Thermally driven heat pump and thermally driven heat pumping method

Abstract

: The invention relates to a thermally driven heat pump (1), in particular a type I or type II heat transformer, comprising: - a heat engine portion (2) designed to carry a working medium such that the working medium exchanges heat in a second temperature range (T2) and exchanges heat in a first temperature range (T1), wherein the working medium releases heat in the lower of the first temperature range (T1) and the second temperature range (T2) and the working medium takes up heat in the higher of the first temperature range (T1) and the second temperature range (T2), resulting in a pressure increase, and - a heat pump portion (3) designed to carry the working medium such that the working medium exchanges heat in a fourth temperature range (T4) and exchanges heat in a third temperature range (T3), wherein the working medium releases heat in the higher of the fourth temperature range (T4) and the third temperature range (T3) and takes up heat in the lower of the fourth temperature range (T4) and the third temperature range (T3), resulting in a reduction in pressure of the working medium, wherein the heat engine portion (2) and the heat pump portion (3) are fluidically connected to one another with respect to the working medium, so that the increase in pressure of the working medium in the heat engine portion (2) drives the heat pump portion (3).

Description

[0001] Thermally driven heat pump and thermally driven heat pump operator drive

[0002] The invention relates to a thermally driven heat pump and a thermally driven heat pumping method.

[0003] A thermally driven heat pump serves two purposes: either (Type I, especially an adsorption heat pump) to exergetically combine heat at a low temperature level with heat at a significantly higher temperature level, so that heat at an intermediate temperature is provided, or (Type II, especially a heat transformer) to split heat at an intermediate temperature into two heats at high and low temperatures. Thus, a thermally driven heat pump uses a single heat source to achieve an increase in temperature.

[0004] The absorption heat pump (a thermally driven type I heat pump) is a well-known example. In a type I absorption heat pump, the refrigerant circuit of a compression heat pump (CHP) is coupled with a second circuit, the solvent circuit, with the solvent circuit replacing the compressor of the CHP. Initially, heat is extracted at a comparatively low temperature.

[0005] (Ambient or low-grade waste heat) is absorbed in the evaporator. There, the refrigerant is evaporated at low pressure. This vapor is then absorbed by the solvent in the absorber. This process releases heat at a higher temperature level. The resulting liquid mixture is pumped into the generator (also called the desorber). Here, the pressure is significantly increased. At this increased pressure, the refrigerant is desorbed (i.e., driven out of the solvent). For this process, the drive heat, which has an even higher temperature, is supplied. The solvent is then expanded via a throttle and returned to the absorber. Part of the thermal energy content of the solvent can be used to preheat the incoming mixture flow to the generator via a heat exchanger. Meanwhile, the driven refrigerant flows into the condenser.The enthalpy of condensation released there is released as heat at a similar temperature level to that in the absorber. The pressure of the now liquid refrigerant is then reduced via a further expansion valve, during which it partially evaporates again before being fed to the evaporator. The heat released in the absorber and condenser is available as usable heat.

[0006] A thermally driven heat pump of type II (a heat transformer) is also known. A heat transformer is a process engineering system that splits a heat flow of medium temperature into two heat flows. One of the two generated partial heat flows has a higher temperature level than the original heat flow, the other partial heat flow has a lower temperature level. It can therefore be used to utilize waste heat with an insufficient temperature level. Ideally, a heat transformer is operated solely with heat; in reality, however, mechanical energy (electricity) is still required as auxiliary energy for the process. A heat transformer can be technically implemented, for example, as an absorption heat transformer, i.e., a reverse-running absorption chiller process. In the following, TK is the ambient temperature of the system.Thermodynamically, a heat transformer can be described by a system in which a heat engine drives a heat engine. The heat engine provides work W, which it obtains by splitting off the heat stream QK from the heat stream QM at the intermediate temperature level TM and converting it to the lower temperature level TK. The heat engine uses the provided work W to raise the heat QH split off from the heat QM from the intermediate temperature level TM to the higher temperature level TH. The heat that the heat engine can raise from a lower temperature level to a higher temperature level is thus limited by the work that the heat engine provides to the heat engine. Furthermore, the higher the temperature level TH of the useful heat, the less useful heat QH can be provided.Absorption heat transformers are heat transformers that utilize a reverse absorption chiller process. To implement such a system based on an absorption chiller, the throttles in the high-pressure solvent and refrigerant circuits must be replaced by pumps, while the pump in the low-pressure solvent circuit must be replaced by a throttle. The drive heat is absorbed by the generator and evaporator. The refrigerant, evaporated at elevated pressure in the evaporator, is fed to the absorber, where it is absorbed by the solvent. The resulting mixture is expanded via a throttle and fed to the generator. There, the solvent is driven off at lower pressure by the drive heat. The solvent is then pumped back up to higher pressure and fed to the absorber.In this process, the refrigerant is often preheated via a heat exchanger by the heat from the mixture flow exiting the absorber. The expelled refrigerant is then fed to the condenser. There, due to the lower pressure, it condenses at a significantly lower temperature. The heat released in this process is generally considered waste heat in practice. Subsequently, the liquid refrigerant is pressurized again by a second pump and fed to the evaporator. The usable heat supplied by the heat transformer is the heat of solution released from the refrigerant in the solvent within the absorber. The drive heat must be divided between the generator and the evaporator.

[0007] A disadvantage of conventional absorption heat pumps and heat transformers is that the pressure of the working fluid is reduced in throttles, meaning that the flow energy of the working fluid from the heat engine cannot be used to drive the heat pump. Instead, this occurs indirectly via absorption. Therefore, existing systems are very large, heavy, complex, and expensive, and are inefficient, achieving only a relatively low coefficient of performance (COP) and / or a small temperature increase.

[0008] WO 2024 / 056788 further describes a rotary heat pump comprising: a rotational axis, a number of compression channels in which a working medium, in particular a gas, preferably a noble gas, is directed away from the rotational axis to increase the pressure due to centrifugal acceleration, a number of expansion channels in which the working medium is directed towards the rotational axis to decrease the pressure due to centrifugal acceleration, a number of first heat transfer channels for the working medium and a number of second heat transfer channels for a heat transfer medium, in particular a liquid, so that heat is transferred between the working medium flowing in the first heat transfer channels and the heat transfer medium flowing in the second heat transfer channels, a number of first and second rotor plates which define the compression channels, the expansion channels,The first heat transfer channels are for the working fluid and the second heat transfer channels are for the heat transfer medium, with the first and second rotor plates connected along their main extension planes. This process can be operated counterclockwise as a heat pump or clockwise as a heat engine in the rotating system (in the T-s diagram). Fundamentally, the counterclockwise process requires a higher differential pressure on the compressor side than on the expansion side. This can be explained in the T-s diagram by a divergence of the isobars or by the density differences between compression and expansion in the rotating system. The high density during expansion and the low density during compression result in a pressure difference as the cycle progresses in the rotating potential field.which thermodynamically corresponds to the exergy required for the process. This pressure difference can be provided in the counterclockwise process via a ventilation system, which, along with its drive (electric motor), is also located in the rotating system. The same analogy applies to the clockwise process (the process is the same in the state diagram, e.g., Ts diagram); however, here no pressure difference or exergy is required, but rather a pressure difference is present, which can be dissipated, for example, in a turbine, thereby generating technical work. This work is usually transferred to a generator via shaft power, and electricity is produced.

[0009] It is an object of the invention to mitigate or eliminate at least one of the disadvantages of the prior art. In particular, it is an object of the present invention to provide a thermally driven heat pump that is relatively compact, less complex, has a higher coefficient of performance (COP), higher efficiency, and / or achieves a higher temperature increase.

[0010] This is achieved by a thermally driven heat pump, in particular of type I or type II, comprising:

[0011] - a heat engine section (in particular comprising devices for generating different pressure and temperature levels) which is configured to carry a working medium such that the working medium exchanges heat (in particular with a second heat transfer medium) in a second temperature range and exchanges heat (in particular with a first heat transfer medium) in a first temperature range, wherein in the lower of the first and second temperature ranges the working medium releases heat and in the higher of the first and second temperature ranges the working medium absorbs heat, so that a pressure increase occurs

[0012] (especially the gained exergy is released in the form of a positive pressure difference (pressure increase)), and

[0013] - a heat pump section (in particular comprising devices for generating different pressure and temperature levels) which is configured to guide the working medium such that the working medium exchanges heat (in particular with the second heat transfer medium) in a fourth temperature range and exchanges heat (in particular with a third heat transfer medium) in a third temperature range, wherein in the higher of the fourth and third temperature ranges the working medium releases heat and in the lower of the fourth and third temperature ranges the working medium absorbs heat, so that a pressure reduction occurs (in particular the required exergy in the form of a negative pressure difference (pressure reduction) is required), wherein the heat pump section and the

[0014] The heat pump section is fluidically connected to the working medium, so that the pressure increase (especially the gained exergy or the positive pressure difference) of the working medium in the heat engine section drives the heat pump section.

