DE102019111309A1 - Ejector-based cooling system and cooling method - Google Patents

Abstract

According to various embodiments, a cooling system (100) can set up a basic cooling circuit (102), a subcooling system (112), which can be configured to subcool refrigerant and provide the basic cooling circuit (102), an ejector (118), a part of the refrigerant from the base cooling circuit (102) and receiving another portion of the refrigerant from the subcooling system (112), wherein the ejector (118) is further configured to pressure the portion of the refrigerant received from the subcooling system (112) to increase, and a separator (120) which is set up such that the refrigerant is provided in a gas phase from the separator (120) to the basic circuit (102), and that the refrigerant in a liquid phase from the separator (120) to the Subcooling system (112) is provided.

Description

Various embodiments relate to an ejector-based cooling system and a cooling method.

A cooling system (e.g. a refrigeration system) is used, for example, to preserve food or to regulate the temperature in buildings or vehicles. Such a system is usually based on a refrigerant that circulates through the system and exchanges heat with the environment so that a cooling effect can be achieved in the desired areas. In a conventional refrigeration system, an ejector can be used in conjunction with a compressor to circulate the refrigerant in the system. In particular, an ejector can function with no moving parts and therefore can be used as a simple alternative to a more complex device (such as a pump) for increasing the pressure of the refrigerant in the refrigeration system. For example, an ejector, an evaporator and a collector can form a partial circuit of a refrigeration system, wherein the ejector can be used, for example, to suck in the refrigerant from the evaporator outlet and / or to recirculate the refrigerant in the partial circuit.

The problem with this variant is the recirculation of the refrigeration machine oil, which is usually used to lubricate the compressor. Refrigerating machine oil can collect in the ejector-collector-evaporator sub-circuit so that it is no longer available to the compressor. Furthermore, in such a previously common refrigeration system, the ejector should be adapted to the properties of the evaporator and / or the compressor (e.g. to the operating temperature, the operating pressure, the mass flow, etc.) so that certain desired operating conditions can be met.

Various embodiments relate to an ejector-based cooling system and cooling methods in which oil recirculation into the system is ensured and in which independent control of an ejector is made possible.

The cooling system described herein can be set up in such a way that refrigerating machine oil, which is output from a compression unit during operation, can circulate around the system and be transported back to the compression unit without accumulating at undesired locations along the flow path. Furthermore, the cooling system described herein can have an ejector and be set up in such a way that the ejector is decoupled from a main heat exchanger (e.g. a main evaporator) of the cooling system, so that the operating parameters of the ejector can be selected and adjusted independently of the operating parameters of the main heat exchanger, in particular independently from a mass flow of the main heat exchanger.

According to various embodiments, a cooling system can have a basic cooling circuit, a subcooling system that is configured to subcool refrigerant and provide the base cooling circuit, an ejector configured to receive part of the refrigerant from the base cooling circuit and another part of the refrigerant from the subcooling system, wherein the ejector is further configured to increase a pressure of the part of the refrigerant received by the subcooling system, and a separator which is configured such that the refrigerant is provided in a gas phase from the separator to the basic circuit , and that the refrigerant is provided in a liquid phase from the separator to the subcooling system.

According to various embodiments, a cooling method may include a separation of a gas phase and a liquid phase of a refrigerant, subcooling the liquid refrigerant, providing the gaseous refrigerant and the supercooled liquid refrigerant to a basic cooling circuit, and providing part of the refrigerant to be supercooled and another Part of the refrigerant from the basic cooling circuit is an ejector.

Further advantageous refinements of the cooling method emerge from the description of the cooling system and vice versa.

Embodiments of the invention are shown in the figures and are explained in more detail below.

• 1A ein Kühlungssystem aufweisend einen Ejektor in einer schematischen Darstellung gemäß verschiedenen Ausführungsformen;
• 1B einen Ejektor in einer schematischen Darstellung gemäß verschiedenen Ausführungsformen;
• 2A ein Kühlungssystem aufweisend einen Ejektor in einer schematischen Darstellung gemäß verschiedenen Ausführungsformen;
• 2B ein Kühlungssystem aufweisend einen Ejektor in einer schematischen Darstellung gemäß verschiedenen Ausführungsformen;
• 3 ein Kühlungssystem aufweisend einen Tiefkühlkreislauf in einer schematischen Darstellung gemäß verschiedenen Ausführungsformen; und
• 4 ein Ablaufdiagramm eines Kühlungsverfahrens gemäß verschiedenen Ausführungsformen.

Show it

• 1A a cooling system having an ejector in a schematic illustration according to various embodiments;
• 1B an ejector in a schematic illustration according to various embodiments;
• 2A a cooling system having an ejector in a schematic illustration according to various embodiments;
• 2 B a cooling system having an ejector in a schematic illustration according to various embodiments;
• 3 a cooling system having a deep-freeze circuit in a schematic illustration according to various embodiments; and
• 4th a flow diagram of a cooling method according to various embodiments.

In the following detailed description, reference is made to the accompanying drawings, which form a part hereof, and in which there is shown, for purposes of illustration, specific embodiments in which the invention may be practiced. In this regard, directional terminology such as "top", "bottom", "front", "back", "front", "back", "downstream", "upstream", etc. is used with reference to the orientation of the figure being described ( en) used. Because components of embodiments can be positioned in a number of different orientations, the directional terminology is used for purposes of illustration and is in no way limiting. It goes without saying that other embodiments can be used and structural or logical changes can be made without departing from the scope of protection of the present invention. It goes without saying that the features of the various exemplary embodiments described herein can be combined with one another, unless specifically stated otherwise. Therefore, the following detailed description is not to be taken in a limiting sense, and the scope of the present invention is defined by the appended claims.

In the context of this description, the terms “connected”, “connected” and “coupled” are used to describe both a direct and an indirect connection, a direct or indirect connection and a direct or indirect coupling.

In the context of this description, the term "upstream" is used to describe the relative arrangement of one or more elements in relation to a direction of flow of a fluid (e.g. a refrigerant). For example, the term “upstream in relation to an element” can describe a point which is arranged in front of the element (e.g. in front of an entry of the element), so that the fluid first flows through this point and then into the element. For example, a first element can be arranged upstream with respect to a second element, so that the fluid first flows into the first element and then into the second element. It goes without saying that the term “upstream” does not necessarily mean that the first element and the second element are arranged directly next to one another, but that other elements can also be arranged between the first element and the second element (e.g. along the direction of flow).

In the context of this description, the term "downstream" is used to describe the relative arrangement of one or more elements in relation to a direction of flow of a fluid (e.g. a refrigerant). For example, the term "downstream in relation to an element" can describe a point which is arranged after the element (e.g. after an exit of the element) so that the fluid flows first into the element and then through this point. For example, a first element can be arranged downstream with respect to a second element, so that the fluid first flows into the second element and then into the first element. It goes without saying that the term “downstream” does not necessarily mean that the first element and the second element are arranged directly next to one another, but other elements can also be arranged between the first element and the second element (e.g. along the direction of flow).

In the context of this description, the terms “heat exchanger” and “heat exchanger” are used interchangeably. Similarly, the terms "heat exchange" and "heat transfer" are used interchangeably.

In the figures, identical or similar elements are provided with identical reference symbols, as far as this is appropriate.

1A illustrates a cooling system 100 in a schematic representation according to various embodiments.

The cooling system 100 (For example a refrigeration system, for example in a supermarket or in another building, for which a temperature lower than, for example, 10 ° C. is desired) can have a basic cooling circuit 102 (also marked as basic refrigerant circuit). According to various embodiments, the basic cooling circuit 102 have the components of a conventional vapor compression cycle, as will be explained in more detail below. A refrigerant (eg carbon dioxide, CO ₂ ) can circulate through such a circuit and exchange heat with a fluid to be cooled, so that the fluid can be cooled.

For example, the basic cooling circuit 102 , a first (e.g. heat-absorbing) heat exchanger 104 , a compression unit 106 , a second (e.g. heat-emitting) heat exchanger 108 and a pressure reducing device 110 exhibit.

According to various embodiments, the heat-absorbing heat exchanger 104 an entrance 104a and an exit 104b have, which can be connected to one another by means of a first flow path to coolant between the inlet 104a and the exit 104b to be transported by means of the first flow path. The heat-absorbing heat exchanger 104 can be set up in such a way that the refrigerant flows through the first flow path and this is in a heat exchange relationship with a fluid to be cooled (e.g. air, water, brine, etc.), so that heat is absorbed from the fluid to be cooled into the refrigerant, if this through the heat-absorbing heat exchanger 104 flows. The fluid to be cooled can thus be cooled.

According to various embodiments, the heat-absorbing heat exchanger 104 have a second flow path which is in a heat exchange relationship with the first flow path and through which the fluid to be cooled can flow.

According to various embodiments, the cooling system 100 be set up in such a way that the fluid to be cooled passes the heat-absorbing heat exchanger 104 flows around. For example, a circulation system (eg one or more pipes, a fan, a fan, etc.) can be used to circulate the fluid to be cooled (eg air, water, brine, etc.) around the heat-absorbing heat exchanger 104 to get in motion, so that a more efficient heat exchange between the through the heat-absorbing heat exchanger 104 flowing refrigerant and the fluid to be cooled is made possible.

