WO2015110632A1

WO2015110632A1 - Refrigeration plant

Info

Publication number: WO2015110632A1
Application number: PCT/EP2015/051488
Authority: WO
Inventors: Oliver Javerschek; John Craig
Original assignee: Bitzer Kühlmaschinenbau Gmbh
Priority date: 2014-01-27
Filing date: 2015-01-26
Publication date: 2015-07-30
Also published as: DE102014100916A1

Abstract

In order for a refrigeration plant, comprising a refrigerant circuit in which a total mass flow of a refrigerant is conducted, comprising a heat exchanger which is arranged in the refrigerant circuit and which cools refrigerant at the high-pressure side, comprising an expansion element which is arranged in the refrigerant circuit and which, in the active state, cools the total mass flow of the refrigerant by expansion and, in the process, generates a main mass flow of liquid refrigerant and an additional mass flow of gaseous refrigerant which enter into an intermediate pressure accumulator and are separated in the latter into the main mass flow and the additional mass flow, comprising at least one normal cooling stage which, from the main mass flow in the intermediate pressure accumulator, branches off a normal cooling mass flow and expands the latter in at least one normal cooling expansion unit to a low pressure, and in the process provides refrigeration power for normal cooling, and comprising a refrigerant compressor unit, which compresses the expanded normal cooling mass flow from low pressure to high pressure, to be improved such that, with said refrigeration plant, refrigeration power can also be provided for other applications, it is proposed that there is coupled to the intermediate pressure accumulator a parallel circuit which extracts liquid refrigerant from the main mass flow, supplies said liquid refrigerant to an evaporator and supplies evaporated refrigerant to the additional mass flow.

Description

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COOLING SYSTEM

The invention relates to a refrigeration system comprising a refrigerant circuit, in which a total mass flow of a refrigerant is guided, arranged in the refrigerant circuit, high-pressure side refrigerant cooling heat exchanger, a refrigerant circuit disposed in the expansion device, which cools the total mass flow of the refrigerant in the active state by expansion and thereby a main mass flow of liquid refrigerant and an additional mass flow of gaseous refrigerant generated, which enter an intermediate pressure accumulator and are separated in this in the main mass flow and the additional mass flow, at least one

Normal cooling stage, which dissipates a normal cooling mass flow from the main mass flow in the intermediate pressure accumulator and expands in at least one normal expansion unit to a low pressure and thereby provides cooling capacity for normal cooling, and a refrigerant compressor unit, which compresses the expanded normal mass flow of low pressure to high pressure.

Such refrigeration systems are known from the prior art, for example DE 10 2006 050 232 B3.

In such refrigeration systems, however, there is often the requirement to integrate them into an energy-efficient system concept, for example a building concept with the highest possible energy efficiency.

The invention is therefore based on the object to improve such a refrigeration system such that it can be provided with this for other applications cooling capacity. - -

This object is achieved in a refrigeration system of the type described above according to the invention that is coupled to the intermediate pressure accumulator a parallel circuit, which removes liquid refrigerant from the main mass flow and an evaporator and fed evaporates refrigerant to the additional mass flow.

The advantage of this solution is the fact that parallel to the intermediate pressure collector still cooling capacity can be removed from the refrigeration system in a simple manner, namely cooling capacity which is available at a temperature level corresponding to the intermediate pressure.

Such cooling capacity can be used, for example, for room air conditioning or building air conditioning or other air conditioning tasks.

In order to operate the parallel circuit as simply as possible, it is preferably provided that the evaporator as a flooded evaporator

is trained and works.

This makes it possible to control the cooling capacity taken off at the evaporator in a particularly simple manner, since only the inflow to the flooded evaporator has to be regulated.

It is particularly simple in this case, in particular, when the flooded evaporator operates on the thermosiphon principle, so that in the simplest case, no pump power is required to supply the evaporator with liquid refrigerant.

Alternatively or in addition to the solutions described above, it is also advantageous if in the parallel circuit, a pump for the refrigerant is provided, which supports or maintains the flow of refrigerant in the parallel circuit. - -

Furthermore, it is preferably provided that in the parallel circuit

Control is arranged to control the circulating refrigerant.

Such a control may be formed in the simplest case as a control valve which either releases the refrigerant flow in the parallel circuit, throttles or prevents.

As an alternative to providing a control valve, another advantageous solution provides that the control element is designed as a pump that is controllable with respect to its delivery rate.

In this case, the pump can both the flow of the refrigerant in the

Promote parallel circulation and at the same time but also the amount of

control circulating refrigerant.

The evaporator itself can be used in many different ways.

For example, provides an advantageous solution that the evaporator itself is designed as a heat exchanger for cooling an interior of a building.

Alternatively or additionally, an advantageous solution provides that the evaporator is coupled to a transformer circuit in which a cooling heat exchanger for cooling a building is arranged.

Such a transformer circuit has the advantage that with this in a simple manner, a connection between the evaporator and to be positioned at one or at different locations in a building cooling heat exchangers. - -

Alternatively or in addition to a refrigeration system with the above

described features, the above-mentioned object is also achieved that as an alternative or in addition to the high-pressure side refrigerant cooling heat exchanger, a heat exchanger is provided for heating a building.

In this case, the refrigeration system according to the invention can also be used, for example in winter, to use the heat arising in the high-pressure side heat exchanger for heating the building.

Alternatively or in addition to a refrigeration system with the above

described features, starting from a refrigeration system of the type described above, a further advantageous embodiment that a Tiefkühpansionseinheit is provided which expands a taken from the main mass flow in the intermediate pressure accumulator Tiefkühlgesamtmassenstrom to a Tiefkühlzwischendruck, thereby cooling and a Tiefkühlhauptmassenstrom of liquid refrigerant and a Tiefkühlzusatzmassenstrom produced from gaseous refrigerant and this feeds a Tiefkühlzwischendrucksammler, in which a separation of the main cooling mass flow of the Tiefkühlzusatzmassenstrom takes place, that a Tiefkühlhauptmassenstrom from the Tiefkühlnischendrucksammler laxative Tiefkühlstufe is provided, which has at least one Tiefküh expansion unit and by expansion of the main cooling mass flow to a Tiefkühlniederdruck cooling capacity for freezing

Provides that a freezer compressor unit is provided, which is the deep freeze low pressure expanded main mass flow

compressed and the normal cooling mass flow from low pressure to high pressure compressing refrigerant compressor unit also for compression to high pressure feeds.

The advantage of this solution is the fact that with such a refrigeration system in addition to the possibility of normal cooling and the possibility of freezing is given. - -

Such a refrigeration system can be particularly advantageous in the sense of the above-mentioned task by the fact that with the Tiefkühl- zwischendrucksammler a parallel circuit is coupled, which removes liquid refrigerant from the main cooling mass flow, feeds to an evaporator and fed refrigerant evaporates the Tiefkühlzusatzmassenstrom.

Such a solution has the great advantage that with this there is the possibility to present in the intermediate cryogenic pressure accumulator

Temperatures heat energy from a heat reservoir and deliver to the high-pressure side refrigerant cooling heat exchanger, so that the refrigeration system operates as a heat pump.

For example, such a refrigeration system can be used as a heat pump when a large amount of heat is desired at the high pressure side refrigerant cooling heat exchanger, for example, in the winter for heating systems or buildings, and if this heat another heat reservoir, such as the environment, be it Air or earth, can be removed.

Thus, in this case, the refrigeration system not only serves to generate cooling capacity, but can also be used selectively to generate increased heat output at the high-pressure side refrigerant cooling heat exchanger.

Also in this parallel circuit is preferably provided that the evaporator is designed as a flooded evaporator and works.

