerant does not flow any more, obliging, therefore, the manufacturer to over-charge with refrigerant the cooling unit in order to have always the sufficient quantity of refrigerant flowing into the cooling circuit, so as the cooling unit can properly work in both operating modality.

[0007] Obviously, due to the overcharging of refrigerant, the total production cost of the unit increases. Moreover, the risks of pollution become higher in case of leakage of refrigerant.

[0008] Besides, the increasing of refrigerant charged in the unit is often detrimental to the lubrication of the compressor, compromising its reliability in the long run. Another drawback of cooling units known at present is that forcing the refrigerant to flow through said storage tank in both working modalities, the total thermodynamic efficiency of the unit decreases at least in one of the two working modalities.

[0009] The purpose of this invention is therefore to make a reversible cycle cooling unit free from the above mentioned drawbacks.

[0010] According to the present invention, there is provided a cooling unit with reversible cycle comprising a first heat exchanger in which the refrigerant exchanges heat with the outside environment; a second heat exchanger in which said refrigerant exchanges heat with a generic liquid, a compression device for compressing said refrigerant, and a distributor for distributing said refrigerant and which selectively connects said compression device to said first and said second heat exchangers; said cooling unit also comprising a first joint pipeline which connects said first heat exchanger to said second heat exchanger and, along said first joint pipeline, a first expansion valve in which said refrigerant quickly expands; said cooling unit being characterized in that it also comprises a first check valve and an intercepting valve in sequence along said first joint pipeline prior to said first expansion valve, a drier filter positioned along said first joint pipeline between said first check valve and said intercepting valve, and a by-pass circuit of said first expansion valve; said by-pass circuit comprising a second joint pipeline with a first extremity connected to said first joint pipeline, between said second heat exchanger and said first expansion valve, and the second extremity connected to said first joint pipeline, between said check valve and said intercepting valve, a refrigerant storage tank positioned along the second joint pipeline, and finally a second check valve positioned along the second joint pipeline, between said refrigerant storage tank and said first joint pipeline; the first check valve being oriented in order to permit the refrigerant to flow only from said first heat exchanger towards said second heat exchanger; the second check valve being oriented in order to permit the down flow of the refrigerant only from the refrigerant storage tank to said first joint pipeline; the intercepting valve being capable of selectively do not permit the refrigerant to flow in the first joint pipeline through said first expansion valve; said cooling unit also comprising a third joint pipeline which connects said first heat exchanger to said first joint pipeline between the drier filter and the intercepting valve, and at least a second expansion valve positioned along said third joint pipeline.

[0011] This invention will be now described with reference to the attached drawings, that shows one example, but is in no way limited to the example mentioned in this document but by the attached claims.

° Figure 1 shows in a schematic way a reversible cycle cooling unit made according to the precepts of this invention;

° Figures 2 and 3 show, in a schematic way, the cooling unit of figure 1 in the two possible different operational modes.

[0012] Referring to figure 1, number 1 shows a whole reversible cycle cooling unit that can be used in building centralized air-conditioning systems.

[0013] These systems usually include a series of radiators and/or fan-coils properly distributed in the building inside of which the air temperature has to be controlled, and, at least, a cooling unit able to heat or cool the heat conveying liquid (normally water) conveyed to said radiators and/or fan-coils, through the hydraulic circuits, in the air-conditioning system itself.

[0014] The reversible cycle cooling unit 1 works according to the heat pump principle that permits to transfer heat from one environment to another, using a refrigerant in gas state in a closed thermodynamic cycle as, for example, a Carnot cycle. The thermodynamic principles used in heat pump units are widely known and they will not be further explained.

[0015] The cooling unit 1 comprises of a first heat exchanger 2, with which the refrigerant exchanges heat with the outside environment; a second heat exchanger 3, with which the refrigerant exchanges heat with the heat conveying liquid that flows into the radiators and/or to the fan-coils of the hydraulic circuit of the air-conditioning system; and a refrigerant compression device 4 for compressing said refrigerant (for example with an adiabatic compression), so that the pressure of the refrigerant outgoing the compression device 4 is higher than the pressure that the refrigerant had in the suction side inlet of the compression device itself. The cooling unit 1 also comprises a refrigerant distributor 5, that selectively connects, under control and in the proper way, the delivery 4a and the suction side 4b of the compression device 4 to the heat exchangers 2 and 3.