According to various embodiments, the heat-absorbing heat exchanger 104 an evaporator (eg a tube evaporator, a plate heat exchanger, a lamellar evaporator, etc.) or be set up as an evaporator. According to various embodiments, the heat-absorbing heat exchanger 104 but also be a sublimator or be set up as a sublimator. The use of a sublimator and a refrigerant to be sublimated can make it possible to achieve lower temperature ranges than by means of an evaporator and a refrigerant to be evaporated.

The heat-absorbing heat exchanger 104 can be set up in such a way that the refrigerant undergoes a phase change when it passes through the heat-absorbing heat exchanger 104 flows. For example, the refrigerant can evaporate or sublime when it passes through the heat-absorbing heat exchanger 104 flows. Thus, the heat absorbing heat exchanger 104 be set up in such a way that it receives liquid refrigerant (eg refrigerant in a liquid phase) and emits evaporated refrigerant (eg refrigerant in a gas phase). For example, the heat-absorbing heat exchanger 104 be set up in such a way that the refrigerant can evaporate and absorb latent heat (eg heat of evaporation) when it passes through the heat-absorbing heat exchanger 104 flows.

According to various embodiments, the cooling system 100 be set up so that the refrigerant at the entrance 104a of the heat-absorbing heat exchanger 104 is at such a pressure level that the saturation temperature of the refrigerant is lower (e.g. 5 ° C lower, 10 ° C lower, 20 ° C lower, etc.) than the temperature of the fluid to be cooled, so that the refrigerant heats from the to can absorb cooling fluid in an efficient manner. The cooling system is clear 100 also be set up so that the temperature of the refrigerant at the entrance 104a of the heat-absorbing heat exchanger 104 lower (eg 5 ° C lower, 10 ° C lower, 20 ° C lower, etc.) than the temperature of the fluid to be cooled. According to various embodiments, the cooling system 100 be set up so that the pressure of the refrigerant at the entrance 104a of the heat-absorbing heat exchanger 104 is in a range from approximately 10 bar to approximately 40 bar and / or that the temperature of the refrigerant at the inlet 104a of the heat-absorbing heat exchanger 104 is in a range from about -35 ° C to about 10 ° C, for example in a range from about -20 ° C to about 5 ° C. According to various embodiments, the cooling system 100 be set up in such a way that the mass flow of refrigerant (also referred to as mass flow) through the heat-absorbing heat exchanger 104 is in a range from about 0.4 kg / s to about 0.6 kg / s. The mass flow of refrigerant can be adjusted based on the cooling effect to be achieved.

The pressure ranges, the temperature ranges and the mass flow ranges are selected as examples and can apply to CO ₂ as a refrigerant, for example. It goes without saying that the pressure ranges, the temperature ranges and the mass flow ranges can be dependent on the refrigerant used and / or on the desired operation, and these can be adapted accordingly based on the refrigerant used and / or on the desired operation.

According to various embodiments, the heat-absorbing heat exchanger 104 be set up such that the refrigerant is overheated when it is through the heat-absorbing heat exchanger 104 flows so that the temperature of the heat-absorbing heat exchanger 104 issued refrigerant is higher (e.g. 5 ° C higher, 10 ° C higher, etc.) than the boiling temperature of the refrigerant (e.g. than the boiling temperature at the pressure level of the heat-absorbing heat exchanger 104 issued refrigerant).

According to various embodiments, the compression unit 106 in relation to the heat-absorbing heat exchanger 104 be arranged downstream. The compression unit 106 can be set up, the (eg evaporated or sublimated) refrigerant (eg directly) from the heat-absorbing heat exchanger 104 suck in. According to various embodiments, the compression unit 106 and the exothermic heat exchanger 104 be connected to each other: the compression unit 106 can for example be an input 106a and an exit 106b have, and the entrance 106a the compression unit 106 can with the output 104b of the heat-absorbing heat exchanger 104 (for example by means of a line, such as a suction line) be or will be connected.

According to various embodiments, the compression unit 106 be set up to compress the refrigerant. The compression unit can be clearly illustrated 106 be set up so that the refrigerant at the exit 106b the compression unit 106 is at a higher pressure level (eg in a range from about 50 bar to about 110 bar) than at the inlet 106a the compression unit 106 (e.g. the pressure of the refrigerant at the inlet 106a the compression unit 106 be in a range from about 10 bar to about 40 bar). Accordingly, the refrigerant also has at the outlet 106b the compression unit 106 a higher temperature (eg in a range of about 75 ° C to about 130 ° C) than at the entrance 106a the compression unit 106 (e.g. the temperature of the refrigerant at the entrance 106a the compression unit 106 be in a range from about 0 ° C to about 30 ° C). This means that the boiling point of the refrigerant can also be increased.

That from the compression unit 106 Dispensed refrigerant can thus be in a high pressure and high temperature state (e.g. the pressure of the refrigerant can be in a range from about 50 bar to about 110 bar and / or the temperature of the refrigerant can be in a range from about 75 ° C to about 130 ° C). According to various embodiments, the cooling system 100 be set up such that the mass flow of refrigerant through the compression unit 106 is in a range from about 0.4 Kg / s to about 1.1 Kg / s.

According to various embodiments, the compression unit 106 a compressor (for example a reciprocating compressor, a screw compressor, a rotary piston compressor, a turbo compressor, a scroll compressor, etc.) which can be set up to compress the refrigerant. The compressor can, for example, be a single-stage compressor, but also a multi-stage compressor. The compression unit 106 but can also have a plurality of compressors (for example a composite with a plurality of compressors), for example in the event that a larger amount of refrigerant should be compressed. For example, the compressors of the plurality of compressors can be arranged parallel to one another, but alternatively or additionally the compressors of the plurality of compressors can also be arranged in series.

The compression unit 106 can also be set up, the refrigerant through the cooling system 100 to overturn. In other words, the compression unit 106 allow the refrigerant to pass through the cooling system 100 circulates.

According to various embodiments, the cooling system 100 be set up in such a way that the compressed refrigerant is the heat-emitting heat exchanger 108 is fed. For example, the heat-emitting heat exchanger 108 in relation to the compression unit 106 be arranged downstream. According to various embodiments, the compression unit 106 and the exothermic heat exchanger 108 connected to each other: the heat-emitting heat exchanger 108 can have an input 108a and an exit 108b have, and the entrance 108a of the heat-emitting heat exchanger 108 can with the output 106b the compression unit 106 (for example by means of a line, such as a hot gas line) be or will be connected.

According to various embodiments, the input 108a and the exit 108b of the heat-emitting heat exchanger 108 be connected by means of a first flow path to refrigerant between the inlet 108a and the exit 108b to be transported by means of the first flow path. The heat-emitting heat exchanger 108 can be set up in such a way that the refrigerant flows through the first flow path and this is in a heat exchange relationship with a secondary fluid (e.g. air, water, brine, etc.), so that heat is extracted from the refrigerant and absorbed into the secondary fluid, if this through the heat-emitting heat exchanger 108 flows. Thus, the refrigerant can be cooled.

According to various embodiments, the compression unit 106 so set up be that the refrigerant is compressed to such a pressure level that the saturation temperature of the refrigerant at the entrance 108a of the heat-emitting heat exchanger 108 higher (e.g. 5 ° C higher, 10 ° C higher, 15 ° C higher, etc.) than the temperature of the secondary fluid. This allows the refrigerant to transfer heat to the secondary fluid in an efficient manner. The cooling system is clear 100 be set up so that the temperature of the refrigerant at the entrance 108a of the heat-emitting heat exchanger 108 higher (e.g. 5 ° C higher, 10 ° C higher, 15 ° C higher, etc.) than the temperature of the secondary fluid. According to various embodiments, the pressure of the refrigerant at the inlet 108a of the heat-emitting heat exchanger 108 be in a range from about 50 bar to about 110 bar and / or the temperature of the refrigerant at the entrance 108a of the heat-emitting heat exchanger 108 be in a range from about 75 ° C to about 130 ° C. According to various embodiments, the cooling system 100 be set up in such a way that the mass flow of refrigerant through the heat-emitting heat exchanger 108 is in a range from about 0.4 Kg / s to about 1.1 Kg / s.

According to various embodiments, the heat-emitting heat exchanger can 108 have a second flow path which is in heat exchange relationship with the first flow path and through which the secondary fluid can flow.

According to various embodiments, the cooling system 100 be set up such that the secondary fluid is the heat-emitting heat exchanger 108 flows around. For example, a circulation system (e.g. one or more pipes, a fan, a fan, etc.) can be used to circulate the secondary fluid (e.g. air, water, brine, etc.) around the heat-emitting heat exchanger 108 to get in motion, so that a more efficient heat exchange between the through the heat-emitting heat exchanger 108 flowing refrigerant and the secondary fluid is enabled.

According to various embodiments, the heat-emitting heat exchanger can 108 a condenser (eg an air-cooled condenser, a water-cooled condenser, an evaporative condenser, etc.) or be set up as a condenser. The heat-emitting heat exchanger 108 can be set up as a condenser, for example, if the refrigerant has a conventional (eg subcritical) refrigerant. In this embodiment, the refrigerant can be condensed when it is passed through the heat-emitting heat exchanger 108 flows.

Alternatively, the heat-emitting heat exchanger 108 a gas cooler (e.g. a lamellar gas cooler, a gas cooler with ribs, etc.) or be set up as a gas cooler. The heat-emitting heat exchanger 108 can be set up, for example, as a gas cooler if the refrigerant has a supercritical refrigerant (eg CO ₂ ). In this embodiment, the refrigerant can be cooled when it is through the heat-emitting heat exchanger 108 flows without a phase change occurring.