Such an evaporator can thus be operated and controlled or regulated particularly easily. - -

In particular, operation of the evaporator is favorable when the flooded evaporator operates on the thermosiphon principle, so that in principle no pumping power is required to circulate the refrigerant.

Alternatively or additionally, it is also conceivable that a pump for generating the required refrigerant flow is provided in the parallel circuit.

Furthermore, it is for controlling or regulating the heat absorbed by the evaporator advantageous if a control element for controlling the circulating refrigerant is arranged in the parallel circuit.

Such a control element can be designed, for example, as a control valve which releases, throttles or prevents the flow of circulating refrigerant.

Alternatively, it is also conceivable if the control is designed as a controllable pump in terms of their capacity.

In such a refrigeration system, for example, the evaporator itself may be formed as a heat exchanger for heat absorption from a heat reservoir.

Alternatively, it is also possible that the evaporator is coupled to a transformer circuit in which a heat exchanger for

Absorption of heat from the heat reservoir is arranged.

In a further advantageous embodiment, it is preferably provided that the additional mass flow from the intermediate pressure accumulator is expanded via an expansion element and supplied to the intermediate cryogenic pressure accumulator such that in the intermediate cryogenic pressure accumulator a liquid phase formed by expansion by means of the expansion element in the main cryogenic mass flow within the intermediate cryogenic pressure accumulator - - separates and that a forming in the intermediate cryogenic pressure accumulator gas phase of the additional mass flow is fed together with the Tiefkühlzusatz- mass flow of an additional mass flow compressor unit for compressing to high pressure.

The advantage of this solution is the fact that the cooling of the additional mass flow upon expansion of the same and a resulting formation of a liquid phase is exploited on the one hand to supply the liquid phase to the main cooling mass flow, so that it can still be used advantageously and on the other hand is achieved by that the gas phase of the additional mass flow can be supplied largely free from the liquid phase of an additional mass flow compressor unit and thereby the problems can be avoided, which arise by suction of liquid in a compressor.

It is particularly advantageous if the gas phase of the additional mass flow is supplied together with the Tiefkühlzusatzmassenstrom of the Tiefkühlzwischendrucksammler expansion of the Zusatzmassenstromverdichter- unit, so that no loss of performance caused by further expansion of the same.

Furthermore, it is favorable if a frozen intermediate pressure in the intermediate cryogenic pressure accumulator lies in a pressure range which extends from the low pressure up to the intermediate pressure.

Preferably, the intermediate cryogenic pressure is at most 5 bar (50 N / cm ² ) above the low pressure.

A particularly favorable solution provides that the intermediate cryogenic pressure is in the range of low pressure. - -

In principle, a separate compressor unit could be provided as an additional mass flow compressor unit, for example a power-controlled or speed-controlled compressor unit with which it would be possible to regulate the intermediate cryogenic pressure to a pressure value which is favorable for the operation of the refrigeration system.

A particularly cost-effective solution, however, provides that the refrigerant compressor unit comprises the additional mass compressor unit, so that no separate compressor unit is necessary, but the compression of the gas phase of the additional mass flow and the Tiefkühlzusatz- mass flow from the Tiefkühlzwischendrucksammler can be done by the already existing refrigerant compressor unit.

A particularly favorable solution provides that the gas phase of the additional mass flow is supplied together with the Tiefkühlzusatzmassenstrom of the intermediate cryogenic pressure collector together with the expanded to low pressure normal cooling mass flow of the refrigerant compressor unit, so that there is the possibility to connect the Tiefkühlzwischendrucksammler with the normal cooling mass flow leading to the refrigerant compressor unit line ,

With regard to the guidance of the expanded additional mass flow in the cryogenic intermediate pressure accumulator so far no further details have been made.

Thus, a particularly advantageous solution that by the

Expansionsorgan expanded additional mass flow the cryogenic intermediate pressure collector spatially separated from a leading away from the intermediate cryogenic pressure collector discharge line opens.

In particular, the confluence of the expanded Tiefkühlzusatzmassen- stream in the Tiefkühlzwischendrucksammler is placed so that it enters the bubble in Tiefkühlzwischendrucksammler. - -

Preferably, the distance between the junction of the

expanded additional mass flow in the cryogenic intermediate pressure accumulator and the discharge line as large as possible, preferably greater than half of the expansion of the cryogenic intermediate pressure accumulator in the direction of his

maximum extent chosen to have a sufficiently large distance for separating the liquid phase from the expanded additional mass flow before a gaseous phase of the expanded additional mass flow is discharged through the discharge line from the cryogenic intermediate pressure accumulator.

Preferably, it is provided that a flow velocity of the refrigerant in the discharge line is less than 2m / s (meters per second), even better less than 0.5m / s and more preferably less than 0.3m / s.

At such low flow velocities in the discharge line, it can be ensured that there are no more appreciable liquid fractions in the gaseous phases of the freezing additive mass flow and the gaseous additional mass flow discharged through the discharge line.

It is particularly useful if a liquid content of the above

The discharge line from the cryogenic intermediate pressure accumulator refrigerant is less than 5 m% (mass percent), more preferably less than 3% by mass, and preferably less than 1% by mass flow of the gaseous phases.

In connection with the previous explanations of the solution according to the invention was not set out in more detail how the expansion of the additional mass flow to take place in detail. - -

An advantageous solution provides that the additional mass flow from the forming in the intermediate pressure accumulator bladder via a discharge line to the intermediate cryogenic pressure accumulator and is relaxed by the provided in the discharge line expansion device to the intermediate cryogenic pressure.

In particular, it is provided that the relaxed by the expansion device additional mass flow is fed directly to the bubble in the intermediate cryogenic pressure collector, from which starting then settles the liquid phase of the expanded additional mass flow.

In particular, it is advantageous if the expander of the expanded part of the additional mass flow of the bubble in the intermediate cryogenic pressure collector in a Abscheidehöhe of 300 mm to 400 mm above the

structurally predetermined maximum achievable liquid level of the bath of the main cooling mass flow in the intermediate cryogenic pressure collector is supplied.

In such a supply of the expanded additional mass flow is likely to be sufficient with a sufficient separation of the liquid phase in the intermediate cryogenic pressure collector.

The refrigeration system described so far, however, operates less efficiently when the high pressure is to be at a high pressure level, that is, in particular in all the times in which there is a high temperature at the high-pressure side refrigerant cooling heat exchanger.

For this reason, a further advantageous solution provides that the refrigeration plant has a Zusatzmassenstromabfuhreinheit with which at least in certain operating modes at least a portion of the additional mass flow removed from the intermediate pressure accumulator and supplied without further expansion, starting from the intermediate pressure of a compression to high pressure. - -

Such a refrigeration system has the advantage that it can work more efficiently at a very high pressure level of the high pressure.

In order to ensure, however, in this case that as possible no liquid is contained in the compression of the guided from the Zusatzmassenstromabfuhreinheit part of the additional mass flow and to a

Damage to the compressor used for this purpose, preferably the Zusatzmassenstromabfuhreinheit is formed so that it has a heat exchanger for heating the additional mass flow before compressing it to high pressure.

Although this heat exchanger reduces the efficiency of the refrigeration system, but provides increased safety for the compressor, which is to compress the mass flow from the Zusatzmassenstromabfuhreinheit.

The heat exchanger could be flowed through by any heat-releasing medium.

It has proven to be particularly favorable if the heat exchanger is flowed through by the deep-freeze compactor unit which has been heated up by the compression in the deep-freezer unit, so that on the one hand this mainstream bulk mainstream can be cooled before further compression by the inventive refrigerant compressor unit on the other hand, the mass flow guided by the additional mass flow discharge unit warms up and consequently it can be ensured that no damage to the compressor used for this purpose is to be feared when the mass flow carried by the additional mass flow discharge unit is compressed.

