Patent Application
20070234719
1. Field of the Invention
The present invention relates to an improved arrangement of heat exchanging portions of devices using regenerative gas cycle (e.g. Stirling cycle, Ericsson cycle, Vuilleumier cycle, Gifford McMahon cycle, Sibling cycle and similar) such as cryocoolers, heat engines, refrigerators and pumps. More particularly, the customary used regenerator is replaced by counterflow heat exchanger; heat machine is coupled with the heat accumulator or heat machine is coupled with another heat machine, operating in regenerative antiphase, by the said counterflow heat exchanger into one highly efficient device.
2. Description of the Related Art
The present discussion will be primarily directed to heat machines operating on a regenerative thermodynamic cycle with cyclic compression and expansion of the working fluid at different temperature levels using repeated heating and cooling of a sealed amount of working gas, usually air or other gases such as hydrogen or helium. Physical correlations between empirical parameters such as pressure, volume and temperature, instantiated by the statistical mechanics, dictates gas flow within the system, thereby converting gas volume changes and heat energy into mechanical work or vice versa. In principle, gas pressure rises when heated, delivering mechanical energy to the piston to produce a power stroke. Gas pressure is then drops when cooled, thereby decreasing recompression energy needed in the return stroke, and giving a net gain in power available on the shaft.
The total net of mechanical work gained by the thermodynamic process, is due to the difference in pressure between compressed hot gas and decompressed cold gas multiplied by the chamber volume. A “cycle efficiency” η, can then be defined as the proportion between total net work gained Qeff divided by the total thermal energy invested Qin.
η=Qeff/Qin
According to the “Carnot theorem” this efficiency ηis equal to the proportion between difference between the highest Thigh and lowest Tlow temperatures in the system divided by the highest Thigh temperature, thereby defining a “theoretical efficiency” boundary that can not be broken.
η=(Thigh−Tlow)/Thigh
It follows, that the cycle must contain methods of heating and cooling the gas within one cycle. The highest gas temperature within the cycle is gained by an external heat source while the lowest one is determined by the reservoir temperature. It follows that Qloss can be determined by subtracting Qin with Qeff.
Qloss=Qin−Qeff (
Dissipation of waste heat is especially complicated because the coolant temperature is kept as low as possible to maximize thermal efficiency. This drives up the size of the radiators markedly which can make packaging difficult.
A known problem, common to all mentioned above heat devices, is finding efficient methods for reducing the amount of energy lost to the reservoir (Qloss). The problem was partly solved by the installation of a heat capacitor, commonly referred to as a “regenerator”. The process of which the regenerator is involved, allows a partial consumption of energy loss, by returning it back to the cycle as Qin. The other part, Qwaste is irreversibly lost to the reservoirs (
Referring to
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The present invention is directed at addressing the above-mentioned problems of the prior art. The object of this invention is to improve the performance of the said heat machines using regenerative gas cycle (e.g. Stirling cycle, Ericsson cycle, Vuilleumier cycle, Gifford McMahon cycle, Sibling cycle and similar).
In accordance with the present invention the energy conversion device includes at least two displacer units, at least one counterflow heat exchanger, at least one work machine, a controlling device and connecting conduits. Each displacer unit has an internal chamber with displacer elements dividing the chamber into enclosed zones: hot zone and cold zone, operating mechanism for moving displacers, actuating medium which can be gas or liquid. An actuating medium is able to flow back and forth between the two enclosed zones through the connecting counterflow hat exchanger and conduits. The said hot and cold zones may have internal and external heat exchanging surfaces of different types, such as flat surface, fins. The counterflow heat exchanger is comprised of two identical heat exchanging channels that enable countercurrent gas flow, and separation wall that physically isolates channels but, at the same time, enables heat exchange between countercurrent flowing of fluid and heat carrier within these channels. Each channel of the said counterflow heat exchanger is connected by conduits with each displacer unit. Displacing elements can be, for example, a piston-displacer, a fan of any type, a pump of any type or any other device capable of displacing the actuating medium. The motion of the displacing elements is performed by operating mechanism (external drive) actuated by the controlling device. The controlling device can be kinematical mechanism of different construction or process managing unit with drives and actuating devices (mechanical, electrical, hydraulic or pneumatic etc.). Additional valves and conduits can be introduced for the improving device regenerative cycle and redirecting the flow of actuating mediums. The work machine has at least one input/output for receiving or transmitting pressure variations of actuating medium. When the present invention is implemented as a heat engine configuration at least one heat source should be added and at least one work machine should be equipped with at least one input, capable of receiving and converting pressure variations into effective work. When the present invention is implemented as a heat pump configuration the work machine should be capable of generating pressure variations and be equipped with at least one output, enabling the transmission of said pressure variations.