[0015] This is further achieved through a thermally driven heat pump process, comprising the following steps:

[0016] - Guiding a working medium in a heat engine section, wherein the working medium exchanges heat in a second temperature range and exchanges heat in a first temperature range, wherein in the lower of the first temperature range and the second temperature range the working medium releases heat and in the higher of the first temperature range and the second temperature range the working medium absorbs heat, so that a pressure increase occurs,

[0017] - Guiding the working medium in a heat pump section, wherein the working medium exchanges heat in a fourth temperature range and exchanges heat in a third temperature range, wherein in the higher of the fourth temperature range and the third temperature range the working medium releases heat and in the lower of the fourth temperature range and the third temperature range the working medium absorbs heat, so that a pressure reduction of the working medium occurs,

[0018] - Guiding the working medium from the heat engine section to the heat pump section, so that the pressure increase of the working medium in the heat engine section drives the heat pump section.

[0019] The flow energy of the working fluid, obtained in the heat engine section, directly drives the heat pump section. Preferably, the flow energy obtained in the heat engine section is used without conversion.

[0020] (especially in a form of energy other than thermal or heat energy) introduced into the heat pump section.

[0021] In particular, the thermally driven heat pump of type I absorbs heat from the working fluid in the second and fourth temperature ranges and releases heat in the first and third temperature ranges. In particular, in the heat transformer of type II, the working fluid absorbs heat in the first and third temperature ranges and releases heat in the second and fourth temperature ranges. Specifically, the second and fourth temperature ranges lie between the first and third temperature ranges. In particular, the heat transfers occur between the working fluid and heat transfer media. Preferably, three different flows of heat transfer media (in particular, a low temperature, a medium temperature, and a high temperature) are provided. In particular, the first and third temperature ranges do not overlap.Preferably, there is a difference of at least 50 °C between the first temperature range and the third temperature range, preferably at least 80 °C, and even more preferably at least 100 °C.

[0022] Preferably, the working fluid is gaseous, particularly throughout the entire process in the thermally driven heat pump. In particular, the thermally driven heat pump is designed to maintain the working fluid in a gaseous state during operation. By using a purely gaseous working fluid (which does not undergo any phase transitions from liquid to gaseous and vice versa during the process), the temperatures can be shifted arbitrarily within the temperature range. Preferably, no phase change of the working fluid occurs during operation of the thermally driven heat pump. In particular, an outlet of the thermal engine section is fluidically connected to an inlet of the heat pump section, and an outlet of the heat pump section is fluidically connected to an inlet of the thermal engine section.

[0023] The pressure increase in the heat engine section occurs primarily through the heat engine section itself; that is, the pressure of the working fluid flowing into the heat engine section is higher than the pressure of the working fluid flowing out of the heat engine section. The pressure decrease in the heat pump section also occurs primarily through the heat pump section itself; that is, the pressure of the working fluid flowing into the heat pump section is lower than the pressure of the working fluid flowing out of the heat pump section.

[0024] Preferably, the clockwise cycle in the heat pump section is repeated several times, thereby increasing the pressure of the working fluid in each cycle (which in total represents the pressure increase of the heat pump section). This allows even small temperature differences between the medium and high temperatures in the heat pump section to generate a large pressure difference through repeated cycles, thus enabling a large temperature lift in the heat pump process. This decouples the temperature relationships between the second and first temperature ranges and between the fourth and third temperature ranges.

[0025] With reference to the method, this preferably comprises the step of guiding the working medium from the heat pump section to the heat engine section. Preferably, the method includes the use of the thermally driven heat pump in any embodiment described in this disclosure. In particular, the working medium is guided in such a thermally driven heat pump.

[0026] In this disclosure, the terms "counterclockwise" and "clockwise" refer to the shape of the curve in the Ts diagram. Where this disclosure refers to a "number," it can refer to a number of one or more elements.

[0027] It is preferred if the heat exchange of the working medium in the first temperature range is isothermal, isobaric, or a combination thereof. It is preferred if the heat exchange of the working medium in the second temperature range is isothermal, isobaric, or a combination thereof. It is preferred if the heat exchange of the working medium in the third temperature range isothermal, isobaric, or a combination thereof. It is preferred if the heat exchange of the working medium in the fourth temperature range isothermal, isobaric, or a combination thereof.

[0028] It is preferred if the second temperature range corresponds to the fourth temperature range, i.e., that they overlap at least partially, and preferably the minimum and / or maximum temperatures of the two temperature ranges differ by less than 40 °C, particularly preferably by less than 20 °C (especially less than 10 °C). Thus, in particular, the upper temperature of the clockwise process (i.e., the heat engine section) corresponds essentially to the lower temperature of the counterclockwise process (i.e., the heat pump section). In particular, the four temperature ranges can thus be reduced to three temperature ranges (low, medium, and high temperature levels – LT, LT, HT). This simplifies the design, as only three heat transfer media are used instead of four.This reduces cross-sections and the number of rotating seals. This therefore represents, in particular, a crossover point in the counterclockwise and clockwise processes in the Ts diagram.

[0029] It is advantageous if the heat engine section is configured (in particular, the heat engine section has a compression section and an expansion section configured to do so) to effect a pressure change of the working medium from a second pressure range to a first pressure range and from the first pressure range to a fourth pressure range, and if the heat pump section is configured (in particular, the heat pump section has a compression section and an expansion section configured to do so) to effect a pressure change of the working medium from the fourth pressure range to a third pressure range and from the third pressure range to a second pressure range;and the second pressure range and the fourth pressure range lie between the first pressure range and the third pressure range. In particular, it is preferred if either (especially in the embodiment as a thermally driven heat pump type II, in particular a heat transformer): the first pressure range is lower than the second pressure range, the second pressure range is lower than the fourth pressure range, and the fourth pressure range is lower than the third pressure range, and / or there is a compression from the fourth pressure range to the third pressure range, a release from the third pressure range to the second pressure range, a release from the second pressure range to the first pressure range, and a compression from the first pressure range to the fourth pressure range;or (especially in the version as a thermally driven heat pump type I): the third pressure range is lower than the second pressure range, the second pressure range is lower than the fourth pressure range, and the fourth pressure range is lower than the first pressure range, and / or there is a pressure expansion from the fourth pressure range to the third pressure range, a pressure expansion from the third pressure range to the second pressure range, a pressure expansion from the second pressure range to the first pressure range, and a pressure expansion from the first pressure range to the fourth pressure range. In particular, the first and third pressure ranges do not overlap. The pressure difference between the second and fourth pressure ranges represents the pressure increase or decrease in the heat pump section and the thermal energy generator section.

[0030] Preferably, the thermally driven heat pump has a rotor, wherein the rotor has: an axis of rotation, a number of first compression channels in which the working medium is directed away from the axis of rotation to increase the pressure due to centrifugal acceleration, a number of first expansion channels in which the working medium is directed towards the axis of rotation to decrease the pressure due to centrifugal acceleration, a number of second compression channels in which the working medium is directed away from the axis of rotation to increase the pressure due to centrifugal acceleration, a number of second expansion channels in which the working medium is directed towards the axis of rotation to decrease the pressure due to centrifugal acceleration;The heat engine section has a certain number of first compression channels and a certain number of first expansion channels, while the heat pump section has a certain number of second compression channels and a certain number of second expansion channels. By forming the corresponding channels on the rotor, the heat pump and heat engine functions can be easily implemented. Compression and expansion can thus be achieved by utilizing centrifugal acceleration. With appropriate dimensioning (especially low relative flow velocities, e.g., less than 10 m / s average velocity in the channels), compression and expansion in the rotating potential field can achieve isentropic efficiencies of up to 99.9%. This results in a particularly efficient thermally driven heat pump.

[0031] Preferably, a motor is provided to drive the rotation of the rotor.

[0032] For the purposes of this disclosure, the location and direction specifications refer to the intended operating condition of the rotor, where "radial", "axial" and "circumferential" refer to the axis of rotation. With regard to the flow of the working or heat transfer medium, "inside" means closer to the axis of rotation of the rotor and "outside" means further away from the axis of rotation.

[0033] It is preferred that the rotor comprises a number of first and second rotor plates, each comprising the first compression channels, the first expansion channels, the second compression channels, and the second expansion channels, wherein the first and second rotor plates are connected to one another along their principal planes of extension. The arrangement of the first and second rotor plates forms a compact rotor element that is particularly stable against rotational forces. To form the rotor element, the first and second rotor plates are stacked in contact with one another and connected to each other at their intersecting principal planes of extension. In the first and / or second rotor plates, the working medium flows through flow channels that form the first compression channels, the first expansion channels, the second compression channels, and the second expansion channels.It has also proven advantageous that the first and second rotor plates are virtually immovable relative to each other, thus significantly reducing the number of balancing runs or even eliminating them entirely. In a preferred embodiment, the principal planes of extension of the first and second rotor plates, i.e., their plate planes in which the first and second rotor plates each have their greatest extent, are arranged essentially perpendicular to the axis of rotation. Preferably, the axis of rotation passes through the centers of both the first and second axes of rotation. Furthermore, it is advantageous if the first and second rotor plates are arranged essentially congruently when viewed along the axis of rotation.