It is understood that the cooling system 100 can also have further (eg heat-emitting) heat exchangers, which for example are in series and / or parallel to one another (eg in series and / or parallel to the heat-emitting heat exchanger 108 ) can be arranged. The other heat exchangers can be used, for example, for heat recovery (e.g. domestic water heating, heating, etc.).

That from the heat-emitting heat exchanger 108 Dispensed refrigerant can be in a high pressure state and / or high temperature state, e.g. the pressure of the refrigerant can be in a range from about 50 bar to about 110 bar and / or the temperature of the refrigerant can be in a range from about 10 ° C to about 50 Be ° C.

According to various embodiments, the cooling system 100 be set up in such a way that the cooled refrigerant of the pressure reduction device 110 is fed. The pressure reducing device 110 can for example in relation to the heat-emitting heat exchanger 108 be arranged downstream.

According to various embodiments, the pressure reduction device 110 be set up in such a way that the pressure of the refrigerant is reduced (for example reduced by 5 bar, by 10 bar, by 15 bar, etc.) when this is effected by the pressure reducing device 110 flows. In other words, the pressure reducing device 110 be set up in such a way that a pressure drop (of, for example, 5 bar, 10 bar, 15 bar, etc.) occurs in the refrigerant when the refrigerant passes through the pressure reducing device 110 flows. The temperature of the refrigerant is also clearly reduced (eg reduced by 5 ° C, 10 ° C, 15 ° C, etc.) when this is done by the pressure reducing device 110 flows. Thus, the pressure reducing device 110 used to regulate the pressure and / or temperature of the refrigerant.

That from the pressure reducing device 110 discharged refrigerant may thus be in a low pressure state. For example can be the pressure of the refrigerant at the outlet 110b the pressure reducing device 110 be in a range from about 10 bar to about 40 bar and / or the temperature of the refrigerant at the outlet 110b the pressure reducing device 110 in a range from about -35 ° C to about 10 ° C, for example in a range from about -20 ° C to about 5 ° C. According to various embodiments, the cooling system 100 be set up such that the mass flow through the pressure reduction device 110 is in a range from about 0.4 kg / s to about 0.6 kg / s.

The pressure reducing device 110 can be any suitable device (e.g. an ejector, an expander, a throttle valve, a capillary tube, an expansion valve, such as a thermal expansion valve, an electronic expansion valve, a manual expansion valve, etc.) which is set up to reduce the pressure of the refrigerant .

According to various embodiments, the cooling system 100 be set up in such a way that the pressure reduction device 110 refrigerant output to the heat-absorbing heat exchanger 104 is fed. The pressure reducing device 110 can in relation to the heat-absorbing heat exchanger 104 be arranged upstream, and for example, the pressure reducing device 110 with the heat-absorbing heat exchanger 104 (e.g. directly) connected. For example, the pressure reducing device 110 an entrance 110a and an exit 110b have, and the exit 110b the pressure reducing device 110 can with the entrance 104a of the heat-absorbing heat exchanger 104 (for example by means of a line, such as a liquid line) be or will be connected.

According to various embodiments, the pressure reduction device 110 be set up, the amount (eg the mass flow) of refrigerant, which the heat-absorbing heat exchanger 104 is fed to regulate. For example, the amount of refrigerant can be based on the performance of the heat-absorbing heat exchanger 104 be adjusted. According to various embodiments, the pressure reduction device 110 be set up, the pressure difference between the heat-emitting heat exchanger 108 (High pressure, for example the high pressure can be higher than the pressure of the critical point of the refrigerant, for example in a range from approximately 50 bar to approximately 110 bar) and the heat-absorbing heat exchanger 104 (Low pressure, for example in a range from approximately 10 bar to approximately 40 bar).

The pressure drop in the pressure reducing device 110 can cause some of the refrigerant in the pressure reducing device 110 starts to boil and evaporates (so-called flash gas is created), so that the refrigerant is at the outlet 110b the pressure reducing device 110 can be in a two-phase mixed state (gas phase and liquid phase). For example, the vapor quality of the refrigerant at the exit 110b the pressure reducing device 110 be less than 0.4, for example less than 0.25. The vapor quality represents that part of the refrigerant that is in the gas phase.

The pressure drop can change the phase of the refrigerant in the heat-absorbing heat exchanger 104 facilitate: the pressure drop reduces the saturation temperature of the refrigerant, so that heat between the refrigerant and the fluid to be cooled is more efficient in the heat-absorbing heat exchanger 104 can be transferred.

It goes without saying that there are also other elements in the basic cooling circuit 102 and / or in the cooling system 100 may be present. For example, temperature sensors and / or pressure sensors can be used to detect the temperature and / or the pressure of the refrigerant in different areas of the cooling circuit. The recorded temperature and / or the recorded pressure can be used as feedback parameters to determine the operating parameters of the elements of the basic cooling circuit 102 to control or regulate.

According to various embodiments, the cooling system 100 have a control system or a control system with a control loop. The control system or the regulating system can be set up, for example, the pressure reducing device 110 based on the detected temperature and / or on the detected pressure to control or regulate in such a way that a larger or a smaller amount of refrigerant the heat-absorbing heat exchanger 104 is fed. According to various embodiments, the control system or the regulation system can be set up, the compression unit 106 (e.g. a speed of a compressor in the compression unit 106 ) based on the detected temperature and / or on the detected pressure to control or regulate in such a way that the pressure and / or the flow rate of the refrigerant at the outlet 106b the compression unit 106 can be enlarged or reduced.

According to various embodiments, the refrigerant can have a subcritical refrigerant which remains in the cooling circuit in the subcritical area of the phase diagram. The refrigerant can also be supercritical Have refrigerant, which can be compressed from the subcritical area into the supercritical area. According to various embodiments, the refrigerant can contain a natural refrigerant, for example the refrigerant can contain carbon dioxide (CO ₂ , R-744). Carbon dioxide is a natural refrigerant with negligible (e.g. in relation to a fluorinated refrigerant) global warming potential (GWP), without ozone depletion potential (ODP), non-flammable and non-toxic. The refrigerant can, however, also have a hydrocarbon-based refrigerant, such as R170, R290, R600, etc. Alternatively or additionally, the refrigerant can also have a fluorinated refrigerant, such as R134a, R32, R1234yf, etc. According to various embodiments, the refrigerant can be a mixture from a plurality of refrigerants such as R404A, R410A, R407C, etc. It should be understood that the refrigerant can be selected based on the desired operation of the cooling system 100 (e.g. on the temperature range to be achieved).

According to various embodiments, the cooling system 100 a subcooling system 112 have, which is set up to subcool the refrigerant and the basic cooling circuit 102 provide. The subcooling system 112 can for example in relation to the heat-emitting heat exchanger 108 be arranged downstream, and / or with respect to the pressure reducing device 110 be arranged upstream.

The subcooling system 112 can be set up such that the temperature of the subcooling system 112 issued refrigerant is lower (e.g. 5 ° C lower, 10 ° C lower, etc.) than the boiling temperature of the refrigerant (e.g. than the boiling temperature at the pressure level of the subcooling system 112 issued refrigerant). The temperature of the subcooling system 112 The refrigerant dispensed may for example be in a range from about -35 ° C to about 10 ° C, for example in a range from about -20 ° C to about 5 ° C.

The subcooling of the refrigerant allows less flash gas in the pressure reducing device 110 is produced. This can reduce the efficiency of the cooling system 100 increase as a larger amount of liquid refrigerant enters the heat-absorbing heat exchanger 104 is available when less flash gas is in the pressure reducing device 110 is generated, and thus more heat can be absorbed in the refrigerant. The subcooling of the refrigerant also enables a higher enthalpy difference for the heat exchange in the heat-absorbing heat exchanger 104 is available, so that a higher cooling capacity is available and a more efficient heat exchange between the heat-absorbing heat exchanger 104 flowing refrigerant and the fluid to be cooled is made possible.

According to various embodiments, the subcooling system 112 a subcooling heat exchanger 114 have which is set up to subcool refrigerant. According to various embodiments, the supercooling heat exchanger 114 be an evaporator (e.g. a supercooling evaporator) or set up as an evaporator. The subcooling heat exchanger 114 but can also be a sublimator or be set up as a sublimator.

The subcooling heat exchanger 114 can for example have a first input 114a and a first exit 114b have, which can be connected to one another by means of a first flow path to coolant between the first inlet 114a and the first exit 114b to be transported by means of the first flow path. The subcooling heat exchanger 114 can also have a second entrance 114c and a second exit 114d which can be connected to one another by means of a second flow path to coolant between the second inlet 114c and the second exit 114d to be transported by means of the second flow path. According to various embodiments, the supercooling heat exchanger 114 be set up in such a way that the first flow path is in a heat exchange relationship with the second flow path, so that the refrigerant flowing into the first flow path can give off heat to the refrigerant flowing into the second flow path and can thus be subcooled. In other words, the subcooling heat exchanger 114 be set up in such a way that the refrigerant is supercooled when it is passed through the supercooling heat exchanger 114 (e.g. through the first flow path) flows.