[0016] More in detail, distributor 5 selectively connects the delivery 4a and the suction 4b of the compression device 4 to said heat exchangers 2 and 3, so as to enable the cooling unit 1, on choice, to chill the heat conveying liquid circulating in the hydraulic circuit of the air-conditioning system, transferring heat to the outside environment, or to heat the heat conveying liquid circulating in the hydraulic circuit of the air-conditioning system, taking heat from the outside environment.

[0017] The heat exchangers 2 and 3 and the compression device 4 are widely used in this field and so, here, are not described in details.

[0018] Referring to figure 1, the heat exchanger 2 permits the heat exchange between the refrigerant and the outside environment in such a way as to cause the condensation or the evaporation of the refrigerant, depending on the difference in temperature between the refrigerant and the external temperature.

[0019] Moreover, if the refrigerant that flows into the heat exchanger 2 has a higher temperature than the outside environment, heat exchanger 2 permits the refrigerant to cool progressively transferring heat to the outside environment, with the possibility to change state from gas to liquid.

[0020] On the contrary, in the case that the refrigerant that goes into heat exchanger 2 has a lower temperature than the outside environment, heat exchanger 2 permits the refrigerant, that flows through the exchanger itself, to warm up progressively taking heat from the outside environment, with the possibility to change its state from liquid to gas.

[0021] In the illustrated example, heat exchanger 2 is provided with two inlets and two outlets for the refrigerant that are properly connected between them in order to have, inside heat exchanger 2, a cooling path, flowing into which the refrigerant with high temperature progressively cools giving heat to the outside environment with the possibility to change state from gas to liquid, and a heating path, flowing into which the refrigerant with low temperature grows progressively hot taking heat from the outside environment with the possibility to change state from liquid to gas.

[0022] In the illustrated example, more in detail, heat exchanger 2 is constituted of a forced air heat exchanger for external installation of known kind, that is provided with an inlet 2a for the high temperature refrigerant in gas state, with an outlet 2b for the low temperature refrigerant in liquid state, with an inlet 2c for the low temperature refrigerant in liquid state, and finally with an outlet 2d for the high temperature refrigerant in gas state that is the inlet 2a.

[0023] The inlet 2a and the outlet 2b of the heat exchanger 2 are the limits of the cooling path and are connected the first directly to the distributor 5 by a first joint pipeline 6, and the second directly to heat exchanger 3 by a first joint pipeline 7, comprising of a check valve 8, a drier filter 9 and an intercepting valve 10, connected in series.

[0024] The check valve 8 is orientated in order to permit the downflow of the refrigerant only from heat exchanger 2 to the drier filter 9. The intercepting valve 10 selectively does not permit the flowing of the refrigerant along the pipeline 7 from said drier filter 9 to the heat exchanger 3.

[0025] The inlet 2c and the outlet 2d of the heat exchanger 2 are, instead, the limits of the heating path, and are connected the first directly to the heat exchanger 3 by a joint pipeline 11 that joins itself to pipeline 7 between the drier filter 9 and the intercepting valve 10, and the second directly to distributor 5 by pipeline 6.

[0026] Referring to figure 1, heat exchanger 3 permits the refrigerant to exchange heat with the heat conveying liquid that is flowing into the radiators and/or fan-coils, so as to increase or reduce the temperature of the refrigerant, taking away or giving heat to the heat conveying liquid circulating in the air-conditioning system.

[0027] Moreover, when the refrigerant that goes into heat exchanger 3 has a higher temperature than the heat conveying liquid, the heat exchanger 3 permits the refrigerant that flows through the heat exchanger to cool progressively giving heat to the heat conveying liquid that in this way warms up.

[0028] On the contrary, when the refrigerant that goes into heat exchanger 3 has a lower temperature than the heat conveying liquid, heat exchanger 3 permits the refrigerant that flows through the heat exchanger to warm up progressively absorbing heat from the heat conveying liquid that in this way cools.

[0029] Heat exchanger 3 comprises of a primary circuit through which flows the heat conveying liquid circulating into the radiators and/or to the fan-coils of the system, and a secondary circuit through which flows the refrigerant.

