Patent Application
20240263851
The present invention relates to temperature-controlling a space to be temperature-controlled and in particular to refrigeration or heat generation and distribution in mobile or stationary refrigeration applications.
In particular, the present invention relates to methods and apparatuses for refrigeration or heat generation or distribution in mobile refrigeration applications or heating applications and can be used for road-bound motor vehicles or trailers or semi-trailers with a refrigeration structure or a heating structure, a rail-bound or sea-bound refrigerated or heated structure or container, or generally for spaces to be temperature-controlled in ventilation or air-conditioning applications, which are refrigerated or heated by means of a compression refrigeration machine for example.
Furthermore, this invention can also be used in the field of comfort air conditioning in mobile applications such as buses or rail-bound passenger cars in rail transport. In principle, however, from a purely technical point of view is not necessary to restrict the invention to these fields, as the solutions described here can also be used to advantage in stationary applications.
The compression refrigeration machine is the most common design of refrigeration machines. This design uses the physical effect of evaporation heat when the aggregate state changes from liquid to gaseous or from gaseous to liquid. In a compression refrigeration machine, a refrigerant with suitable thermal dynamic properties is moved in a closed cycle, as shown in
The refrigerant cycle essentially consists of the following four components: compressor 1, condenser 2, expansion element 3, and evaporator 4. In a single-stage or multi-stage refrigeration system, a distinction is generally made between the high-pressure and the low-pressure side. The high-pressure side extends from the pressure side of the compressor to the inlet of the refrigerant into the expansion element. The low-pressure side comprises the part of the refrigerant cycle from the outlet of the refrigerant out of the expansion element to the compressor inlet. This also applies if the refrigerant cycle is operated as a heat pump, i.e. the heat output provided by the condenser is used instead of the refrigerating capacity of the evaporator. As described, the heat output can be used to heat up the application or to defrost the evaporator.
Regardless of the application, the refrigerant used in the circular process in the cycle should have as little impact on the environment as possible, be cost-effective and particularly energy-efficient. A key measure of the environmentally harmful effect of a refrigerant is its global warming potential (GWP). This value is given for refrigerants in relation to the GWP value of CO2(carbon dioxide). By definition, CO2 has a GWP value of 1. For the F-gases (or fluorinates gases) frequently used as refrigerants, the global warming potential can have values of several thousand. This in turn means that one kilogram of F-gas released into the atmosphere during its production, use, or disposal can be equivalent to the greenhouse effect of several tons of CO2.
The most important components of F-gases are carbon, hydrogen, and fluorine. F-gases often decompose very slowly and, once released, sometimes remain in our atmosphere for hundreds or several thousand years. Regardless of their residence time and the level of global warming potential, decomposition products are formed when F-gases decompose. These substances, such as trifluoroacetic acid or hydrogen fluoride, often have long-term negative effects on humans and the environment. For these reasons, international legislation is increasingly restricting or even prohibiting the use of F-gases as refrigerants by means regulations and ordinances. The acceptance of the F-gases as refrigerants by consumers and users of refrigeration technology, but also by society as a whole, is decreasing, and as a result, the refrigeration and heat pump manufacturing industry is increasingly demanding alternatives to the existing refrigeration technology based on the use of F-gases.
DE 202022100810 U1 shows a heat pump system with a heat pump, a consumer circuit and a buffer storage configured as a gas separator in the consumer circuit. Propane is used in the heat pump, and the heat pump is arranged in a safety area outside a building.
DE 102007039195 A1 shows an arrangement for air-conditioning of a vehicle, wherein a first cycle can be switched between a refrigeration mode and heating mode. CO2 circulates as a heat exchange fluid in the first super critically operable cycle. A coolant for a motor drive of the vehicle circulates in a second cycle.
