EP2365271B1 - Evaporator which can be subjected to air, air-water heat pump and method for producing and adjusting an evaporator which can be subjected to air or an air-water heat pump - Google Patents

Description

The invention relates to an evaporator which can be charged with air, in particular for an air-water heat pump, having at least one first and at least one second refrigerant line, wherein the first refrigerant line extends in a first evaporator region of the evaporator and the second refrigerant line extends in a second evaporator region According to claim 1, an air-water heat pump according to claim 8 and a method for the preparation of an air-blowing evaporator and an air-water heat pump according to claim 9, according to claim 9 first prevalent in the operation of the evaporator, a greater air flow rate.
For example, from the DE 10 2008 024 562 A1 or DE 10 2005 029 048 B4 are known Luftbeaufschlagbare evaporator. Such evaporators have a plurality of refrigerant-carrying pipes (lines) which are in heat exchange with flowing air. The efficiency of such luftbeaufschlagbarer evaporator or corresponding air-water heat pump, however, is still perceived as unsatisfactory overall. DE 10 2005 029 048 B4 describes an evaporator according to the preamble of claim 1.

The invention is therefore based on the object to propose a luftbeaufschlagbaren evaporator, an air-water heat pump and a method for producing or setting a luftbeaufschlagbaren evaporator or an air-water heat pump, the efficiency should be improved.

According to a first aspect, the object is achieved by an air-susceptible evaporator, in particular for an air-water heat pump, with at least a first and a second airbeaufschlagbaren refrigerant line, wherein the first refrigerant line runs in a first evaporator region of the evaporator and the second refrigerant line in a second Evaporator region extends, wherein in the first region in the operation of the evaporator prevails a greater air flow rate than in the second region, wherein the refrigerant lines are so deviating designed or adaptable, that an evaporation efficiency in the second refrigerant line is greater than an evaporation efficiency in the first refrigerant line.

According to the invention, "evaporation efficiency" is to be understood as meaning that a higher proportion of a fluid flowing through can be vaporized at a (fictitious) constant air flow velocity in the various regions, in a line having a "greater evaporation efficiency". In other words, overheating in the refrigerant piping having a "greater evaporative efficiency" at the end thereof is greater than the corresponding overheating in the refrigerant piping having "lower evaporative efficiency" (fictitious); assuming that the refrigerant is completely evaporated.

By "overheating" is meant the absorbed energy in the form of heat, based on the point of complete evaporation of the refrigerant.

A core idea of the invention is that inhomogeneities with respect to the air flow rate can be at least partially compensated by a corresponding configuration or adaptation of the refrigerant lines. As a result, the evaporator can be operated with a comparatively slight overheating without the risk of an unstable overheating signal. In particular, the so-called "minimal stable signal" (MSS) is comparatively low. The term "minimum stable signal" refers in particular to the point where the overheating changes from the stable to the unstable state. By a comparatively low minimum stable signal or a comparatively low overheating higher evaporation temperatures can be realized. As a result, the efficiency of the luftbeaufschlagbaren evaporator or a corresponding air-water heat pump is increased.

According to a general idea, the varying formation, in particular interconnection, of individual refrigerant lines (circuits) of an air-susceptible evaporator is claimed independently as a function of an (inhomogeneous) flow profile. A corresponding adaptation of the evaporator can be realized, for example, via a pressure loss, in particular over the length and / or the diameter and / or a throttle of the individual refrigerant lines (capillary lines).

By adjusting the refrigerant lines (circuits) of the evaporator to the actual flow profile, the minimum stable signal and thus the efficiency can be improved.

An uneven application of air results in practice, for example, by the installation situation of the evaporator in a compact device.

Preferably, the refrigerant lines are formed or formulated differently from each other such that the refrigerant lines during operation fluid flowing through in the first refrigerant line undergoes a lower pressure loss than the second refrigerant line. As a result, the evaporation efficiency can be increased particularly easily, which improves the efficiency.

In the narrower sense, "air" can be understood as meaning the air present in the environment, but in general it should be understood as meaning any "gas". Insofar as "water" is mentioned here and below, it can be understood as H ₂ O, but in general it means any vaporizable medium. According to a general idea, "air" or "gas" can also be understood to mean any fluid, in particular a liquid, or "air" and "gas" can be replaced by a fluid or a liquid, respectively.

In the second refrigerant line, a preferably controllable pressure reducing means may be provided, through which preferably the pressure within the second refrigerant line relative to the first refrigerant line can be lowered. As a result, the efficiency is improved in a simple manner.

Preferably, at least one / the at least one controllable pressure reducing means in the second refrigerant line comprises an additional length and / or an at least partially enlarged diameter and / or a throttle device, like a throttle valve. As a result, the pressure can be reduced in a structurally simple manner and the efficiency can be increased. The second refrigerant line may for example be extended and / or widened by at least 10%, preferably by at least 20%, more preferably by at least 50%, compared to the first refrigerant line.

