WASTE HEAT INTEGRATION INTO PUMPED THERMAL ENERGY STORAGE

Abstract

A technique increases the round-trip efficiency (“RTE”) of a pumped thermal energy storage system by changing the coefficient of performance (“COP”) and efficiency of the cycles by changing the temperature ratios of each, which is accomplished by using two separate low temperature reservoirs (“LTRs”) that are at different temperatures. More particularly, the disclosed technique accomplishes this by using a low-temperature thermal reservoir during the charging process that is at a higher temperature than the generating cycle's low-temperature thermal reservoir. The low-temperature thermal reservoirs are “decoupled” and “independently existing”, in that their temperature and utilization are independent of one another. In general, decoupled and independently existing reservoirs may also be different in their independent reservoir media, reservoir location, and heat exchangers.

Description

TECHNICAL FIELD

This present disclosure is directed to a Pumped Thermal Energy Storage (“PTES”) system and, more particularly, a technique by which round-trip efficiency (“RTE”) for a PTES system may be increased.

BACKGROUND

Pumped thermal energy storage (“PTES”) systems, also known as electro-thermal energy storage systems, are used to store and generate energy. PTES systems generally consist of a configurable thermodynamic cycle where thermal energy is transferred between a high temperature reservoir and a low temperature reservoir via working fluid in a working fluid circuit. The PTES typically operates in at least two cycles—a charging cycle and a generating cycle. The PTES operates as a heat pump during the charging cycle and as a heat engine during the generating cycle.

During the “charging” cycle of operation, the thermodynamic cycle, which is a heat pump cycle in a nominally forward direction, may be used to increase the thermal energy in a high temperature reservoir. In some instances, an electrical motor may be used to drive a compressor, which increases the pressure and temperature of the working fluid, whereby the thermal energy in the fluid is transferred to and stored in the high temperature reservoir either by using a high temperature heat exchanger or by direct contact between the fluid and the thermal medium of the reservoir. Following the heat transfer to the high temperature reservoir, the fluid may be expanded through a turbine, which produces shaft work that may be used to drive the gas compressor. This working fluid expansion may lower the pressure and temperature of the working fluid. After exiting the turbine, the working fluid may transfer heat from a low temperature reservoir. The working fluid may then be returned to approximately its initial state (e.g., pressure and temperature).

During a “generating” cycle of operation, the directions of fluid and heat circulation are reversed. A pump may increase the pressure of the working fluid and move the working fluid through the high temperature heat exchanger or through the direct contact between the fluid and the thermal medium of the reservoir, which transfers heat from the high temperature reservoir to the working fluid. The heated working fluid may be expanded by a turbine, producing shaft work. The shaft work from the turbine may exceed the compressor work, and the excess work may be converted to electrical power by a generator and distributed to an electrical grid electrically coupled to the generator. Following the turbine expansion, the working fluid may be cooled by passing through the low temperature heat exchanger that is connected to a low temperature reservoir before entering the pump. Upon exit of the low temperature heat exchanger, the working fluid may be returned to approximately its initial state (i.e., pressure and temperature).

SUMMARY

Disclosed herein is a technique by which the round-trip efficiency (“RTE”) of a pumped thermal energy storage system may be increased by changing the coefficient of performance (“COP”) and efficiency of the cycles by changing the temperature ratios of each, which is accomplished by using two separate low temperature reservoirs (“LTRs”) that are at different temperatures. More particularly, the disclosed technique accomplishes this by using a low-temperature thermal reservoir during the charging process that is at a higher temperature than the generating cycle's low-temperature thermal reservoir. The low-temperature thermal reservoirs are “decoupled” and “independently existing”, in that their temperature and utilization are independent of one another. In general, decoupled and independently existing reservoirs may also be different in their independent reservoir media, reservoir location, and heat exchangers.

Thus, in a first aspect, a method for use in a Pumped Thermal Energy Storage System (“PTES”) comprises: circulating a working fluid through a working fluid circuit; and operating the PTES through a charging cycle and a generating cycle while circulating the working fluid. During the charging cycle, heat is transferred from a first low-temperature thermal reservoir to the working fluid, the first low-temperature thermal reservoir operating at a first temperature. During the generating cycle, heat is transferred from the working fluid to a second low-temperature thermal reservoir, the second low-temperature thermal reservoir existing independently of the first low-temperature reservoir, being decoupled from the first low-temperature thermal reservoir, and operating at a second temperature less than the first temperature.

In a second aspect, a Pumped Thermal Energy Storage System (“PTES”), comprises: a first low-temperature thermal reservoir; a second low temperature thermal reservoir; and a working fluid circuit through which a working fluid is circulated in operation. The working fluid circuit includes, during a charging cycle, a first low-temperature heat exchanger that, in operation, transfers heat from the first low-temperature thermal reservoir to the working fluid, the first low-temperature thermal reservoir operating at a first temperature. During a generating cycle, the working fluid circuit includes a second low-temperature heat exchanger that, in operation, transfers heat from the working fluid to a second low-temperature thermal reservoir. The second low-temperature thermal reservoir exists independently of the first low-temperature reservoir, is decoupled from the first low-temperature thermal reservoir, and operates at a second temperature less than the first temperature.

The above presents a simplified summary in order to provide a basic understanding of some aspects of the invention. This summary is not an exhaustive overview of the invention. It is not intended to identify key or critical elements of the invention or to delineate the scope of the invention. Its sole purpose is to present some concepts in a simplified form as a prelude to the more detailed description that is discussed later.

BRIEF DESCRIPTION OF THE DRAWINGS

The present disclosure is best understood from the following detailed description when read with the accompanying Figures. It is emphasized that, in accordance with the standard practice in the industry, various features are not drawn to scale or are shown in simplified form. In fact, the dimensions of the various features may be arbitrarily increased or reduced for clarity of discussion.