An embodiment may have an apparatus for temperature-controlling a space to be temperature-controlled with a space limitation separating the space to be temperature-controlled from a surrounding area, comprising: a primary heat pump circuit with an evaporator, a condenser, a compressor, and an expansion element, wherein the primary heat pump circuit comprises a natural primary working fluid, wherein the evaporator, the liquefier, the compressor, and the expansion element are suitable to be arranged outside of the space to be temperature-controlled; a secondary circuit thermally coupled to and fluidically decoupled from the evaporator or the condenser via a heat exchanger and comprising a temperature-controlling element configured to be arranged in the space to be temperature-controlled and configured to be connected to the heat exchanger via a line arrangement comprising a secondary fluid that differs from the primary working fluid, wherein the line arrangement is suitable to penetrate the space limitation, wherein the secondary circuit is configured as a thermosiphon cycle, and wherein a controllable pump configured to reverse a conveying direction in the secondary circuit as a response to a control signal is arranged in the secondary circuit; wherein the apparatus is configured to cool the space by means of the temperature-controlling element in a refrigeration mode; and a controller configured to cause, as a response to a control signal, a heat pump cycle reversal in the primary heat pump circuit so that, in the refrigeration mode, energy is dissipated from the heat exchanger through the primary heat pump circuit, and so that, in a defrosting mode, energy is supplied to the heat exchanger through the primary heat pump circuit in order to defrost the temperature-controlling element, and the conveying direction in the secondary circuit is reversed by the controllable pump.
Another embodiment may have a space to be temperature-controlled, comprising: a space limitation separating a space from a surrounding area of the space; and an apparatus according the invention.
Another embodiment may have a method for temperature-controlling a space to be temperature-controlled with a space limitation separating the space to be temperature-controlled from a surrounding area, with a primary heat pump circuit with an evaporator, a condenser, a compressor, and an expansion element, wherein the evaporator, the liquefier, the compressor, and the expansion element are arranged outside of the space to be temperature-controlled; and a secondary circuit thermally coupled to and fluidically decoupled from the evaporator or the condenser via a heat exchanger and comprising a temperature-controlling element arranged in the space to be temperature-controlled and connected to the heat exchanger via a line arrangement comprising a secondary fluid that differs from the primary working fluid, wherein the line arrangement penetrates the space limitation, wherein the secondary circuit is configured as a thermosiphon cycle, and wherein a controllable pump configured to reverse a conveying direction in the secondary circuit as a response to a control signal is arranged in the secondary circuit, comprising: using, in the primary heat pump circuit, a natural primary working fluid; using, in the line arrangement of the secondary circuit, a secondary fluid that differs from the primary working fluid, wherein temperature-controlling in a refrigeration mode comprises cooling the space by means of the temperature-controlling element; and as a response to the control signal, causing a heat pump cycle reversal in the primary heat pump circuit so that, in the refrigeration mode, energy is dissipated from the heat exchanger through the primary heat pump circuit, and so that, in a defrosting mode, energy is supplied to the heat exchanger through the primary heat pump circuit, in order to defrost the temperature-controlling element, and the conveying direction in the secondary circuit is reversed by the controllable pump.
Another embodiment may have a method for manufacturing an apparatus for temperature-controlling a space to be temperature-controlled with a space limitation separating the space to be temperature-controlled from a surrounding area, comprising: a primary heat pump circuit with an evaporator, a condenser, a compressor, and an expansion element, wherein the primary heat pump circuit comprises a natural primary working fluid, wherein the evaporator, the liquefier, the compressor, and the expansion element are arranged outside of the space to be temperature-controlled; a secondary circuit thermally coupled to and fluidically decoupled from the evaporator or the condenser via a heat exchanger and comprising a temperature-controlling element arranged in the space to be temperature-controlled and connected to the heat exchanger via a line arrangement comprising a secondary fluid that differs from the primary working fluid, wherein the line arrangement penetrates the space limitation, wherein the secondary circuit is configured as a thermosiphon cycle, and wherein a controllable pump configured to reverse a conveying direction in the secondary circuit as a response to a control signal is arranged in the secondary circuit, wherein, in a refrigeration mode, the apparatus is configured to cool the space by means of the temperature-controlling element, the method comprising: introducing a natural primary working fluid into the primary heat pump circuit; manufacturing a line arrangement that penetrates the space limitation; introducing, into the line arrangement, a secondary fluid that differs from the primary working fluid; and manufacturing a controller configured to cause, as a response to the control signal, a heat pump cycle reversal in the primary heat pump circuit so that, in the refrigeration mode, energy is dissipated from the heat exchanger through the primary heat pump circuit, and so that, in a defrosting mode, energy is supplied to the heat exchanger through the primary heat pump circuit so as to defrost the temperature-controlling element, and a conveying direction in the secondary circuit is reversed by means of the controllable pump.