[0034] Preferably, the rotor has: a number of working medium heat transfer channels for the working medium and a number of heat transfer medium heat transfer channels for a heat transfer medium, in particular a liquid, such that heat is transferred between the working medium flowing in the working medium heat transfer channels and the heat transfer medium flowing in the heat transfer medium heat transfer channels. The working medium also flows through the working medium heat transfer channels. Preferably, a first, a second, and a third heat transfer medium flow through corresponding first, second, and third heat transfer medium heat transfer channels. The number of available heat exchanger surfaces can be increased as desired during rotor operation.Preferably, the maximum temperature difference between the first heat transfer medium and the working medium during heat exchange in the first temperature range is less than 30 °C, particularly preferably less than 20 °C. Preferably, the maximum temperature difference between the third heat transfer medium and the working medium during heat exchange in the third temperature range is less than 30 °C, particularly preferably less than 20 °C. Preferably, the maximum temperature difference between the second heat transfer medium and the working medium during heat exchange in the second and fourth temperature ranges is less than 40 °C, particularly preferably less than 20 °C.

[0035] It is advantageous if the number of first rotor plates each has at least one of the first compression channels, at least one of the first expansion channels, at least one of the second compression channels, at least one of the second expansion channels, and at least one of the working medium heat transfer channels, and the number of second rotor plates each has at least one of the heat transfer medium heat transfer channels.

[0036] It is advantageous if the rotor, in particular the first rotor plates each, has at least one flow channel for the working medium with a number of (preferably extending substantially circumferentially) first heat transfer flow channel sections for forming the first of the working medium heat transfer channels for heat transfer in the first temperature range, with a number of (preferably extending substantially circumferentially) second heat transfer flow channel sections for forming the second of the working medium heat transfer channels for heat transfer in the second temperature range, with a number of (preferably extending substantially circumferentially) third heat transfer flow channel sections for forming the third of the working medium heat transfer channels for heat transfer in the third temperature range.and with a number of (preferably essentially circumferentially extending) fourth heat transfer flow channel sections to form the fourth of the working medium heat transfer channels for heat transfer in the fourth temperature range. The number of first heat transfer flow channel sections, the number of second heat transfer flow channel sections,The number of third heat transfer flow channel sections and the number of fourth heat transfer flow channel sections constitute, in particular, flow channel sections of the respective flow channel. Preferably, each of the first rotor plates has at least one flow channel. Preferably, the flow channel (or each of the flow channels) has an inlet opening for the working medium at a first end and an outlet opening for the working medium at a second end. Thus, the working medium can be distributed via the inlet openings to the flow channels within the first rotor plates. Subsequently, the working medium flows along the flow channels to the outlet openings, where the working medium is discharged from the rotor element. The individual flow channel sections are interconnected.so that the working medium can flow through the flow channel within the first rotor plate from the inlet to the outlet opening. Preferably, the inlet and outlet openings are fluidically connected, with the connection preferably being formed on an adjacent rotor plate. In a preferred embodiment, the inlet and / or outlet openings for the working medium are each aligned, i.e., arranged in a line parallel to the axis of rotation. Preferably, the inlet and / or outlet openings are each congruent when viewed in the direction parallel to the axis of rotation.

[0037] Preferably, the number of heat transfer medium heat transfer channels comprises: a number of first heat transfer medium heat transfer channels, such that heat is transferred between the working medium flowing in the first working medium flow channel sections and the heat transfer medium flowing in the first heat transfer medium heat transfer channels; a number of second heat transfer medium heat transfer channels, such that heat is transferred between the working medium flowing in the second working medium flow channel sections and in the fourth working medium flow channel sections and the heat transfer medium flowing in the second heat transfer medium heat transfer channels; a number of third heat transfer medium heat transfer channels.so that heat is transferred between the working medium flowing in the third working medium flow channel sections and the heat transfer medium flowing in the third heat transfer medium heat transfer channels. Preferably, the first heat transfer medium heat transfer channels each have an inlet opening for a first heat transfer medium at a first end and an outlet opening for the first heat transfer medium at a second end. Preferably, the second heat transfer medium heat transfer channels each have an inlet opening for a second heat transfer medium at a first end and an outlet opening for the second heat transfer medium at a second end. Preferably, the third heat transfer medium heat transfer channels each have an inlet opening for a third heat transfer medium at a first end and an outlet opening for the third heat transfer medium at a second end.

[0038] It is preferred that the second and fourth heat transfer flow channel sections are arranged radially between the first and third heat transfer flow channel sections. The first heat transfer flow channel sections can be arranged further outwards and the third heat transfer flow channel sections further inwards, or the third heat transfer flow channel sections can be arranged further outwards and the first heat transfer flow channel sections further inwards. Preferably, the heat transfer in the second and fourth heat transfer flow channel sections occurs in substantially the same temperature range; in particular, the temperature ranges overlap or one temperature range is contained within the other.Preferably, the working fluid flows directly from the second heat transfer flow channel sections to the fourth heat transfer flow channel sections, or vice versa. Preferably, the second heat transfer flow channel sections connect directly to the fourth heat transfer flow channel sections, or vice versa.

[0039] Preferably, the at least one flow channel further comprises: a number of preferably substantially radially outwardly extending first compression flow channel sections for forming the first compression channels, a number of preferably substantially radially inwardly extending first expansion flow channel sections for forming the first expansion channels, a number of preferably substantially radially outwardly extending second compression flow channel sections for forming the second compression channels, and a number of preferably substantially radially inwardly extending second expansion flow channel sections for forming the second expansion channels.Preferably, the first compression flow channel sections each extend from a first end of the first heat transfer flow channel sections to a first end of the second heat transfer flow channel sections, and the first expansion flow channel sections extend from a second end of the first heat transfer flow channel sections to a second end of the second heat transfer flow channel sections. Preferably, the second compression flow channel sections each extend from a first end of the third heat transfer flow channel sections to a first end of the fourth heat transfer flow channel sections, and the second expansion flow channel sections extend from a second end of the third heat transfer flow channel sections to a second end of the fourth heat transfer flow channel sections.

[0040] It is preferred if the number of first compression flow channel sections, the number of first expansion flow channel sections, the number of first heat transfer flow channel sections, and the number of second heat transfer flow channel sections form a number of closed loops of the heat engine section, except for one inlet and one outlet, and if the number of second compression flow channel sections, the number of second expansion flow channel sections, the number of third heat transfer flow channel sections, and the number of fourth heat transfer flow channel sections form a number of closed loops of the heat pump section, except for one inlet and one outlet. The number of loops can be one or more in each case.Any number of cycles can be executed in each of the two processes to generate the necessary pressure increase from the thermal power process for the heat pump process. The ratio of the temperature differences (high-medium to medium-low) does not have to be equal, but can be compensated for by the ratio of the number of thermodynamic "spirals" or "turns." For example, even with very small temperature differences between medium and low, a high pressure increase can be generated by a relatively high number of cycles, in order to overcome the necessary high pressure difference required for the high temperature difference for heat pumping from medium to high temperature. This degree of freedom is comparable to the number of turns in electrical coils used to transform the voltage level.

[0041] Preferably, the loops of the heat engine section and / or the loops of the heat pump section are spirally shaped. Preferably, a downstream number of first heat transfer flow channel sections and a downstream number of second heat transfer flow channel sections are arranged radially between an upstream number of first heat transfer flow channel sections and an upstream number of second heat transfer flow channel sections, or vice versa.Preferably, a downstream arrangement of the number of third heat transfer flow channel sections and a downstream arrangement of the number of fourth heat transfer flow channel sections are located radially between an upstream arrangement of the number of third heat transfer flow channel sections and an upstream arrangement of the number of fourth heat transfer flow channel sections, or vice versa.

[0042] It is advantageous if at least one flow channel has a connecting flow channel section that connects the outlet of the heat engine section to the inlet of the heat pump section or the outlet of the heat pump section to the inlet of the heat engine section.

[0043] It is preferred if the second rotor plates have at least one connecting flow channel that connects the outlet of the heat engine section to the inlet of the heat pump section or the outlet of the heat pump section to the inlet of the heat engine section.

[0044] It is advantageous if the number of loops in the heat pump section and / or the number of loops in the heat engine section is at least two.

[0045] Optionally, the number of loops in the heat pump section differs from the number of loops in the heat engine section; in particular, the number of loops in the heat pump section is optionally higher than the number of loops in the heat engine section. It is preferred if two flow channels, especially those of the first rotor plates, are arranged mirrored with respect to a symmetry plane stretched in the axial and radial directions.

[0046] For the integral formation of the individual flow channels, it is advantageous if the first compression channels, the first expansion channels, the second compression channels, the second expansion channels, the first of the working medium heat transfer channels, the second of the working medium heat transfer channels, the third of the working medium heat transfer channels, and the fourth of the working medium heat transfer channels are formed as recesses originating from preferably substantially planar first outer surfaces of the first rotor plates. Preferably, the heat transfer medium channels are formed i. as recesses originating from preferably substantially planar outer surfaces of the second rotor plates or ii. as recesses originating from preferably substantially planar second outer surfaces of the first rotor plates.The first and second rotor plates preferably have substantially planar outer surfaces parallel to their main planes of extension. In the first embodiment (i.), the working fluid flows in the recesses of the first rotor plates, while the heat transfer medium flows in the recesses of the second rotor plates. Due to the connection of the first and second rotor plates along their main planes of extension, the recesses of the first rotor plate and the adjacent outer surfaces of the second rotor plates form closed flow channels in cross-section. In the second embodiment (ii.), the working fluid and the heat transfer medium each flow in separate recesses of the first rotor plates, which are formed on the opposing outer surfaces of the first and second rotor plates.These recesses, together with the adjacent outer surfaces of the second rotor plates, form closed flow channels in cross-section for the working fluid and the heat transfer medium. In a preferred embodiment, the first rotor plates and the second rotor plates are connected to each other via diffusion bonds, i.e., by diffusion bonding.