According to various embodiments, the subcooling system 112 be set up such that a first part of the refrigerant the first inlet 114a of the subcooling heat exchanger 114 is supplied, and that a second part of the refrigerant to the second inlet 114c of the subcooling heat exchanger 114 is supplied, for example, the second part can be smaller than the first part. For example, the subcooling system 112 be set up such that the mass flow through the first flow path is in a range from approximately 0.4 kg / s to approximately 0.6 kg / s, and that the mass flow through the second flow path is in a range from approximately 0.025 kg / s to is approximately 0.25 Kg / s.

According to various embodiments, the supercooling heat exchanger 114 be set up such that heat is withdrawn from the refrigerant flowing through the first flow path and absorbed into the refrigerant flowing through the second flow path. Thus, the refrigerant flowing through the first flow path can be subcooled and the basic cooling circuit 102 to be provided. According to various embodiments, the supercooling heat exchanger 114 be set up such that the refrigerant flowing through the second flow path (for example partially) evaporates (or sublimates) due to the heat exchange between the refrigerant flowing through the second flow path and the refrigerant flowing through the first flow path. According to various embodiments, the supercooling heat exchanger 114 be set up such that the refrigerant flowing into the second flow path can evaporate at a lower pressure level than the refrigerant flowing into the first flow path, so that the undercooling of the refrigerant is made possible.

According to various embodiments, the first output 114b of the subcooling heat exchanger 114 and the entrance 110a the pressure reducing device 110 (for example by means of a line, such as a suction line, a liquid line, etc.) be or will be connected. The pressure reducing device 110 can thus be used to calculate the amount of heat from the subcooling heat exchanger 114 to regulate the refrigerant output, which the heat-absorbing heat exchanger 104 is fed.

According to various embodiments, the supercooling heat exchanger 114 be set up as a direct current heat exchanger, so that the refrigerant flowing through the first flow path and the refrigerant flowing through the second flow path flow in the same direction. Alternatively, the subcooling heat exchanger 114 be set up as a countercurrent heat exchanger, so that the refrigerant flowing through the first flow path and the refrigerant flowing through the second flow path flow in opposite directions. A more uniform temperature difference can be achieved in a counterflow heat exchanger, so that a more uniform heat flow density can be achieved. The subcooling heat exchanger 114 but can also be set up as a cross-flow heat exchanger in which the first flow path and the second flow path are arranged perpendicular to one another.

According to various embodiments, the subcooling system 112 be set up such that the temperature of the refrigerant at the first input 114a of the subcooling heat exchanger 114 higher (e.g. 5 ° C higher, 10 ° C higher, 15 ° C higher, etc.) than the temperature of the refrigerant at the second inlet 114c of the subcooling heat exchanger 114 so that the refrigerant flowing through the first flow path can be cooled (eg subcooled). For example, the temperature of the refrigerant at the first input 114a of the subcooling heat exchanger 114 be in a range from about 0 ° C to about 15 ° C, and the temperature of the refrigerant at the second inlet 114c of the subcooling heat exchanger 114 can be in a range from about -35 ° C to about 10 ° C, for example in a range from about -20 ° C to about -5 ° C.

According to various embodiments, the subcooling system 112 a pressure reducing device 116 (e.g. an ejector, an expander, a throttle valve, a capillary tube, an expansion valve, such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.), which can be set up in such a way that the pressure of the refrigerant is reduced (e.g. reduced by 5 bar, by 10 bar, by 15 bar, etc.) if this is done by the pressure reducing device 116 flows. In this way, the temperature of the refrigerant can also be reduced (eg reduced by 5 ° C, 10 ° C, 15 ° C, etc.), if this is done by the pressure reducing device 116 flows. The pressure reducing device 116 can for example in relation to the second input 114c of the subcooling heat exchanger 114 be arranged upstream, so that refrigerant the second inlet 114c is provided, which has a lower temperature (eg 5 ° C lower, 10 ° C lower, 15 ° C lower, etc.) than that of the first input 114a of the subcooling heat exchanger 114 provided refrigerants. Alternatively or additionally, the pressure reduction device 116 or some other pressure reducing device also downstream with respect to the subcooling heat exchanger 114 be arranged.

It is understood that other elements in the subcooling system 112 may be present. For example, temperature sensors and / or pressure sensors can be used to measure the temperature and / or the pressure of the refrigerant in different areas of the subcooling system 112 capture.

The detected temperature and / or the detected pressure can be used as feedback parameters in order to determine the operating parameters of the elements of the subcooling system 112 to control or regulate. For example, the control system or regulating system can be set up, the pressure reducing device 116 to control or regulate based on the detected temperature and / or on the detected pressure in such a way that a greater or lesser amount of refrigerant to the second inlet 114c of the subcooling heat exchanger 114 is fed.

According to various embodiments, the cooling system 100 an ejector 118 exhibit. The ejector 118 may be set up to take part of the refrigerant from the basic cooling circuit 102 to receive and another part of the refrigerant from the subcooling system 112 to recieve. According to various embodiments, the ejector 118 in relation to the exothermic heat exchanger 108 be arranged downstream and / or with respect to the subcooling system 112 be arranged upstream.

For example, the ejector can have a primary input 118a (e.g. a driving nozzle, in English "motive nozzle"), a secondary entrance 118c (e.g. a suction nozzle, in English "suction nozzle") and an exit 118b exhibit. According to various embodiments, the primary input 118a with the basic cooling circuit 102 connected: for example, the primary input 118a with the heat-emitting heat exchanger 108 (e.g. with the exit 108b of the heat-emitting heat exchanger 108 ) be or will be connected, e.g. by means of a line such as a suction line, a liquid line, etc.

According to various embodiments, the secondary input 118c with the subcooling system 112 connected: for example the secondary input 118c with the subcooling heat exchanger 114 (e.g. with the second exit 114d of the subcooling heat exchanger 114 ) be or will be connected, for example by means of a line, such as a suction line. According to various embodiments, the ejector 118 be set up, the refrigerant from the subcooling heat exchanger 114 (e.g. through the secondary entrance 118c ) to suck in.

According to various embodiments, the cooling system 100 be set up such that the mass flow through the primary input 118a of the ejector 118 is in a range from about 0.4 Kg / s to about 1.1 Kg / s and that the mass flow through the secondary input 118c of the ejector 118 is in a range from about 0.025 kg / s to about 0.25 kg / s.

According to various embodiments, the ejector 118 set up the pressure of the subcooling system 112 to increase the received part of the refrigerant. In other words, the ejector can 118 be set up by the subcooling system 112 to compress the received refrigerant. For example, the ejector 118 be set up in such a way that the pressure of the refrigerant dispensed is approximately 3 times (eg 5 times, 10 times, etc.) the pressure of the subcooling system 112 received refrigerant. The ejector 118 can thus be set up, the refrigerant in the subcooling system 112 to overturn so that the ejector 118 thanks to the pressure increase of the subcooling system 112 received part of the refrigerant a recirculation of the refrigerant in the subcooling system 112 provides. Thus, the use of pumps or other active components in the cooling system 100 in order to enable such a recirculation of the refrigerant to be avoided.

The ejector 118 can be of any suitable type of ejector (eg a steam jet ejector, a liquid jet ejector, a two-phase ejector, a “high-lift” ejector, etc.).

The ejector 118 can thus be set up in such a way that this is at the primary input 118a High pressure refrigerant (eg the pressure of the refrigerant can be in a range from about 50 bar to about 110 bar) from the basic cooling circuit 102 (e.g. from the heat-emitting heat exchanger 108 ) and that this is received at the secondary input 118c Low pressure refrigerant (eg the pressure of the refrigerant can be in a range of about 10 bar to about 30 bar) from the subcooling system 112 (e.g. from the subcooling heat exchanger 114 ) receives. According to various embodiments, this can be done by the ejector 118 refrigerant dispensed are at a medium pressure level (for example in a range from approximately 30 bar to approximately 65 bar), and the temperature of the by the ejector 118 For example, the refrigerant dispensed may be in a range from about 0 ° C to about 15 ° C.

According to various embodiments, the ejector 118 be set up in such a way that the ejector 118 the refrigerant dispensed is in a mixed (e.g. two-phase) state. For example, this can be done by the ejector 118 dispensed refrigerant comprise a first part of gaseous refrigerant and a second part of liquid refrigerant. For example, the steam quality of the ejector 118 refrigerant output should be approximately 0.5.

It is understood that the cooling system 100 can also have a plurality of ejectors (for example a network of ejectors) which can be set up to include part of the refrigerant from the basic cooling circuit 102 to receive and another part of the refrigerant from the subcooling system 112 to recieve. The ejectors of the plurality of ejectors can be arranged in parallel with one another, so that a high output (e.g. a high flow rate) can be achieved. The ejectors of the plurality of ejectors can, however, alternatively or additionally be arranged in series, so that a stronger compression of the refrigerant can be achieved. The ejectors of the plurality of ejectors can be configured in the same way. However, the ejectors of the plurality of ejectors can also be set up or operated with different operating parameters, so that different operating conditions of the cooling system 100 can be made possible.

According to various embodiments, the cooling system 100 a separator 120 exhibit. The separator 120 can in terms of the ejector 118 be placed downstream so that the separator 120 can be set up by the ejector 118 receive refrigerant dispensed. The separator 120 can have an input 120a have, which for example with the output 118b of the ejector 118 (for example by means of a line, such as a suction line, a liquid line, etc.) be or can be connected.