One embodiment discloses a an energy conversion device providing a method of preserving and regenerating heat energy. A first displacing unit is connected to a heat source on one end and on the other end connected to a reservoir, said unit has an actuating medium, which flows back and forth between two enclosed zones. This actuating medium will be referred further on as fluid (e.g. hydrogen, helium, nitrogen, air). Equivalently the second displacing unit functions as a heat accumulator. The actuating medium which flows back and forth between heat accumulator's enclosed zones will be referred to as heat carrier (e.g. gas or liquid). The first displacing unit has the internal and external heat exchanging surfaces. The heat accumulating device may be constructed in the same way as a first displacer unit, but with no external dissipation or utilization of thermal energy. According to this embodiment, the displacer is thermally coupled to a heat accumulating device (heat accumulator) through the counterflow heat exchanger, wherein the displacing unit and the heat accumulator cycles have opposite heat regenerative phases.
The heat energy exchange is performed in the counterflow heat exchanger between fluid and heat carrier during concurrent and countercurrent flow of the said actuating mediums.
A combination of several displacer units with a heat accumulating device is also possible. Such combination is enabled on condition that the proper operation of the each heat exchanger, coupling two displacing units-each displacer unit and the heat accumulator, is preserved. The process should be particularly implemented with the optimized amount of heat transferring in both channels of a heat exchanger and recuperating with minimal losses.
The method of storing and regenerating of heat energy is implemented within an energy conversion device comprising of displacer unit thermally coupled through the counterflow heat exchanger with heat accumulator. The flow of said heat carrier is synchronized with the flow of said fluid; both mediums are forced to flow concurrently through the thermally coupled channels of counterflow heat exchanger.
The configuration of the current embodiment of energy conversion device demands the assembly of at least one heat source; the equipping of work machine with at least one input capable of receiving pressure variations generated by the displacer unit. This way, the regenerative cycle of the energy conversion device operating as a heat engine can be characterized by the following successive main phases:
At the first phase of the cycle the fluid is enclosed in the hot zone of the displacer unit, is being expanded, thereby high pressure is being received at the work machine input and is being converted into the net work. Simultaneously the heat carrier is enclosed in the cold zone of the heat accumulator, preserving low thermal energy for the determined time interval.
At the next phase the fluid is moving to the cold zone through the heat exchanger, part of the fluid heat energy is transferred to the heat carrier, which moves in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the temperature of the fluid flowing into the cold zone is almost at the temperature of the stored heat carrier at the previous phase. Synchronously the heat carrier is being moved to the hot zone through the heat exchanger, the heat energy of the fluid is being absorbed by the heat carrier, which is being moved in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the temperature of the heat carrier flowing into its hot zone is almost at the temperature of the previously fluid coming from its hot zone.
At the next phase of the cycle the fluid is enclosed in the cold zone of the displacer unit is being cooled and compressed, thereby low pressure is being received at the work machine input. Simultaneously the heat carrier is enclosed in the hot zone of the heat accumulator, preserving high thermal energy for the determined time interval
At the next phase the fluid is moving to its hot zone through the heat exchanger absorbing the preserved high thermal energy (of previously phase) from the heat carrier which is being moved in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the temperature of the fluid flowing into its hot zone is almost at the temperature of the stored heat carrier of the previous stage. Synchronously the heat carrier is being moved to its cold zone through the heat exchanger, wherein the heat energy is transferred to the fluid, which is being moved in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the temperature of the heat carrier flowing into its cold zone is almost at the temperature of the fluid in its cold zone in the previous phase.