[0047] Depending on the embodiment, preferably at least 50, in particular at least 200, for example from 300 to 800, first rotor plates and / or at least 50, in particular at least 200, for example from 300 to 800, second rotor plates are provided. The first and / or the second rotor plates can have a wall thickness, i.e., an extent perpendicular to the main plane of extension or plate from one outer surface to the other, of, for example, 0.2 mm to 5 mm, in particular from 0.5 mm to 4 mm, for example from 1 mm to 2 mm. The flow channels can have a width, i.e., an extent on the outer surface of the respective first or second rotor plate transverse to the flow direction, of, for example, 0.5 mm to 5 mm, in particular from 1 mm to 3 mm. The depth of the flow channels, i.e. their extent perpendicular to the main extension plane at the deepest point, can be, for example, from 0.2 mm to 3 mm, in particular from 0.5 mm to 1.5 mm.

[0048] Referring to the method according to the invention, the working medium is preferably guided in a thermally driven heat pump according to one of the embodiments described in this disclosure. The method particularly comprises the step of driving a rotation of the rotor about the axis of rotation.

[0049] The procedure preferably includes the following step:

[0050] Supplying a first, a second and a third heat transfer medium to the rotor.

[0051] In principle, additional heat can be transferred very easily in a rotating system during pressure increases or decreases (compression and expansion). This means that the design of the processes is not limited to those previously known in thermodynamics. Instead, the process, and especially the heat transfer, can proceed in various ways, including any combination of the following examples:

[0052] Example 1: Sobaric heat dissipation is achieved by keeping the radius in the rotating system constant, thereby maintaining an approximately constant pressure. Here, the usual relationship applies that the two media in the heat exchanger should ideally have the same capacity mass flow rates (specific heat capacity times mass flow rate) to minimize the exergy losses of the heat exchanger. The temperature difference between the inlet and outlet of the heat exchanger is determined by the medium, the mass flow rate, and the heat output.

[0053] Example 2: I. Sothermal heat removal is achieved by continuously increasing the radius during heat removal, thereby compensating for the temperature drop that normally occurs when heat is removed from a sensible medium (such as a gas). The radius increase during heat removal is dimensioned such that the temperature remains constant. The same analogy applies to heat input. Here, however, the radius is continuously decreased to cause expansion and thus a temperature drop. The radius reduction and the associated theoretical temperature drop should be dimensioned such that the supplied heat compensates for the temperature drop, and thus the heat input occurs at a constant temperature.

[0054] Example 3: Heat dissipation with increasing temperature during heat dissipation, achieved by increasing the radius than the temperature reduction that would otherwise occur during heat dissipation. This can be advantageous for dimensioning as a direct-flow heat exchanger and offers an additional degree of freedom for the heat exchanger's design. The same analogy applies, but in reverse, to heat input.

[0055] Example 4: Heat removal with a significantly reduced temperature during heat removal. Here, the radius can be deliberately reduced during heat removal to achieve large temperature differences as efficiently as possible (with low exergy losses). In addition to the temperature reduction that would otherwise occur due to heat removal, a continuous expansion with further temperature reduction is carried out. The same analogy applies, but in reverse, to heat input. This flexible design allows, for example, the "special forms" of previously known processes to be modeled, e.g.:

[0056] 1) Joule or Joule Brayton with approximately isentropic compression and expansion and approximately isobaric heat input and output.

[0057] 2) Carnot process with approximately isentropic compression and expansion as well as approximately isothermal heat input and output.

[0058] Calculation example:

[0059] - Working medium (gas): Krypton

[0060] - High-temperature heat output at 160°C (usable heat)

[0061] - Low-temperature heat output at 30°C

[0062] - Rotor speed: 5200 rpm

[0063] - Average radius of the NT heat exchanger area: approx. 0.19m

[0064] - Average radius of the MT heat exchanger area: approx. 0.35m

[0065] - Average radius of the high-temperature (HT) heat exchanger section: approx. 0.5 m. The rotational speed is determined by the temperature difference between the HT and LT circuits. The average thermodynamic temperature difference of the heat exchanger between the working fluid and the respective heat transfer media is assumed to be 10 K. The average temperature of the heat absorption is determined by the ratio of the number of loops / turns in the medium / high-temperature circuit (here: heat pump section) to the number of loops / turns in the medium / low-temperature circuit (here: heat engine section). The influence of the ratio of the number of loops / turns in the medium / high-temperature circuit to the medium / low-temperature circuit is shown below:

[0066] That is, the higher the number of loops in the heat engine section relative to the heat pump section, the lower the temperature difference can be in the heat engine section.

[0067] The following shows the influence of the heat exchangers at smaller mean thermodynamic temperature differences:

[0068] The invention further relates to a thermally driven heat pump, comprising a rotor having: an axis of rotation, a number of compression channels, in particular a number of first compression channels and a number of second compression channels, in which a working medium is carried away from the axis of rotation to increase the pressure due to centrifugal acceleration, a number of expansion channels, in particular a number of first expansion channels and a number of second expansion channels, in which the working medium is carried towards the axis of rotation to decrease the pressure due to centrifugal acceleration, a number of working medium heat transfer channels for the working medium, and a number of heat transfer medium heat transfer channels for heat transfer media.so that heat is transferred between the working medium flowing in the working medium heat transfer channels and the respective heat transfer media flowing in the heat transfer medium heat transfer channels, wherein the heat transfer medium heat transfer channels comprise: a number of first heat transfer medium heat transfer channels for a first heat transfer medium, in particular for heat transfer in a low temperature range, a number of second heat transfer medium heat transfer channels for a second heat transfer medium, in particular for heat transfer in a medium temperature range, a number of third heat transfer medium heat transfer channels for a third heat transfer medium, in particular for heat transfer in a high temperature range,wherein preferably the middle temperature range lies between the low temperature range and the high temperature range. This alternative embodiment of the thermally driven heat pump is preferably designed according to one of the embodiments of the thermally driven heat pump described in this disclosure, in particular of the rotor.

[0069] The invention is explained below with reference to preferred embodiments shown in the figures, which, however, are not limiting for the invention.

[0070] Optionally, a fan is provided to drive the flow of the working fluid. The fan can be used to provide additional exergy (or additional pressure increase), particularly if the heat engine process is to be operated outside the design point.

[0071] Fig. 1a schematically shows a partial sectional view of a preferred embodiment of a thermally driven heat pump in a first side view.

[0072] Fig. 1b schematically shows the embodiment of the thermally driven heat pump of Fig. 1 in a view from the opposite direction to Fig. 1a.

[0073] Fig. 1c schematically shows the embodiment of the thermally driven heat pump of Fig. 1 in a side view from a second direction.

[0074] Fig. 1d schematically shows the embodiment of the thermally driven heat pump of Fig. 1 in a side view from a direction opposite to the second direction. Fig. 1le schematically shows the embodiment of the thermally driven heat pump of Fig. 1 in a top view.

[0075] Fig. 2 schematically shows a section of a first preferred embodiment of a rotor plate.

[0076] Fig. 3 shows an exemplary Ts diagram for the execution of Fig. 2.

[0077] Fig. 4 shows an exemplary Ts diagram for a thermally driven heat pump with a second preferred design on rotor plates.

[0078] Fig. 5 shows an exemplary Ts diagram for a thermally driven heat pump with a third preferred design form on rotor plates.

[0079] Fig. 6 shows an exemplary pH diagram for the implementation form of Fig. 5.

[0080] Fig. 7 shows an enlarged section of the pH diagram from Fig. 6.

[0081] Fig. 8 schematically shows a preferred embodiment of a rotor with first and second rotor plates in a partial exploded view.

[0082] Fig. 9 schematically shows a first rotor plate of the rotor of Fig. 8 in more detail.

[0083] Fig. 10 schematically shows a second rotor plate of the rotor of Fig. 8 in more detail.

[0084] Fig. 11 schematically shows the Ts diagram for another preferred embodiment of the thermally driven heat pump type I.

[0085] Fig. 12 schematically shows a partial sectional view of another preferred embodiment of a thermally driven heat pump in an oblique view. Fig. 1a schematically shows a partial sectional view of a preferred embodiment of a thermally driven heat pump 1. Fig. 1b shows this in a view from the opposite direction to Fig. 1a; Fig. 1c in a side view from a second direction; Fig. 1d in a side view from a direction opposite to the second direction; and Fig. 1e in a top view. In this embodiment, the thermally driven heat pump 1 is designed as a type II (heat transformer), i.e., to divide heat at a medium temperature into two heats with high and low temperatures. The thermally driven heat pump 1 has a stationary casing 40 in which a negative pressure can prevail.The housing 40 contains a rotor 4 which is rotatably mounted about an axis of rotation 5 via rotary bearings 41 (not shown in detail). The axis of rotation 5 is preferably horizontal in the operating state. A motor (not shown) is provided to drive the rotation of the rotor 4.