[0030] The inlet and the outlet of the primary circuit, later on indicated with 3a and 3b, are connected to the hydraulic circuit of the air-conditioning system, whereas the inlet and the outlet of the secondary circuit, later on indicated with 3c and 3d, are connected one directly to heat exchanger 2 and the other to the distributor 5.

[0031] Moreover, inlet 3c of heat exchanger 3 is directly connected to pipeline 7, whereas outlet 3d is connected to distributor 5 by the joint pipeline 13.

[0032] Referring figure 1, the compression device is, as said before, of known kind and consists of a traditional screw or piston (or similar) compressor 14 for compressing gas state refrigerants , and a liquid/gas separating tank 15, positioned upstream of the suction inlet of compressor 14 in order to avoid the refrigerant in liquid state to reach the suction inlet of compressor 14, damaging it irreparably. The compression device 4 also comprises of a check valve 16 positioned immediately downstream of the delivery outlet of compressor 14 and orientated in order to permit the refrigerant to flow only in outlet from the compressor 14 itself.

[0033] Referring to figure 1, distributor 5 of unit 1 comprises of a traditional reversing four way valve with electrical control.

[0034] The reversing four way valve 17, in particular, is a slide valve and is provided with four inlets, selectively connectable directly to one another in pairs, and it is made to operate alternatively in two distinct operative configurations enabling two of the four inlets of the valve to be directly and alternatively connected either to one or the other of the remaining two inlets of the valve.

[0035] With other words, the reversing four way valve 17 comprises of two primary and two secondary inlets.

[0036] The primary inlets can be connected selectively and alternatively to all of the secondary inlets of the valve, without coming into direct contact with each other.

[0037] Moreover, the reversing four way valve 17 is provided with four inlets, indicated respectively with 17a,17b,17c,17d, and can take two different operative configurations: in the first, inlet 17a is in direct communication with inlet 17b and inlet 17c is in direct communication with inlet 17d; in the second, inlet 17a is in direct communication with inlet 17d and inlet 17c is in direct communication with inlet 17b.

[0038] For what concerns the connection between the reversing four way valve and the other components of the cooling unit 1, inlet 17a of the reversing four way valve 17 is connected with the delivery 4a of the compression device 5 by pipeline 18; inlet 17b is connected directly to pipeline 6; inlet 17c is connected by pipeline 19 directly to the suction side 4b of the compression device 4; finally inlet 17d of the reversing four way valve 17 is directly connected to pipeline 13 that comes from heat exchanger 3.

[0039] Is obvious that inlets 17a and 17c are primary inlets of the reversing four way valve 17, and that inlets 17b and 17d are secondary inlets of the valve.

[0040] With reference to figure 1, the cooling unit 1 finally comprises of at least one expansion valve 20 that permits the quick expansion of the refrigerant, in order to complete the closed thermodynamic cycle in contrast with the compression device 4 that causes, on the contrary, the quick compression of the refrigerant.

[0041] Moreover, expansion valve 20 permits the quick expansion of the flowing refrigerant, in order to make the pressure of the refrigerant outgoing from expansion valve 20 much lower that the pressure that the refrigerant had in the inlet of the valve itself, and it is obviously positioned along the pipeline that connects the heat exchanger, at which the refrigerant coming out from the compression device cools, to the heat exchanger at which the refrigerant warms up before returning to the compression device 4.

[0042] In the illustrated example, in particular, cooling unit 1 comprises of three expansion valves 20: the first is positioned along pipeline 7 between inlet 3c of the heat exchanger 3 and the intercepting valve 10, whereas the second and the third expansion valves 20 are positioned along pipeline 11 in correspondence of inlet 2c of the heat exchanger 2.

[0043] Referring to figure 1, the cooling unit 1 finally comprises of also a by-pass circuit 21 of the expansion valve 20 positioned along the pipeline 7.

[0044] The by-pass circuit 21 comprises of a joint pipeline 22, that has the first extremity connected in offtake to pipeline 7 between inlet 3c of heat exchanger 3 and expansion valve 20, and the second extremity connected in offtake to pipeline 7 between check valve 8 and drier filter 9; a refrigerant storage tank 23 positioned along the joint pipeline 22; and finally a check valve positioned on pipeline 22 between the storage tank 23 and pipeline 7.