According to various embodiments, the separator 120 be set up to separate the gas phase of the (for example two-phase) refrigerant from the liquid phase of the refrigerant. According to various embodiments, the separator 120 be set up in such a way that the refrigerant is in the gas phase from the separator 120 the basic cycle 102 is provided, and that the refrigerant is in the liquid phase from the separator 120 the subcooling system 112 provided.

According to various embodiments, the separator 120 be a medium pressure separator or set up as a medium pressure separator. The operating pressure of the separator 120 can for example be in a range from about 30 bar to about 65 bar.

According to various embodiments, the separator 120 a gas outlet 120b and a liquid outlet 120c have, the gas outlet 120b with the basic cycle 102 (for example by means of a line, such as a suction line) can be or be connected, and wherein the liquid outlet 120c with the subcooling system 112 (for example by means of a line, such as a liquid line) be or can be connected. For example, the cooling system 100 be set up in such a way that the refrigerant is in the gas phase from the separator 120 the compression unit 106 provided.

The separator 120 that allows the subcooling system 112 (and with it the subcooling evaporator 114 ) liquid refrigerant is supplied, so that the efficiency of the heat exchange in the subcooling system 112 can be increased. Furthermore, the separator enables 120 that the compression unit 106 gaseous refrigerant is supplied, so that a higher compression efficiency can be achieved. The compression unit can be clearly illustrated 106 be set up by the separator 120 to compress released gaseous refrigerants.

According to various embodiments, the cooling system 100 an additional pressure reducing device 122 (for example an ejector, an expander, a throttle valve, a capillary tube, an expansion valve, such as a thermal expansion valve, an electronic expansion valve, a manual expansion valve, etc.), which between the gas outlet 120b of the separator 120 and the entrance 106a the compression unit 106 can be arranged. The additional pressure reducing device 122 can be set up so that at the entrance 106a the compression unit 106 that from the separator 120 received refrigerant and that from the heat-absorbing heat exchanger 104 received refrigerants are at the same or a similar pressure level.

The separator 120 can also be set up as a collector so that it collects a portion (eg 5%, 10%, 20%, etc.) of the liquid refrigerant. The accumulated refrigerant can be fed into the system (e.g. the basic cooling circuit 102 and / or the subcooling system 112 ), if a larger amount of refrigerant is required (e.g. if more cooling and / or more subcooling is required).

An arrangement of the cooling system 100 as described herein allows refrigeration oil to pass through the cooling system 100 can circulate. The refrigeration machine oil is particularly important for the operation of the compression unit 106 where the compression of the refrigerant can be achieved by moving mechanical components. These mechanical components should be well lubricated to prevent malfunction. Refrigeration machine oil is also important for the sealing and, in some cases, also the cooling of compressing parts in the compression unit 106 (eg in a compressor, such as for the seal between the piston and cylinder in a reciprocating compressor). If refrigerant from the compression unit 106 is dispensed, some refrigerator oil is also dispensed. This refrigeration machine oil can pass through the cooling system 100 run through, for example on the same flow path as the refrigerant, and can thus to the compression unit 106 be transported back.

The cooling system 100 can thus be set up for a recirculation of the refrigerating machine oil through the cooling system 100 to facilitate. The (e.g. direct) connection between the compression unit 106 and the heat absorbing heat exchanger 104 enables such a recirculation of the refrigerating machine oil. According to various embodiments, the compression unit 106 be set up, the refrigerant always directly from the heat-absorbing heat exchanger 104 sucked in so that there is no refrigeration oil trap.

In contrast, a heat-absorbing heat exchanger in a conventional cooling system can be part of a sub-circuit which, for example, can have a heat-absorbing heat exchanger, an ejector and a separator. In such an arrangement, the refrigeration machine oil collects in this partial circuit and is no longer available to the compression unit (e.g. the compressor).

It goes without saying that the elements of the cooling circuit 100 have been described in a schematic and exemplary manner, and that other arbitrarily suitable configurations can also be used.

1B illustrates an ejector 118 in a schematic representation according to various embodiments.

The operation of the ejector 118 is explained in more detail below. According to various embodiments, the ejector 118 a nozzle (eg a propellant nozzle) 123, a suction area (eg a premixing area) 124, a mixing area 126 and a diffuser 128 exhibit.

The ejector 118 can be set up in such a way that the high-pressure refrigerant (also referred to as the propellant flow, for example the pressure of the high-pressure refrigerant can be in a range from approximately 50 bar to approximately 110 bar) at the primary inlet 118a receives. The nozzle 123 can be set up in such a way that the high pressure of the refrigerant is converted into speed, so that that of the nozzle 123 issued refrigerant has a lower pressure (eg 10 bar lower, 20 bar lower, 30 bar lower, etc.) and a higher speed (eg a supersonic speed) than that of the ejector 118 at the primary entrance 118a received refrigerants. According to various embodiments, the nozzle 123 have a converging-diverging geometry.

The pressure drop in the motive flow creates a low pressure zone in the suction area 124 . Because of this low-pressure zone, the refrigerant (also referred to as suction flow, for example the pressure of the refrigerant can be in a range from approximately 10 bar to approximately 30 bar) is passed through the secondary inlet 118c into the ejector 118 sucked in. Thus, the ejector can 118 be set up in such a way that it removes the refrigerant from the subcooling system 112 sucks, due to the in the suction area 124 resulting low pressure zone. The motive flow and the suction flow to the mixing area 126 are supplied in which the propellant flow (e.g. that of the basic cooling circuit 102 received refrigerant) with the suction flow (e.g. that from the subcooling system 112 received refrigerant) is mixed. The mixture can, for example, through the diffuser 128 are supplied, which can be set up such that the speed of the mixture is converted into pressure energy in it. The diffuser 128 can thus be set up in such a way that the ejector 118 The refrigerant output is at a pressure level (eg a medium pressure level) which is between the high pressure level of the basic cooling circuit 102 received refrigerant and the low pressure level of the subcooling system 112 received refrigerant. According to various embodiments, the pressure of the ejector 118 dispensed refrigerant be in a range of about 30 bar to about 65 bar.

According to various embodiments, the ejector 118 be controllable. For example, the control system or regulating system can be set up to specify an opening degree of the nozzle 123 to control or regulate in such a way that the flow of driving current through the ejector 118 can be adjusted so that the suction pressure can also be regulated. For example, the nozzle 123 a valve (eg a needle valve) which can be used, an opening degree of the nozzle 123 zoom in and / or out. The control system or regulating system can be set up, the valve of the nozzle 123 to control or regulate in such a way that an opening degree of the nozzle 123 can be enlarged and / or reduced.

An arrangement of the cooling system 100 as described herein allows the operating parameters (e.g. the degree of opening of the nozzle 123 , the length of the mixing area 126 , etc.) of the ejector 118 regardless of the operating parameters (eg the operating temperature, the operating pressure, the mass flow, such as an evaporation mass flow, etc.) of the heat-absorbing heat exchanger 104 can be customized.

In a conventional cooling system in which an ejector is coupled to a main heat exchanger (eg a main evaporator), the ejector should be set up in such a way that it draws in the refrigerant from the main heat exchanger and the pressure of such a refrigerant increases. Alternatively, a conventional ejector can be set up in such a way that it provides the refrigerant to the main heat exchanger. For an efficient heat exchange between the refrigerant and a fluid to be cooled, a high mass flow through the main heat exchanger is desirable (for example from 0.4 kg / s to 1.5 kg / s). Therefore, an ejector that is coupled to the main heat exchanger should be able to work with such high mass flows. However, the efficiency of an ejector (e.g. the efficiency of the compression of the refrigerant taken in at the secondary inlet) decreases as the mass flow of the (e.g. sucked in) refrigerant increases because more work is required to achieve the compression. Therefore, it can be problematic to achieve efficient operation of an ejector while maintaining a sufficiently high mass flow through the main heat exchanger of the cooling system.

In the cooling system described herein 100 can the ejector 118 be set up in such a way that it removes the refrigerant from the subcooling heat exchanger 114 sucks. In this arrangement, the operating parameters of the subcooling heat exchanger 114 thus to the operating parameters of the ejector 118 be adjusted. For example, the pressure in the subcooling heat exchanger 114 the ideal characteristic of the ejector 118 adjusted so that the refrigerant can be recompressed in a more efficient manner.

Therefore, the operating parameters of the ejector are subject 118 less stringent requirements than in a conventional cooling system. One from the heat absorbing heat exchanger 104 independent regulation of the ejector 118 can thus be achieved in a simpler manner.

2A illustrates a cooling system 100 having an ejector 118 in a schematic representation according to various embodiments.

According to various embodiments, the cooling system 100 an additional compression unit 230 exhibit. The additional compression unit 230 can be parallel to the compression unit 106 be arranged.

Using the ejector 118 can lead to an increased flash gas mass flow in the separator 120 is generated so that the additional compression unit 230 can be used to ensure the compression and / or recirculation of the additional gas mass flow. According to various embodiments, the cooling system 100 be set up so that a first part of the gas outlet 120b of the separator 120 issued refrigerant (e.g. 50% of the inflowing refrigerant, 70% of the refrigerant, 90% of the refrigerant, etc.) of the additional compression unit 230 is provided, and that a second part of the gas outlet 120b of the separator 120 issued refrigerant (e.g. 10% of the inflowing refrigerant, 30% of the refrigerant, 50% of the refrigerant, etc.) of the compression unit 106 provided. According to various embodiments, the cooling system 100 be set up in such a way that the mass flow through the additional compression unit is in a range from approximately 0.4 kg / s to approximately 0.6 kg / s.