The configuration of the current embodiment of energy conversion device demands the assembly of the work machine equipped with at least one output, capable of transmitting pressure variations generated by the said work machine. This way, the regenerative cycle of the energy conversion device operating as a heat pump, can be characterized by the following successive main phases:
At the first phase of the cycle the fluid enclosed in the hot zone of the displacer unit, is being compressed as result of the high pressure transmitted from the output of the work machine, thereby said fluid is heated and the heat energy is delivered to the hot zone of the heat exchanger surface of the displacer unit. Simultaneously the heat carrier is enclosed in the cold zone of the heat accumulator, preserving low thermal energy for the determined time interval.
At the next phase the fluid is moving to the cold zone through the heat exchanger, part of the fluid heat energy is transferred to the heat carrier, which moves in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the temperature of the fluid flowing into its cold zone is almost at the temperature of the stored heat carrier at the previous phase. Synchronously the heat carrier is being moved to the hot zone through the heat exchanger, the heat energy of the fluid is being absorbed by the heat carrier, which is being moved in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the temperature of the heat carrier flowing into its hot zone is almost at the temperature of the previously fluid coming from its hot zone.
At the next phase of the cycle the fluid enclosed in the cold zone of the displacer unit, is being expanded as result of the low pressure transmitted from the outlet of the work machine, thereby said fluid is being cooled and absorbing heat energy from the heat exchanger surface of the cold zone. Simultaneously the heat carrier is enclosed in the hot zone of the heat accumulator preserving high thermal energy for the determined time interval.
At the next phase the fluid is moving to the hot zone through the heat exchanger absorbing the preserved high thermal energy (of previously phase) from the heat carrier which is being moved in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the temperature of the fluid flowing into the hot zone is almost at the temperature of the stored heat carrier of the previous stage. Synchronously the heat carrier is being moved to the cold zone through the heat exchanger, wherein the heat energy is transferred to the fluid, which is being moved in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the temperature of the heat carrier flowing into its cold zone is almost at the temperature of the fluid in its cold zone in the previous phase.
A further embodiment of the present invention discloses a method of preserving and regenerating heat energy, and an energy conversion device utilizing this method. This can be done by replacing conventional regenerators of coupled heat machines by counterflow heat exchanger and combining at least two heat machines in one by the way of arranging their cycles with opposite regenerative phases. Furthermore, coupling of unidentical heat machines is also possible, on condition that the proper operation of the counterflow heat exchanger is preserved-particularly the optimal amount of the heat is transferred and recuperated with minimal losses in both channels of the said counterflow heat exchanger.
An actuating medium of heat machine, which flows back and forth between two enclosed zones of displacer units, will be referred further on as fluid (e.g. hydrogen, helium, nitrogen, air). Heat machine has the internal and external heat exchanging means (heat exchange surface). According to this embodiment both displacer units are thermally coupled wherein coupled displacer units have cycle with opposite heat regenerative phases. Additional valves can be introduced for the improving device according to this invention and redirecting the flow of fluid. Furthermore an optional implementation of said displacer unit integrates the operation of a work machine; therefore there is no need for standalone work machine unit. In this instance, implementing kinematical mechanism as controlling device, is more advantageous, than actuating device with process manager unit.
The method of storing and regenerating of heat energy is implemented within an energy conversion device comprising of two displacer unit thermally coupled through the counterflow heat exchanger. The regenerative cycle for one displacer unit can be identical and synchronous but different in phase for other coupled machine.
To release effective work, the variations of fluid pressure are guided to a work machine when the fluid is being expanded and being compressed in their associated zones. The configuration of the current embodiment of energy conversion device demands to assemble at least one heat source, to equip work machine with at least two inputs capable to receive pressure variations generated by the displacer units.