FIG. 1A and FIG. 1B illustrate a PTES system during a charging cycle and during a generating cycle, respectively in accordance with one or more embodiments.

FIG. 2A and FIG. 2B illustrate respectively, a high-temperature heat exchange including a high-temperature thermal reservoir comprised of two fluid tanks and a low-temperature heat exchange including a low-temperature thermal reservoir comprised of two fluid tanks, as may be used in some embodiments.

FIG. 3A and FIG. 3B illustrate a recuperated PTES system during a charging cycle and during a generating cycle, respectively in accordance with one or more embodiments.

FIG. 4 is a flow control system as may be used in configuring the PTES system of FIG. 1A-FIG. 1B and/or FIG. 3A-FIG. 3B according to one or more examples of the disclosure.

While the disclosed technique is susceptible to various modifications and alternative forms, the drawings illustrate specific embodiments herein described in detail by way of example. It should be understood, however, that the description herein of specific embodiments is not intended to limit that which is claimed to the particular forms disclosed, but on the contrary, the intention is to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the appended claims.

DETAILED DESCRIPTION

Illustrative examples of the subject matter claimed below will now be disclosed. In the interest of clarity, not all features of an actual implementation are described in this specification. It will be appreciated that in the development of any such actual implementation, numerous implementation-specific decisions may be made to achieve the developers' specific goals, such as compliance with system-related and business-related constraints, which will vary from one implementation to another. Moreover, it will be appreciated that such a development effort, even if complex and time-consuming, would be a routine undertaking for those of ordinary skill in the art having the benefit of this disclosure.

Thus, in a charging cycle, heat is added to the working fluid from the low-temperature reservoir (“LTR”) and removed from the working fluid to the high-temperature reservoir (“HTR”). And, in a generating cycle, heat is added to the working fluid from the high-temperature reservoir and removed from the working fluid to the low-temperature reservoir. A PTES system typically uses a low-temperature thermal resource to supply heat to the heat pump in the charging cycle. Typically, the same thermal resource is used to reject heat by the heat engine in the generating cycle. The thermal resource may be stored in an engineered reservoir (such as a contained reservoir like a fluid tank) or in a natural reservoir (such as ambient air).

A figure of merit for a heat pump is coefficient of performance (“COP”), defined as the ratio of energy product (high-temperature heat, Q_h) to energy cost (net work, W). The figure of merit for a heat engine is thermal efficiency (η), defined as the ratio of energy product (net work, W) to energy cost (high-temperature heat, Q_h). The combined figure of merit for a PTES system is round-trip efficiency (“RTE”), defined as the product of COP and n.

Based on Carnot principles, COP increases as the temperature ratio between the high-temperature reservoir and low-temperature reservoir (T_h/T_c) decreases. Conversely, η increases as T_h/T_c increases. In a PTES system, the heat pump and the heat engine typically share common reservoirs. Thus, decreasing Thor increasing T_c is expected to increase COP while decreasing η. Similarly, increasing T_h or decreasing T_c is expected to decrease COP while increasing η. In general, reservoir temperature changes that benefit one cycle's performance are a detriment to the other cycle's performance, muting the overall impact to RTE.

A simplified numerical model of a PTES system, in which the charging and generating processes are represented by imperfect Carnot heat pump and Carnot heat engines can be considered:

${\mathrm{COP}}_{\mathrm{hp}}=C_{\mathrm{hp}}\frac{1}{1-\left(\frac{T_{c,\mathrm{chg}}}{T_h}\right)}$ ${\eta }_{\mathrm{gen}}=C_{\mathrm{gen}}\left[1-\left(\frac{T_{c,\mathrm{gen}}}{T_h}\right)\right]$

Where the “C” factors represent the actual performance of the cycles relative to the Carnot ideal. The RTE can be represented by the mathematical product of the two terms above:

$\mathrm{RTE}=C_{\mathrm{hp}}{C}_{\mathrm{gen}}\left[\frac{1-\left(\frac{T_{c,\mathrm{gen}}}{T_h}\right)}{1-\left(\frac{T_{c,\mathrm{chg}}}{T_h}\right)}\right]$

Since T_c,chg>T_c,gen, we can represent T_c,chg=T_c,gen+ΔT. Substituting in the above, and assuming ΔT<<T_h−T_c,gen, we can find

$\mathrm{RTE}=C_{\mathrm{hp}}{C}_{\mathrm{gen}}\left(1+\frac{\Delta T}{T_h-T_{c,\mathrm{gen}}}\right)$

For the baseline case, where ΔT=0, RTE_bl=C_hpC_gen, so

$\frac{\mathrm{RTE}}{{\mathrm{RTE}}_{\mathrm{bl}}}=1+\frac{\Delta T}{T_h-T_{c,\mathrm{gen}}}$

For example, in the case where T_h−T_c,gen=300 K, and the charging heat source was 15 K warmer than the generating heat source, the projected improvement in RTE would be 5%, or an increase from a baseline RTE of 60% to 63%.

An example of this situation would be a PTES system that is co-located with an existing closed-cycle power generating station. Most closed-cycle power plants, such as nuclear, coal-fired, concentrating solar or combined cycle gas turbine plants, use steam as the working fluid to convert high-temperature thermal energy to mechanical and electrical power using a turbine. To close the steam cycle, low-pressure steam at the turbine discharge must be condensed back to a liquid state.

The heat that is recovered from this process is typically at temperatures that are low compared to the steam turbine inlet temperature, but at temperatures that are higher than the ambient air temperature by at least 15° C. or more to enable transfer of that residual heat to the ambient environment. In the disclosed concept, the PTES system would use this residual heat as the heat source during the charging process. At a later time, the PTES system would generate power, and reject heat to the ambient environment, thus achieving a higher RTE than could be achieved by a standalone PTES system that was charged from an ambient resource.