How the compression of the portion of the additional mass flow discharged from the additional mass flow discharge unit is to be carried out has hitherto not been described in detail. - -

Thus, an advantageous solution provides that the additional mass flow discharge unit supplies the discharged part of the additional mass flow to an economizer connection of refrigerant compressors of the refrigerant compressor unit, so that the same refrigerant compressors already used in the refrigerant compressor unit can also be used for compressing the mass flow from the additional mass flow discharge unit.

Another advantageous solution provides that the Zusatzmassenstromabfuhreinheit supplies the discharged part of the additional mass flow to a parallel compressor, in addition to the refrigerant compressor unit

is provided.

For example, the parallel compressor then works from the

Intermediate pressure and compresses the part of the additional mass flow supplied by the Zusatzmassenstromabfuhreinheit this to high pressure.

In order to be able to regulate the intermediate pressure in a simple manner, it is preferably provided that the parallel compressor is power-controlled, in particular speed-controlled.

Furthermore, it is preferably provided that by power control of the

Parallel compressor, a control of the intermediate pressure to a predetermined value.

However, in order to dissipate additional mass flow with the Zusatzmassenstromabfuhreinheit under operating conditions in which the high pressure is at a very low value and in particular the temperature at the high-pressure side refrigerant cooling heat exchanger, it is preferably provided that the Zusatzmassenstromabfuhreinheit by a switching device with the intermediate pressure accumulator connectable or separable from this. - -

Furthermore, it is preferably provided that the Zusatzmassenstromabfuhr- unit is connected by a switching device with the Tiefkühlzwischendrucksammler for removing the gas phase of the additional mass flow together with the Tiefkühlzusatzmassenstrom and separable from this.

By this Zuschaltorgan thus there is the possibility, then, if the Zusatzmassenstromabfuhreinheit can no longer be meaningfully used to remove a portion of the additional mass flow from the intermediate pressure collector, the Zusatzmassenstromabfuhreinheit also to dissipate the gas phase of the additional mass flow together with the Tiefkühlzusatzmassenstrom from the Tiefkühlzwischendrucksammler.

In this case, in particular when the additional mass flow discharge unit leads to a parallel compressor, it is possible to use the

Parallel compressor to use to compress the gas phase of the additional mass flow together with the Tiefkühlzusatzmassenstrom from the Tiefkühlzwischendrucksammler.

For a control, it is also very advantageous if the Zuschaltorgan is arranged so that optionally not only the gas phase of the additional mass flow can be compressed together with the Tiefkühlzusatzmassenstrom from the Tiefkühlzwischendrucksammler, but also optionally at least a portion of the expanded to low pressure normal cooling mass flow.

In this case, in particular the power-controlled parallel compressor is advantageous if it works parallel to the refrigerant compressor unit.

More generally, theoretically, the refrigerant compressor unit could include multiple power controlled refrigerant compressors.

Advantageously, it is provided that at least one of the refrigerant compressors of the refrigerant compressor unit is power-controlled. - -

Usually, however, for cost reasons, only one of the refrigerant compressor of the refrigerant compressor unit is power controlled.

Operation of the refrigeration system in various operating modes provides, for example, that in a first operating mode, the additional mass flow discharge unit is separated from the intermediate pressure accumulator and that the entire additional mass flow is expanded and supplied to the intermediate cryogenic pressure accumulator.

This solution has the advantage that it can be ensured by simple means and independently of the temperature in which the high-pressure compressed refrigerant cooling heat exchanger, that the refrigerant compressors used suck no significant amounts of liquid.

Operation in the various operating modes, for example, further provides that in a second mode of operation the additional mass flow discharge unit is connected to the intermediate pressure accumulator and discharges part of the additional mass flow and another part of the additional mass flow is supplied to the intermediate cryogenic pressure accumulator.

This solution has the advantage that it increases the efficiency of the refrigeration system, as part of the additional mass flow is compressed directly from the intermediate pressure to high pressure.

Operation in the various operating modes provides, as an alternative or in addition to the second operating mode, that in a third operating mode, the additional mass flow discharge unit is connected to the intermediate pressure accumulator and discharges the entire additional mass flow.

This solution is particularly at high temperatures to the high-pressure compressing heat exchanger advantageous because in these the refrigeration system works with the greatest possible efficiency. - -

In addition, the object set in the introduction is achieved by an energy-efficient building, which has one or more features of a refrigeration system described above.

Further features and advantages of the invention are the subject of the following description and the drawings of some

Embodiments.

In the drawing show:

Fig. 1 is a schematic representation of a first Ausfüh

Example, a refrigeration system according to the invention;

Fig. 2 is a schematic representation of a second Ausfüh

Example, a refrigeration system according to the invention;

Fig. 3 shows an illustration of a third exemplary embodiment of a refrigeration system according to the invention;

4 shows an illustration of a fourth exemplary embodiment of a refrigeration system according to the invention;

5 shows an illustration of a fifth exemplary embodiment of a refrigeration system according to the invention;

Fig. 6 is an illustration of a sixth embodiment of a refrigeration system according to the invention and

Fig. 7 is a schematic representation of a building with a refrigeration system according to the invention.

A first embodiment of a refrigeration system according to the invention, shown in FIG. 1, includes a whole designated 10 - -

Refrigerant circuit in which a designated as a whole with 12 refrigerant compressor unit is arranged, which in the illustrated embodiment, a plurality of individual refrigerant compressor, for example, three

Refrigerant compressor 14i to 14 ₃ , which all operate in parallel in the refrigerant compressor unit 12.

Each of the refrigerant compressors 14i to 14 ₃ has a suction-side port 16i to 16 ₃ , wherein all the suction-side ports 16 of the individual refrigerant compressors 14 are connected to a suction port line 18 of the refrigerant compressor unit 12.

Furthermore, each of the refrigerant compressors 14 has a pressure-side connection 22i to 22 ₃ , wherein all pressure-side connections 22 of the individual refrigerant compressors 14 are connected to a pressure connection line 24 of the refrigerant compressor unit 12.

Thus, all the refrigerant compressors 14 operate in parallel, but it is possible to vary the compressor capacity of the refrigerant compressor unit 12 by operating individual refrigerant compressors 14 and by not operating individual refrigerant compressors 14.

Furthermore, it is possible to control the compressor power of the refrigerant compressor unit 12 by a variable-speed control of either a working refrigerant compressor 14 or to control the speed of individually operating refrigerant compressor 14 individually.

The refrigerant compressor unit 12 thus compresses refrigerant from a suction pressure applied in the suction connection line 18, which corresponds to a low pressure PN of a standard cooling stage to be described, on one in the pressure connection line 24 of the refrigerant compressor unit 12

present high pressure PH, which may for example be in the range between 45 bar (450 N / cm ² ) and 100 bar (1000 N / cm ² ). - -

The refrigerant present under high pressure PH at the pressure connection line 24 initially forms a total mass flow G which flows away from the pressure connection line 24 of the refrigerant compressor unit 12

Flows through the oil separator 32 and after the oil separator 32 flows through a high-pressure side heat exchanger 34 through which a cooling of the refrigerant compressed to high pressure takes place.

Depending on whether there is a subcritical cyclic process or a supercritical cyclic process, the cooling of the total mass flow G of the high-pressure refrigerant in the high-pressure side heat exchanger 34 causes it to liquefy or merely to cool it to a lower temperature, in the case of a supercritical cyclic process only a sensible heat change takes place.

If the refrigerant used is carbon dioxide, that is to say C0 ₂ , conventional ambient conditions usually involve a supercritical cyclic process in which only a cooling takes place to a temperature which corresponds to an isotherms running outside the dew and boiling curve or saturation curve, so that none Liquefaction of the

Refrigerant enters.