[0086] The thermally driven heat pump 1 comprises a heat engine section 2 and a heat pump section 3. Heat engine section 2 is configured to circulate a working fluid such that the working fluid exchanges heat in a second temperature range T2 and in a first temperature range TI. In this configuration as a type II heat transformer, the first temperature range TI is lower than the second temperature range T2. In the first temperature range TI, the working fluid transfers heat to a heat transfer medium, and in the second temperature range T2, the working fluid absorbs heat from a heat transfer medium, resulting in a pressure increase of the working fluid. For ease of understanding, the respective temperature ranges are indicated at exemplary points where a temperature in the respective temperature range could be present.

[0087] Section 3 of the heat pump is designed to guide the working fluid so that it exchanges heat in a fourth temperature range T4 and in a third temperature range T3. In this configuration as a type II heat transformer, the third temperature range T3 is higher than the fourth temperature range T4, whereby in the third temperature range T3 the working fluid releases heat to a heat transfer medium and in the fourth temperature range T4 the working fluid absorbs heat from a heat transfer medium, resulting in a pressure reduction of the working fluid.

[0088] In this system, the heat engine section 2 and the heat pump section 3 are fluidically connected with respect to the working medium, so that the pressure increase of the working medium in the heat engine section 2 drives the heat pump section 3.

[0089] In this implementation, the second temperature range T2 corresponds to the fourth temperature range T4, i.e., they partially (in particular, largely) overlap. Therefore, the first temperature range TI can also be referred to as the low temperature (or low temperature range), the second temperature range T2 and the fourth temperature range T4 as the medium temperature (or medium temperature range), and the third temperature range T3 as the high temperature (or high temperature range).

[0090] The thermally driven heat pump 1 has a supply line 42a and a discharge line 42b for a first heat transfer medium (low temperature medium), a supply line 43a and a discharge line 43b for a second heat transfer medium (medium temperature medium) and a supply line 44a and a discharge line 44b for a third heat transfer medium (high temperature medium).

[0091] The thermally driven heat pump 1, in particular the rotor 4, has a symbolically represented low-pressure / low-temperature heat exchanger 45a, a symbolically represented medium-pressure / medium-temperature heat exchanger 45b, and a symbolically represented high-pressure / high-temperature heat exchanger 45c. The first heat transfer medium is carried in the low-pressure / low-temperature heat exchanger 45a, so that the first heat transfer medium absorbs heat from the working medium (in the first temperature range TI). The second heat transfer medium is carried in the medium-pressure / medium-temperature heat exchanger 45b, so that the second heat transfer medium transfers heat to the working medium (in the second temperature range T2 or fourth temperature range T4). The third heat transfer medium is carried in the high-pressure / high-temperature heat exchanger 45c, so that the third heat transfer medium absorbs heat from the working medium (in the third temperature range T3).In this embodiment, the low-pressure / low-temperature heat exchanger 45a is therefore part of the heat engine section 2, the high-pressure / high-temperature heat exchanger 45c is part of the heat pump section 3, and the medium-pressure / medium-temperature heat exchanger 45b is (partially) part of the heat engine section 2 and (partially) part of the heat pump section 3.

[0092] The medium-pressure / medium-temperature heat exchanger 45b is designed in two separate parts. In this design, the working medium flows from the part of the medium-pressure / medium-temperature heat exchanger 45b furthest from the axis of rotation 5 to the high-pressure / high-temperature heat exchanger 45c, from there to the part of the medium-pressure / medium-temperature heat exchanger 45b closer to the axis of rotation 5, from there to the low-pressure / low-temperature heat exchanger 45a, and from there again to the part of the medium-pressure / medium-temperature heat exchanger 45b furthest from the axis of rotation 5, thus forming a closed circuit for the working medium.

[0093] Section 2 of the heat engine is configured to effect a pressure change of the working medium from a second pressure range p2 to a first pressure range pl and from the first pressure range pl to a fourth pressure range p4. Section 3 of the heat pump is configured to effect a pressure change of the working medium from the fourth pressure range p4 to a third pressure range p3 and from the third pressure range p3 to a second pressure range p2. The second pressure range p2 and the fourth pressure range p4 are located between the first pressure range pl and the third pressure range p3.

[0094] In this embodiment as a type II heat transformer, the heat engine section 2 is specifically designed to cause a pressure reduction of the working medium from the second pressure range p2 to the first pressure range pl (in particular by directing the working medium away from the axis of rotation 5 to the pressure reduction due to centrifugal acceleration) and a pressure increase from the first pressure range pl to the fourth pressure range p4 (in particular by directing the working medium away from the axis of rotation 5 to the pressure increase due to centrifugal acceleration), and the heat pump section 3 is designed toto cause a pressure increase of the working medium from the fourth pressure range p4 to the third pressure range p3 (in particular by directing the working medium away from the axis of rotation 5 to increase the pressure due to centrifugal acceleration) and a pressure decrease from the third pressure range p3 to the second pressure range p2 (in particular by directing the working medium away from the axis of rotation 5 to increase the pressure due to centrifugal acceleration). When implemented as a heat transformer, the first pressure range p1 is lower than the second pressure range p2, the latter lower than the fourth pressure range p4, and the latter lower than the third pressure range p3. The difference (or mean difference) between the second and fourth pressure ranges p2, p4 corresponds to the pressure increase or pressure decrease in section 2 of the heat engine or section 3 of the heat pump, respectively.

[0095] Four pressure reduction / increase functions are provided on the rotor:

[0096] - belonging to section 2 of the heat engine, a first compression channel 21, in which the working medium is directed away from the axis of rotation 5 to increase the pressure due to centrifugal acceleration, and a first expansion channel 22, in which the working medium is directed towards the axis of rotation 5 to decrease the pressure due to centrifugal acceleration, and

[0097] - belonging to the heat pump section 3, a second compression channel 31, in which the working medium is directed away from the axis of rotation 5 to increase the pressure due to centrifugal acceleration, and a second expansion channel 32, in which the working medium is directed towards the axis of rotation 5 to decrease the pressure due to centrifugal acceleration.

[0098] Furthermore, the rotor 4 has a working medium heat transfer channel 8 for the working medium (in the heat exchangers 45a, 45b, 45c) and a number of heat transfer medium heat transfer channels 9 for heat transfer media (in the heat exchangers 45a, 45b, 45c), so that heat is transferred between the working medium flowing in the working medium heat transfer channel 8 and the heat transfer media flowing in the heat transfer medium heat transfer channels 9.

[0099] Mirrored around the axis of rotation 5, the thermally driven heat pump contains another identically designed heat engine section 2 and heat pump section 3 (these are only partially visible in the partial section view).

[0100] In a preferred embodiment of the thermally driven heat pump 1, the rotor 4 has at least one rotor plate 6, 7, which in particular each extend in principal planes perpendicular to the axis of rotation 5. Particularly preferred is a number of first rotor plates 6 and second rotor plates 7 which are connected to each other along their principal planes.

[0101] Fig. 2 shows a section of a first preferred embodiment of a first rotor plate 6 of a rotor 4. The section shows one quarter / quadrant of the rotor plate 6, wherein the other quarters / quadrants are each mirrored about planes passing through the axis of rotation 5 (cf. Fig. 9). Fig. 3 shows a corresponding Ts diagram for the working medium.

[0102] The rotor plate 6 has a number of first compression channels 21 in which the working medium is directed away from the axis of rotation 5 to increase the pressure due to centrifugal acceleration, a number of first expansion channels 22 in which the working medium is directed towards the axis of rotation 5 to decrease the pressure due to centrifugal acceleration, a number of second compression channels 31 in which the working medium is directed away from the axis of rotation 5 to increase the pressure due to centrifugal acceleration, and a number of second expansion channels 32 in which the working medium is directed towards the axis of rotation 5 to decrease the pressure due to centrifugal acceleration;wherein the heat engine section 2 has a number of first compression channels 21 and a number of first expansion channels 22, and the heat pump section 3 has a number of second compression channels 31 and a number of second expansion channels 32. The first rotor plate 6 also has a number of working medium heat transfer channels 8 for the working medium.

[0103] Specifically, each quarter / quadrant of the first rotor plate 6 has a flow channel 10 with a number of first heat transfer flow channel sections 8a, preferably extending substantially circumferentially 11, for forming the first of the working medium heat transfer channels 8 for heat transfer in the first temperature range TI, with a number of second heat transfer flow channel sections 8b, preferably extending substantially circumferentially 11, for forming the second of the working medium heat transfer channels 8 for heat transfer in the second temperature range T2, with a number of third heat transfer flow channel sections 8c, preferably extending substantially circumferentially 11, for forming the third of the working medium heat transfer channels 8 for heat transfer in the third temperature range T3.and with a number of fourth heat transfer flow channel sections 8d, preferably extending substantially in the circumferential direction 11, to form the fourth of the working medium heat transfer channels 8 for heat transfer in the fourth temperature range T4. The second heat transfer flow channel sections 8b and the fourth heat transfer flow channel sections 8d are arranged in the radial direction 12 between the first heat transfer flow channel sections 8a and the third heat transfer flow channel sections 8c.