An apparatus for temperature-controlling a space to be temperature-controlled with a space limitation separating the space to be temperature-controlled from a surrounding area includes a primary heat pump circuit with an evaporator, a condenser, a compressor, and an expansion element, wherein the primary heat pump circuit comprises a natural primary working fluid, wherein the evaporator, the condenser, the compressor, and the expansion element are arranged outside of the space to be temperature-controlled. This apparatus further includes a circuit that is thermally coupled to and fluidically decoupled from the evaporator and the condenser via a heat exchanger, and that comprises one or several temperature-controlling elements arranged in the space to be temperature-controlled and connected to the heat exchanger via a line arrangement comprising a secondary fluid that differs from the primary fluid, wherein the line arrangement penetrates the space limitation.
The present invention is based on the finding that in the primary heat pump circuit arranged outside of the space to be temperature-controlled, i.e. in the surrounding area of the space to be temperature-controlled, a natural primary working fluid that may have properties that are unfavorable for a closed space when being breathed in by an organism, such as flammability, is used. On the other hand, a different secondary fluid that is typically harmless or has low risks for an organism because it is non-flammable is used in the secondary circuit. Thus, according to the invention, primary working fluids and secondary fluids that have favorable properties for a compression or a primary heat pump circuit on the one hand and for the temperature control in a (closed) space to be temperature-controlled on the other hand can be combined with each other.
In particular, the use of flammable primary working fluids as an example of a natural refrigerant enables high environmental compatibility and good energy-efficient properties in a compressing refrigerating/heating cycle. On the other hand, such refrigerants/heating agents can generally only be used in closed spaces with considerable additional effort due to their flammability. Such refrigerants are, for example, hydrocarbons (HC) such a propane (R290) or propene (R1270). Other primary working fluids without F-gases include NH3 or NH3/DME (R723), which are only slightly flammable, but toxic to the human organism in closed spaces and are therefore undesirable. This group of working fluids for refrigeration also includes fluorinated hydrocarbons, which are flammable due to their molecular composition.
On the other hand, non-flammable and therefore low-risk refrigerant/heat transfer media can be used in the secondary circuit, which is not used for refrigeration or heat generation, but only for cold distribution and heat distribution, which ideally undergo a change of phase when transporting cold or heat. Advantageously, a secondary fluid that changes its aggregate state during a heat transport is used. Heat is absorbed or released at a constant temperature and the thermosiphon principle is driven by the difference in density between vapor and liquid.
The line arrangement penetrating through the space limitation and the elements of the primary heat pump circuit, including at least part of the heat exchanger, being arranged outside of the space prevents a natural, such as a flammable, working fluid from entering the closed space. Only a non-critical heating medium with the heat/cold to be transported enters the closed space and releases the transported heat/cold into the space via the temperature-controlling element. The temperature-controlling element will typically be a secondary fluid-air heat exchanger, while the heat exchanger will be a primary working fluid-secondary fluid heat exchanger. The heat exchanger is then coupled to the condenser of the primary heat pump circuit if heating is to be achieved as the temperature control. However, if cooling is to be used as the temperature control, then the heat exchanger is thermally coupled to the evaporator of the primary heat pump circuit. In embodiments, the evaporator and the condenser are configured so that corresponding elements of the primary heat pump circuit can perform both functions depending on the operating direction of the compressor.