[0045] The check valve 24 is orientated in order to permit the downflow of the refrigerant only from the storage tank 23 to drier filter 9, but not vice-versa.

[0046] The working of the cooling unit 1 will be now described under the hypothesis that this is initially in the summer season configuration. This means, cooling unit 1 operates only to cool the heat conveying liquid circulating in heat exchanger 3 and transferring heat to the outside environment by heat exchanger 2.

[0047] In this working mode, the intercepting valve 10 is in opened position, and the reversing four way valve 17 is in the first operative position so that inlet 17a is in direct communication with inlet 17b and inlet 17c is in direct communication with inlet 17d.

[0048] With reference to figure 2, the refrigerant outgoing from compressor 14 flows through check valve 16 and reaches inlet 17a of the reversing four way valve 17 of the distributor 5. Once it has reached inlet 17a, the refrigerant flows through the reversing four way valve 17 and goes out from inlet 17b, then flows along pipeline 6 as far as inlet 2a of the heat exchanger 2, at which it gives heat to the outside environment, cooling itself.

[0049] The refrigerant comes out from the heat exchanger 2 through outlet 2b and, flowing along pipeline 7, flows through, in sequence, the check valve 8, drier filter 9, intercepting valve 10 and finally expansion valve 20, at which it is subjected to a quick expansion before going in inlet 3c of heat exchanger 3.

[0050] Inside heat exchanger 3 the refrigerant takes heat from the heat conveying liquid circulating in the hydraulic circuit of the air-conditioning system, to flow, after, along pipeline 13 to distributor 5 and from here again to compressor 14, upon passage in the liquid/gas separator tank 15.

[0051] Moreover, the refrigerant leaving heat exchanger 3 flows through pipeline 13 as to reach inlet 17d of reversing four way valve 17, goes out from inlet 17c of the valve itself and from here flows through pipeline 19 as far as the liquid/gas separating tank 15 which communicates directly with the suction of compressor 14.

[0052] It is appropriate to underline that, in this working mode, outlet 3d of heat exchanger 3 is in direct communication with suction side 4b of the compression device 4, the latter being able to suck by depression not only the refrigerant flowing in pipeline 7, but also all the refrigerant accumulated in the by-pass circuit 21, comprising of pipeline 22 and storage tank 23. Taking into consideration the orientation of check valve 24, it's clear that the emptying of by-pass circuit 21 doesn't cause any obstacle to the normal downflow of the refrigerant from heat exchanger 2 along pipeline 7.

[0053] With reference to figure 3, in case that it is necessary to warm up the heat conveying liquid circulating in the hydraulic circuit of the air-conditioning system, that is, if it's necessary to switch from the summer season configuration to the winter season configuration, the electronic control device (not illustrated) that controls the working of the cooling unit 1 closes the intercepting valve 10 and enables the commutation of the reversing four way valve 17 from the first to the second operative position.

[0054] In this case, the refrigerant leaving from compressor 14 flows through check valve 16, reaches inlet 17a of the reversing four way valve 17 of the distributor 5, goes out from inlet 17d of the reversing four way valve 17, flows through pipeline 13 and goes in the heat exchanger 3 through the outlet 3d.

[0055] The refrigerant, after having given heat to the heat conveying liquid circulating in the heat exchanger 3, goes out from inlet 3c of heat exchanger 3; flows through pipeline 7 and goes into the by-pass circuit 21 before reaching the expansion valve 20 in pipeline 7; flows through pipeline 22 flowing through, in sequence, the storage tank 23 and the check valve 24; finally reaches again pipeline 7 upstream the drier filter 9.

[0056] At these conditions, the intercepting valve 10, in the closed position, obstructs the flow of the refrigerant along pipeline 7 where the expansion valve 20 is positioned.

[0057] When the pipeline 7 is reached again, the refrigerant goes through drier filter 9 and flows in pipeline 11 to the expansion valve 20 reaching inlet 2c of the heat exchanger 2. As in previous cases, flowing through the expansion valve 20, the refrigerant is subjected to a quick expansion (for example to an adiabatic expansion) with following quick drop of its temperature.