[0104] The arrangement of the channels 8 in the circumferential direction at constant radius, as shown in Fig. 8, results in a substantially isobaric heat transfer.

[0105] The second rotor plates 7 (not shown in this embodiment, but see Fig. 10 for another embodiment of the second rotor plates 7) have a number of heat transfer channels 9 for heat transfer media, so that heat is transferred between the working medium flowing in the working medium heat transfer channels 8 and the heat transfer medium flowing in the heat transfer channels 9. Specifically, the number of heat transfer channels 9 comprises: a number of first heat transfer channels 9a, so that heat is transferred between the working medium flowing in the first heat transfer channel sections 8a and the heat transfer medium flowing in the first heat transfer channels 9a; and a number of second heat transfer channels 9b.so that heat is transferred between the working medium flowing in the second heat transfer channel sections 8b and in the fourth heat transfer channel sections 8d and the heat transfer medium flowing in the second heat transfer medium heat transfer channels 9b, and a number of third heat transfer medium heat transfer channels 9c, so that heat is transferred between the working medium flowing in the third heat transfer channel sections 8c and the heat transfer medium flowing in the third heat transfer medium heat transfer channels 9c. The first rotor plates 6 have eight passage openings 18 per quarter / quadrant for the three heat transfer medium flows.

[0106] The flow channel further comprises: a number of preferably substantially radially outwardly extending first compression flow channel sections 21a for forming the first compression channels 21, a number of preferably substantially radially inwardly extending first expansion flow channel sections 22a for forming the first expansion channels 22, a number of preferably substantially radially outwardly extending second compression flow channel sections 31a for forming the second compression channels 31, and a number of preferably substantially radially inwardly extending second expansion flow channel sections 32a for forming the second expansion channels 32.

[0107] The number of first, second, third and fourth heat transfer flow channel sections 8a, 8b, 8c, 8d, the number of first and second compression flow channel sections 21, 31 and the number of first and second expansion flow channel sections 22, 32 of each flow channel 10 is one in this embodiment.

[0108] The number of first compression flow channel sections 21a, the number of first expansion flow channel sections 22a, the number of first heat transfer flow channel sections 8a, and the number of second heat transfer flow channel sections 8b of each flow channel 10 form a number of loops 23 of the heat engine section 2, closed except for one inlet and one outlet. The number of second compression flow channel sections 31a, the number of second expansion flow channel sections 32a, the number of third heat transfer flow channel sections 8c, and the number of fourth heat transfer flow channel sections 8d form a number of loops 33 of the heat pump section 3, closed except for one inlet and one outlet.The number of loops 23 of the heat engine section 2 and the number of loops 33 of the heat pump section 3 of each flow channel 10 is one in this embodiment.

[0109] In this embodiment, the flow channel 10 transitions directly from the heat engine section 2 to the heat pump section 3. In other words, the flow channel 10 has a connecting flow channel section 13 that connects the outlet of the heat engine section 2 with the inlet of the heat pump section 3.

[0110] The flow channel 10 has an inlet opening 15 at one end and an outlet opening 16 at the other. The second rotor plates 7 (not shown in this embodiment) have a connecting flow channel 14 that connects the outlet opening 16 and the inlet opening 15, and thus the outlet of the heat pump section 3 with the inlet of the heat engine section 2. The working fluid is therefore circulated in a closed loop.

[0111] The Ts diagram in Fig. 3 shows exemplary pressure, temperature, and entropy values. The temperature profile of the three heat transfer media is shown as dashed lines. The working fluid cycle is as follows: A substantially isobaric heat transfer occurs (in the Ts diagram: l->2) (in the third temperature range T3) in the third heat transfer flow channel section 8c. Then, a substantially isentropic expansion (in the Ts diagram: 2->3) takes place from the third pressure range p3 to the second pressure range p2 in the second expansion flow channel section 32a. Via the connecting flow channel 14 on the second rotor plate 7 (not shown), the working fluid is guided substantially from the end of the heat pump section 3 to the heat engine section 2. Then, an essentially isobaric heat absorption takes place (in the Ts diagram: 3->4 ) (in the second temperature range T2 ) in the second heat transfer flow channel section 8b .Then, an essentially isentropic expansion (in the Ts diagram: 4->5) occurs from the second pressure range p2 to the first pressure range pl in the first expansion flow channel section 22a. Then, an essentially isobaric heat transfer (in the Ts diagram: 5->6) (in the third temperature range T3) occurs in the third heat transfer flow channel section 8a. Then, an essentially isentropic compression (in the Ts diagram: 6->7) occurs from the first pressure range pl to the fourth pressure range p4 in the first compression flow channel section 21a. The working fluid is conveyed from the end of the heat engine section 2 to the heat pump section 3 via the connecting flow channel section 13. In this embodiment, the two sections 2, 3 connect directly to each other, so that the connecting flow channel section 13 can be considered as part of the first compression flow channel section 21a and / or the fourth heat transfer flow channel section 8d.Then, an essentially isobaric heat absorption (in the Ts diagram: 7->8) (in the fourth temperature range T4) takes place in the fourth heat transfer flow channel section 8d. Then, an essentially isentropic compression (in the Ts diagram: 8->l) takes place from the fourth pressure range p4 to the third pressure range p3 in the second compression flow channel section 31a.

[0112] As can be seen from the Ts diagram, the second and fourth temperature ranges T2 and T4 largely overlap. On the other hand, the heat engine section 2 causes a pressure increase (in this example by approximately 3 bar, namely from 147 bar to 150 bar), which drives the pressure reduction in the heat pump section 3.

[0113] With the low-temperature heat transfer medium, the temperature is (for example) increased from 21°C to 30°C (first temperature range TI), with the medium-temperature heat transfer medium it is cooled from 94°C to 84°C (second and fourth temperature ranges T2, T4), and with the high-temperature heat transfer medium it is increased from 150°C to 160°C (third temperature range).

[0114] With a 1:1 ratio, the number of loops / circuits in heat pump section 3 (i.e., medium / high temperature) and the number of loops / circuits in heat engine section 2 (medium / low temperature) are equal. It follows that the same amount of heat is transferred from the medium temperature level to the high temperature level as is transferred from the medium temperature level to the low temperature level. Therefore, the medium temperature requires twice the heat output provided by heat pump section 3 at the high temperature level and by heat engine section 2 at the low temperature level. For example:

[0115] - High-temperature heat output: 700 kW

[0116] - Average heat input: 1400 kW

[0117] - Low-temperature heat output: 700 kW

[0118] Fig. 4 shows an exemplary Ts diagram of another embodiment of the thermally driven heat pump 1 with a second preferred embodiment of the rotor plates 6, 7. In this embodiment, the heat engine section 2, unlike the embodiment of Figs. 2 and 3, has two loops 23 of the heat engine section 2 (and furthermore a loop 33 of the heat pump section 3). This allows the mean temperature level (second temperature range T2 and fourth temperature range T4) to be lowered compared to the embodiment of Figs. 2 and 3, while the low and high temperature levels remain essentially unchanged. Thus, waste heat at lower temperatures can already be utilized.

[0119] With this 1:2 ratio of loops 33 of the heat pump section 3 to the heat engine section 2, twice the heat output is transferred from the medium temperature level to the low temperature level as is transferred from the medium temperature level to the high temperature level. For example:

[0120] - High-temperature heat output: 700 kW

[0121] - Average heat input: 2100 kW

[0122] - Low-temperature heat output: 1400 kW

[0123] Fig. 5 shows an exemplary Ts diagram of the working medium of another embodiment of the thermally driven heat pump 1 with a third preferred embodiment of the rotor plates 6, 7. In this embodiment, the heat engine section 2 differs from the

[0124] In the embodiment shown in Figures 2 and 3, four loops 23 of the heat engine section 2 (and furthermore one loop 33 of the heat pump section 3) are provided. This allows the average temperature level (second temperature range T2 and fourth temperature range T4) to be further reduced compared to the embodiment shown in Figures 2 and 3 and the embodiment shown in Figure 4, while the low and high temperature levels remain essentially unchanged.

[0125] Fig. 6 shows an exemplary pH diagram of the working medium for the embodiment of Fig. 5. Fig. 7 shows an enlarged section of the pH diagram of Fig. 6. The heat engine section 2 achieves an overall pressure increase from the level of line 3-4 to the level of line 19-20, and in the heat pump section 3, a reverse pressure decrease occurs.

[0126] With a ratio of 1:4 between the loops 33 of the heat pump section 3 and the loops 23 of the heat engine section 2, four times the heat output is transferred from the medium temperature level to the low temperature level as is transferred from the medium temperature level to the high temperature level. For example:

[0127] - High-temperature heat output: 700 kW

[0128] - Average heat input: 3500 kW

[0129] - Low-temperature heat output: 2800 kW

[0130] Ratios with non-integer numbers are also possible, for example, 30 circuits MT / HT with 50 circuits MT / NT. The ratio 1:1.66 of the 33 loops of heat pump section 3 to the 23 loops of the heat engine section 2 then lies accordingly between 1:1 and 1:2.