According to various embodiments, the additional compression unit 230 in relation to the separator 120 (e.g. on the gas outlet 120b of the separator 120 ) be arranged downstream. For example, the additional compression unit 230 with the separator 120 (e.g. directly) connected: the additional compression unit 230 can have an input 230a and an exit 230b have, and the entrance 230a can with the gas outlet 120b of the separator 120 (for example by means of a line, such as a suction line) be or will be connected.

The additional compression unit 230 can thus be set up, a first part of the from the separator 120 (e.g. from the gas outlet 120b of the separator 120 ) to compress the refrigerant dispensed (e.g. 50% of the refrigerant, 70% of the refrigerant, 90% of the refrigerant, etc.). In this embodiment, the compression unit 106 be set up a second part of the from the separator 120 (e.g. from the gas outlet 120b of the separator 120 ) to compress the refrigerant dispensed (e.g. 10% of the refrigerant, 30% of the refrigerant, 50% of the refrigerant, etc.). According to various embodiments, the pressure of the refrigerant at the inlet 230a the additional compression unit 230 be in a range from about 30 bar to about 65 bar, for example in a range from about 35 bar to about 55 bar, and the pressure of the refrigerant at the outlet 230b the additional compression unit 230 can be in a range from about 45 bar to about 120 bar.

The use of parallel compression units 106 , 230 can increase the coefficient of performance (COP) of compression (e.g. the coefficient of performance can be 5% higher, 10% higher, 20% higher, etc.).

According to various embodiments, the cooling system 100 be set up in such a way that the additional compression unit 230 compressed refrigerant to the heat-emitting heat exchanger 108 is fed.

According to various embodiments, the additional compression unit 230 a compressor (for example a reciprocating compressor, a screw compressor, a rotary compressor, a centrifugal compressor, a scroll compressor, etc.) which can be set up to compress the refrigerant. The compressor can be a single-stage compressor or a multi-stage compressor. The additional compression unit 230 but can also have a plurality of compressors (for example a network with a plurality of compressors). For example, the compressors of the plurality of compressors can be arranged parallel to one another, but alternatively or additionally the compressors of the plurality of compressors can also be arranged in series.

According to various embodiments, the additional pressure reduction device 122 be set up as a bypass valve (eg as a bypass valve, such as a flash gas bypass valve). In this embodiment, the additional pressure reduction device 122 between the additional compression unit 230 and the compression unit 106 be arranged. The additional pressure reducing device 122 can be set up, the division of the gas output 120b of the separator 120 to adjust the refrigerant output. In other words, the additional pressure reduction device 122 be set up the amount of from the gas outlet 120b of the separator 120 issued refrigerant to regulate which of the additional compression unit 230 provided. The additional pressure reducing device 122 also be set up the amount of from the gas outlet 120b of the separator 120 to regulate the refrigerant dispensed, which of the compression unit 106 provided. For example, the additional pressure reducing device 122 used when the additional compression unit 230 is not in operation and / or if the additional compression unit 230 runs at maximum speed (e.g. if the additional compression unit 230 compresses the maximum volume flow).

According to various embodiments, the separator 120 be set up in such a way that part of the refrigerant in the gas phase (for example 50% of the refrigerant) the subcooling system 112 is provided, and that another part of the refrigerant in the gas phase (eg 50% of the refrigerant) the basic cooling circuit 102 is provided, such as in 2 B is shown. In this embodiment, the second input 114c the subcooling heat exchanger 114 with the gas outlet 120b of the separator 120 (for example by means of a line such as a suction line) be or will be connected, and the subcooling heat exchanger 114 can be set up in such a way that gaseous refrigerant flows through the second flow path of the subcooling heat exchanger 114 flows, and that liquid refrigerant flows through the first flow path of the subcooling heat exchanger 114 flows.

According to various embodiments, the subcooling system 112 an additional heat exchanger 234 have, for example in 2 B which is shown with reference to the second input 114c of the subcooling heat exchanger 114 can be arranged upstream. The additional heat exchanger 234 can be set up to take heat from the subcooling heat exchanger 114 to withdraw provided refrigerant.

For example, the additional heat exchanger 234 a first entrance 234a and a first exit 234b which can be connected by means of a first flow path to refrigerant between the first inlet 234a and the first exit 234b to be transported by means of the first flow path. Furthermore, the additional heat exchanger 234 a second entrance 234c and a second exit 234d which can be connected by means of a second flow path to refrigerant between the second inlet 234c and the second exit 234d to be transported by means of the second flow path.

The first flow path can be in a heat exchange relationship with the second flow path, so that the additional heat exchanger 234 can be set up such that heat from the through the first flow path of the additional heat exchanger 234 withdrawn flowing refrigerant and into the through the second flow path of the additional heat exchanger 234 flowing refrigerant is absorbed.

According to various embodiments, the additional heat exchanger 234 be set up (eg gaseous) refrigerant from the separator 120 to recieve. For example, the first input 234a with the gas outlet 120b of the separator 120 be or are connected, for example by means of a line such as a suction line, and the second input 234c can for example with an additional gas outlet of the separator 120 be or will be connected, for example by means of a line such as a suction line.

According to various embodiments, the additional heat exchanger 234 be set up as a co-current heat exchanger, so that the refrigerant flowing through the first flow path and that through the second flow path flowing refrigerant flow in the same direction. Alternatively, the additional heat exchanger 234 be set up as a countercurrent heat exchanger, so that the refrigerant flowing through the first flow path and the refrigerant flowing through the second flow path flow in opposite directions. A more uniform temperature difference can be achieved in a counterflow heat exchanger, so that a more uniform heat flow density can be achieved. The additional heat exchanger 234 but can also be set up as a cross-flow heat exchanger in which the first flow path and the second flow path are arranged perpendicular to one another.

According to various embodiments, the refrigerant can be at the first inlet 234a of the additional heat exchanger 234 be saturated steam. When the refrigerant flows through the first flow path, heat is transferred to the refrigerant flowing through the second flow path, so that the refrigerant flowing through the first flow path partially condenses and at the first exit 234b is present in two phases. Thus, a refrigerant having a lower vapor mass fraction can enter the second input 114c of the subcooling heat exchanger 114 can be provided so that a greater enthalpy difference between that through the first flow path of the subcooling heat exchanger 114 flowing refrigerant and through the second flow path of the subcooling heat exchanger 114 flowing refrigerant is available. Thus, the heat transfer in the subcooling heat exchanger 114 can be improved (e.g. the heat flux density can be increased).

According to various embodiments, the subcooling system 112 be set up in such a way that from the first output 234b of the additional heat exchanger 234 refrigerant output to the subcooling heat exchanger 114 is fed. For example, the additional heat exchanger 234 and the subcooling heat exchanger 114 can be connected, e.g. the first output 234b of the additional heat exchanger 234 and the second entrance 114c of the subcooling heat exchanger 114 (for example by means of a line, such as a suction line, a liquid line, etc.) be or will be connected. According to various embodiments, the subcooling system 112 be set up in such a way that from the first output 234b of the additional heat exchanger 234 dispensed refrigerant into the pressure reducing device 116 flows and the subcooling heat exchanger 114 is fed. For example, the pressure reducing device 116 between the first exit 234b of the additional heat exchanger 234 and the second entrance 114c of the subcooling heat exchanger 114 be arranged.

According to various embodiments, the subcooling system 112 be set up in such a way that the second output 234d of the additional heat exchanger 234 refrigerant output to the basic cooling circuit 102 (e.g. the compression unit 106 ) is supplied.

According to various embodiments, the subcooling system 112 another pressure reducing device 236 (e.g. an ejector, an expander, a throttle valve, a capillary tube, an expansion valve, such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.), which can be set up in such a way that the pressure of the refrigerant is reduced (e.g. reduced by 5 bar, by 10 bar, etc.), if this is done by the other pressure reducing device 236 flows. This means that the temperature of the refrigerant can also be reduced (for example reduced by 5 ° C, 10 ° C, 15 ° C, etc.) if this is done by the other pressure reducing device 236 flows. According to various embodiments, the other pressure reduction device 236 in relation to the second entrance 234c of the additional heat exchanger 234 be arranged upstream, so that refrigerant the second inlet 234c of the additional heat exchanger 234 is provided which has a lower temperature (e.g. 5 ° C lower, 10 ° C lower, 15 ° C lower, etc.) than that of the first input 234a of the additional heat exchanger 234 provided refrigerants.

3 illustrates a cooling system 100 in a schematic representation according to various embodiments.

According to various embodiments, the cooling system 100 a deep-freeze circuit 338 exhibit. The freezing cycle 338 can be set up in such a way that a fluid to be frozen is cooled (eg deep-frozen) when refrigerant passes through the freezing circuit 338 flows.

According to various embodiments, the deep-freeze circuit 338 a heat absorbing heat exchanger 340 , a compression unit 342 and a pressure reducing device 344 exhibit.