[0058] When flowing in heat exchanger 2, the refrigerant warms up taking heat from the outside environment; the refrigerant goes out from the exchanger 2 through inlet 2d and flows along pipeline 6 as far as the inlet 17b of the reversing four way valve 17.

[0059] After entering in four way valve 17, the refrigerant goes out from inlet 17c of the valve, flows through pipeline 19 as far as the liquid gas separator 15 that communicates directly with the suction side of the compressor 14.

[0060] As in the previous case, in winter season working mode outlet 2d of heat exchanger 2 is in direct communication with the suction side 4b of the compression device 4, so as to suck by depression the refrigerant coming from pipeline 11.

[0061] The benefits of the cooling unit 1 are evident: the new position of the check valve 8, of the drier filter 9, of the intercepting valve 10 and of the expansion valve 20 along the pipeline 7 and the by-pass circuit 21 made in this way, enable the quick and complete emptying of the components of the circuit that are not used when in summer season working mode, that is the by-pass circuit 21. This design enables to minimize the quantity of refrigerant used in the unit.

[0062] Another benefit of cooling unit 1 above described and illustrated is that this design enables the refrigerant to go through the tank 23 only if it's necessary, that is, during the winter season working mode, improving a lot the efficiency of the unit.

Claims

1. A cooling unit (1) with reversible cycle comprising a first heat exchanger (2) in which the refrigerant exchanges heat with the outside environment, a second heat exchanger (3) in which said refrigerant exchanges heat with a generic liquid, a compression device (4) for compressing said refrigerant, and a distributor (5) for distributing said refrigerant and which selectively connects said compression device (4) to said first (2) and said second (3) heat exchangers;
said cooling unit (1) also comprising a first joint pipeline (7) which connects said first heat exchanger (2) to said second heat exchanger (3) and, along said first joint pipeline (7), a first expansion valve (20) in which said refrigerant quickly expands;
said cooling unit (1) being characterized in that it also comprises a first check valve (8) and an intercepting valve (10) in sequence along said first joint pipeline (7) prior to said first expansion valve (20), a drier filter (9) positioned along said first joint pipeline (7) between said first check valve (8) and said intercepting valve (10), and a by-pass circuit (21) of said first expansion valve (20);
said by-pass circuit (21) comprising a second joint pipeline (22) with a first extremity connected to said first joint pipeline (7), between said second heat exchanger (3) and said first expansion valve (20), and the second extremity connected to said first joint pipeline (7), between said check valve (8) and said intercepting valve (10), a refrigerant storage tank (23) positioned along the second joint pipeline (22), and finally a second check valve (24) positioned along the second joint pipeline (22), between said refrigerant storage tank (23) and said first joint pipeline (7);
said first check valve (8) being oriented in order to permit the refrigerant to flow only from said first heat exchanger (2) towards said second heat exchanger (3); said second check valve (24) being oriented in order to permit the downflow of the refrigerant only from said refrigerant storage tank (23) to said first joint pipeline (7); the intercepting valve (10) being capable of selectively not permitting the refrigerant to flow in the first joint pipeline (7) through said first expansion valve (20);
said cooling unit (1) also comprising a third joint pipeline (11) which connects said first heat exchanger (2) to said first joint pipeline (7) between the drier filter (9) and the intercepting valve (10), and at least a second expansion valve (20) positioned along said third joint pipeline (11).

2. A cooling unit as claimed in Claim 1, characterized in that said second joint pipeline (22) is connected to said first joint pipeline (7) between said first check valve (8) and said drier filter (9).

3. A cooling unit as claimed in any one of the foregoing Claims, characterized in that said first heat exchanger (2) is directly connected to said distributor (5) by a fourth joint pipeline (6).

4. A cooling unit as claimed in any one of the foregoing Claims, characterized in that said second heat exchanger (3) is directly connected to said distributor (5) by a fifth joint pipeline (13).

5. A cooling unit as claimed in any one of the foregoing Claims, characterized in that said distributor (5) comprises a reversing four way valve (17) that has four inlets (17a, 17b, 17c, 17d) selectively connectable directly to one another in pairs.