In contrast, a subcritical cycle process provides that cooling takes place through the high-pressure-side heat exchanger 34 to a temperature which corresponds to an isotherm passing through the dew and boiling curve or saturation curve of the refrigerant.

The cooled by the high-pressure side heat exchanger 34 refrigerant is supplied to a arranged in a pressure line 36 expansion member 38 which controls the high pressure PH predetermined by a controller 40 values and which, for example, as by the - -

Control 40 driven expansion element 38 is formed and which expands under high pressure PH refrigerant of the total mass flow G to an intermediate pressure PZ, which corresponds to a the tau and boiling curve or saturation curve of the refrigerant passing isotherms.

The controller 40 controls the expansion member 38 according to a temperature in the heat exchanger 34 and these predetermined limits of use of the refrigerant compressor 14th

The intermediate pressure PZ is, for example, in the range between 35 bar and 45 bar and is maintained in all possible operating states at a predetermined value, so that the deviation of the predetermined value is a maximum of ± 3 bar.

By the expansion member 38, the total mass flow G of the refrigerant is placed in a thermodynamic state in which a main mass flow H in the form of liquid refrigerant and an additional mass flow Z in the form of gaseous refrigerant.

Both mass flows H and Z are in an intermediate pressure accumulator 42 having a reservoir for both the main mass flow H and the additional mass flow Z, collected and separated in the intermediate pressure accumulator 42, wherein the main mass flow H in the intermediate pressure accumulator 42 as a bath 44 of liquid refrigerant forms, over which a gas volume 46 is gaseous refrigerant, so that the bath 44 receives the main mass flow H and the gas volume 46 receives the additional mass flow Z.

From the main mass flow H forming the bath 44 of liquid refrigerant flows from the intermediate pressure accumulator 42 a mass flow of mass N of the main mass flow H to a designated as a whole by 52 normal cooling stage, which has one or more, for example, two parallel Normalalkühlexpansionseinheiten 54a and 54b. - -

Each of these normal refrigeration expansion units 54 comprises a normal-cooling expansion element 56, by which an expansion of the part of the normal cooling mass flow N arriving at intermediate pressure PZ to low-pressure PN takes place, wherein cooling of the refrigerant occurs in a known manner through this expansion, which opens up the possibility of absorb heat to the respective normal cooling heat exchanger 58 following the normal cooling expansion element 56, whereby an enthalpy increase occurs. The low pressure PN is for example in the range between 25 bar and 30 bar and is kept as constant as possible in all operating conditions, that is within a maximum of ± 3 bar of the predetermined value of the low pressure PN.

The total normalized mass flow N, which has been expanded to low-pressure PN, is supplied by the normal-cooling heat exchangers 58 to a suction line 62

supplied, which in turn is connected to the suction connection line 18 of the refrigerant compressor unit 12, so that this expanded normal cooling mass flow N can be compressed by the refrigerant compressor unit 12 back to high pressure PH.

From the main mass flow H in the intermediate pressure accumulator 42 not only the normal cooling mass flow N is diverted as a partial flow, but as a further partial flow a Tiefkühlgesamtmassenstrom TG, which is fed to a Tiefkühl- zwischendruckexpansionseinheit 72, which also

For example, is designed as an expansion element or expansion valve.

By Tiefkühlzwischendruckexpansionseinheit 72 takes place an expansion of Tiefkühlgesamtmassenstroms TG to a Tiefkühlzwischendruck PTZ, which preferably corresponds to the low pressure PN and, for example, between 25 bar and 30 bar, so that from the liquid refrigerant

existing Tiefkühlhauptmassenstrom TG a Tiefkühlhauptmassenstrom TH at a below the temperature of the main mass flow temperature and a Tiefkühlzusatzmassenstrom TZ from vapor - -

Refrigerants arise, which are fed together to a cryogenic intermediate pressure accumulator 74, wherein the intermediate cryogenic pressure accumulator 74 a

Reservoir both for the main cooling main flow TH and for the Tiefkühlzusatzmassenstrom TZ, this collects and separated from each other, the Tiefkühlhauptmassenstrom TH forms as a bath 76 of liquid refrigerant, while the Tiefkühlzusatzmassenstrom TZ lying above the bath 76 gas volume 78 of gaseous refrigerant forms in the cryogenic intermediate pressure accumulator 74.

Thus, in the intermediate cryogenic pressure accumulator 74, a separation of the main refrigerated mass flow TH from the additional frozen mass flow TZ takes place.

Starting from the intermediate cryogenic pressure accumulator 74, the main chilled-matter mass flow TH is supplied to a deep-freezing stage 82, which has one or more, for example two, parallel deep-freeze expansion units 84, which are connected in parallel, each of these deep-freeze expanding units 84 having a deep-free expansion element 86 which forms part of the deep-freeze mass flow TH expands from the Tiefkühlzwischendruck PTZ to a Tiefkühlniederdruck PTN and thus cools, the Tiefkühlniederdruck PTN is kept as constant as possible in all operating conditions, so that the deviations maximum ± 3 bar and, for example, between 10 bar and 15 bar.

The refrigerant cooled to low-pressure low-pressure PTN is then subsequently supplied to a low-pressure low-pressure side heat exchanger 88 and is able to absorb heat in the respective deep-freeze heat exchanger 88 at cryogenic temperatures, thereby increasing the enthalpy.

The total frozen main mass flow TH expanded in the deep-freezing stage 82 to the low-pressure low-pressure PTN is fed to a deep-freeze suction line 92, which is connected to both deep-freeze heat exchangers 88 and supplies the deep-frozen low-pressure PTN to an overall free-flowing mass TH of a deep-freeze unit denoted as a whole by 102, which for example - - A plurality of parallel-working deep-freeze compressors 104i to 104 ₃ , each having suction ports 106i to 106 ₃ , which are connected to a Tiefkühlsauganschluss 108 of the deep freezer unit 102, which in turn is connected to the Tiefkühlsaugleitung 92 and expanded to Tiefkühlniederdruck PTN Tiefkühlhauptmassenstrom TH receives.

The deep-freeze compressors 104 further have pressure-side connections 112i to 112 ₃ , which in turn are in turn connected to a deep-freeze pressure connection line 114 of the deep-freeze compressor unit 102.

The deep-freeze compressor unit 102 compresses the main bulk cooling flow TH, which has flowed through the deep-freezing stage 82 and expanded to the deep-freeze pressure PTN, again to the normal low-pressure PN, the deep-freeze mass flow TH compressed to the normal low-pressure PN being supplied via a line 116 to the suction connection line 18 of the refrigerant compressor unit 12.

If necessary, a heat exchanger 118 can optionally be connected in the line 116, which permits an optionally favorable cooling of the compacted main cooling mass flow TH.

In the previous explanation of the function of the refrigerant circuit 10, no information was given for guiding the frozen additional mass flow TZ and the additional mass flow Z.

In order to remove the additional frozen mass flow TZ, which is present in the intermediate intermediate cryogenic pressure accumulator 74 on the intermediate cryogenic pressure PTZ, in order to keep the intermediate frozen pressure PTZ as constant as possible, the intermediate cryogenic pressure accumulator 74 is provided with a discharge line 122, which supplies the gas volume 78 in the intermediate cryogenic pressure accumulator 74 with the Suction line 62 connects, which leads from the normal cooling stage 52 to the suction port 18 of the refrigerant compressor unit 12. - -

Thus, the intermediate cryogenic pressure PTZ corresponds approximately to the normal low-pressure PN.

