Refrigeration appliance with multiple temperature zones

Abstract

A refrigeration appliance includes first and second temperature zones and a refrigerant circuit having first and second parallel branches. The first branch has a controllable first restriction point and a first heat exchanger for setting a temperature of the first temperature zone, and the second branch has a second restriction point and a second heat exchanger for setting a temperature of the second temperature zone. A branching point, at which the refrigerant circuit splits into the two branches, is configured as a separator for separating gas and liquid and the second branch is connected to a liquid outlet of the separator.

Claims

1. A refrigeration appliance or domestic refrigeration appliance, comprising: first and second temperature zones; a refrigerant circuit having a branching point at which said refrigerant circuit splits into first and second parallel branches, said branching point being configured as a separator for separating gas and liquid, said separator having a liquid outlet and a gas outlet; said first branch having a controllable first restriction point and a first heat exchanger for setting a temperature of said first temperature zone, said first branch being connected to said gas outlet of said separator; and said second branch having a second restriction point and a second heat exchanger for setting a temperature of said second temperature zone, said second branch being connected to said liquid outlet of said separator.

2. The refrigeration appliance according to claim 1, wherein said controllable first restriction point is configured to be set for a pressure drop being smaller than a pressure drop of said second restriction point.

3. The refrigeration appliance according to claim 1, wherein said first branch has a controllable third restriction point downstream of said first heat exchanger.

4. The refrigeration appliance according to claim 3, which further comprises a fourth restriction point disposed in said second branch downstream of said second heat exchanger.

5. The refrigeration appliance according to claim 1, wherein said separator has a hollow space, and an inlet, said liquid outlet and said gas outlet are formed at said hollow space.

6. The refrigeration appliance according to claim 5, wherein said liquid outlet is located lower than said gas outlet.

7. The refrigeration appliance according to claim 6, wherein a height difference between said liquid outlet and said gas outlet is adjusted to a fill level of said refrigerant circuit, permitting liquid refrigerant to overflow into said gas outlet if refrigerant backs up at said first restriction point.

8. The refrigeration appliance according to claim 5, wherein said gas outlet does not have an upwardly open cross-sectional surface.

9. The refrigeration appliance according to claim 5, wherein said separator contains a drying material.

10. The refrigeration appliance according to claim 9, wherein said drying material is accommodated in said hollow space.

11. The refrigeration appliance according to claim 10, wherein said inlet is disposed above said drying material and at least said liquid outlet is disposed below said drying material.

12. The refrigeration appliance according to claim 1, which further comprises a condenser connected upstream of said separator in said refrigerant circuit.

13. The refrigeration appliance according to claim 1, wherein said refrigerant circuit has a merging point at which said branches come together and an evaporator connected downstream of said merging point.

14. The refrigeration appliance according to claim 1, wherein said refrigerant circuit includes a speed-regulated compressor.

Description

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

(1) FIG. 1 is a schematic diagram of a refrigeration appliance according to the invention;

(2) FIG. 2 is an axial sectional view through a first embodiment of a separator of the refrigeration appliance;

(3) FIG. 3 is an axial sectional view through a second embodiment of the separator; and

(4) FIG. 4 is an axial sectional view through a third embodiment of the separator.

DETAILED DESCRIPTION OF THE INVENTION

(5) Referring now to the figures of the drawings in detail and first, particularly, to FIG. 1 thereof, there is seen a schematic diagram of a domestic refrigeration appliance with a heat-insulating housing 1, in which multiple temperature zones 2, 3, 4, each in the form of a compartment that can be closed by a door, are formed. The figure shows three such temperature zones but more can be provided.

(6) Each temperature zone 2, 3, 4 is assigned a heat exchanger 5, 6, 7, e.g. a plate heat exchanger of the roll-bond or tube-on-sheet type. Such a heat exchanger can be mounted in the interior of the compartment of the temperature zone 2, 3, 4 and exposed in front of a wall or in the wall, between a heat insulation layer and an inner container delimiting the compartment.

(7) Alternatively the temperature zones 2, 3, 4 can also be subdivided into a storage compartment and a heat exchanger chamber, with a fan 8 driving the exchange of air between the storage compartment and the heat exchanger chamber.

(8) The heat exchangers 5, 6, 7, together with a speed-regulated compressor 9, a condenser 10, a separator 11, multiple restriction points and a refrigerant line 12 connecting them, form a refrigerant circuit 13. A high-pressure segment of the refrigerant line 12 runs from the compressor 9 by way of the condenser 10 to the separator 11. The high-pressure segment splits into two branches 14, 15 at the separator 11. A restriction point 16, the heat exchanger 5 and a restriction point 17 are connected in series at the branch 14. A restriction point 18, the heat exchanger 6 and a restriction point 19 are connected in series at the branch 15. The branches 14, 15 come together again at a merging point 20. A low-pressure segment of the refrigerant line 12 extends from the merging point 20 by way of the heat exchanger 7 back to the compressor 9.

(9) The restriction points 16-19 keep the heat exchangers 5, 6 at a higher pressure than the heat exchanger 7. Since the lowest evaporation temperature thus prevails in the heat exchanger 7, the temperature zone 4 is typically used as a freezer zone. The permitted flow through the restriction points 18, 19 is selected in such a way that the evaporation temperature that results in the heat exchanger 6 is significantly higher than that of the heat exchanger 7 and the temperature zone 3 can be used as a standard or keep-fresh zone.