[0131] The ratio can also be 2:1 of the loops 33 of the heat pump section 3 to the loops 23 of the heat engine section 2 (i.e. greater than 1) and shifts the average temperature closer to the high temperature and thus also the heat outputs, e.g.:

[0132] - High-temperature heat output: 700 kW - Medium-temperature heat input: 1050 kW

[0133] - Low-temperature heat output: 350 kW

[0134] Fig. 8 schematically shows a preferred embodiment of a rotor 4 with first rotor plates 6 and second rotor plates 7 in a partial exploded view. Fig. 9 schematically shows one of the first rotor plates 6 in more detail. Fig. 10 schematically shows one of the second rotor plates 7 in more detail. Such a rotor 4 could, for example, be used in the thermally driven heat pump 1 of Fig. 1.

[0135] The first rotor plates 6 and the second rotor plates 7 are arranged alternately, with adjacent rotor plates 6, 7 being connected to each other along their main extension planes.

[0136] The following describes the construction of individual rotor plates 6, 7, whereby the other rotor plates of the first and second rotor plates 6, 7 are constructed in the same way.

[0137] As can best be seen in Fig. 9, the first rotor plate 6 has at least one of the first compression channels 21, at least one of the first expansion channels 22, at least one of the second compression channels 31, at least one of the second expansion channels 32, and at least one of the working medium heat transfer channels 8. In particular, the first rotor plate 6 has a flow channel 10 in each quadrant, each flow channel 10 having: a number of substantially circumferentially extending first heat transfer flow channel sections 8a for forming the first of the working medium heat transfer channels 8 for heat transfer in the first temperature range TI; a number of substantially circumferentially extending second heat transfer flow channel sections 8b for forming the second of the working medium heat transfer channels 8 for heat transfer in the second temperature range T2.a third heat transfer flow channel section 8c extending substantially in the circumferential direction 11 for forming a third of the working medium heat transfer channels 8 for heat transfer in the third temperature range T3, and a fourth heat transfer flow channel section 8d extending substantially in the circumferential direction 11 for forming a fourth of the working medium heat transfer channels 8 for heat transfer in the fourth temperature range T4, a number of first compression flow channel sections 21a extending substantially radially outwards for forming the first compression channels 21, a number of first expansion flow channel sections 22a extending substantially radially inwards for forming the first expansion channels 22, a second compression flow channel section 31a extending substantially radially outwards for forming the second compression channels 31,and a radially inwardly extending second relaxation flow channel section 32a for the formation of the second relaxation channels 32 .,

[0138] The number of first compression flow channel sections 21a, the number of first expansion flow channel sections 22a, the number of first heat transfer flow channel sections 8a, and the number of second heat transfer flow channel sections 8b form a number of loops 23 of the heat engine section 2, closed except for one inlet and one outlet. In this embodiment, four loops 23 of the heat engine section 2 are formed. The second compression flow channel section 31a, the second expansion flow channel section 32a, the third heat transfer flow channel section 8c, and the fourth heat transfer flow channel section 8d form a loop 33 of the heat pump section 3, closed except for one inlet and one outlet. The ratio is therefore 4 : 1 of the loops 23 of the heat engine section 2 to the loops 33 of the heat pump section 3.Thus, for example, the Ts diagram and pH diagram of Figures 5 to 7 can illustrate the process in this embodiment. To connect the heat engine section 2 and the heat pump section 3, the flow channel 10 has, on the one hand, a connecting flow channel section 13, which connects the outlet of the heat engine section 2 with the inlet of the heat pump section 3. On the other hand, the flow channel 10 has an inlet opening 15 at a first end and an outlet opening 16 at a second end, each of which forms a connection to an adjacent second rotor plate 7. The second rotor plates 7 (see Fig. 10) have a connecting flow channel 14 that connects the outlet opening 16 and the inlet opening 15, and thus the outlet of the heat pump section 3 with the inlet of the heat engine section 2. The working fluid is therefore circulated in a closed loop.

[0139] As can best be seen in Fig. 10, the second rotor plate 7 has a number of heat transfer channels 9. Specifically, the second rotor plate 7 has the following number of heat transfer channels 9 per quadrant: a number of first heat transfer channels 9

[0140] heat transfer channels 9a, such that heat is transferred between the working medium flowing in the first heat transfer channel sections 8a and the first heat transfer medium flowing in the first heat transfer medium heat transfer channels 9a, a number of second heat transfer medium heat transfer channels 9b, such that heat is transferred between the working medium flowing in the second heat transfer channel sections 8b and in the fourth heat transfer channel sections 8d and the second heat transfer medium flowing in the second heat transfer medium heat transfer channels 9b, and a third heat transfer medium heat transfer channel 9c, such that heat is transferred between the working medium flowing in the third heat transfer channel section 8c and the heat transfer medium flowing in the third heat transfer medium heat transfer channel 9c.The first rotor plate 6 has through-openings 18 to guide the three heat transfer fluid flows to the corresponding heat transfer fluid channels 9a, 9b, 9c. The through-openings 18 for the heat transfer fluid flows are each aligned, i.e., arranged in a line parallel to the axis of rotation 5, and are each congruent when viewed in the direction parallel to the axis of rotation 5. Thus, the heat transfer fluids can be supplied to the second rotor plates 7 and distributed to the second rotor plates 7 via inlet openings 19a, 19b, 19c of the heat transfer fluid channels 9a, 9b, 9c, passing through the through-openings 18 of the first rotor plates 6 arranged between them.The heat transfer media are discharged from the second rotor plates 7 via the outlet openings 20a, 20b, 20c of the heat transfer channels 9a, 9b, 9c and discharged from the rotor 4 via the through-openings 18 of the first rotor plates 6 and via the outlet openings 20a, 20b, 20c of the second rotor plates 7 located downstream. The inlet openings 19a, 19b, 19c and the outlet openings 20a, 20b, 20c are aligned with the corresponding through-openings 18.

[0141] In all embodiments, it is preferred if the working medium is gaseous and, in particular, remains in a gaseous state throughout the entire process.

[0142] Fig. 11 schematically shows the Ts diagram of the working medium for another preferred embodiment of the thermally driven heat pump 1. In this embodiment, the thermally driven heat pump 1 is type I (functionally comparable to an absorption heat pump type I). In contrast to Fig. 3, here the upper loop represents the heat engine section 2 and the lower loop the heat pump section 3. Thus, T1 represents the high temperature range and T3 the low temperature range. The Ts diagram is traversed in reverse order (compared to Fig. 3) (i.e., l->8->7->6->5->4->3->2->!).

[0143] Here, unlike in a Type II heat transformer, the exergy required to drive a heat pump cycle is not generated by heat flow from a medium temperature to a low temperature, but rather from a high temperature to a medium temperature, in order to then drive a heat pump cycle from a low temperature to a medium temperature. The process is qualitatively the same as in a Type II heat transformer, but it proceeds in the opposite direction, and the heat transfer fluid temperatures switch to the opposite side of the Ts diagram to reverse the heat transfer. That is, the working fluid absorbs heat at the first temperature T1 and the third temperature T3, and releases heat at the second temperature T2 and the fourth temperature T4.

[0144] Specifically, the process regarding the working medium proceeds as follows in this form of execution:

[0145] • l->8 essentially isentropic expansion (from the first pressure region pl to the fourth pressure region p4 )

[0146] • 8->7 essentially isobaric heat transfer to a heat transfer medium of medium temperature (in the fourth temperature range T4)

[0147] • 7->6 essentially isentropic expansion (from the fourth pressure range p4 to the third pressure range p3 )

[0148] • 6->5 essentially isobaric heat absorption from a low-temperature heat transfer medium (in the third temperature range T3)

[0149] • 5->4 essentially isentropic compression (from the third pressure range p3 to the second pressure range p2)

[0150] • 4->3 essentially isobaric heat transfer to a heat transfer medium of medium temperature (in the second temperature range T2)

[0151] • 3->2 essentially isentropic compression (from the second pressure range p2 to the first pressure range pl )

[0152] • 2->l essentially isobaric heat absorption from a high-temperature heat transfer medium (in the first temperature range TI)

[0153] The pressure increase in heat engine section 2 (difference p4-p2) thus drives heat pump section 3, which causes a pressure decrease. In this configuration, the same number of loops 23 of heat engine section 2 and loops 33 of heat pump section 3 are provided. To shift the mean temperature, the process can again be repeated multiple times between the mean temperature and high temperature to raise the mean temperature to a higher level. The same analogy applies as with the type II heat transformer.

[0154] The rotor 4, in particular the first and second rotor plates 6, 7, can be designed identically, as described, for example, in connection with Fig. 2. The low-, medium-, and high-temperature heat exchangers are then fundamentally located at the same position on the rotor 4 (high temperature on the outside, medium temperature in the middle, and low temperature in the center). Only the heat flow directions of each heat exchanger section for all four temperature ranges or three temperature levels are reversed when switching from TYPE II to TYPE I. This means, for example, that in the high-temperature heat exchanger in the TYPE II design, heat is transferred from the working medium to a heat transfer medium, while in the TYPE I design, heat is transferred from a high-temperature heat transfer medium to the working gas.