To remove the additional mass flow Z from the intermediate pressure accumulator 42 and to keep the intermediate pressure PZ as constant as possible, opens a

Discharge line 132 on the one hand in the gas volume 46 of the intermediate pressure accumulator 42 and on the other hand in the gas volume 78 in Tiefkühlzwischen- pressure accumulator 74, wherein additionally in the discharge line 132 still a

Expansion element 134 is provided, which expands the emerging from the intermediate pressure accumulator 42 additional mass flow Z of the intermediate pressure PZ on the Tiefkühlzwischendruck PTZ and thus of the saturated gas phase into the wet steam area and thus causes an additional cooling of the same, so that the additional mass flow Z still under generating liquid on is cooled before it enters the Tiefkühlzwischendruck- collectors 74.

The expansion member 134 regulates the intermediate pressure PZ in the intermediate pressure accumulator 42 to a predetermined value.

About the Tiefkühlzwischendruckexpansionseinheit 72, the volume of the bath 44 of liquid refrigerant in the intermediate pressure accumulator 42 and the volume of the bath 76 liquid refrigerant in Tiefkühlzwischendruck- collector 72 is set so that on the one hand the bath 74 has a sufficiently large volume and on the other hand, the bath 44 also has sufficiently large volume.

In particular, it is provided that the expanded by the expansion member 134 of the additional mass flow Z the gas volume 78 in Tiefkühl- zwischendrucksammler 74 in a separation height of 300 mm to 400 mm above the constructive predetermined maximum achievable liquid level of the bath 76 of the Tiefkühlhauptmassenstrom TH in Tiefkühlzwischendruck- collectors 74th is supplied. - -

With such a supply of the expanded additional mass flow Z is to be expected with a high probability with a sufficient separation of the liquid phase in the intermediate cryogenic pressure collector 74.

The confluence of the discharge line 132 into the deep-freezing intermediate pressure accumulator 74 is such that the additional mass flow Z entering the intermediate intermediate pressure accumulator 74 is sufficiently far away from the discharge line 122, in particular a junction of the discharge line 122 into the intermediate deep-freeze accumulator 74, to ensure that the By the expansion member 134 cooled additional mass flow Z in the gas volume 78 of the intermediate cryogenic pressure accumulator 74 entrains and formed by the cooling due to the expansion in the expansion member 134 liquid fraction in the intermediate cryogenic pressure collector 74 and then thereafter the remaining gaseous additional mass flow Z again through the discharge line 122 into the suction line 62nd entry.

The additional mass flow Z 'flowing through the discharge line 122 is reduced by the mass of the liquid fraction of the additional mass flow Z deposited in the intermediate cryogenic pressure collector 74, which, however, is in the range of less than 10%, so that approximately the additional mass flow Z' corresponds to the additional mass flow Z.

Thus, the discharge line 122 flows through not only the Tiefkühlzusatzmassen- mass flow TZ, but also of the gas volume 78 in the intermediate cryogenic pressure collector 74 passed through substantially gaseous portion of the additional mass flow Z, which then both enter the suction line 62.

Preferably, the liquid content of the additional mass flows flowing through the discharge line 122, namely the additional frozen mass flow TZ and the additional mass flow Z ', is in total less than 5 m% (mass percent), more preferably less than 3 m% and preferably less than - -

1 m-% of the total mass flow rates passing through the Abfuh 122, so that sichergestel lt is that the refrigerant compressor 14 of the refrigerant compressor unit 10 suck in all len operating conditions substantially liquid keitsfreies refrigerant.

The indication of the mass flows is a mean value which is set during operation of the refrigeration cycle 10 in the manner described during the respective operating periods.

A separation of the liquid components of the additional mass flow Z in the gas volume 78 of the intermediate cryogenic pressure accumulator 74 can be achieved in a particularly advantageous manner if the flow velocity of the

Refrigerant in the effluent line is less than 2 m / s (meters per second), more preferably less than 0.5 m / s and preferably less than 0.3 m / s.

In a second embodiment of a refrigeration system 10 according to the invention, shown in Fig. 2, those elements which are identical to those of the first embodiment, densel ben reference numerals, so that with respect to the description of the same fully content I on the ie

Embodiments of the first embodiment can be made reference.

In contrast to the first exemplary embodiment are the second

The refrigerant compressor 14 is configured so as not only to have a suction side port 16 and a backward port 22, but an economizer port 21, with all economizer ports 21i to 21 ₃ having a common port 152

are connected . - -

Between the respective economizer Anschlus 21 and the Anschl ussleitung 152 is still in each of the refrigerant Verdichter 14 'own valve 154i to 154 ₃ angeord net, with which a connection between the

Economizer Anschl uss 21 and the common Anschl ussleitung 152 for al le Kältemittelverd ichter 14 'can be interrupted.

The connection line 152 leads to a heat exchanger 156 and of this heat exchanger 156 leads a recording line 158 for the

Additional mass flow Z from the interim rucksammler 42 to the discharge line 132 and flows into these between the mouth of the discharge line 132 in the Gasvol chambers 46 and the expansion element 134, so that at least a portion of the additional mass flow Z or the entire additional mass flow Z discharged with the receiving line 158 can be, without that d this part of the additional mass flow Z or this dissipated total additional mass ^¬ flow Z in the Gasvol trees 78 of Tiefkühlzwischendrucksammlers 74th

flows.

The heat exchanger 156 liegt further in turn in the line 116, the ciently leads of the Tiefkühldruckanschl ussleitung 114 to the Sauganschl 18, so that by the heat exchanger 156 d the possi probability consists, over the receiving line 158 discharged part of the additional mass flow Z as far to heat up that this ieser contains no more liquid components before this d ieser part of the additional mass flow Z via the economizer connections 21 the individual NEN refrigerant compressors 14 of the refrigerant compressor unit 12 is supplied, ie the sucked-in part of the additional mass flow Z from the intermediate pressure PZ to high pressure Consolidate PH.

By means of the valves 154, it is also possible to control the proportion of the additional mass flow Z which is supplied to the economizer connection 21 or, if appropriate, to stop it completely so that in this case at least one appreciable part remains not the entire additional mass flow Z, via the expansion element 134 enters the gas volume 78 of the Tiefkühlzwischend rucksammlers 74. - -

In the second embodiment, the connecting line 152 with the valves 154, the heat exchanger 156 and the receiving line 158 form a Zusatzmassenstromabfuhreinheit 160, with which from the Zwischendruck- collector 42 at least a portion of the additional mass flow Z can be discharged without an expansion is required, so that this part of the additional mass flow Z can be compressed based on the intermediate pressure PZ to high pressure PH and thus the efficiency of the refrigeration system is improved.

By closing the valves 154, however, it is also possible to deactivate the additional mass flow discharge unit 160.

In the second embodiment, those elements which are identical to those of the first embodiment are provided with the same reference numerals, so that with regard to the description of the same can be made in full content to the comments on the first embodiment.

In a third embodiment of a refrigeration system 10 according to the invention, shown in Fig. 3, the receiving line 158 is provided in the same manner as in the second embodiment, which leads to the heat exchanger 156 and of the heat exchanger 156 leads in this case, a suction line 162 to an addition to The parallel compressor 164 provided in the refrigerant compressor unit 12, namely to a suction port 166 thereof, the pressure port 172 is in turn connected to the pressure connection line 24, so that by appropriate speed-controlled control of the parallel compressor 164 the possibility to remove a portion of the additional mass flow Z from the intermediate pressure accumulator 42. - -

Incidentally, in the third embodiment, the elements identical to the first and second embodiments are given the same reference numerals, so that with respect to the description thereof

full content can be made to the comments on the first and second embodiments.

In a fourth embodiment, shown in Fig. 4, those elements which are identical to those of the first, second and third embodiment, provided with the same reference numerals, so that with respect to the description of the same in full to the comments on these

Embodiments can be referenced.