Preferably, at least one measuring device is provided for measuring operationally relevant parameters, in particular the flow velocity and / or the pressure and / or the temperature in the evaporator, in particular the refrigerant lines and / or an evaporator housing. As a result, the efficiency or the efficiency can be increased. Measured values of the at least one measuring device, in particular the flow velocity of the air, are preferably detectable for controlling the evaporation efficiency, in particular the pressure reduction, preferably of the pressure reducing means, by an external control unit optionally provided in / on the evaporator. This facilitates the setting or design or adaptation of the refrigerant pipes.

The design or adaptation of the refrigerant lines can preferably be made by the manufacturer or, for example, during assembly of the evaporator. Optionally, an adaptation can also take place during operation or the evaporator can be designed accordingly to make this possible.

Preferably, at least three refrigerant lines are provided, wherein at least two refrigerant lines are switchable / connected in series such that they form an overall refrigerant line, wherein the total refrigerant line is preferably arranged in a region with comparatively low flow velocity during operation of the evaporator. As a result, the length of the refrigerant lines can be changed by simple means and thus the pressure reduction can be adjusted.

The above object is achieved independently by an air-water heat pump with a luftbeaufschlagbaren evaporator of the type described above.

1. a) Bereitstellen mindestens eines Verdampferbereiches, insbesondere mindestens eines Verdampfergehäuses;
2. b) Bestimmen, insbesondere Errechnen und/oder Messen, einer Strömungsgeschwindigkeit der Luft innerhalb mindestens eines ersten und eines zweiten Gehäuse-Bereiches; und
3. c) Anordnen mindestens einer ersten Kältemittelleitung im ersten Bereich und einer zweiten Kältemittelleitung in dem zweiten Bereich, wobei die Kältemittelleitungen derart ausgebildet sind bzw. ausgebildet werden, dass die Verdampfungseffektivität in der Kältemittelleitung, die sich in dem Bereich befindet, bei dem die größere Strömungsgeschwindigkeit der Luft bestimmt wurde, kleiner ist als in der anderen Kältemittel-Leitung.

Furthermore, the object is achieved independently by a method for producing or setting an air-susceptible evaporator, in particular of the type described above, and / or for producing or setting an air-to-water heat pump of the type described above with the steps:

1. a) providing at least one evaporator area, in particular at least one evaporator housing;
2. b) determining, in particular calculating and / or measuring, a flow velocity of the air within at least a first and a second housing region; and
3. c) arranging at least a first refrigerant line in the first region and a second refrigerant line in the second region, wherein the refrigerant lines are formed such that the evaporation efficiency in the refrigerant line that is in the region where the larger flow velocity of the Air is determined smaller than in the other refrigerant line.

The steps b) and c) are preferably controlled or regulated, in particular by means of a control and / or regulating unit, for example automatically, more preferably during operation. With regard to the advantages of the method, reference is made to the comments on the air-actuated evaporator.

Preferably, the refrigerant lines are deviated from each other so that the refrigerant lines in operation fluid flowing in the refrigerant line, which is in the area in which the operation of the evaporator, a larger air flow rate than in the other area is determined, a lower pressure drop is exposed as the fluid in the other (second) refrigerant line. For this purpose, a corresponding pressure reducing means can be provided.

In particular, to reduce the pressure, the length and / or the diameter can be changed or a throttle device can be provided.

Preferably, at least one operational parameter, in particular the flow rate and / or the pressure and / or the temperature in the evaporator, in particular the refrigerant lines and / or the evaporator housing is measured. Corresponding measured values can be used to control the evaporation efficiency, in particular the pressure reduction, preferably the pressure reduction means, by means of an optionally provided control unit in or on the evaporator be used. The change in the refrigerant piping length is preferably carried out by connecting two or more refrigerant lines in series or correspondingly eliminating an in-line circuit.

Further embodiments emerge from the subclaims.

The invention will also be described in terms of further features and advantages based on embodiments, which are explained in more detail with reference to the drawings.

Fig. 1

ein Diagramm eines Strömungsprofils innerhalb eines Verdampfers bzw. Verdampfergehäuses; und

Fig. 2

eine schematische Darstellung einer Ausführungsform des Verdampfers.

Hereby show:

Fig. 1

a diagram of a flow profile within an evaporator or evaporator housing; and

Fig. 2

a schematic representation of an embodiment of the evaporator.

The diagram according to Fig. 1 shows the flow rate within an evaporator housing in which refrigerant lines 11 may be arranged, depending on the evaporator width and the evaporator height. As Fig. 1 can be taken, resulting in both the evaporator width and the evaporator height an inhomogeneous (non-uniform) course of the flow velocity.

The evaporator according to Fig. 2 comprises an evaporator housing 16 (generally evaporator section) in which refrigerant lines 11 to 15 are arranged. The refrigerant lines 12 to 15 are arranged in a first region 17 and the refrigerant line 11 in a second region 18. In the second region 18, the air flow rate is comparatively low, which is indicated by the arrows 19. The air flow velocity in the first region 17 is comparatively high, which is indicated by the arrows 20.