According to various embodiments, the heat-absorbing heat exchanger 340 of the deep-freeze circuit 338 an entrance 340a and an exit 340b which can be connected by means of a first flow path to refrigerant between the inlet 340a and the exit 340b by means of the first flow path transport. The heat-absorbing heat exchanger 340 can be set up in such a way that the refrigerant flows through the first flow path and this is in a heat exchange relationship with a fluid to be frozen (e.g. air, water, brine, etc.), so that heat from the fluid to be frozen is absorbed into the refrigerant when this through the heat-absorbing heat exchanger 340 flows. Thus, the fluid to be frozen can be frozen. The heat-absorbing heat exchanger is clear 340 of the deep-freeze circuit 338 be set up in such a way that the fluid to be frozen is cooled to a temperature which is lower (eg 5 ° C. lower, 10 ° C. lower, 20 ° C. lower, etc.) than the temperature to which the heat-absorbing heat exchanger is used 104 of the basic cooling circuit 102 cooled fluid to be cooled is cooled. For example, the fluid to be refrigerated can be refrigerated to a temperature in a range from about -30 ° C to about -10 ° C, and the fluid to be cooled can be cooled to a temperature in a range from about -5 ° C to about 10 ° C will.

For example, the heat-absorbing heat exchanger 104 of the basic cooling circuit 102 and the heat absorbing heat exchanger 340 of the deep-freeze circuit 338 be set up in such a way that they have different steam temperatures. For example, the steam temperature of the heat-absorbing heat exchanger 340 lower (e.g. 5 ° C lower, 10 ° C lower, 15 ° C lower, etc.) than the steam temperature of the heat-absorbing heat exchanger 104 .

According to various embodiments, the heat-absorbing heat exchanger 340 having a second flow path which is in a heat exchange relationship with the first flow path and through which the fluid to be frozen can flow.

According to various embodiments, the cooling system 100 be set up in such a way that the fluid to be frozen passes the heat-absorbing heat exchanger 340 of the deep-freeze circuit 338 flows through. For example, a circulation system (e.g. one or more pipes, a fan, a fan, etc.) can be used to circulate the fluid to be frozen (e.g. air, water, brine, etc.) around the heat-absorbing heat exchanger 340 of the deep-freeze circuit 338 to get in motion, so that a more efficient heat exchange between the through the heat-absorbing heat exchanger 340 flowing refrigerant and the fluid to be frozen is enabled.

According to various embodiments, the heat-absorbing heat exchanger 340 an evaporator (eg a tube evaporator, a plate heat exchanger, a lamellar evaporator, etc.) or be set up as an evaporator. The heat-absorbing heat exchanger 340 but can also be a sublimator or be set up as a sublimator.

According to various embodiments, the compression unit 342 in relation to the heat-absorbing heat exchanger 340 be arranged downstream. For example, the compression unit 342 be set up, the refrigerant (eg directly) from the heat-absorbing heat exchanger 340 suck in. According to various embodiments, the compression unit 342 and the exothermic heat exchanger 340 be connected to each other (e.g. directly): the compression unit 342 can have an input 342a and an exit 342b have, and the entrance 342a the compression unit 342 can with the output 340b of the heat-absorbing heat exchanger 340 (for example by means of a line, such as a suction line) be or will be connected.

The compression unit 342 can be set up to compress the refrigerant (eg the pressure of the compression unit 342 refrigerant dispensed may be in a range from about 10 bar to about 50 bar).

According to various embodiments, the compression unit 342 a compressor (for example a reciprocating compressor, a screw compressor, a rotary compressor, a centrifugal compressor, a scroll compressor, etc.) which can be set up to compress the refrigerant. The compressor can be, for example, a single-stage compressor or a multi-stage compressor. According to various embodiments, the compression unit 342 have a plurality of compressors (for example a network with a plurality of compressors). For example, the compressors of the plurality of compressors can be arranged parallel to one another, but alternatively or additionally the compressors of the plurality of compressors can also be arranged in series.

According to various embodiments, the cooling system 100 be set up such that by means of the compression unit 342 of the deep-freeze circuit 338 compressed refrigerant to the basic cooling circuit 102 is fed. For example, the cooling system 100 be set up such that by means of the compression unit 342 of the deep-freeze circuit 338 compressed refrigerant of the compression unit 106 of the basic cooling circuit 102 is fed. For example, the entrance 106a the compression unit 106 of the basic cooling circuit 102 with the exit 342b the compression unit 342 of Freezing cycle 338 (for example by means of a line, such as a suction line) be or will be connected.

According to various embodiments, the pressure reduction device 344 in relation to the exothermic heat exchanger 340 be arranged upstream, and can be set up in such a way that the pressure of the refrigerant is reduced (for example reduced by 5 bar, by 10 bar, by 15 bar, etc.) when this is effected by the pressure reducing device 344 flows.

The pressure reducing device 344 can be any suitable device (e.g. an ejector, an expander, a throttle valve, a capillary tube, an expansion valve such as a thermal expansion valve, an electronic expansion valve, a manual expansion valve, etc.) which is set up to reduce the pressure of the refrigerant .

According to various embodiments, the deep-freeze circuit 338 be set up in such a way that the pressure reduction device 344 refrigerant output to the heat-absorbing heat exchanger 340 is fed. For example, the pressure reducing device 344 with the heat-absorbing heat exchanger 340 be connected: the pressure reducing device 344 can have an input 344a and an exit 344b have, and the exit 344b the pressure reducing device 344 can with the entrance 340a of the heat-absorbing heat exchanger 340 (for example by means of a line, such as a liquid line) be or will be connected.

According to various embodiments, the subcooling system 112 also be set up, the supercooled refrigerant to the freezing circuit 338 provide. For example, the subcooling system 112 be set up, a first part of the supercooled refrigerant (for example 50% of the supercooled refrigerant) the basic cooling circuit 102 provide and a second part of the supercooled refrigerant (eg 50% of the supercooled refrigerant) to the freezing circuit 338 provide.

According to various embodiments, the subcooling system 112 an additional subcooling heat exchanger 346 have which is set up to subcool refrigerant. The additional subcooling heat exchanger 346 can be an evaporator (eg a supercooling evaporator) or be set up as an evaporator. The additional subcooling heat exchanger 346 but can also be a sublimator or be set up as a sublimator.

The additional subcooling heat exchanger 346 can have a first input 346a and a first exit 346b which are connected by means of a first flow path to refrigerant between the first inlet 346a and the first exit 346b to be transported by means of the first flow path. The additional subcooling heat exchanger 346 can also have a second entrance 346c and a second exit 346d , which are connected by a second flow path to refrigerant between the second inlet 346c and the second exit 346d to be transported by means of the second flow path. According to various embodiments, the additional supercooling heat exchanger 346 be configured such that the first flow path is in a heat exchange relationship with the second flow path, so that heat is extracted from the refrigerant flowing through the first flow path and absorbed into the refrigerant flowing through the second flow path. The refrigerant flowing through the first flow path can thus be subcooled.

According to various embodiments, the subcooling system 112 be set up in such a way that part of the refrigerant reaches the first inlet 346a of the additional subcooling heat exchanger 346 is supplied, and that another part of the refrigerant is fed to the second inlet 346c of the additional subcooling heat exchanger 346 is fed. For example, the subcooling system 112 be set up such that the mass flow through the first flow path of the additional subcooling heat exchanger 346 is in a range from approximately 0.4 Kg / s to approximately 0.6 Kg / s, and that the mass flow through the second flow path of the additional subcooling heat exchanger 346 is in a range from about 0.025 kg / s to about 0.25 kg / s.

According to various embodiments, the subcooling system 112 be set up in such a way that by means of the subcooling heat exchanger 114 subcooled refrigerants to the basic cooling circuit 102 is supplied and / or that by means of the additional supercooling heat exchanger 346 subcooled refrigerants to the freezing circuit 338 is fed. It goes without saying that any other suitable arrangements and connections are also possible.

According to various embodiments, the first output 346b of the additional subcooling heat exchanger 346 with the freezing circuit 338 (e.g. with the entrance 344a the pressure reducing device 344 ) be or will be connected, e.g. by means of a line such as a suction line, a liquid line, etc.

According to various embodiments, the first output 114b of the subcooling heat exchanger 114 with the basic cooling circuit 102 (e.g. with the entrance 110a the pressure reducing device 110 ) be or will be connected, e.g. by means of a line such as a suction line, a liquid line, etc.

According to various embodiments, the subcooling system 112 an additional pressure reducing device 348 (e.g. an ejector, an expander, a throttle valve, a capillary tube, an expansion valve such as a thermal expansion valve, an electronic expansion valve, a manual expansion valve, etc.), which can be set up in such a way that the pressure of the refrigerant is reduced (e.g. reduced by 5 bar, by 10 bar, by 15 bar, etc.) if this is done by the pressure reducing device 348 flows. This means that the temperature of the refrigerant can also be reduced (eg reduced by 5 ° C, by 10 ° C, by 15 ° C) if this is effected by the pressure reducing device 348 flows. According to various embodiments, the pressure reduction device 348 in relation to the second entrance 346c of the additional subcooling heat exchanger 346 be arranged upstream, so that refrigerant the second inlet 346c is provided which has a lower temperature (e.g. 5 ° C lower, 10 ° C lower, 15 ° C lower, etc.) than that of the first input 346a of the additional subcooling heat exchanger 346 provided refrigerants.