The regenerative cycle of the energy conversion device can be characterized by the following successive main phases:
The fluid enclosed in the hot zone of the first displacer unit, is being heated and expanded, thereby high pressure is received at the first work machine input. Simultaneously the fluid is enclosed in the cold zone of the second displacer unit, is being cooled and compressed, thereby low pressure is received at the second work machine input.
After the process of expansion, the fluid of the first displacer unit is being moved to the cold zone through the counterflow heat exchanger, transferring almost all of its heat energy to the fluid (of the coupled machine) being moved in the opposite direction through the thermally coupled channel of the said counterflow heat exchanger. Thus the fluid flowing into the cold zone is almost at the temperature of the previously cooled fluid of the coupled displacer unit.
The fluid enclosed in the cold zone of the first displacer unit, is being cooled and compressed, thereby low pressure is received at the first work machine input. Simultaneously the fluid enclosed in the hot zone of the second displacer unit, is being heated and expanded, thereby high pressure is received at the second work machine input.
After the process of compression the fluid of the first displacer unit is moved to its hot zone, through the counterflow heat exchanger, absorbing almost all of the heat energy of the second displacer unit fluid moving in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the fluid flowing into the hot zone is almost at the temperature of the previously heated fluid of the coupled displacer unit.
Third implementation (
To obtain temperature gradient, transfer of the heat is provided from the heat exchange surface of the cold zone to the heat exchange surface of the hot zone of a displacer unit. Work machine generates and transmits from its at least two outputs the variations of fluid pressure, thereby the fluid is being compressed and heated when affected from low to higher pressure and expanded and cooled when affected from high to lower pressure. The configuration of the current embodiment of energy conversion device demands to assemble the work machine equipped with at least two outputs capable to transmit pressure variations generated by work machines, then the regenerative cycle of the energy conversion device operating as a heat pump can be characterized by the following successive main phases.
The fluid enclosed in the hot zone of the first displacer unit is being compressed as result of the high pressure transmitted from the first output of the work machine, thereby said fluid is being heated and the heat energy is delivered to the hot zone of the heat exchange surface of the first displacer unit. Simultaneously the fluid enclosed in the cold zone of the second displacer unit is expanding as result of low pressure transmitted from the second output of the work machine, thereby said fluid is being cooled and absorbing heat energy from the cold zone heat exchange surface of the second displacer unit.
After the process of compression, the fluid of the first displacer unit is being moved to the cold zone through the counterflow heat exchanger, transferring almost all of its heat energy to the fluid (of the coupled machine) being moved in the opposite direction through the thermally coupled channel of the said counterflow heat exchanger. Thus the fluid flowing into the cold zone is almost at the temperature of the previously cooled fluid of the coupled displacer unit.
The fluid enclosed in the cold zone of the first displacer unit is expanding as result of the low pressure transmitted from the first output of the work machine, thereby said fluid is cooled and the heat energy is absorbed from the cold zone of the heat exchanger surface of the first displacer unit. Simultaneously the fluid enclosed in the hot zone of the second displacer unit is being compressed as result of high pressure transmitted from the second output of the work machine, thereby said fluid is being heated, delivering heat energy to the hot zone heat exchange surface of the second displacer unit.
After the process of expansion the fluid of the first displacer unit is moved to its hot zone, through the counterflow heat exchanger, absorbing almost all of the heat energy of the second displacer unit fluid moving in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the fluid flowing into the hot zone is almost at the temperature of the previously heated fluid of the coupled displacer unit.
For the improved operation of the presented heat machine, the motion of displacers should be stick-slip from the one extreme position to another. Moreover the combined heat machines can be of different useful capacity and different purposes. For instance one heat machine can be used for temporary storage of the heat energy for one device or several devices combined with the said heat machine; or can be the heat receiver of another device or several devices. Therefore, when combined with more than one device, the heat capacity of the fluid should be enough to supply the heat to its combined devices; the motion of the piston when operating in the regenerative phase with one of the combined devices is preformed incrementally from one extreme position to another within the determined step. The heat capacity of fluid displaced by one step should be equal to the heat capacity of countercurrent flow of fluid of another heat machine through the counterflow heat exchanger.