The power generating station could be one source of waste heat, with possible source locations including generating turbine condensate or cooling tower water. Additionally, many industrial plants (such as refineries, pulp and paper mills, and cement plants) have numerous sources of waste heat. Broadly speaking, if a waste heat source is warmer than ambient air, it can be used by a PTES system to boost COP without detriment to η, for a net increase to RTE.

For power generating stations using steam cycles in cold climates, the impact would be even higher than the previous example. If the heat source temperature is from a steam condenser, the temperature is fixed to avoid ice accumulation in the cooling towers, and the lower ambient temperature would increase ΔT further. As an added benefit, the extraction from the heat source would also reduce the parasitic cooling loads (e.g., cooling tower fan work) of the steam cycle.

Turning now to the drawings, FIG. 1A and FIG. 1B illustrate a PTES system 100 during a charging cycle 103 and during a generating cycle 106, respectively. Those in the art will appreciate that, although shown in two different drawings, the charging cycle 103 in FIG. 1A and the generating cycle 106 in FIG. 1B are two different configurations of a single PTES system 100 not otherwise shown. The configuration includes controlling the working fluid flow through a working fluid circuit by operation of flow control valves in a manner more fully disclosed below.

Those in the art will also appreciate that there are some details omitted from FIG. 1A and FIG. 1B. For example, any particular implementation will include a variety of sensors to measure, for instance, temperatures, pressures, and flow rates at various points in the working fluid circuit. Omitted features may also include things such as fill ports, drains, relief valves, and power supply connections. These kinds of omitted features are ubiquitous and well known in the art and may be routinely implemented. Thus, those skilled in the art having the benefit of this disclosure will both be able to recognize their applicability and readily implement these omitted details. Accordingly, these kinds of details are omitted for the sake of clarity and so as not to obscure that which is claimed below.

Returning now to FIG. 1A, in the charging cycle 103, the working fluid circuit 109a includes a low-temperature heat exchange 112, a compression process 115, a high-temperature heat exchange 118, and an expansion process 121. The PTES 100, when in this configuration, may be referred to as a “heat pump”. This configuration of the working fluid circuit 109 may be referred to as the “charging configuration” or the “heat pump configuration” of the PTES 100. The working fluid in the embodiments illustrated herein is Carbon dioxide (CO₂), but alternative embodiments may use alternative working fluids.

The compression process 115 is downstream from the low temperature heat exchange 112 and upstream from the high-temperature heat exchange 118. The compression process 115, among other things, provides the motive force for circulating the working fluid through the working fluid circuit 109a during the charging cycle 103. The compression process 115 revolves around the operation of a compression device 124. The compression device 124 may be a compressor. Examples of suitable compressors include, without limitation, reciprocating compressors, centrifugal compressors, and scroll compressors. Those skilled in the art having the benefit of this disclosure may appreciate other kinds of compressors that may be suitable in various embodiments, including means of equivalent structure performing the disclosed function. The compression process 115 receives the working fluid from the low-temperature exchange 112, compresses the working fluid to increase the temperature and pressure thereof, and discharges the working fluid to the high-temperature heat exchange 118.

The expansion process 121 is downstream from the high-temperature heat exchange 118 and upstream from the low temperature heat exchange 112. The expansion process 121 revolves around the operation of an expansion device 127, such as an expander. Examples of suitable expanders include, without limitation, an adiabatic expansion valve or a mechanical expander depending on the embodiment. A mechanical expander may be, for instance, a turbine. Those skilled in the art having the benefit of this disclosure may appreciate other kinds of expanders that may be suitable in various embodiments, including means of equivalent structure performing the disclosed function. The expansion process 121 receives the working fluid from the high-temperature exchange 118, expands the working fluid to reduce the temperature and pressure thereof, and discharges the working fluid to the low-temperature exchange 112.

The high-temperature heat exchange 118 exchanges heat between the working fluid and a high-temperature thermal reservoir HTR_C. A first exchange medium (not separately shown) circulates between the high-temperature thermal reservoir HTR_C and the high-temperature heat exchanger HTX_C. The first exchange medium circulates through the lines 130 on a first side 133 of the high-temperature heat exchanger HTX_C. The working fluid enters the high-temperature heat exchanger HTX_C from the compression process 115 and exits to the expansion process 121 on a second side 136 of the high-temperature heat exchanger HTX_C. In the high-temperature heat exchanger HTX_C, heat is exchanged from the working fluid to the first exchange medium for storage in the high-temperature thermal reservoir HTR_C.

The high-temperature thermal reservoir HTR_C may be an engineered, contained reservoir, like a fluid tank. The contained reservoir may include a thermal medium such as sand or gravel, concrete, encapsulated phase-change materials, bulk phase-change materials, or a combination thereof. Note that in some embodiments, the high-temperature thermal reservoir HTR_C may include two fluid tanks HTR1 and HTR2 as shown in FIG. 2A.

The low-temperature heat exchange 112 exchanges heat between the working fluid and a low-temperature thermal reservoir LTR_C. A second exchange medium (not separately shown) circulates between the low-temperature reservoir LTR_C and the low-temperature heat exchanger LTX_C. The second exchange medium circulates through the lines 139 on one side 142 of the low-temperature heat exchanger LTX_C. The working fluid enters the low-temperature heat exchanger LTX_C from the expansion process 121 and exits to the compression process 115 on a second side 145 thereof. In the low-temperature heat exchanger LTX_C, heat from the low-temperature thermal reservoir LTR_C is exchanged from the second exchange medium to the working fluid.

The low-temperature thermal reservoir LTR_C may be an engineered reservoir or a natural reservoir. If engineered, the low-temperature thermal reservoir LTR_C may be a contained reservoir, like a fluid tank. The contained reservoir may include a thermal medium such as sand or gravel, concrete, encapsulated phase-change materials, bulk phase-change materials, or a combination thereof. If a natural reservoir, the low-temperature thermal reservoir LTR_C may be, for example, ambient atmosphere or a geothermal reservoir. Note that in some embodiments, the low-temperature thermal reservoir LTR_C may include two fluid tanks LTR1 and LTR2 as shown in FIG. 2B.