[0155] Fig. 12 schematically shows a partial sectional view of another preferred embodiment of a thermally driven heat pump 1 in an oblique view. A rotor 4 is again provided in the stationary housing 40. The rotor 4 has a plurality of first and second rotor plates 6, 7, which are arranged alternately (and are shown together as a block). These can be designed, for example, as shown in Figs. 8 to 10.

Claims

44 Claims:

1. Thermally driven heat pump (1) , in particular comprising a heat transformer of type I or type II, comprising: - a heat engine section (2) which is configured to carry a working medium such that the working medium exchanges heat in a second temperature range (T2) and in a first temperature range (TI), wherein in the lower of the first temperature range (TI) and the second temperature range (T2) the working medium releases heat and in the higher of the first temperature range (TI) and the second temperature range (T2) the working medium absorbs heat, so that a pressure increase occurs, and - a heat pump section (3) which is configured to guide the working medium such that the working medium exchanges heat in a fourth temperature range (T4) and exchanges heat in a third temperature range (T3), wherein in the higher of the fourth temperature range (T4) and the third temperature range (T3) the working medium releases heat and in the lower of the fourth temperature range (T4) and the third temperature range (T3) the working medium absorbs heat, such that a pressure reduction of the working medium occurs, wherein the heat engine section (2) and the heat pump section (3) are fluidically connected to each other with respect to the working medium, such that the pressure increase of the working medium in the heat engine section (2) drives the heat pump section (3).

2. Thermally driven heat pump (1) according to claim 1, wherein the second temperature range (T2) corresponds to the fourth temperature range (T4).

3. Thermally driven heat pump (1) according to one of the preceding claims, wherein the heat engine section (2) is configured to effect a pressure change of the working medium from a second pressure range (p2) to a first pressure range (pl) and from the first pressure range (pl) to a fourth pressure range (p4), wherein the heat pump section (3) is configured to 45 to effect a pressure change of the working medium from the fourth pressure area (p4) to a third pressure area (p3) and from the third pressure area (p3) to a second pressure area (p2); wherein the second pressure area (p2) and the fourth pressure area (p4) are located between the first pressure area (pl) and the third pressure area (p3).

4. Thermally driven heat pump (1) according to one of the preceding claims, comprising a rotor (4) comprising: a rotational axis (5), a number of first compression channels (21) in which the working medium is directed away from the rotational axis (5) to increase the pressure due to centrifugal acceleration, a number of first expansion channels (22) in which the working medium is directed towards the rotational axis (5) to decrease the pressure due to centrifugal acceleration, a number of second compression channels (31) in which the working medium is directed away from the rotational axis (5) to increase the pressure due to centrifugal acceleration, a number of second expansion channels (32) in which the working medium is directed towards the rotational axis (5) to decrease the pressure due to centrifugal acceleration;wherein the heat engine section (2) has the number of first compression channels (21) and the number of first expansion channels (22) and the heat pump section (3) has the number of second compression channels (31) and the number of second expansion channels (32).

5. Thermally driven heat pump (1) according to claim 4, wherein the rotor (4) comprises: a number of first rotor plates (6) and second rotor plates (7) comprising the first compression channels (21), the first expansion channels (22), the second compression channels (31) and the second expansion channels (32), wherein the first and the second rotor plates (6, 7) are arranged along 46 of their main extension planes are interconnected.

6. Thermally driven heat pump (1) according to one of claims 4 or 5, wherein the rotor (4) , in particular the first and second rotor plates (6, 7) , comprises: a number of working medium heat transfer channels (8) for the working medium and a number of heat transfer medium heat transfer channels (9) for at least one heat transfer medium, in particular a liquid, such that heat is transferred between the working medium flowing in the working medium heat transfer channels (8) and the heat transfer medium flowing in the heat transfer medium heat transfer channels (9).

7. Thermally driven heat pump (1) according to claim 5 and claim 6, wherein the number of first rotor plates (6) each has at least one of the first compression channels (21), at least one of the first expansion channels (22), at least one of the second compression channels (31), at least one of the second expansion channels (32), and at least one of the working medium heat transfer channels (8), and the number of second rotor plates (7) each has at least one of the heat transfer medium heat transfer channels (9).

8. Thermally driven heat pump (1) according to one of claims 4 to 7, wherein the rotor (4), in particular the first rotor plates (7), each has at least one flow channel (10) with a number of first heat transfer flow channel sections (8a) extending preferably substantially circumferentially (11) for forming first of the working medium heat transfer channels (8) for heat transfer in the first temperature range (11), with a number of second heat transfer flow channel sections (8b) extending preferably substantially circumferentially (11) for forming second of the working medium heat transfer channels (8) for heat transfer in the second temperature range (12), with a number of preferably substantially in circumferentially extending third heat transfer flow channel sections (8c) for forming third of the working medium heat transfer channels (8) for heat transfer in the third temperature range (T3), and with a number of preferably substantially circumferentially extending fourth heat transfer flow channel sections (8d) for forming fourth of the working medium heat transfer channels (8) for heat transfer in the fourth temperature range (T4).

9. Thermally driven heat pump (1) according to claim 6 and claim 8, wherein the number of heat transfer medium heat transfer channels (9) comprises: a number of first heat transfer medium heat transfer channels (9a) such that heat is transferred between the working medium flowing in the first heat transfer channel sections (8a) and the heat transfer medium flowing in the first heat transfer medium heat transfer channels (9a); a number of second heat transfer medium heat transfer channels (9b) such that heat is transferred between the working medium flowing in the second heat transfer channel sections (8b) and in the fourth heat transfer channel sections (8d) and the heat transfer medium flowing in the second heat transfer medium heat transfer channels (9b); a number of third heat transfer medium heat transfer channels (9c).so that heat is transferred between the working medium flowing in the third heat transfer channel sections (8c) and the heat transfer medium flowing in the third heat transfer medium heat transfer channels (9c).

10. Thermally driven heat pump (1) according to one of claims 8 or 9, wherein the second heat transfer flow channel sections (8b) and the fourth heat transfer flow channel sections (8d) are arranged radially (12) between the first heat transfer flow channel sections (8a) and the third heat transfer flow channel sections (8c) are arranged .

11. Thermally driven heat pump according to one of claims 8 to 10, wherein the at least one flow channel (10) further comprises: a number of preferably substantially radially outwardly extending first compression flow channel sections (21a) for forming the first compression channels (21), a number of preferably substantially radially inwardly extending first expansion flow channel sections (22a) for forming the first expansion channels (22), a number of preferably substantially radially outwardly extending second compression flow channel sections (31a) for forming the second compression channels (31), and a number of preferably substantially radially inwardly extending second expansion flow channel sections (32a) for forming the second expansion channels (32).

12. Thermally driven heat pump (1) according to claim 11, wherein the number of first compression flow channel sections (21a), the number of first expansion flow channel sections (22a), the number of first heat transfer flow channel sections (8a) and the number of second heat transfer flow channel sections (8b) form a number of loops (23) of the heat pump section (2) closed except for one inlet and one outlet, and the number of second compression flow channel sections (31a), the number of second expansion flow channel sections (32a), the number of third heat transfer flow channel sections (8c) and the number of fourth heat transfer flow channel sections (8d) form a number of loops (33) of the heat pump section (3) closed except for one inlet and one outlet. . 49 13. Thermally driven heat pump (1) according to claim 12, wherein the at least one flow channel (10) has a connecting flow channel section (13) that connects the outlet of the heat engine section (2) to the inlet of the heat pump section (3) or the outlet of the heat pump section (3) to the inlet of the heat engine section (2).

14. Thermally driven heat pump (1) according to one of claims 12 or 13, wherein the second rotor plates (7) have at least one connecting flow channel (14) that connects the outlet of the heat engine section (2) to the inlet of the heat pump section (3) or the outlet of the heat pump section (3) to the inlet of the heat engine section (2) connects.

15. Thermally driven heat pump (1) according to any one of claims 12 to 14, wherein the number of loops (33) of the heat pump section (3) and / or the number of loops (23) of the heat engine section is at least two.

16. Thermally driven heat pump (1) according to one of claims 12 to 15, wherein the number of loops (33) of the heat pump section (3) is different from the number of loops (23) of the heat engine section (2) .

17. Thermally driven heat pumping method comprising the steps: - Guiding a working medium in a heat engine section (2) , wherein the working medium exchanges heat in a second temperature range (T2) and exchanges heat in a first temperature range (TI), wherein in the lower of the first temperature range (TI) and the second temperature range (T2) the working medium releases heat and in the higher of the first temperature range (TI) and the second temperature range (T2) the working medium absorbs heat, so that a pressure increase occurs, - Guiding the working medium in a heat pump section (3) , wherein the working medium exchanges heat in a fourth temperature range (T4) and in a third temperature range 50 (T3) exchanges heat, whereby in the higher of the fourth (T4) temperature range and the third temperature range (T3) the working medium releases heat and in the lower of the fourth temperature range (T4) and the third temperature range (T3) the working medium absorbs heat, so that a pressure reduction of the working medium occurs, - Guiding the working medium from the heat engine section (2) to the heat pump section (3) so that the pressure increase of the working medium in the heat engine section (2) drives the heat pump section (3).

18. Method according to claim 17, wherein the working medium is guided in a thermally driven heat pump (1) according to any one of claims 1 to 16.

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