The duration of holding the displacer in the hot zone have to be controlled due to the wide-range adjustment of output power, mostly when the invented heat machine operates as a heat engine.
In as much as the invented heat machine is symmetrical, then the disorder of symmetric operation of this displacer unit leads to disorder of the symmetry of work of the counterflow heat exchanger. The problem is solved by increasing the mass of the heat exchanger. In another words, the increasing of the mass of the walls separating counterflow heat exchanger's channels, (and therefore increasing its heat capacity), provide the properties of a regenerator (working as a heat accumulator). Therefore, the heat could be effectively recovered to the hot zone as in said symmetrical cycles.
To improve the compactness of the invented device it is useful to obtain the reduction of total length of the counterflow heat exchanger. Therefore it should be crafted with a material of specific heat conductance anisotropy of walls of separating channels of heat conductance to achieve less thermal resistance across the walls of separating channels of opposite fluid flows than the thermal resistance along the walls of separating channels of opposite fluid flows.
Fourth implementations (
For enabling continuous control of the output power of the energy conversion device which is comprised of two combined heat machines, is suggested to implement a method of intermediate storage and regeneration of heat energy. Therefore, for this purpose, the heat accumulator is designed with enough heat capacity enabling to store the heat energy generated by the displacer units. A certain amount of almost all heat energy of the fluid of the first displacer unit, is transferred through the first counterflow heat exchanger to the heat carrier of the heat accumulator, which is preserved there for certain controllable time, and then transferred to the fluid of the second displacer unit, through the second counterflow heat exchanger. The process of the heat energy transfer is then performed symmetrically from the second displacer unit to the first displacer unit.
The device in accordance with further implementation of the present invention includes at least two displacer units (two displacing units), at least two counterflow heat exchangers, heat accumulator (one displacing unit), a controlling device, at least one work machine, valves for redirection of actuating medium and connecting conduits. Heat exchanger is inserted between each displacer unit and heat accumulator. Thereby each displacer unit is thermally coupled with the heat accumulator through respective counterflow heat exchanger.
Valves are installed in conduits to enable the redirection of the heat carrier to the corresponding acting heat exchanger. Additional valves can be further implemented for improving the fluid flows within regenerative cycle of energy conversion device.
When the device is in heat engine configuration, pressure variations of fluid are generated by displacer units, work machine receives and converts variations of pressure into efficient work. When the device is in heat pump configuration pressure variations of fluid are generated by work machine actuated by some external source of energy, thereby variations of fluid pressure are transmitted to displacer units. The controlling device manages valves and displacer means to provide the proper flow of heat carrier and fluids through counterflow heat exchangers according to a predefined scenario which includes phases of the above-stated method.
The regenerative cycle for the energy conversion device can be characterized by the following main phases.
The fluid of the first displacer unit is enclosed in its hot zone. The heat carrier is enclosed in the cold zone of the heat accumulator, preserving low thermal energy for the determined time interval.
The fluid of the first displacer unit is moving to its cold zone through the first heat exchanger transferring the hot zone fluid heat energy to the heat carrier moving in the opposite direction through the thermally coupled channel of the first heat exchanger. Thus the fluid of the first displacer unit flowing into its cold zone is almost at the temperature of the previously stored heat carrier. Synchronously the heat carrier is moving to its hot zone through the first heat exchanger absorbing the heat energy of the fluid of the first displacer unit moving in the opposite direction through the thermally coupled channel of the first heat exchanger. Thus the heat carrier flowing into its hot zone is almost at the temperature of the previous fluid from its hot zone. The flow of the fluid of the second displacer unit is blocked while the flows of actuating medium through the second heat exchanger are blocked by valves.
The fluid of the first displacer unit is enclosed in its cold zone. The heat carrier is enclosed in the hot zone of the heat accumulator, preserving high thermal energy for the determined time interval.