Furthermore, an implementation of the heat exchanger can be configured in such a way that the actual evaporator or condenser of the primary heat pump circuit is connected in series to the primary working fluid-secondary fluid heat exchanger. Alternatively, the functionality can also be integrated in a single element, which on the one hand achieves the evaporation/condensation in the primary heat pump circuit, and on the other hand transfers the heat or cold from the primary heat pump circuit to the secondary circuit. If the primary working fluid-secondary fluid heat exchanger is connected in series to the actual condenser or evaporator of the primary heat pump circuit, the arrangement of the two elements. i.e. whether the actual condenser or evaporator of the primary heat pump circuit is arranged in front of or behind the primary working fluid-secondary fluid heat exchanger in the direction of flow of the primary working fluid, freely selectable according to the actual conditions. If the two functions of evaporation or condensation of the primary heat pump circuit and that of heat transfer from one fluid to the other, while the two fluids are strictly decoupled from each other, are integrated into a single element, this element is also arranged outside of the space to be temperature-controlled, i.e. in the surrounding area separated from the space to be temperature-controlled by the space limitation.
In embodiments, the temperature-controlling element is an air-secondary fluid heat exchanger with a phase transition. In this case, the line arrangement of the secondary circuit comprises a first part through which the liquid secondary fluid flows, and a second part through which the vaporous secondary fluid flows. Depending on implementation, the secondary circuit can be implemented without a drive, i.e. solely according to the thermosiphon concept, in such a way that the secondary fluid is transported in the secondary circuit solely due to gravity and the difference in density between the vapor and liquid phases of the secondary fluid. Depending on the embodiment, however, a pump can also be arranged in a liquid-carrying part of the line arrangement to support the circulation of the secondary fluid, or a fan can be arranged in the vapor-carrying part of the line arrangement.
Especially when using such a support in the secondary circuit, it is advantageous to provide a controller that, depending on the direction of pumping or ventilation in the secondary circuit, causes defrosting to be carried out at certain times during a normal refrigeration application in the space to be temperature-controlled in order avoid icing of the temperature-controlling element and thus a loss of efficiency. In addition, the pump or fan controlled by the controller can also be used to switch to a refrigeration mode at selected times when the space to be temperature-controlled is actually to be heated, for example when a constant temperature is to be achieved, e.g. when air conditioning is to be achieved over a wide temperature range.
Advantageously, the controller is configured to change the cycle reversal in the primary heat pump circuit as well, which is equivalent to reversing the conveying direction of the compressor so that, for example, if the primary heat pump circuit operates in such a way that the evaporator is coupled to the heat exchanger, i.e. a cooling application is being carried out, the primary heat pump circuit operates in such a way that the evaporator becomes a condenser by switching the conveying direction of the compressor. This supplies heat to the heat exchanger, which means that heat is also supplied to space to be temperature-controlled. Switching the conveying direction the compressor can be achieved by switching the rotational direction of a compressor wheel or by switching a four-way valve coupled to the pressure side and the suction side of the evaporator and condenser of the primary heat pump circuit.
If the secondary circuit does not have a pump or a fan, i.e. if it purely operates according to a thermosiphon principle, by switching the conveying direction of the compressor or by reversing the refrigeration cycle, e.g. by means of valves in the primary heat pump circuit, it can also be achieved that a switch is made from a refrigeration mode to a heating mode, for short-term defrosting, or from a “normal” heating mode to a refrigeration mode, e.g. for temperature-controlling purposes, etc., while also suppling cold or heat to the element to be temperature-controlled.
An alternative to the use F-gases as refrigerants is the use of so-called natural refrigerants. The use of hydrocarbons (HC) is particularly advantageous here, as these substances, in contrast to F-gases, have a very low or negligible global warming potential and enable a high energy efficiency of the refrigerant process and therefore only little drive energy is required per refrigerating or heating capacity. A disadvantage of hydrocarbons is their high flammability, which restricts the use in small closed spaces, such as with the refrigeration structures and refrigeration containers considered here, but also other closed spaces to be cooled or air-conditioned, or virtually excludes their safe use.