In the illustrated embodiment, the low-temperature thermal reservoir LTR_C may alternatively be a waste heat source—that is, a heat generated by another process. A waste heat source may comprise waste heat, low-value heat, or low-grade heat, or heat from other processes that are low impact to the original process but are not completely waste heat. For example, a power generating station may be a source of waste heat in its turbine discharge flow. Possible source locations in a power generating station may include generating turbine condensate or cooling tower water. Additionally, many industrial plants (such as refineries, pulp and paper mills, and cement plants) have numerous sources of waste heat. This waste heat may be captured from a medium that may be used for the low-temperature thermal reservoir LTR_C in the illustrated embodiment.

In the illustrated embodiment, the low-temperature thermal reservoir LTR_C may be an ambient atmosphere. As noted above, broadly speaking, if a waste heat source is warmer than ambient air, it can be used by a PTES system to boost COP without detriment to η, for a net increase to RTE. Thus, in the illustrated embodiment, the ambient atmosphere is cooler (and has less thermal energy) than the waste heat source. In some embodiments, the ambient atmosphere may be 5° C. or more cooler than the waste heat source.

Referring again to FIG. 1A, during the “charging” cycle of operation, the thermal energy in the high temperature reservoir is increased. The compression process 115 increases the pressure and temperature of the working fluid. The high-temperature heat exchange 118 transfers thermal energy to the high temperature reservoir HTR_C and is stored. Following the heat transfer to the high temperature reservoir HTR_C, the working fluid is expanded through the expansion process 121, which lowers the pressure and temperature of the working fluid. After exiting the expansion process 121, the working fluid passes through a low-temperature heat exchange 112. The low-temperature heat exchange 112 transfers heat from the low temperature reservoir LTR_C to the working fluid. Upon exiting the low-temperature heat exchange 112, the working fluid is returned to approximately its initial state (e.g., pressure and temperature).

Referring now to FIG. 1B, in the generating cycle 106, the working fluid circuit 109b includes a low-temperature heat exchange 150, a compression process 153, a high-temperature heat exchange 156, and an expansion process 159. The PTES 100 operates as a heat engine in this configuration. This configuration of the working fluid circuit 109b may be referred to as the “generating configuration”, “discharging configuration”, or “heat engine configuration” of the PTES 100. The working fluid in the embodiments illustrated herein is still Carbon dioxide (CO₂), but alternative embodiments may use alternative working fluids.

The compression process 153 is downstream from the low-temperature heat exchange 150 and upstream from the high-temperature exchange 156. The compression process 153, among other things, provides the motive force for circulating the working fluid through the working fluid circuit 109b during the generating cycle 106. The compression process 153 revolves around the operation of a compression device 162.

The compression device 162 may be a pump or gas-phase compressor. Examples of suitable compression devices include, without limitation, centrifugal pumps, positive displacement pumps, centrifugal compressors and axial compressors. Those skilled in the art having the benefit of this disclosure may appreciate other kinds of compression devices that may be suitable in various embodiments, including means of equivalent structure performing the disclosed function. The compression process 153 receives the working fluid from the low-temperature exchange 150, compresses the working fluid to increase the temperature and pressure thereof, and discharges the working fluid to the high-temperature heat exchange 156.

The expansion process 159 is downstream from the high-temperature heat exchange 156 and upstream from the low temperature heat exchange 150. The expansion process 159 revolves around the operation of an expansion device 165, such as an expander. Examples of suitable expanders include, without limitation, a mechanical expander depending on the embodiment. A mechanical expander may be, for instance, a turbine. Those skilled in the art having the benefit of this disclosure may appreciate other kinds of expanders that may be suitable in various embodiments, including means of equivalent structure performing the disclosed function. The expansion process 159 receives the working fluid from the high-temperature exchange 156, expands the working fluid to reduce the temperature and pressure thereof, and discharges the working fluid to the low-temperature exchange 150.

The high-temperature heat exchange 156 exchanges heat between the working fluid and a high-temperature thermal reservoir HTR_G. A first exchange medium (not separately shown) circulates between the high-temperature thermal reservoir HTR_G and the high-temperature heat exchanger HTX_G. The first exchange medium circulates through the lines 168 on a first side 171 of the high-temperature heat exchanger HTX_G. The working fluid enters the high-temperature heat exchanger HTX_G from the compression process 153 and exits to the expansion process 159 on a second side 173 of the high-temperature heat exchanger HTX_G. In the high-temperature heat exchanger HTX_G, heat is exchanged from the high-temperature thermal reservoir HTR_G via the first exchange medium to the working fluid.

The high-temperature thermal reservoir HTR_G may be an engineered, contained reservoir, like a fluid tank. The contained reservoir may include a thermal medium such as sand or gravel, concrete, encapsulated phase-change materials, bulk phase-change materials, or a combination thereof. Note that in some embodiments, the high-temperature thermal reservoir HTR_G may include two fluid tanks HTR1 and HTR2 just as the high-temperature thermal reservoir HTR_C for the charging cycle is shown in FIG. 2A.

The low-temperature heat exchange 150 exchanges heat between the working fluid and a low-temperature thermal reservoir LTR_G. A second exchange medium (not separately shown) circulates between the low-temperature reservoir LTR_G and the low-temperature heat exchanger LTX_G. The second exchange medium circulates through the lines 174 on one side 177 of the low-temperature heat exchanger LTX_G. The working fluid enters the low-temperature heat exchanger LTX_G from the expansion process 159 and exits to the compression process 153 on a second side 180 thereof. In the low-temperature heat exchanger LTX_G, heat from the working fluid is exchanged from the second exchange medium to the low-temperature thermal reservoir LTR_G.