According to various embodiments, the cooling system 100 an additional ejector 350 exhibit. The additional ejector 350 may be set up to remove some of the refrigerant from the separator 120 to receive and another part of the refrigerant from the subcooling system 112 to recieve. For example, the primary entrance 350a of the additional ejector 350 with the gas outlet 120b of the separator 120 (for example by means of a line, such as a suction line) be or will be connected. It goes without saying that the primary input 350a of the additional ejector 350 alternatively with the liquid outlet 120c of the separator 120 (for example by means of a line, such as a liquid line) be or can be connected. In this refinement, this can be done by the separator 120 Received refrigerant serve as a motive flow to the refrigerant from the subcooling system 112 (e.g. from the second exit 346d of the additional subcooling heat exchanger 346 ) to suck in.

According to various embodiments, the cooling system 100 be set up in such a way that the additional ejector 350 refrigerant output to the basic cooling circuit 102 (e.g. the compression unit 106 of the basic cooling circuit 102 ) is supplied. For example, the exit 350c of the additional ejector 350 with the entrance 106a the compression unit 106 of the basic cooling circuit 102 (for example by means of a line, such as a suction line, a liquid line, etc.) be or will be connected. In this embodiment, the work of the compression unit 106 of the basic cooling circuit 102 be reduced.

4th Figure 11 illustrates a flow diagram of a cooling method 400 , according to various embodiments.

The procedure 400 For example, it can include: in 410 Separating a gas phase and a liquid phase of a refrigerant; in 420 Subcooling of the liquid refrigerant, for example by means of a subcooling system 112 as above in relation to the 1 to 3 was depicted; in 430 Providing the gaseous refrigerant and the supercooled liquid refrigerant in a basic cooling circuit, the basic cooling circuit in the same or similar manner as the basic cooling circuit described herein 102 can be set up; in 440 Providing part of the refrigerant to be subcooled and another part of the refrigerant from the basic cooling circuit to an ejector, the ejector in the same or a similar manner as the ejector described herein 118 can be set up.

According to various embodiments, the method 400 also have features relating to the cooling system 100 and the 1 to 3 have been described.

The cooling system 100 and the cooling method 400 can be used in applications which require an increased cooling capacity (e.g. from about 20 kW to about 2000 kW, e.g. from about 50 kW to about 500 kW).

The cooling system 100 and the cooling method 400 can be used, for example, in chillers and / or in refrigerated containers. For example, the cooling system 100 and the cooling method 400 be used in refrigeration cabinets to cool food. The cooling system 100 and the cooling method 400 can be used, for example, to air-condition trucks.

Various examples are described below which relate to what has been described and illustrated above.

Example 1 is a cooling system which may have a basic cooling circuit Subcooling system, which is set up to subcool refrigerant and provide the basic cooling circuit, an ejector set up to receive part of the refrigerant from the basic cooling circuit and to receive another part of the refrigerant from the subcooling system, wherein the ejector is further set up, to increase a pressure of the part of the refrigerant received by the subcooling system, and a separator, which is set up such that the refrigerant is provided in a gas phase by the separator to the basic circuit, and that the refrigerant is provided in a liquid phase by the separator to the subcooling system becomes.

In example 2, the subject matter of example 1 can optionally have the basic cooling circuit having a heat-absorbing heat exchanger, a compression unit, a heat-emitting heat exchanger and a pressure-reducing device.

In example 3, the subject matter of example 2 can optionally include that the heat-absorbing heat exchanger is an evaporator or is set up as an evaporator. The heat-absorbing heat exchanger can, however, also be a sublimator or be set up as a sublimator.

In example 4, the subject matter of example 2 or 3 can optionally include that the heat-emitting heat exchanger is a condenser or is set up as a condenser.

In example 5, the subject matter of example 2 or 3 can optionally include that the heat-emitting heat exchanger is a gas cooler or is set up as a gas cooler.

In example 6, the subject matter of examples 2 to 5 can optionally include that the compression unit is set up to draw in the refrigerant directly from the heat-absorbing heat exchanger.

In Example 7, the subject matter of Examples 2 to 6 can optionally include that the cooling system has an additional compression unit.

In example 8, the subject matter of example 7 can optionally include that the additional compression unit is arranged parallel to the compression unit.

In example 9, the subject matter of examples 1 to 8 can optionally include that the refrigerant comprises a supercritical refrigerant.

In example 10, the subject matter of examples 1 to 9 can optionally include that the refrigerant comprises a natural refrigerant.

In example 11, the subject matter of examples 1 to 10 can optionally include the refrigerant comprising carbon dioxide.

The refrigerant can, however, also comprise a hydrocarbon-based refrigerant, e.g. R170, R290, R600, etc. Alternatively or in addition, the refrigerant can also contain a fluorinated refrigerant, e.g. R134a, R32, R1234yf, etc. However, the refrigerant can also comprise a mixture of a plurality of refrigerants, e.g. R404A, R410A, R407C, etc.

In Example 12, the subject matter of Examples 1 to 11 can optionally indicate that the supercooling system has a supercooling heat exchanger which is an evaporator (e.g. a supercooling evaporator) or is set up as an evaporator (e.g. as a supercooling evaporator). The undercooling heat exchanger can, however, also be a sublimator or be set up as a sublimator.

In example 13, the subject matter of example 12 can optionally include that the supercooling heat exchanger is set up as a cocurrent heat exchanger.

In example 14, the subject matter of example 12 can optionally include that the supercooling heat exchanger is set up as a countercurrent heat exchanger.

The subcooling heat exchanger can also be set up as a cross-flow heat exchanger.

In example 15, the subject matter of examples 12 to 14 can optionally include that the ejector is set up to suck in the refrigerant from the subcooling heat exchanger.

In example 16, the subject matter of examples 12 to 15 can optionally include that the supercooling system has an additional heat exchanger which is set up to cool the refrigerant provided to the supercooling heat exchanger.

In Example 17, the subject matter of Examples 1 to 16 can optionally include the ejector having a primary input and a secondary input, the primary input being connected to the basic cooling circuit and the secondary input being connected to the subcooling system.

In Example 18, the subject matter of Examples 1 to 17 can optionally include that the separator is a medium-pressure separator or is set up as a medium-pressure separator.

In Example 19, the subject matter of Examples 1 to 18 can optionally have an operating pressure of the separator in a range from approximately 30 bar to approximately 65 bar.

In example 20, the subject matter of examples 1 to 19 can optionally include that the separator is set up as a collector.

In example 21, the subject matter of examples 1 to 19 can optionally include that the ejector is set up in such a way that a pressure of the refrigerant output by the ejector is 3 times (eg 5 times, 10 times, etc.) the Pressure of the refrigerant received by the subcooling system.

In Example 22, the subject matter of Examples 1 to 21 can optionally include that the cooling system has a freezing cycle.

In example 23, the subject matter of example 22 can optionally include that the deep-freeze circuit has a heat-absorbing heat exchanger, a compression unit and a pressure reduction device.

In example 24, the subject matter of example 22 or 23 can optionally include that the subcooling system is set up to provide the subcooled refrigerant to the freezing circuit.

Example 25 is a cooling method which comprises separating a gas phase and a liquid phase of a refrigerant, supercooling the liquid refrigerant, providing the gaseous refrigerant and the supercooled liquid refrigerant to a basic cooling cycle, and providing part of the refrigerant to be supercooled and another Part of the refrigerant from the basic cooling circuit may have an ejector.

Claims (10)

Cooling system (100) comprising: • a basic cooling circuit (102); • a subcooling system (112) which is set up to subcool refrigerant and to provide it to the basic cooling circuit (102); • an ejector (118) configured to receive part of the refrigerant from the basic cooling circuit (102) and another part of the refrigerant from the subcooling system (112), wherein the ejector (118) is further configured to a pressure of the increase the portion of the refrigerant received by the subcooling system (112); and • a separator (120), which is set up in such a way that the refrigerant is provided in a gas phase by the separator (120) to the basic circuit (102), and that the refrigerant in a liquid phase from the separator (120) to the subcooling system ( 112) is provided. The cooling system (100) according to Claim 1 , wherein the basic cooling circuit (102) has a heat-absorbing heat exchanger (104), a compression unit (106), a heat-emitting heat exchanger (108) and a pressure-reducing device (110). The cooling system (100) according to Claim 2 , wherein the compression unit (106) is set up to suck in the refrigerant from the heat-absorbing heat exchanger (104). The cooling system (100) according to Claim 2 or 3 , further comprising an additional compression unit (230) which is arranged parallel to the compression unit (106). The cooling system (100) according to one of the Claims 1 to 4th , wherein the refrigerant comprises carbon dioxide. The cooling system (100) according to one of the Claims 1 to 5 , wherein the subcooling system (112) has a subcooling heat exchanger (114) which is set up as a counterflow heat exchanger or as a cocurrent heat exchanger or as a crossflow heat exchanger. The cooling system (100) according to Claim 6 , wherein the ejector (118) is configured to suck in the refrigerant from the subcooling heat exchanger (114). The cooling system (100) according to one of the Claims 1 to 7th wherein the ejector (118) has a primary input (118a) and a secondary input (118c), the primary input (118a) being connected to the basic cooling circuit (102) and the secondary input (118c) being connected to the subcooling system (112) is connected. The cooling system (100) according to one of the Claims 1 to 8th , wherein the separator (120) is set up as a medium pressure separator. The cooling system (100) according to one of the Claims 1 to 9 , further comprising a cryogenic circuit (338), wherein the subcooling system (112) is set up to provide the supercooled refrigerant to the freezing circuit (338).

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