In contrast to the third embodiment is in the fourth

Embodiment in the receiving line 158, a switching valve 182 is provided which allows to prevent a recording of refrigerant from the gas volume 46 of the intermediate pressure accumulator 42.

In addition, between the switching valve 182 and the heat exchanger 156 a branched from the receiving line 158 connecting line 184 is provided to the suction line 62, in which a designated as a whole by 186 check valve is provided which only a flow of refrigerant from the suction line 62 in the direction of the receiving line 158th allowed.

By closing the switching valve 182 is in operation of the parallel compressor 164 the ability to support the refrigerant compressor 14 of the refrigerant compressor unit 12 in terms of their compressor performance, since in this case via the check valve 186 refrigerant from the suction line 62 can be sucked into the receiving line 158 and on the Suction line 162 may be supplied to the preferably speed-controlled parallel compressor 164, which thus operates in parallel with the refrigerant compressors 14 of the refrigerant compressor unit 12, preferably one of - -

Refrigerant compressor 14 is also speed-controlled, so that a total of two power-controlled or variable-speed refrigerant compressor are available.

Further, a controller 192 is provided which on the one hand controls the switching valve 182 and on the other hand the parallel compressor 164, namely

according to the existing load conditions.

Thus, at full load operation, for example, in summer, the refrigerant circuit 10 is operated such that the high pressure PH, for example, is about 90 bar.

The intermediate pressure PZ in the intermediate pressure accumulator 42 is maintained at about 40 bar.

Further, for example, the low pressure PN is about 28 bar.

In this case, the parallel compressor 164 operates with the switching valve 182 open, so that the entire additional mass flow Z via the receiving line 158, the heat exchanger 156 and the suction line 162 to the suction port 166 of the parallel compressor 164 is supplied, which then compresses the additional mass flow to the high pressure PH, the at the pressure port 172 of the same.

In a part-load operation, for example in winter, the high pressure PH is lowered, for example, to 45 bar. In this case, the control valve 192, the switching valve 182 is closed and the parallel compressor 164 operates in parallel to the refrigerant compressor unit 12, for this purpose via the branch line 184 and the check valve 186 refrigerant from the suction line 62 is sucked into the receiving line 158, the heat exchanger 156 flows through and is supplied via the suction line 162 to the suction port 166 of the parallel compressor 164. - -

In this case, the additional mass flow Z flows via the expansion element 134, which is arranged in the discharge line 132, from the gas volume 46 in the intermediate pressure accumulator 42 into the gas volume 78 of the intermediate cryogenic pressure accumulator 74, wherein, as already described in detail in connection with the first exemplary embodiment in which the gas volume 78 in the intermediate cryogenic pressure accumulator 74 is deposited, a separation of liquid arising as a result of expansion of the additional mass flow Z in the intermediate cryogenic pressure accumulator 74.

Thus, the parallel compressor 164 sucks in the partial load operation refrigerant from the suction line 62 at low pressure PN and compresses the refrigerant to the high pressure PH, which is only in the range of, for example, in this case, 45 bar.

In a fifth embodiment of a refrigeration system according to the invention, shown in FIG. 5, those elements are those of the

preceding embodiments are identical, provided with the same reference numerals, so that in this regard is made in full content to the comments on the preceding embodiments reference.

In contrast to the fourth embodiment, a three-way valve 202 is provided in the receiving line 158 instead of the switching valve 182, which is able to connect either the branch line 184 with the receiving line 158 and the connection between the receiving line 158 and the discharge line 132 to interrupt or Connection between the

Make receiving line 158 and the discharge line 132 and to interrupt the connection between the branch line 184 and the receiving line 158. - -

This three-way valve 202 is also controlled by a controller 192, which also controls the parallel compressor 164, in the same manner as described in connection with the fourth embodiment, now instead of driving the switching valve 182, a control of the three-way valve 202 is carried out to the same

To realize operating conditions.

In a sixth embodiment of an inventive

Refrigeration system, shown in Fig. 6, those elements which are identical to those of the preceding embodiments are the same

Provided with reference numerals, so that in this regard to the full content

Embodiments to the preceding embodiments reference

can be taken.

In contrast to the fifth embodiment, instead of the

Three-way valve 202, a three-way valve 204 is provided, which on the one hand with the suction line 18 on the other hand connected to the suction line 162 and is able to connect one of these lines 18 or 162 with the suction port 166 of the parallel compressor 164.

Thus, the three-way valve 204 provides the possibility of the parallel compressor 164 either a part of the additional mass flow Z or the entire additional mass flow Z via the suction line 162, the heat exchanger 156 and the receiving line 158 or the parallel compressor 164 via the suction line 18 expanded refrigerant from the

Normal cooling mass flow N and the main cooling mass flow TH supplied for compression. - -

The three-way valve 204 is also controllable by the controller 192, which also controls the parallel compressor 164, in the same manner as described in connection with the fourth embodiment, wherein instead of driving the switching valve 182 a

Control of the three-way valve 204 is carried out to realize the same operating conditions.

A refrigeration system 10 according to the embodiments described above can be - as shown in Fig. 7 - in particular for energy-optimized operation of a building 210, in particular a

Food market, with facilities 210 are provided in an interior 212 of the building.

In the interior 212 of the building 210, for example, a cooling device 214 is provided, in which refrigerated goods or objects, such as food, at a normal cooling temperature, that is maintained at a temperature in the range of usually 0 ° C to 5 ° C, wherein the cooling of this cooling device is performed by the normal cooling stage 52 of the refrigeration system 10 according to the invention.

Furthermore, a deep-freezing device 216 is provided in the interior space 212, in which deep-frozen material or objects, for example frozen goods, on

Frozen temperature is maintained, for example at a temperature in the range of -30 ° C to -10 ° C.

The cooling of the deep-freezing device 216 takes place through the deep-freezing stage 82 of the refrigeration system 10 according to the invention.

Except for the normal cooling stage 52, the freezing stage 82 and the heat exchanger 34, all other components of the refrigeration system 10 according to the invention are preferably arranged in a space 218 which is either part of the

Building 210 may be located next to building 210. - -

For its part, the heat exchanger 34 arranged outside the space 218, for example, draws in ambient air 222 in order to cool the high-pressure PH refrigerant with this ambient air 222.

In order to be able to operate the building 210 in an energy-efficient manner, the high-pressure-side heat exchanger 34, which is arranged outside the building 210 and serves for heat exchange with the ambient air 222, is connected in parallel with a heat exchanger 224, which is assigned to the building 210 and serves to enter the building Inner space 212 of the building 210 to be heated indoor air to heat 226, for which purpose the heat exchanger 224 can suck according to requirements ambient air 222 of the building 210 and / or indoor air of the building 210 for heating.

Thus, the resulting on the high pressure side of the refrigeration systems 10 heat according to the invention can be used energy efficient for building heating, especially in times when the outside temperature of the building 210 is below an aspired in the interior 212 of the same room temperature.

In addition, in the building 210, in particular in the interior 212 of the same, nor a cooling heat exchanger 232 is provided which serves to cool the interior 212 of the building 210 at high outside temperatures or sunlight.

The cooling heat exchanger 232 is thereby fed, for example, by a parallel circuit 242 assigned to the intermediate pressure collector 42, which receives liquid refrigerant at a temperature corresponding to the intermediate pressure PZ in the intermediate pressure accumulator 42 from the bath 44 of the liquid refrigerant in the intermediate pressure accumulator 42 via a supply line 244, evaporates in an evaporator 246 and via a derivative 248 again the gas volume 46 of the intermediate pressure accumulator 42 supplies. - -

In this case, preferably, the evaporator 246 is designed as a flooded evaporator, which is cooled by gravity due to the entering into this liquid refrigerant, said refrigerant then evaporates in this evaporator 246.