Ansprüche

1. Kühlaggregat mit umkehrbarem Kreislauf, mit einem ersten Wärmetauscher (2), in welchem ein Kühlmittel Wärme mit der äußeren Umgebung austauscht, einem zweiten Wärmetauscher (3), in welchem das Kühlmittel Wärme mit einer allgemeinen Flüssigkeit austauscht, einer Kompressionseinrichtung (4) zum Komprimieren des Kühlmittels, und einem Verteiler (5) zum Verteilen des Kühlmittels, welcher wahlweise die Kompressionseinrichtung (4) mit dem ersten (2) und dem zweiten (3) Wärmetauscher verbindet;
wobei das Kühlaggregat (1) weiterhin eine erste Verbindungsrohrleitung (7), welche den ersten Wärmetauscher (2) mit dem zweiten Wärmetauscher (3) verbindet, und ein entlang der ersten Verbindungsrohrleitung (7) angeordnetes erstes Expansionsventil (20) aufweist, in welchem das Kühlmittel schnell expandiert;
wobei das Kühlaggregat (1) dadurch gekennzeichnet ist, dass es weiterhin ein erstes Rückschlagventil (8) und ein Sperrventil (10), welche hintereinander entlang der ersten Verbindungsrohrleitung (7) vor dem ersten Expansionsventil (20) angeordnet sind, einen Filtertrockner (9), welcher entlang der ersten Verbindungsrohrleitung (7) zwischen dem ersten Rückschlagventil (8) und dem Sperrventil (10) angeordnet ist, und einen Bypass-Kreislauf (21) des ersten Expansionsventils (20) aufweist;
wobei der Bypass-Kreislauf (21) eine zweite Verbindungsrohrleitung (22) mit einem ersten, mit der ersten Verbindungsrohrleitung (7) zwischen zweiten Wärmetauscher (2) und dem ersten Expansionsventil (20) verbundenen Ende und einem zweiten, mit der ersten Verbindungsrohrleitung (7) zwischen dem Rückschlagventil (8) und dem Sperrventil (10) verbundenen Ende, einen Kühlmittelspeichertank (23), welcher entlang der zweiten Verbindungsrohrleitung (22) angeordnet ist, und weiterhin ein zweites Rückschlagventil (24) aufweist, welches entlang der zweiten Verbindungsrohrleitung (22) zwischen dem Kühlmittelspeichertank (23) und der ersten Verbindungsrohrleitung (7) angeordnet ist;
wobei das erste Rückschlagventil (8) derart ausgerichtet ist, dass es dem Kühlmittel lediglich erlaubt, von dem ersten Wärmetauscher (2) zu dem zweiten Wärmetauscher (3) zu fließen; wobei das zweite Rückschlagventil (24) derart ausgerichtet ist, dass es lediglich den Abfluss des Kühlmittels von dem Kühlmittelspeichertank (23) zu der ersten Verbindungsrohrleitung (7) erlaubt; wobei das Sperrventil (10) dazu ausgebildet ist, wahlweise ein Fließen des Kühlmittels in der ersten Verbindungsrohrleitung (7) durch das erste Expansionsventil (20) zu verhindern;
wobei das Kühlaggregat (1) weiterhin eine dritte Verbindungsrohrleitung (11), welche den ersten Wärmetauscher (2) mit der ersten Verbindungsrohrleitung (7) zwischen dem Filtertrockner (9) und dem Sperrventil (10) verbindet, und wenigstens ein zweites Expansionsventil (20) aufweist, welches entlang der dritten Verbindungsrohrleitung (11) angeordnet ist.

2. Kühlaggregat nach Anspruch 1, dadurch gekennzeichnet, dass die zweite Verbindungsrohrleitung (22) mit der ersten Verbindungsrohrleitung (7) zwischen dem ersten Rückschlagventil (8) und dem Filtertrockner (9) verbunden ist.

3. Kühlaggregat nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der erste Wärmetauscher (2) direkt mit dem Verteiler (5) mittels einer vierten Verbindungsrohrleitung (6) verbunden ist.

4. Kühlaggregat nach wengistens einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass der zweite Wärmetauscher (3) direkt mit dem Verteiler (5) mittels einer fünften Verbindungsrohrleitung (13) verbunden ist.