The fluid of the first displacer unit is moving to its hot zone through the first heat exchanger absorbing the previously stored high thermal energy from the heat carrier moving in the opposite direction through the thermally coupled channel of the first heat exchanger. Thus the fluid of the first displacer unit flowing into the hot zone is almost at the temperature of the previously stored heat carrier. Synchronously the heat carrier is moving to its cold zone through the first heat exchanger transferring the heat energy to the fluid moving in the opposite direction through the thermally coupled channel of the first heat exchanger. Thus the heat carrier flowing into its cold zone is almost at the temperature of the previous fluid of the first displacer unit from its cold zone. The flow of fluid of the second displacer unit is withheld and flows of actuating medium through the second heat exchanger are blocked by valves.
The fluid of the second displacer unit is enclosed in its hot zone. The heat carrier is enclosed in the cold zone of the heat accumulator, preserving low thermal energy for the determined time interval.
The fluid of the second displacer unit is moving to its cold zone through the second heat exchanger transferring the hot zone fluid heat energy to the heat carrier moving in the opposite direction through the thermally coupled channel of the first heat exchanger. Thus the fluid of the second displacer unit flowing into its cold zone is almost at the temperature of the previously stored heat carrier. Synchronously the heat carrier is moving to its hot zone through the second heat exchanger absorbing the heat energy of the fluid of the second displacer unit moving in the opposite direction through the thermally coupled channel of the said heat exchanger. Thus the heat carrier flowing into its hot zone is almost at the temperature of the previous fluid of the second displacer unit from its hot zone. The flow of fluid of the first displacer unit is withheld and flows of actuating medium through the first heat exchanger are blocked by valves.
The fluid of the second displacer unit is enclosed in its cold zone. The heat carrier is enclosed in the hot zone of the heat accumulator, preserving high thermal energy for the determined time interval.
The fluid of the second displacer unit is moving to its hot zone through the second heat exchanger absorbing the previously stored high thermal energy from the heat carrier moving in the opposite direction through the thermally coupled channel of the second heat exchanger. Thus the fluid of the second displacer unit flowing into the hot zone is almost at the temperature of the previously stored heat carrier. Synchronously the heat carrier is moving to the cold zone through the second heat exchanger transferring the heat energy to the fluid moving in the opposite direction through the thermally coupled channel of the second heat exchanger. Thus the heat carrier flowing into its cold zone is almost at the temperature of the previous fluid of the second displacer unit from its cold zone. The flow of fluid of the first displacer unit is blocked while the flows of actuating medium through the first heat exchanger are blocked by valves.
Using the device of
The presented method enables to combine heat machines even with different heat capacity of fluids and different working volumes. Then the heat capacity of the heat carrier should be less or equal to the largest heat capacity of the fluid contained within one of the heat machines. The potion of the heat carrier flowing through the heat exchangers should be adjusted in order to prevent thermal energy losses. Therefore, the step of the moving the displacing element of the heat accumulator should be adjusted respectively.
The device as illustrated in
Advantages
The advantage of the present invention is that the heat energy, stored in the said heat accumulator, can be much better isolated from the working volume of the heat machine than in the conventional regenerators, consequently increasing the efficiency of the heat machine. Moreover the duration of heat storage within the heat accumulator, can be longer than in said regenerator.
A further advantage of the present invention is that it enables adjustment of the output power for two combined heat machines when their opposite regenerative phases are not concurrent or there is a time delay between said phases, thereby storing the heat energy for some short-duration phase of regenerative cycle.
A further advantage of the present invention is that the counterflow heat exchanger can be introduced as a regenerator with an unlimited heat capacity. Replacing both regenerators with a single, more efficient counterflow heat exchanger, allows total heat machine efficiency improvement by the same ratio. Moreover, regenerator's heat capacity is limited and constituted by its material and geometrical structures. Increasing heat machine's working volume size, might lead to a total efficiency reduction, if the heat that must be captured during said cycle is higher than the maximum regenerator heat capacity. Unlike regenerators, counterflow heat exchanger's heat capacity is unlimited. Therefore, replacing regenerators with a single counterflow heat exchanger, allows the increasing of total heat machine's working volume, consequently, improving working volume to dead volume ratio.