The low-temperature thermal reservoir LTR_G may be an engineered reservoir or a natural reservoir. If engineered, the low-temperature thermal reservoir LTR_G may be a contained reservoir, like a fluid tank or may be a fluid stream of some kind. The contained reservoir may include a thermal medium such as sand or gravel, concrete, encapsulated phase-change materials, bulk phase-change materials, or a combination thereof. If a natural reservoir, the low-temperature thermal reservoir LTR_G may be, for example, ambient atmosphere or a geothermal reservoir. Note that in some embodiments, the low-temperature thermal reservoir LTR_G may include two fluid tanks LTR1 and LTR2 as shown in FIG. 2B for the low-temperature reservoir LTR_C in the charging cycle.

In the illustrated embodiment, the low-temperature thermal reservoir LTR_G may be an ambient atmosphere or a geothermal reservoir. As noted above, broadly speaking, if a waste heat source is warmer than ambient air, it can be used by a PTES system to boost COP without detriment to η, for a net increase to RTE. Thus, in the illustrated embodiment, the ambient atmosphere is cooler than is the waste heat source. In some embodiments, the ambient atmosphere may be 5° C. or more cooler than the waste heat source.

During the “generating” cycle of operation, the directions of fluid and heat circulation are reversed relative to the charging cycle discussed above. The compression process 153 increases the pressure of the working fluid and moves the working fluid through the high temperature heat exchange 156, which transfers heat from the high temperature reservoir to the working fluid. The heated working fluid may be expanded by the expansion process 159 by, for example, a turbine producing shaft work. The shaft work from the turbine may exceed the compressor work, and the excess work may be converted to electrical power by a generator and distributed to an electrical grid electrically coupled to the generator. Following the expansion process 159, the working fluid may be cooled by passing through the low temperature heat exchange 150 that is connected to a low temperature reservoir LTR_G before entering the compression process 153 (e.g., a pump). Upon exit from the low temperature heat exchange 150, the working fluid may be returned to approximately its initial state (i.e., pressure and temperature).

In accordance with the subject matter claimed below, the low-temperature thermal reservoirs LTR_C and LTR_G are “decoupled”, “independently existing”, and operate at different temperatures. The low-temperature thermal reservoirs LTR_C and LTR_G are “decoupled” and “independently existing” in that their temperature and utilization are independent of one another. In general, decoupled and independently existing reservoirs may also be different in their independent reservoir media, reservoir location, and heat exchangers. More particularly, the second temperature at which the low-temperature thermal reservoir LTR_G operates in the generating cycle is less than the first temperature at which the low-temperature thermal reservoir LTR_C operates in the charging cycle by an amount exceeding at least about 5° C. In some embodiments, the second temperature is about 15° C. less than the first temperature. Some embodiments may manifest even greater temperature differentials.

Thus, referring to both FIG. 1A and FIG. 1B, collectively, the PTES 100 comprises a first low-temperature thermal reservoir LTR_C; a second low temperature thermal reservoir LTR_C; and a working fluid circuit 109a, 109b through which a working fluid is circulated in operation. The working fluid circuit 109a includes, during a charging cycle 103, a first low-temperature heat exchanger LTX_C that, in operation, transfers heat from the first low-temperature thermal reservoir LTR_C to the working fluid, the first low-temperature thermal reservoir LTR_C operating at a first temperature. During a generating cycle, the working fluid circuit 109b includes a second low-temperature heat exchanger LTX_G that, in operation, transfers heat from the working fluid to a second low-temperature thermal reservoir LTR_G. The second low-temperature thermal reservoir LTR_G is decoupled from the first low-temperature thermal reservoir LTR_C and operates at a second temperature less than the first temperature.

Furthermore, a method for use in a PTES 100 comprises: circulating a working fluid through a working fluid circuit 109a, 109b and operating the PTES 100 through a charging cycle 103 and a generating cycle 106 while circulating the working fluid. During the charging cycle 103, heat is transferred from a first low-temperature thermal reservoir LTR_C to the working fluid, the first low-temperature thermal reservoir LTR_C operating at a first temperature. During the generating cycle, heat is transferred from the working fluid to a second low-temperature thermal reservoir LTR_G, the second low-temperature thermal reservoir LTR_G being decoupled from the first low-temperature thermal reservoir LTR_C and operating at a second temperature less than the first temperature.

Those in the art having the benefit of this disclosure will appreciate additional embodiments not illustrated in the drawings hereof. For instance, the embodiments illustrated herein perform the heat exchanges using a heat exchangers. However, as mentioned above, some embodiments may omit the heat exchanger and perform the heat exchange by direct contact between the thermal medium of the thermal reservoir and the working fluid. This change, in turn, would eliminate the exchange media of the illustrated embodiments since the heat exchange is direct rather than indirect. This may be true of one or both of the high-temperature heat exchange and the low temperature exchange depending on the embodiment. This may also be true in one or both of the charging cycle and the generating cycle.

For another example, the PTES 100 of FIG. 1A-FIG. 1B is not a recuperated PTES—i.e., there is no recuperator in that design. A recuperated PTES 300 is shown in FIG. 3A and FIG. 3B in a charging cycle 303 and a generating cycle 306 respectively. A recuperated PTES adds to the working fluid circuits 309a, 309b an internal heat exchanger to transfer heat after (in working fluid circuit 309a) or before (in working fluid circuit 309b) the high-temperature heat exchanger (“HTX”) to preheat (in working fluid circuit 309a) or precool (in working fluid circuit 309b) the fluid exiting (in working fluid circuit 309a) or entering (in working fluid circuit 309b) the low-temperature heat exchanger (“LTX”).

This internal heat exchanger is the “recuperator” (“RCX”). By preheating the fluid medium, a higher post-compressor temperature can be attained at a reasonable pressure ratio. The recuperated PTES 300 includes a recuperator RCX_C in the charging cycle 303 and a recuperator RCX_G in the generating cycle 306. Note that, in most embodiments, the recuperator RCX_C in the charging cycle 303 and the recuperator RCX_G in the generating cycle 306 may be implemented using the same physical device. Note that the PTES 300 of FIG. 3A-FIG. 3B includes many like parts relative to the PTES 100 in FIG. 1A-FIG. 1B and that like parts bear like designations.