To minimize risks, the goal is therefore to use as little refrigerant as possible and to prevent the refrigerant from entering the closed refrigeration structures and refrigeration containers and other closed spaces to be air-conditioned. This results in the use of components for refrigeration with a minimum refrigerant volume in order to the keep the filling level of the refrigerant as low possible. Micro-channel technology and plate heat exchangers are particularly suitable technologies for the heat exchangers. In addition, the compactness of the overall system and the avoidance of storage volumes, such as frequently used refrigerant collectors, has to be taken into account. The compressor should have a low refrigerant volume and a low filling level of oil in order to further reduce the refrigerant mass required for the process. This approach of refrigerant reduction or minimization also applies to all other components to be used in the process and should ideally be taken into account when selecting and positioning them.
Embodiments of the present invention will be detailed subsequently referring to the appended drawings, in which:
When the secondary circuit is coupled to the evaporator 4 via the heat exchanger 7, the arrangement is in the refrigerating (or cooling) mode for the space to be temperature-controlled. Temperature-controlling is then refrigeration and the temperature-controlling element 14 functions as a refrigerating element. In contrast, when the secondary circuit is coupled to the condenser 2 of the primary heat pump circuit via the heat exchanger 7, the apparatus for temperature-controlling is used as a heating apparatus, and temperature-controlling the space 5 is heating, wherein the temperature-controlling element 14 functions as a heating element.
Thus, the heat exchanger 7 may comprise the evaporator or liquefier as well as the heat exchanger 10 illustrated in the various drawings. The temperature-controlling element 14 may consist of the heat exchanger 11 illustrated in the various drawings or may comprise one or several additional elements, such as sensors or the blower of
In the embodiment, a controller 30 is provided so as to switch the compressor 1 of the primary heat pump circuit in its conveying direction, i.e. via a control signal 31, so as to switch the primary heat pump circuit with respect to the flow direction of the primary working fluid. With the same coupling of the secondary circuit, this achieves that the function of the secondary circuit is changed as well, i.e. the secondary circuit is in the refrigeration mode or in the heating mode. If the secondary circuit is normally in the refrigeration mode, the heating mode is used so as to achieve defrosting of the temperature-controlling element 14. However, if the secondary circuit is mainly in the heating mode, intermittent refrigeration can be used to keep a certain set temperature bandwidth. The initiative to output the control signal 31 or the control signal 32 from the controller 30 to a pump or ventilator element possibly arranged in the secondary circuit, such as the element 8, may originate from a sensor, a clock generator, or an external signal, as illustrated by the control input 33. However, if the controller is configured to be controlled via a sensor input or a clock generator, the clock generator or the sensor input would be connected to the control input 33, or the control input 33 would not exist and the initiative for the output of the control signal 31/32 is generated from the controller 30.
Switching the conveying direction of the compressor may be achieved in several ways. In one embodiment, the compressor 1 has a conveyor wheel. In this case, the compressor is configured to reverse a rotational direction of the conveyor wheel as a response to the control signal 31 for reversing the conveying direction.
In another embodiment, the compressor includes a four-way valve. In this case, for reversing the conveying direction, the compressor is configured to, as a response to the control signal 31, e.g. on the basis of the refrigeration mode, fluidically decouple a suction side of the compressor from the evaporator 4 and fluidically connect the same to the condenser 2 or to fluidically decouple a pressure side of the compressor from the condenser 2 and to fluidically connect the same to the evaporator 4. In this case, the element that was in the refrigeration mode takes over the function of the condenser in the heating mode or defrosting mode.
On the basis of the defrosting mode, for reversing the conveying direction, a suction side of the compressor is fluidically decoupled from the condenser (which was the evaporator in the defrosting mode) and the same is fluidically connected to the evaporator 4 (which was the condenser in the defrosting mode), and a pressure side of the compressor is fluidically decoupled from the evaporator 4 (which was the condenser in the defrosting mode) and is fluidically connected to the condenser 2 (which was the evaporator in the defrosting mode).