A further advantage of the present invention is that the counterflow heat exchanger can be crafted with less gas-dynamic drag and less dead volume than conventional regenerator; that is additionally increases the efficiency of operation of the invented device.
A further advantage of the present invention is that the dissipated power is dramatically decreased and this allows downsizing cooler means and simplifying construction.
Another advantage of the present invention is that the embodiment of two identical heat machines into double acting uniform mechanism improves overall bulk properties of machine.
Another advantage of the present invention is that the efficiency of the invented heat machine is almost stable at any level of power.
Another advantage of the present invention is that the invented heat machine can be quickly stopped and launched again with minimum latency within these two processes.
Various additional advantages and features of novelty which characterize the invention are further pointed out in the claims that follow. However, for a better understanding of the invention and its advantages, reference should be made to the accompanying drawings and descriptive matter which illustrate and describe preferred embodiments of the invention.
These and further features and advantages of the invention will become more clearly understood in the light of the ensuing description of a few preferred embodiments thereof, given by way of example only, with reference to the accompanying drawings (FIGS.), wherein.
Referring first to
Each displacer unit is comprised of a displacer chamber (2, 79), displacer (1, 78), a hot zone (3, 77), a cold zone (4, 80) and an actuating drives (14, 83) to drive the displacers by the commands of the external control unit. Displacer chamber of Heat Machine 1 further includes two heat exchangers: the first heat exchanger surface (7) which enables heat exchange of the high temperature heat energy between the heat source (6) and the hot zone (3) and a second heat exchange surface (5) which enables heat exchange of the low temperature heat energy between the cold zone (4) and the reservoir. Actuating devices (72, 84) are controlled by the process manager unit (74) with control drives (75, 85). The counterflow heat exchanger (Heat Exchanger 1) is comprised of two identical heat exchanging elements—channels (13, 33), that enable countercurrent gas flow, and separation wall (18) that physically isolates channels but enables heat exchange between countercurrent flowing of fluid and heat carrier within these channels.
The heat machine's hot zone (3) is attached to the work machine (16) through a conduit formed by pipes (11, 10). The hot zone (3) is also connected to the counterflow heat exchanger channel (13) through part of the conduit formed by the pipe, (11) allowing gas flow in both directions. The cold zone (4) is connected to the counterflow heat exchanger channels (13) as well, through the conduit (12) allowing gas flow in both directions.
The heat accumulator's hot (77) and cold (80) zones are part of the chamber (79) volume. The chamber's functionality is directed at storing the heat carrier charged by thermal energy during regenerative cycle. The heat accumulator's hot zone (77) is connected to the counterflow heat exchanger channel (13) through conduit (81) allowing gas flow in both directions. The heat accumulator's cold zone (80) is connected to the counterflow heat exchanger channel (33) as well, through conduit (82) allowing gas flow in both directions.
Referring first to
Each displacer unit is comprised of: a displacer chamber (2, 22); a displacer (1,21); a heat exchange surface (7, 27), which exchanges high temperature heat between the heat source (6, 26) and the fluid in the hot zone (3, 23); heat exchange mean (5, 25) which exchange low temperature heat between the fluid in the cold zone (4, 24) and the reservoir; actuating drives (14, 34) that drives the displacers by the controlling device's commands. The actuating devices (72, 73) are controlled by the process manager unit (74) with the control drives (75, 76). The counterflow heat exchanger is comprised of two identical heat exchanging elements: channels (13, 33), that enable countercurrent gas flow and separation wall (18) that physically isolates channels but, at the same time, enables heat exchange between countercurrent flowing of fluids within these channels.