5. Kühlaggregat nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass der Verteiler (5) ein Umschalt-Vierwegeventil (17) aufweist, das mit vier Einlässen (17a, 17b, 17c, 17d) versehen ist, die wahlweise direkt miteinander paarweise verbindbar sind.

Revendications

1. Unité de refroidissement (1) à cycle réversible, comportant un premier échangeur de chaleur (2) dans lequel le fluide réfrigérant échange de la chaleur avec l'environnement extérieur, un second échangeur de chaleur (3) dans lequel ledit fluide réfrigérant échange de la chaleur avec un liquide générique, un dispositif de compression (4) destiné à comprimer ledit fluide réfrigérant, et un distributeur (6) destiné à distribuer ledit fluide réfrigérant et qui raccorde sélectivement ledit dispositif de compression (4) auxdits premier (2) et second (3) échangeurs de chaleur ;
ladite unité de refroidissement (1) comportant aussi une première canalisation (7) de jonction qui raccorde ledit premier échangeur de chaleur (2) audit second échangeur de chaleur (3) et, le long de ladite première canalisation de jonction (7), un premier détendeur (20) dans lequel ledit fluide réfrigérant se détend rapidement ;
ladite unité de refroidissement (1) étant caractérisée en ce qu'elle comporte aussi un premier clapet de retenue (8) et une vanne d'interception (10) en séquence le long de ladite première canalisation de jonction (7) avant ledit premier détendeur (20), un filtre sécheur (9) positionné le long de ladite première canalisation de jonction (7) entre ledit premier clapet de retenue (8) et ladite vanne d'intersection (10), et un circuit de dérivation (21) dudit premier détendeur (20) ;
ledit circuit de dérivation (21) comportant une seconde canalisation de jonction (22) dont une première extrémité est raccordée à ladite première canalisation de jonction (7), entre ledit second échangeur de chaleur (3) et ledit premier détendeur (20), et la seconde extrémité est raccordée à ladite première canalisation de jonction (7), entre ledit clapet de retenue (8) et ladite vanne d'interception (10), un réservoir (23) de stockage de fluide réfrigérant positionné le long de la seconde canalisation de jonction (22) et, enfin, un second clapet (24) positionné le long de la seconde canalisation de jonction (22), entre ledit réservoir (23) de stockage de fluide réfrigérant et ladite première canalisation de jonction (7) ;
ledit premier clapet de retenue (8) étant orienté de façon à permettre au fluide réfrigérant de s'écouler uniquement dudit premier échangeur de chaleur (2) vers ledit second échangeur de chaleur (3) ; ledit second clapet de retenue (24) étant orienté de façon à permettre l'écoulement du fluide réfrigérant uniquement dudit réservoir (23) de stockage de fluide réfrigérant vers ladite première canalisation de jonction (7) ; la vanne d'interception (10) pouvant sélectivement ne pas permettre au fluide réfrigérant de s'écouler dans la première canalisation de jonction (7) à travers ledit premier détendeur (20) ;
ladite unité de refroidissement (1) comportant aussi une troisième canalisation de jonction (11) qui raccorde ledit premier échangeur de chaleur (2) à ladite première canalisation de jonction (7) entre le filtre sécheur (9) et la vanne d'interception (10), et au moins un second détendeur (20) positionné le long de ladite troisième canalisation de jonction (11).

2. Unité de refroidissement selon la revendication 1, caractérisée en ce que ladite deuxième canalisation de jonction (22) est raccordée à ladite première canalisation de jonction (7) entre ledit premier clapet de retenue (8) et ledit filtre sécheur (9).

3. Unité de refroidissement selon l'une quelconque des revendications précédentes, caractérisée en ce que ledit premier échangeur de chaleur (2) est raccordé directement audit distributeur (5) par une quatrième canalisation de jonction (6).

4. Unité de refroidissement selon l'une quelconque des revendications précédentes, caractérisée en ce que ledit second échangeur de chaleur (3) est raccordé directement audit distributeur (5) par une cinquième canalisation de jonction (13).

5. Unité de refroidissement selon l'une quelconque des revendications précédentes, caractérisée en ce que ledit distributeur (5) comporte une vanne d'inversion (17) à quatre voies qui a quatre entrées (17a, 17b, 17c, 17d) pouvant être raccordées sélectivement et directement entre elles par paires.

Drawing