As shown in
The refrigeration process 6, as illustrated in
The generated cold and heat of the refrigerant process is subsequently transported indirectly via a suitable heat exchanger, such as a plate heat exchanger 7, with a non-flammable secure working medium, a so-called secondary fluid, into the refrigeration structure, refrigeration container, or space to be cooled in general. Therefore, the refrigeration system consists of a primary cycle for refrigeration and a secondary cycle for the transport of cold or heat.
This secondary cycle for distributing the generated cold and heat can be carried out in different ways. There is the possibility to use a brine that is conveyed from a suitable pump 8 and therefore removes the heat from the space to be cooled or introduces the same into the space to be heated and transports the same to the refrigerant-carrying part of the machine, i.e. the primary cycle, without a change of phase in the secondary cycle 9.
A further variation is the use of a substance that is also conveyed by means of a pump with a change of phase and flows through the heat exchanger of the closed space and in this way removes the heat from the same or introduces the heat. In this case, the secondary cycle transports the heat to the refrigerant-filled part of the machine, i.e. the primary cycle. Advantageously, the change of phase is a liquid-gaseous change of phase so as to ensure the ability to pump the secondary fluid. A change of phase from solid to liquid in the form of a slurry, i.e. a mixture of watery ice and glycol, is generally not ruled out.
Forced-driven secondary cycles, i.e. with the use of a pump, have the disadvantage that the pump possibly needs energy for overcoming the flow resistances of the secondary system. An alternative that does not require the use of a pump is the design of the secondary cycle as a thermosiphon cycle, shown in
In the use case in which heat has to be transported to the closed space or the evaporator is to be defrosted, the process is reversed by now supplying energy to the heat exchanger 10 and by evaporating the liquid phase of the secondary fluid 10a and by the same exiting the heat exchanger as a gaseous phase 10b and by supplying the same to the heat exchanger 11 in the closed space via a suitable pipeline. The refrigerant enters the heat exchanger in the closed space 11 as vapor 11, is then condensed, dissipates its heat, and flows in its liquid form 11a back out of the heat exchanger into the refrigerating heat exchanger 10 of the machine, where the evaporation process starts again. When transporting heat into the closed space, this process is also carried out exclusively on the basis of the geodetic height difference of the liquid phase in the two heat exchangers by having a level equalization in both components due to gravity.
When being designed accordingly, each of the described methods also enables the reversal of the cycle, so that the heat exchanger 11 of
The condenser of the refrigerating part of the machine, as well as the heat exchanger in the closed space, or of the container, are usually operated with a force convection generated by an appropriate blower on the air side. Similar to the refrigerating part of the machine, the primary cycle, with respect to the secondary cycle it should be also taken into account that the filling quantities of the working medium are kept at a minimum and that a cooler that not only has a small inner volume but also a small thermal mass is used so as to be able to carry out the defrosting process as quickly and therefore energy-efficient as possible. Thus, all heat exchangers with a low refrigerant filling quantity and a minimum use of material can be used for the heat exchanger 11 in the closed space, e.g. micro-channel technologies, which particularly correspond to the requirements. Other structures, such as finned heat exchangers can be also used as an alternative. Both heat exchanger types are ideally operated in a flooded manner.
Due to the omission of pumps through the use of thermosiphon solutions and the resulting energetic advantages as well as the decrease of complexity of the system, such solutions have particular advantages compared to the initially described conventional technology and are therefore advantageous in the field of compact systems with spatial distances of advantageously up to 10 meters and refrigerating or heating capacities of below 50 kW and particularly advantageously of up to 2 meters between the two heat exchangers 10 and 11 and with low refrigerating and heating capacities of below 10 kW.