Preferably, a control element 252 is provided for controlling or regulating the parallel circuit 242, which in the simplest case may be a valve or, in the somewhat more complex case, a power-controlled pump for liquid refrigerant.

The evaporator 246, for example, in turn cools a transformer circuit 262, in which, for example, a heat transfer medium, such as air, brine or water circulates, which in turn flows through the cooling heat exchanger 232 in the building 210 and can be used there to cool an air stream 264, said air stream 264 in the simplest case may be an air flow of circulated indoor air 226 of the building 210.

Typically, temperatures between 5 ° C. and 0 ° C. are present in the intermediate pressure accumulator 42, so that the cooling heat exchanger 232 is operated at these temperatures and thus the air flow 264, which flows through the cooling heat exchanger 232, can be cooled in a simple manner.

On the other hand, such cooling in turn requires an increased

Additional mass flow Z, which accumulates in the intermediate pressure accumulator 42 and must be introduced either via the discharge line 132 and the expansion element 134 in the intermediate cryogenic pressure accumulator 74 and then after the same must be compressed by the refrigerant compressor unit 12 or discharged through the Zusatzmassenstromabfuhreinheit 160. In any case, this results in more heat on the high pressure side, which can either be dissipated by the heat exchanger 34 to the environment of the building 210 or optionally at low - -

Conditions can be used by the heat exchanger 224 to heat the building 210, for example, after dehumidification of outside air, which the indoor air 226 can be supplied to the building 210 as supply air.

Furthermore, the intermediate cryogenic pressure accumulator 74 is associated with a parallel circuit 272, which has one of the bath 76 in the intermediate cryogenic pressure accumulator 74 liquid refrigerant receiving supply line 274 which supplies this refrigerant to an evaporator 276, which in turn vaporizes the liquid refrigerant and a drain 278 again the gas volume 78th fed in Tiefkühlzwischendrucksammler 74.

Also in this parallel circuit 272, the evaporator 276 is formed, for example, as a flooded evaporator, so that the liquid refrigerant enters due to gravity, is vaporized in the evaporator 276 and then returned to the gaseous via the supply line 274 the gas volume 78 in Tiefkühlzwischendrucksammler 74.

In order to control or regulate the parallel circuit 272, a control element 282 is likewise provided in the supply line 274, which may be designed either in the form of a switching valve or possibly also in the form of a power-controlled pump.

The evaporator 276 is further coupled to a circuit 292 in which an external heat exchanger 294 is disposed outside of

Building 210 and also outside the room 218 is arranged.

With this heat exchanger 294, for example, it is possible to absorb heat at low ambient temperatures and to supply this heat to the refrigerant circuit 12, in turn, more heat to the - -

Heat exchanger 224 for cooling the compressed at high pressure PH

To have available refrigerant and thus, for example, in winter at low outside temperatures to heat the interior 212 of the building 210.

That is, in this case, the refrigeration system 10 according to the invention not only serves to operate the cooling device 214 and the deep cooling device 216 in the building 210, but at the same time also to heat the interior 212 of the building via the heat exchanger 224.

For example, at normal pressures in the intermediate cryogenic pressure accumulator 74, the refrigerant is present at a temperature between -12 ° C and -5 ° C, so that at outside temperatures which are higher than the saturated temperature in the intermediate cryogenic pressure accumulator 74, heat can always be absorbed via the heat exchanger 294 , which in turn can then be discharged via the heat exchanger 224 into the interior 212 of the building 210.

Claims

PATENT APPLICATIONS

1. refrigeration system comprising a refrigerant circuit (10), in which a total mass flow (G) of a refrigerant is guided, a in the refrigerant circuit (10) arranged, high-pressure side refrigerant cooling heat exchanger (34), in the refrigerant circuit (10) arranged expansion element (38) cooling in the active state, the total mass flow (G) of the refrigerant by expansion, thereby generating a main mass flow (H) of liquid refrigerant and an additional mass flow (Z) of gaseous refrigerant entering an intermediate pressure accumulator (42) and in this in the main mass flow (H) and the additional mass flow (Z) are separated, at least one normal cooling stage (52), which from the

Main mass flow (H) in the intermediate pressure accumulator (42) dissipates a normal cooling mass flow (N) and expanded in at least one normal cooling expansion unit (54) to a low pressure (PN), thereby providing cooling capacity for normal cooling, and a refrigerant compressor unit (12) compresses the expanded normal cooling mass flow (N) from low pressure (PN) to high pressure (PH),

There is coupled to the intermediate pressure accumulator (42) a parallel circuit (242) which removes liquid refrigerant from the main mass flow (H), feeds it to an evaporator (246), and supplies vaporized refrigerant to the additional mass flow (Z).

2. Refrigeration system according to claim 1, characterized in that the

Evaporator (246) is designed as a flooded evaporator (246) and operates.

3. refrigeration system according to claim 2, characterized in that the flooded evaporator (246) operates on the thermosiphon principle.

4. Refrigeration system according to one of the preceding claims, characterized in that in the parallel circuit (242), a pump (252) is provided.

5. Refrigeration system according to one of the preceding claims, characterized

in that a control element (252) for controlling the circulating refrigerant is arranged in the parallel circuit (242).

6. Refrigeration system according to claim 5, characterized in that the

Control (252) is designed as a control valve.

7. refrigeration system according to claim 5 or 6, characterized in that the control element (252) is designed as controllable in terms of their capacity pump.

8. Refrigeration system according to one of the preceding claims, characterized

characterized in that the evaporator (246) itself as a heat exchanger (34, 226) for cooling an interior (212) of a building (210) is formed.

9. Refrigeration system according to one of the preceding claims, characterized

in that the evaporator (246) is coupled to a refrigeration transmission circuit (262) in which a cooling heat exchanger (232) for cooling a building (210) is arranged.

10. Refrigeration system according to the preamble of claim 1 or according to one of the preceding claims, characterized in that cooling as an alternative or in addition to the high-pressure side refrigerant

Heat exchanger (34) is a heat exchanger (226) for heating a building (210) is provided.

11. A refrigeration system according to the preamble of claim 1 or any one of the preceding claims, characterized in that a Tiefkühlzwischenpischendruckexpansionseinheit (72) is provided, which from the main mass flow (H) in the intermediate pressure collector (42) taken Tiefkühlgesamtmassenstrom (TG) to a Tiefkühlzwischendruck (PTZ) expands, thereby cooling and a Tiefkühlhauptmassenstrom (TH) of liquid refrigerant and a Tiefkühl- zusatzmassenstrom (TZ) generated from gaseous refrigerant and this feeds a Tiefkühlzwischendrucksammler (74), in which a separation of the Tiefkühlhauptmassenstroms (TH) of the frozen - Additional mass flow (TZ) takes place, that a Tiefkühlhauptmassenstrom (TH) from the Tiefkühlzwischendrucksammler (74) laxative Tiefkühlstufe (82) is provided, which has at least one Tiefkühl- expansion unit (84) and by expansion of the Tiefkühlhauptmassenstroms (TH) to a Tiefkühlniederdruck (PTN) Cooling capacity for freezing provides that a freezer compressor unit (102) is provided, which compresses the deep-freeze low pressure (PTN) expanded main mass cooling (TH) and the normalized mass flow (N) of low pressure (PN) to high pressure (PH) compressing refrigerant compressor unit (12 ) also for compression to high pressure (PH) supplies.

12. A refrigeration system according to claim 11, characterized in that with the Tiefkühlzwischendrucksammler (74) a parallel circuit (272) is coupled, which takes liquid refrigerant from the main cooling mass flow (TH), an evaporator (276) feeds and vaporized refrigerant the Tiefkühlzusatzmassenstrom (TZ) supplies.