As was mentioned above, the configuration of the working fluid circuit 109a, 109b between the charging cycle shown in FIG. 1A and the generating cycle shown in FIG. 1B may be controlled by fluid flow valves. Although such control systems are readily known to those in the art, one such control system 400 is shown in FIG. 4 for the sake of completeness. The control system 400 may include a plurality of fluid flow valves 405 and a controller 410 sending control signals over electrical lines 415.

The controller 410 includes a processor-based resource 420 that may be, for example and without limitation, a microcontroller, a microprocessor, an Application Specific Integrated Circuit (“ASIC”), an Electrically Erasable Programmable Read-Only Memory (“EEPROM”), or the like. Depending on the implementation of the processor-based resource, the controller 410 may also include a memory 425 encoded with instructions (not shown) executable by the processor-based resource 420 to implement the functionality of the controller 410. Again, depending on the implementation of the processor-based resource 420, the memory 425 may be a part of the processor-based resource 420 or a stand-alone device. For example, the instructions may be firmware stored in the memory portion of a microprocessor or they may be a routine stored in a stand-alone read-only or random-access memory chip. Similarly, in some implementations of the processor-based resource 420—e.g., an ASIC—the memory 435 may be omitted altogether.

Referring now collectively to FIG. 1A-FIG. 1B and FIG. 4, a controller such as the controller 410 may be used to configure the working fluid circuit 109a, 109b between the charging cycle as shown in FIG. 1A and generating cycle shown in FIG. 1B. The controller 410 may send control signals to the fluid flow valves 405 to control the working fluid flow. Thus, to configure the working fluid circuit 109a for the charging cycle 103, the controller 410 controls the fluid flow valves 405 to direct the working fluid to the compression process 115 and the expansion process 121 while diverting the working fluid away from the expansion process 159 and the compression process 153. Conversely, to configure the working fluid circuit 109b for the generating cycle 106, the controller 410 controls the fluid flow valves 405 to direct working fluid to the expansion process 159 and the compression process 153 while diverting the working fluid away from the compression process 115 and the expansion process 127.

Note that, in accordance with usage in the art, the terms “high-temperature” and “low-temperature” in the “high-temperature heat exchange” and the “low-temperature heat exchange” are defined relative to one another. That is, the terms indicate that the heat exchange in the “high-temperature heat exchange” occurs at a temperature higher than the temperature at which the heat exchange in the “low-temperature heat exchange” occurs. Some embodiments may perform a high-temperature heat exchange at 350° C. and a low-temperature heat exchange at 20° C. with differentials (a/k/a approach temperatures) of approximately 5° C. However, the quantification of the temperatures at which these heat exchanges occur will be an implementation specific detail for any given embodiment, as will be the temperature differential of the temperature at which these exchanges occur. In the phrases pertaining to equipment, such as “low-temperature heat exchanger”, “low-temperature reservoir”, “high-temperature heat exchanger”, and “high-temperature reservoir”, the terms indicate the particular heat exchange in which the equipment is used.

Furthermore, the terms “low-temperature heat exchange” and “high-temperature heat exchange”, on their face, imply a single temperature. Those in the art having the benefit of this disclosure will appreciate that there may be different temperatures at various points of the heat exchange. For example, the temperature at the inlet to the heat exchange may be one temperature, the temperature of the medium may be a second temperature, and the temperature at the outlet may be a third temperature. In accordance with the practice in the art, however, the heat exchange may be represented or conceptualized as a single temperature for practical purposes in operation and discussion. The present disclosure, when referencing such a single temperature, generally references the temperature from the storage reservoir entering the respective heat exchanger.

Terms of equivocation such as “about”, “approximately”, etc. relative to any quantity in this disclosure indicates that some deviation from the stated quantity may be tolerated so long as the actual quantity is within some margin for error in which the operation of the overall system achieves some desired level of efficiency. For example, as discussed above, the difference in the temperature at which the low-temperature heat exchange occurs during the generating cycle may be at least about 5° C. less than the temperature at which the low-temperature heat exchange occurs during the charging cycle. However, a difference of +0.1° C. or greater may be experienced because of operational conditions such that the difference may be only 4.9° C. or less. Such a deviation may be tolerated so long as the operation of the overall system achieves some desired level of efficiency. The same is true of any other quantity discussed or disclosed herein. Accordingly, in accordance with the technique disclosed herein, the first low-temperature reservoir (i.e., the low-temperature reservoir of the charging cycle) is, relative to the second low-temperature reservoir (i.e., the low-temperature reservoir of the generating cycle): independently existing, decoupled, and operating at a higher temperature. Either or both of the first and second low-temperature reservoirs may be either an engineered source or a natural reservoir. An engineered source may be, for instance, a contained reservoir or a waste (e.g., low-grade or low value) heat source from another process. A natural reservoir may be, for example, an ambient atmosphere or a geothermal source.

Thus, in a first embodiment, a method for use in a Pumped Thermal Energy Storage System (“PTES”), the method comprises circulating a working fluid through a working fluid circuit; and operating the PTES through a charging cycle and a generating cycle while circulating the working fluid. During the charging cycle, heat is transferred from a first low-temperature thermal reservoir to the working fluid, the first low-temperature thermal reservoir operating at a first temperature. During the generating cycle, heat is transferred from the working fluid to a second low-temperature thermal reservoir. The second low-temperature thermal reservoir exists independently of the first low-temperature thermal reservoir, is decoupled from the first low-temperature thermal reservoir, and operates at a second temperature less than the first temperature.

In a second embodiment, the second temperature in the first embodiment is less than the first temperature by an amount exceeding about 5° C.