(10) The pressure drop at the restriction point 16 can be set between values that allow the temperature zone 2 also to be used as a standard or keep-fresh zone and almost zero. If the pressures in the condenser 10 and heat exchanger 5 are practically identical, the refrigerant does not only condense in the condenser 9 but also in the heat exchanger 5 and this heats the temperature zone 2 to a temperature above ambient temperature.

(11) A necessary consequence of condensation in the heat exchanger 5 is that not only liquid refrigerant but also vapor leaves the condenser 9 and presses forward in the refrigerant line. If the vapor entered the branch 15, it would expand again at the restriction point 18 and the work performed by the compressor 9 on the vapor would then be lost without any useful cooling effect. Conversely liquid refrigerant, passing from the condenser 9 into the branch 14, could no longer release any significant heat at its heat exchanger 5 but would also no longer be available to cool the temperature zone 3. The separator 11 ensures that the refrigerant that has already condensed in the condenser 9 is fed selectively to the heat exchanger 6, so that the latter benefits from the heat emitting capacity of the condenser 9 without loss, while the vapor is fed into the heat exchanger 5 and its heating capacity is thus not tangibly reduced by the upstream condenser 9.

(12) FIG. 2 shows an axial section through the separator 11 according to a first embodiment. A housing 21 is formed by a preferably metal pipe, which tapers at its ends to form an inlet 22 for a phase mixture originating from the condenser 9 and an outlet 23 for a liquid refrigerant. One end of the branch 15 is soldered into the outlet 23. An opening is drilled into the housing 21 about halfway up and enclosed by a sleeve to form an outlet 24 for refrigerant vapor. One end of the branch 14 is inserted into the outlet 24.

(13) The interior of the housing 21 is subdivided by a screen or grid 25 into an upper and a lower chamber 26, 27. The inlet 22 opens into the upper chamber 26, which is filled with a drying material 28. The outlets 23, 24 leave the lower chamber 27. The inflowing phase mixture therefore first passes through the drying material 28 in the separator 11, where moisture carried in the refrigerant that was originally adsorbed when the refrigerant circuit was assembled on the insides of the refrigerant line 12 and the heat exchangers 5, 6, 7 is absorbed and removed from the circuit. The granular drying material 28 and the grid 25 can at the same time also form a filter for trapping particulate contaminants from the refrigerant flow.

(14) Liquid refrigerant drips from the grid 25 to the bottom of the chamber 27 and leaves the separator by way of the outlet 23 exiting from there. In order to keep liquid refrigerant away from the outlet 24, it may be sufficient if the latter's cross-sectional surface is open to the side or at the bottom, as shown in FIG. 2, so that nothing can drip into it. In the example shown in FIG. 2 the grid 25 is enclosed by a peripheral apron 29, the lower edge of which forms a drip edge horizontally removed from the outlet 24. This prevents liquid refrigerant from flowing down the inner wall of the housing 21 and being carried by the vapor flow into the outlet 24.

(15) FIG. 3 shows a second embodiment of the separator 11. In this embodiment a housing 21 is also formed by a pipe with tapered ends but there is no need to drill an opening, since outlets 23, 24 for liquid and vapor are formed by ends of the branches 14, 15 inserted into a lower end of the housing 21. The branch 15 only reaches so far into the housing 21 that the outlet 23 is located at the lowest point of its interior and liquid refrigerant can flow away by way of the outlet 23 in its entirety. The branch 14 extends further into the housing 21 so that the outlet 24 is higher than the outlet 23.

(16) The outlet 24 could be a straight cut pipe end that is open at the top as is shown in FIG. 3 for the outlet 23. Small quantities of liquid refrigerant, passing to the heat exchanger 5 by way of such a pipe end, do not significantly impair its heating capacity, since they only make up a small part of its volume throughput. In order to also keep such small quantities away from the heat exchanger 5, the grid 25 over the outlet 24 could also be made locally impermeable, so that no drips form above the outlet 24, which could drip down. In the example shown in this case the end of the branch 14 is slightly bent and cut along a substantially vertical surface, to form the outlet 24.

(17) FIG. 4 shows an embodiment of the separator 11 according to the centrifugal principle. An inlet 22 in this case is formed by a pipe 30, which opens into the housing 21 and is offset orthogonally in relation to an axis 31 of the housing 21 and laterally relative to the axis 31. The offset allows the refrigerant in the housing 21 to rotate about the axis 31, so that liquid components are deposited on the housing wall and pass into the branch 15 by way of an outlet 23 at the bottom of the housing 21. The vapor leaves the housing by way of an outlet 24 at the end of the branch 14 that engages in the housing 21 from above.

(18) The drying material 28 can be disposed in the pipe 30 or at the bottom of the housing 21. In the latter case substantially only the liquid phase of the refrigerant comes into contact with the drying material but this does not significantly impair the effect of the drying material, since the greater density of the liquid means that water molecules there are much more likely to come into contact with the drying material and be absorbed than in the vapor phase.

(19) Refrigerant that has condensed in the heat exchanger 5 passes by way of the restriction point 17 into the heat exchanger 7 and evaporates again there.

(20) The following is a summary list of reference numerals and the corresponding structure used in the above description of the invention: 1 Housing 2 Temperature zone 3 Temperature zone 4 Temperature zone 6 Heat exchanger 7 Heat exchanger 8 Fan 9 Compressor 10 Condenser 11 Separator 12 Refrigerant line 13 Refrigerant circuit 14 Branch 15 Branch 16 Restriction point 17 Restriction point 18 Restriction point 19 Restriction point 20 Merging point 21 Housing 22 Inlet 23 Outlet 24 Outlet 25 Grid 26 Upper chamber 27 Lower chamber 28 Drying material 29 Apron 30 Pipe 31 Axis