Relations such as "larger", "smaller", "longer", "shorter", and the like are to be understood such that the corresponding quantities are at least not the same. Preferably, a difference of at least 1%, more preferably at least 5%, more preferably at least 10%, even more preferably at least 50%.

Like yourself Fig. 2 can be removed, one of the lines, specifically the refrigerant pipe 11 may be formed extended. But it is also conceivable (what Fig. 2 not directly apparent), for example, to connect the refrigerant lines 12 and 13 in series, which would correspond to a prolonged total refrigerant line.

The air flow rates are predetermined by the structure of the evaporator or the heat pump and can be determined or calculated by methods known to the person skilled in the art.

In the description, the same reference numerals have been used for the same and like parts.

It should be noted at this point that all the above-described parts taken alone and in any combination, in particular the details shown in the drawings, are claimed as essential to the invention. Changes are familiar to the person skilled in the art.

LIST OF REFERENCE NUMBERS

11

Refrigerant line

12

Refrigerant line

13

Refrigerant line

14

Refrigerant line

15

Refrigerant line

16

compressor housing

17

first area

18

second area

19

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20

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Claims (10)

1. Evaporator to which air can be applied, in particular for an air/water heat pump, having at least a first and a second refrigerant line (11, 12) to which air can be applied, wherein the first refrigerant line (11) runs in a first evaporator region (17) of the evaporator and the second refrigerant line (12) runs in a second evaporator region (18), wherein in the first region (17) a greater air flow speed prevails during operation of the evaporator than in the second region (18),
   characterized in that
   the refrigerant lines (11, 12) are differently designed from one another or else are adaptable in such a manner that an evaporation efficiency in the second refrigerant line is greater than in the first refrigerant line, wherein evaporation efficiency should be understood to mean that with a notional constant air flow speed in the first region and also the second region, a higher proportion of a fluid passing through during operation is evaporated in the second refrigerant line or else overheating in the second refrigerant line, at the end thereof, is greater than the corresponding overheating in the first refrigerant line in the event that the refrigerant is completely evaporated.
2. The evaporator according to claim 1,
   Characterized in that
   the refrigerant lines (11, 12) are differently designed from one another or can be configured in such a manner that the fluid flowing through the refrigerant lines (11, 12) during operation is exposed to a smaller pressure loss in the first refrigerant line (11) than in the second refrigerant line (12).
3. The evaporator according to claim 1 or 2,
   Characterized in that
   a preferably controllable pressure-reducing means is provided in the second refrigerant line (12), through which the pressure within the second refrigerant line (12) can be lowered by comparison with the first refrigerant line (11).
4. The evaporator according to one of the preceding claims,
   Characterized in that
   at least one/the at least one, preferably controllable, pressure-reducing means comprises an additional length in the second refrigerating line (12) and/or an at least sectionally enlarged diameter and/or a throttle device such as a throttle valve.
5. The evaporator according to one of the preceding claims,
   Characterized in that
   at least one measuring device for measuring at least one operationally relevant parameter, in particular the flow speed and/or the pressure and/or the temperature in the evaporator, in particular the refrigerant lines (11 to 15) or an evaporator housing (16), is provided.
6. The evaporator according to claim 5,
   Characterized in that
   measurements of the at least one measuring device, in particular the flow speed, can be recorded for controlling the evaporation efficiency, in particular the pressure reduction, preferably of the pressure-reducing means, by a control unit which is provided in/on the evaporator where necessary or is external.
7. The evaporator according to one of the preceding claims,
   Characterized in that
   at least three refrigerant lines are provided, wherein at least two refrigerant lines can be connected in series in such a manner that they form an overall refrigerant line, wherein the overall refrigerant line is preferably arranged in a region with a comparatively smaller flow speed during evaporator operation.
8. An air/water heat pump having an evaporator according to one of the preceding claims.
9. A method for producing or adjusting an evaporator to which air can be applied according to one of claims 1 to 7 and/or for producing or adjusting an air/water heat pump according to claim 8 comprising the steps:

   provision of an evaporator region, in particular an evaporator housing (16), determination, in particular calculation and/or measurement, of the flow speed of the air within at least a first and second partial region of the evaporator regions and

   arrangement of at least a first refrigerant line (11) in the first partial region (17) and a second refrigerant line (12) in the second partial region (18), wherein the refrigerant lines (11, 12) are configured or adapted in such a manner that an evaporator efficiency in the refrigerant line which is located in the region in which a greater air flow speed was determined than in the other region is smaller than in the other region,

   wherein evaporator efficiency should be understood to mean that with a notional, constant air flow speed in the first region and second region, a higher proportion of a through-flowing fluid is evaporated during operation in the second refrigerant line or else overheating in the second refrigerant line, at the end thereof, is greater than the corresponding overheating in the first refrigerant line in the event that the refrigerant is completely evaporated.
10. The method according to claim 9,
    characterized in that
    steps b) and c) are controlled or regulated by means of a control and/or regulating unit, in particularly automatically, preferably during operation.

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