In a third embodiment, the second temperature in the second embodiment is about 15° C. less than the first temperature.

In a fourth embodiment, the working fluid in the first embodiment is Carbon dioxide (CO₂).

In a fifth embodiment, the first low-temperature reservoir of the first embodiment is a waste heat source while the second low-temperature reservoir is an ambient atmosphere.

In a sixth embodiment, the first embodiment further comprises configuring the working fluid circuit for the charging cycle and for the generating cycle.

In a seventh embodiment, the charging cycle of the first embodiment further comprises: exchanging heat between the working fluid and a first high-temperature thermal reservoir; a compression process downstream from the low temperature heat exchange and upstream from the high-temperature heat exchange; and an expansion process downstream from the high-temperature heat exchange and upstream from the low temperature heat exchange. Also, the generating cycle further comprises: exchanging heat between the working fluid and a first high-temperature thermal reservoir; an expansion process downstream from the high temperature heat exchange and upstream from the low temperature heat exchange; and a compression process upstream from the high temperature heat exchange and downstream from the low temperature heat exchange.

In an eighth embodiment, the seventh embodiment further comprises recuperating heat from the working fluid in the charging cycle and in the generating cycle.

In a ninth embodiment, the first embodiment further comprises recuperating heat from the working fluid in the charging cycle and in the generating cycle.

In a tenth embodiment, a Pumped Thermal Energy Storage System (“PTES”), comprises: a first low-temperature thermal reservoir; a second low temperature thermal reservoir; and a working fluid circuit through which a working fluid is circulated in operation. The working fluid circuit includes, during a charging cycle, a first low-temperature heat exchanger that, in operation, transfers heat from the first low-temperature thermal reservoir to the working fluid, the first low-temperature thermal reservoir operating at a first temperature. During a generating cycle, the working fluid circuit includes a second low-temperature heat exchanger that, in operation, transfers heat from the working fluid to a second low-temperature thermal reservoir. The second low-temperature thermal reservoir exists independently of the first low-temperature thermal reservoir, is decoupled from the first low-temperature thermal reservoir, and operates at a second temperature less than the first temperature.

In an eleventh embodiment, the second temperature in the tenth embodiment is less than the first temperature by an amount exceeding about 5° C.

In a twelfth embodiment, the second temperature in the eleventh embodiment is about 15° C. less than the first temperature.

In a thirteenth embodiment, the working fluid of the tenth embodiment is Carbon dioxide (CO₂).

In a fourteenth embodiment, the first low-temperature reservoir of the tenth embodiment is a waste heat source while the second low-temperature reservoir is an ambient atmosphere.

In a fifteenth embodiment, the tenth embodiment further comprises a control system programmed to configuring the working fluid circuit for the charging cycle and for the generating cycle.

In a sixteenth embodiment, the control system of the fifteenth embodiment comprises: a plurality of fluid flow valves; a processor-based resource; and a memory. On the memory resides a plurality of instructions that, when executed by the processor-based resource, cause the processor-based resource to configure the working fluid circuit for the charging cycle and the generating cycle.

In a seventeenth embodiment, the working fluid circuit of the tenth embodiment further includes, during the charging cycle: a high temperature heat exchange between the working fluid and a first high-temperature thermal reservoir; a compression process downstream from the low temperature heat exchange and upstream from the high-temperature heat exchange; and an expansion process downstream from the high-temperature heat exchange and upstream from the low temperature heat exchange. During the generating cycle, the working fluid circuit includes: a high temperature heat exchange between the working fluid and a first high-temperature thermal reservoir; an expansion process downstream from the high temperature heat exchange and upstream from the low temperature heat exchange; and a compression process upstream from the high temperature heat exchange and downstream from the low temperature heat exchange.

In an eighteenth embodiment, the seventeenth embodiment further comprises a recuperator recuperating heat from the working fluid in the charging cycle and in the generating cycle during operation.

In a nineteenth embodiment, the high-temperature thermal reservoir of the seventeenth embodiment is a contained reservoir containing a thermal medium selected from the group comprising sand or gravel, concrete, encapsulated phase-change materials, bulk phase-change materials, or a combination thereof.

In a twentieth embodiment, the tenth embodiment further comprises a recuperator recuperating heat from the working fluid in the charging cycle and in the generating cycle during operation.

In a twenty-first embodiment, A Pumped Thermal Energy Storage System (“PTES”) is as shown and described above.

In a twenty-second embodiment, method for use in a Pumped Thermal Energy Storage System (“PTES”) is as shown and described.

Further, as used herein, the article “a” is intended to have its ordinary meaning in the patent arts, namely “one or more.” Herein, the term “about” when applied to a value generally means within the tolerance range of the equipment used to produce the value, or in some examples, means plus or minus 10%, or plus or minus 5%, or plus or minus 1%, unless otherwise expressly specified. Further, herein the term “substantially” as used herein means a majority, or almost all, or all, or an amount with a range of about 51% to about 100%, for example. Moreover, examples herein are intended to be illustrative only and are presented for discussion purposes and not by way of limitation.

Examples in the present disclosure may also be directed to a non-transitory computer-readable medium storing computer-executable instructions and executable by one or more processors of the computer via which the computer-readable medium is accessed. A computer-readable media may be any available media that may be accessed by a computer. By way of example, such computer-readable media may comprise random access memory (“RAM”); read-only memory (“ROM”); electrically erasable, programmable, read-only memory (“EEPROM”); compact disk read only memory (“CD-ROM”) or other optical disk storage, magnetic disk storage or other magnetic storage devices, or any other medium that may be used to carry or store desired program code in the form of instructions or data structures and that may be accessed by a computer. Disk and disc, as used herein, includes compact disc (“CD”) laser disc, optical disc, digital versatile disc (“DVD”), floppy disk and Blu-ray® disc where disks usually reproduce data magnetically, while discs reproduce data optically with lasers.