13. Refrigeration system according to claim 12, characterized in that the

Evaporator (276) is designed as a flooded evaporator (276) and operates.

14. Refrigeration system according to claim 13, characterized in that the flooded evaporator (276) operates on the thermosiphon principle.

15. Refrigeration system according to one of the preceding claims, characterized

in that a pump (282) is provided in the parallel circuit (272).

16. Refrigeration system according to one of claims 12 to 15, characterized in that in the parallel circuit (276), a control element (282) is arranged to control the circulating refrigerant.

17. Refrigeration system according to claim 16, characterized in that the

Control (282) is designed as a control valve.

18. Refrigeration system according to claim 16 or 17, characterized in that the control element (282) is designed as controllable with respect to their capacity pump.

19. Refrigeration system according to one of claims 12 to 18, characterized in that the evaporator (276) itself is designed as a heat exchanger for heat absorption from a heat source.

20. Refrigeration system according to one of claims 12 to 19, characterized in that the evaporator (276) is coupled to a circuit (292) in which a heat exchanger (294) for receiving heat from the heat reservoir is arranged.

21. Refrigeration system according to one of claims 11 to 20, characterized in that the additional mass flow (Z) from the intermediate pressure accumulator (42) via an expansion element (134) expands and the cryogenic intermediate pressure accumulator (74) is supplied in such a way that in Frozen intermediate pressure collector (74) deposits a liquid phase formed by expansion by means of the expansion member (134) in the main cooling main flow (TH) within the intermediate cryogenic pressure accumulator (74) and in that an intermediate cryogenic pressure accumulator (74) forming gas phase of the additional mass flow (Z) together with the Tiefkühlzusatzmassenstrom (TZ ) an additional mass flow compressor unit (12) for compression to high pressure (PH) is supplied.

22. Refrigeration system according to claim 21, characterized in that the

Gas phase of the additional mass flow (Z) together with the Tiefkühlzusatzmassenstrom (TZ) of the Tiefkühlzwischendrucksammler (74) without expansion of the additional mass flow compressor unit (12) is supplied.

23. Refrigeration system according to claim 22, characterized in that a

Frozen intermediate pressure (PTZ) in Tiefkühlzwischendrucksammler (74) in a pressure range that ranges from the low pressure (N) to the intermediate pressure (PZ).

24. Refrigeration system according to claim 22 or 23, characterized in that the intermediate cryogenic pressure (PTZ) in the region of the low pressure (N).

25. Refrigeration system according to one of claims 21 to 24, characterized in that the refrigerant compressor unit (12) and the additional mass flow compressor unit comprises.

26. Refrigeration system according to one of claims 21 to 25, characterized in that the gas phase of the additional mass flow (Z) together with the Tiefkühlzusatzmassenstrom (TZ) of the Tiefkühlzwischendrucksammler (74) together with the low pressure (PN) expanded normal cooling mass flow (N) of the refrigerant compressor unit (12) is supplied.

27. Refrigeration system according to one of claims 21 to 26, characterized in that by the expansion member (134) expanded

Additional mass flow to the intermediate cryogenic pressure accumulator (74) spatially separated from a Tiefkühlzwischendrucksammler (74)

leading away discharge line (122) for the cryogenic intermediate pressure accumulator (74) opens.

28. Refrigeration plant according to one of claims 21 to 27, characterized in that a flow velocity of the refrigerant in the discharge line (122) is less than 2m / s, even better less than 0.5m / s, and more preferably less than 0, 3m / s.

29. Refrigeration system according to one of claims 21 to 28, characterized in that a liquid content of the discharge line (122) from the intermediate cryogenic pressure collector (74) escaping refrigerant is less than 5 m-%, more preferably less than 3 m-% and preferably less than 1m%.

30. refrigeration system according to one of claims 21 to 29, characterized in that the additional mass flow (Z) from the in the intermediate pressure accumulator (42) forming bubble (46) via a discharge line (132) the deep-frozen intermediate pressure collector (74) and fed through the in the discharge line (152) provided expansion member (134) is relaxed to the Tiefkühlzwischendruck (PTZ).

31. A refrigeration system according to claim 30, characterized in that the by the expansion device (134) relaxed additional mass flow (Z) of a bubble (78) in the intermediate cryogenic pressure collector (74) is supplied.

32. Refrigeration system according to one of claims 21 to 31, characterized in that of the expansion member (134) expanded part of the additional mass flow (Z) of the bladder (78) in Tiefkühlzwischendruck- collectors (74) in a Abscheidehöhe of 300 mm to 400 mm above the bath (76) in the intermediate cryogenic pressure accumulator (74).

33. Refrigeration system according to one of claims 21 to 32, characterized in that a Zusatzmassenstromabfuhreinheit (160) is provided, with which at least in certain operating modes at least a portion of the additional mass flow (Z) from the intermediate pressure collector (42) removed and without further expansion, starting from the

Intermediate pressure (PZ) of a compression to high pressure (PH) is supplied.

34. Refrigeration system according to claim 33, characterized in that the

Additional mass flow discharge unit (160) has a heat exchanger (156) for heating the additional mass flow (Z) prior to its compression to high pressure (PH).

35. Refrigeration system according to claim 34, characterized in that the

Heat exchanger (156) is flowed through by the deep-freeze compressor unit (102) compressed main cooling main mass flow (TH).

36. Refrigeration system according to one of claims 33 to 35, characterized in that the Zusatzmassenstromabfuhreinheit (160) the discharged portion of the additional mass flow (Z) an economizer connection (21) of refrigerant compressors (14 ') of the refrigerant compressor unit (12') supplies.

37. Refrigeration system according to one of claims 33 to 35, characterized in that the Zusatzmassenstromabfuhreinheit (160) supplies the discharged portion of the additional mass flow (Z) a parallel compressor (164), which is provided in addition to the refrigerant compressor unit (12).

38. Refrigeration system according to claim 37, characterized in that the parallel compressor (164) operates under power control.

39. Refrigeration system according to claim 38, characterized in that by regulating the power of the parallel compressor (164), a regulation of the intermediate pressure (PZ) to a predetermined value.

40. Refrigeration system according to one of claims 33 to 39, characterized in that the Zusatzmassenstromabfuhreinheit (160) by a switching member (182, 202, 204) with the intermediate pressure accumulator (42) is connectable or separable from this.

41. Refrigeration system according to one of claims 33 to 40, characterized in that the Zusatzmassenstromabfuhreinheit (160) by a switching member (186, 202, 204) with the Tiefkühlzwischendrucksammler (74) for removing the gas phase of the additional mass flow (Z) together with the Tiefkühlzusatzmassenstrom ( TZ) connectable and separable from this.

42. Refrigeration system according to one of claims 21 to 41, characterized in that at least one of the refrigerant compressor (14 ') of the refrigerant compressor unit (12) is power-controlled.

43. Refrigeration system according to one of claims 33 to 42, characterized in that in a first operating mode the Zusatzmassen- stromabfuhreinheit (160) from the Zwischendrucksammier (42) is separated and that the entire additional mass flow (Z) expands and fed to the Tiefkühlzwischendrucksammler (74) becomes .

44. The refrigeration system according to claim 33, wherein in a second operating mode the additional mass flow discharge unit is connected to the intermediate pressure collector and discharges part of the additional mass flow and Z) is supplied to the cryogenic intermediate pressure accumulator (74).

45. Refrigeration system according to one of claims 33 to 44, characterized in that in a third operating mode, the additional mass flow discharge unit (160) is connected to the intermediate pressure collector (42) and discharges the entire additional mass flow (Z).