Each displacer unit is connected to the work machine (16), which can receive or transmit gas pressure variations, and to a counterflow heat exchanger (Heat Exchanger 1), through conduit formed by pipes (10, 11 and 30, 31) and through conduit (12 and 32) allowing gas flow along the cycle. The hot zones (3, 23) are attached to the work machine (16) through conduits formed by pipes (11, 10 and 30,31). Hot zones (3, 23) are also connected to the counterflow heat exchanger elements (13, 33) through part of the conduit formed by pipe (11, 31), allowing gas flow in both directions. The cold zones (4, 24) are connected to the counterflow heat exchanger channels (13,33) as well, through other conduits (12,32), allowing gas flow in both directions.
Referring to
Referring to
In accordance with further embodiment of the present invention it is suggested to replace the conventional heat machine's regenerator of the heat machine presented on
A further embodiment suggests replacing a conventional regenerator of the heat machine on
According to further embodiment of the present invention it is suggested replacing a conventional regenerator of the heat machine on
Presenting accordance with further embodiment it is suggests replacing a conventional regenerator of the heat machine on
Referring in a more particular way to processes taken place in
Stage A of the cycle is described in
Stage B of the cycle is described in
Stage C of the cycle is described in
Stage D of the cycle is described in
Stage E of the cycle is described in
Stage F of the cycle is described in
Another possible variation of the said invention is described in
Heat Exchanger 1 is inserted between each Displacer unit 1 and Heat Accumulator; Heat Exchanger 2 is inserted between each Displacer unit 2 and Heat Accumulator. Conduit, formed by pipes (90, 86, 81) connects the hot zone of Heat Accumulator through redirecting valve (91) to both heat exchangers. Redirecting valve (91) is controlled by the controlling device with the drive (92) and redirects the flow of heat carrier through pipes (81, 90) or through pipes (81, 86) depending on phase of regenerative cycle of the energy conversion device. Conduit, formed by pipes (87, 82, 93) connects the cold zone of Heat Accumulator through redirecting valve (88) to both heat exchangers. Redirecting valve (88) is controlled by the controlling device with the drive (89) and redirects the flow of heat carrier through pipes (82, 87) or through pipes (82, 93) depending on phase of regenerative cycle of the energy conversion device. Conduit, formed by pipes (10, 11), connects the hot zone of the Displacer unit 1, Heat Exchanger 1 and work machine (16), conduit (12) connects the cold zone of Displacer unit 1 with the counterflow Heat Exchanger 1, thereby enabling the flow of fluid from the hot to cold zone of Displacer unit 1 through the counterflow Heat Exchanger 1, and enabling for work machine (16) to transmit or receive variations of pressure. Conduit, formed by pipes (30, 31), connects the hot zone of the Displacer unit 2, Heat Exchanger 2 and work machine (16), conduit (32) connects the cold zone of Displacer unit 2 with the counterflow Heat Exchanger 2, thereby enabling the flow of fluid from the hot to cold zone of Displacer unit 2 through the counterflow Heat Exchanger 2, and enabling the work machine (16) to transmit or receive variations of pressure. The controlling device comprised of process manager unit (74) and its drives (75, 76, 85), actuating devices (72, 73, 84) and its drives (14, 34, 83). The said controlling device synchronizes the proper switching of valves (88, 91) and motion of displacers to provide the proper flow of heat carrier and fluids through counterflow heat exchangers according to the above-stated method.
It will be seen from the above description of this invention that it provides a method and device which fulfills the objects set forth. By combining the counterflow heat exchanger and redirecting valves in the described way, a greater part of the heat energy is economically conserved, providing greater efficiency. Moreover, the coupling of two identical displacer units in the said way, provides a smoother work energy generation. There is, therefore, a combination of factors which materially contribute to the attainment of efficiencies higher than previously possible in heat engines, and which extends the range of applications
Numerous characteristics, advantages and embodiments of the invention have been described in detail in the foregoing description with reference to the accompanying drawings. However, the disclosure is illustrative only and it is to be understood that the invention is not limited to the precise illustrated embodiments. Various changes and modifications may be effected therein by one skilled in the art without departing from the scope or spirit of the invention.