If, in a use case considered, it is not necessary that the refrigerating machine can also be used to heat the closed space, if required, it is advantageous in any case to arrange the heat exchanger 11 in the closed space 5 geodetically below the heat exchanger 10, where the refrigerant flows through the same, with reference to
In case that only heat has to be introduced into the closed space, with this case being illustrated in
In certain installation situations and operating conditions of the arrangement of the components, illustrated in
These cases use the solution illustrated in
In
The possibility to reverse the conveying direction of the pump by changing the pole of its motor results in the use case of heating the heat exchanger 11 to heat the closed space 5, illustrated in
Finally,
Alternatively to the cases illustrated in
In the case illustrated in
Simultaneously, the first part 15a of the line arrangement is illustrated as it enters into the heat exchanger 7, wherein the second part of the line arrangement 15b entering into the heat exchanger 7 is illustrated as well. 22 in
Even though
However, it is advantageous to integrate both functionalities into one element 10. The primary working fluid flows in the channels 40 illustrated in
In the reverse case, i.e. if the room to be temperature-controlled is to be heated, the exchanger acts as a condenser for the primary working fluid. In this case, vaporous and compressed warm primary working fluids flows into the channels 40, which are located as far in the cool liquid secondary fluid as possible, via the element 42, which now acts as an expander. Through this, the primary working fluid condenses on the inside of the channels 40 and leaves the heat exchanger 10 as a liquid via the element 41, which now acts as a collector. Through this, the secondary fluid evaporates in the heat exchanger 10, and vapor flows across through the connection 15b into the temperature-controlling element 11, 14 so as to heat the space. Through this, the secondary fluid condenses in the temperature-controlling element and returns into the heat exchanger as a liquid due to the siphon principle or via a pump so as to be evaporated again.
In addition, the heat exchanger 10 is shown as a volumetric micro-channel heat exchanger in which the expansion element or collection element 41 couples the line 14a to the individual channels of the micro-channel heat exchanger, while a collection element or expansion element 42 is collecting or distributing the liquid (in the case of two separate elements) or vaporous (in the case of the integrated element and the refrigerating operation) primary fluid on the output side, and only supplies the same to the evaporator or condenser in the case of the separate implementation. Even though this is not shown in
In the apparatus according to an embodiment, the evaporator 4 or the liquefier 2 of the primary heat pump circuit is configured so as to be integrated into the heat exchanger 10. For example, with respect to
Furthermore, an interaction region 43 extending between the third connection portion 15a for the secondary fluid and the fourth connection portion 15b for the secondary fluid is provided. The channel portion 40 is arranged in the same, wherein the channel portion 40 is thermally coupled to the interaction region 43 and fluidically decoupled from the interaction region 43.
Condensation and evaporation of the primary circuit takes place in the channel portion within the interaction space. Furthermore, due to condensation or evaporation in the primary circuit in the interaction region, there is evaporation or condensation of the primary fluid on the outside at the channel portion. Advantageously, the interaction region is the volume limited by a wall hand having the variable liquid level.
Subsequently, implementations of the present invention are summarized as examples.
Even though some aspects have been described within the context of a device, it is understood that said aspects also represent a description of the corresponding method, so that a block or a structural component of a device is also to be understood as a corresponding method step or as a feature of a method step. By analogy therewith, aspects that have been described within the context of or as a method step also represent a description of a corresponding block or detail or feature of a corresponding device. Some or all of the method steps may be performed while using a hardware device, such as a microprocessor, a programmable computer or an electronic circuit. In some embodiments, some or several of the most important method steps may be performed by such a device.
While this invention has been described in terms of several embodiments, there are alterations, permutations, and equivalents which fall within the scope of this invention. It should also be noted that there are many alternative ways of implementing the methods and compositions of the present invention. It is therefore intended that the following appended claims be interpreted as including all such alterations, permutations and equivalents as fall within the true spirit and scope of the present invention.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2021 211 049.5 | Sep 2021 | DE | national |
| 10 2022 201 790.0 | Feb 2022 | DE | national |
This application is a continuation of copending International Application No. PCT/EP2022/076419, filed Sep. 22, 2022, which is incorporated herein by reference in its entirety, and additionally claims priority from German Applications Nos. DE 10 2021 211 049.5, filed Sep. 30, 2021 and DE 10 2022 201, filed Feb. 21, 2022, all of which are incorporated herein by reference in its entirety.
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/EP2022/076419 | Sep 2022 | WO |
| Child | 18618087 | US |