Note also that the software implemented aspects of the subject matter claimed below are usually encoded on some form of program storage medium or implemented over some type of transmission medium. The program storage medium is a non-transitory medium and may be magnetic (e.g., a floppy disk or a hard drive) or optical (e.g., a compact disk read only memory, or “CD ROM”), and may be read only or random access. Similarly, the transmission medium may be twisted wire pairs, coaxial cable, optical fiber, or some other suitable transmission medium known to the art. The claimed subject matter is not limited by these aspects of any given implementation.

The foregoing description, for purposes of explanation, used specific nomenclature to provide a thorough understanding of the disclosure. However, it will be apparent to one skilled in the art that the specific details are not required in order to practice the systems and methods described herein. The foregoing descriptions of specific examples are presented for purposes of illustration and description. They are not intended to be exhaustive of or to limit this disclosure to the precise forms described. Obviously, many modifications and variations are possible in view of the above teachings. The examples are shown and described in order to best explain the principles of this disclosure and practical applications, to thereby enable others skilled in the art to best utilize this disclosure and various examples with various modifications as are suited to the particular use contemplated. It is intended that the scope of this disclosure be defined by the claims and their equivalents below.

Claims

1. A method for use in a Pumped Thermal Energy Storage System (“PTES”), the method comprising: circulating a working fluid through a working fluid circuit; andoperating the PTES through a charging cycle and a generating cycle while circulating the working fluid, in which: during the charging cycle, transferring heat from a first low-temperature thermal reservoir to the working fluid, the first low-temperature thermal reservoir operating at a first temperature; andduring the generating cycle, transferring heat from the working fluid to a second low-temperature thermal reservoir, the second low-temperature thermal reservoir: existing independently of the first low-temperature thermal reservoir;being decoupled from the first low-temperature thermal reservoir; andoperating at a second temperature less than the first temperature.

2. The method of claim 1, wherein the second temperature is less than the first temperature by an amount exceeding about 5° C.

3. The method of claim 2, wherein the second temperature is about 15° C. less than the first temperature.

4. The method of claim 1, wherein the working fluid is Carbon dioxide (CO2).

5. The method of claim 1, wherein: the first low-temperature reservoir is a waste heat source; andthe second low-temperature reservoir is an ambient atmosphere.

6. The method of claim 1, further comprising configuring the working fluid circuit for the charging cycle and for the generating cycle.

7. The method of claim 1, wherein: the charging cycle further comprises: exchanging heat between the working fluid and a first high-temperature thermal reservoir;a compression process downstream from the low temperature heat exchange and upstream from the high-temperature heat exchange; andan expansion process downstream from the high-temperature heat exchange and upstream from the low temperature heat exchange; andthe generating cycle further comprises: exchanging heat between the working fluid and a first high-temperature thermal reservoir;an expansion process downstream from the high temperature heat exchange and upstream from the low temperature heat exchange; anda compression process upstream from the high temperature heat exchange and downstream from the low temperature heat exchange.

8. The method of claim 7, further comprising recuperating heat from the working fluid in the charging cycle and in the generating cycle.

9. The method of claim 1, further comprising recuperating heat from the working fluid in the charging cycle and in the generating cycle.

10. A Pumped Thermal Energy Storage System (“PTES”), comprising: a first low-temperature thermal reservoir;a second low temperature thermal reservoir; anda working fluid circuit through which a working fluid is circulated in operation, the working fluid circuit including: during a charging cycle, a first low-temperature heat exchanger that, in operation, transfers heat from the first low-temperature thermal reservoir to the working fluid, the first low-temperature thermal reservoir operating at a first temperature; andduring a generating cycle, a second low-temperature heat exchanger that, in operation, transfers heat from the working fluid to a second low-temperature thermal reservoir, the second low-temperature thermal reservoir: existing independently of the first low-temperature thermal reservoir;being decoupled from the first low-temperature thermal reservoir; andoperating at a second temperature less than the first temperature.

11. The PTES of claim 10, wherein the second temperature is less than the first temperature by an amount exceeding about 5° C.

12. The PTES of claim 11, wherein the second temperature is about 15° C. less than the first temperature.

13. The PTES of claim 10, wherein the working fluid is Carbon dioxide (CO2).

14. The PTES of claim 10, wherein: the first low-temperature reservoir is a waste heat source; andthe second low-temperature reservoir is an ambient atmosphere.

15. The PTES of claim 10, further comprising a control system programmed to configure the working fluid circuit for the charging cycle and for the generating cycle.

16. The PTES of claim 15, wherein the control system comprises: a plurality of fluid flow valves;a processor-based resource; anda memory on which resides a plurality of instructions that, when executed by the processor-based resource, cause the processor-based resource to configure the working fluid circuit for the charging cycle and the generating cycle.

17. The PTES of claim 10, wherein the working fluid circuit further includes: during the charging cycle: a high temperature heat exchange between the working fluid and a first high-temperature thermal reservoir;a compression process downstream from the low temperature heat exchange and upstream from the high-temperature heat exchange; andan expansion process downstream from the high-temperature heat exchange and upstream from the low temperature heat exchange; andduring the generating cycle: a high temperature heat exchange between the working fluid and a first high-temperature thermal reservoir;an expansion process downstream from the high temperature heat exchange and upstream from the low temperature heat exchange; anda compression process upstream from the high temperature heat exchange and downstream from the low temperature heat exchange.

18. The PTES of claim 17, further comprising a recuperator recuperating heat from the working fluid in the charging cycle and in the generating cycle during operation.

19. The PTES of claim 17, wherein the high-temperature thermal reservoir is a contained reservoir containing a thermal medium selected from the group comprising sand or gravel, concrete, encapsulated phase-change materials, bulk phase-change materials, or a combination thereof.

20. The PTES of claim 10, further comprising a recuperator recuperating heat from the working fluid in the charging cycle and in the generating cycle during operation.