• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Device and method 1 for storing and returning heat energy by a heat transfer fluid 2 connected to an installation 3 which in turn yields calories to the coolant 2 and then takes heat to the coolant 2, implementing:. a first tank 4 partially containing heat transfer fluid 2 at a high temperature T1 and in part a compressed gas 6,. a second tank 5 partially containing heat transfer fluid 2 at a low temperature T2 and partly compressed gas 6,. means 18 for the heat exchange between the installation 3 and the coolant 2,. a means 8 ensuring the flow of heat transfer fluid 2 between the tanks 4, 5,. at least one means 10, 12 connected to a reservoir 4, 5 for maintaining the compressed gas 6 contained in the tanks 4, 5 at constant pressure.
    公开号:FR3019854A1
    申请号:FR1453231
    申请日:2014-04-11
    公开日:2015-10-16
    发明作者:Idrissi El Ganouni Oussama Cherif
    申请人:FIVES；
    IPC主号:
    专利说明:

    [0001] The invention relates to the field of energy recovery and more particularly to equipment for storing and recovering heat energy. For example, the device according to the invention can make it possible to capture the heat energy produced in an ancillary manner by an industrial process at a given moment and to restore it on demand when this same or another industrial process needs to consume heat energy.
    [0002] The invention is particularly suitable in the case of the industry of storing electrical energy by means of compressed air since it produces thermal energy during the compression phase of the air and consumes thermal energy. in the decompression phase of the compressed air. One of the challenges of this industry is to reinforce the energy efficiency of its process which necessarily involves the delayed use of the heat produced by the compression in order not to use an external heat source. It is thus necessary to carry out a thermodynamic cycle called "adiabatic" which consists in using polytropic compressors, to extract the heat of the compressed air after each stage of compression and to store this heat, the compressed air being stored in a tank. When it is desired to restore electrical energy, the compressed air is extracted from the tank, heated by the heat stored during its compression and expanded through a turbine that drives an electric generator. This "adiabatic" cycle makes it possible not to use additional external heat and presents efficiencies greater than 70% taking into account the recovery of the heat produced during the compression. It emits no direct CO2.
    [0003] On the other hand, adiabatic cycles that allow high yields with conventional compression and expansion machines require the storage of large amounts of heat. Storage with sensible heat, that is to say without change of state, call upon either solids like rock, concrete, sand, graphite or ceramics with the difficulty of dimensioning satisfactory exchangers, either at liquids such as oils or molten salts (fluoride, chloride and nitrate), most of which present certain risks for the environment and storage difficulties. Storage latent heat, that is to say with change of state, are still little used despite an interesting potential. Water, with its very high sensible heat, its good thermal conductivity, the possibility of using it as heat transfer fluid and as heat storage fluid, its low cost and finally its absence of danger for the environment represents a excellent candidate. Its main disadvantage is the high storage pressure required to keep the water in a liquid state if it is at a high temperature. The document WO2012160311 describes a use of water as heat transfer fluid in compressed air energy storage equipment. Although this solution is attractive, it nevertheless has drawbacks in its choice of embodiment: - the use of a single tank to contain the cold heat transfer fluid and the hot heat transfer fluid is not very effective because this system will necessarily tend to s' balance in temperature due to unavoidable thermal bridges - The integration of the heat storage tank in the air storage tank is an expensive design and causes a complete immobilisation of the installation in case of intervention on the heat tank. The present invention aims in particular to overcome the aforementioned drawbacks by providing equipment and a method for heat storage efficiently and without risk to the environment.
    [0004] Thus, according to a first aspect, the subject of the invention is a device for storing and returning heat energy by means of a first heat transfer fluid connected to an installation that alternately transfers calories to the first fluid and then takes calories from the first fluid. The device comprises: - a first heat reservoir partially containing the first fluid at a high temperature and partly a second fluid compressed at a first pressure, - a second heat reservoir partially containing the first fluid at a low temperature below the high temperature of the first tank and part of the second fluid compressed at a second pressure, a main means of heating and cooling, in connection with the installation, in fluid connection with the part containing the first fluid of each of the heat tanks allowing the heat exchange between the installation and the first fluid contained in the heat tanks, a pumping means ensuring the flow of the first fluid between the tanks, at least one regulating means in fluid connection with the heat tanks and allowing to maintain the second fluid contained in the first heat reservoir at the first re pressure and heat in the second reservoir to the second pressure. The heat resulting from the installation, for example an electrical production plant, or any other industrial production, can be captured and stored in the heat storage tanks, then returned to the installation if necessary, and with a increased efficiency.
    [0005] According to one embodiment, the device comprises at least one additional means for heating and cooling, in fluid connection with the part containing the second fluid of each of the heat tanks, allowing the flow of the second fluid between the heat tanks and maintaining the temperature and pressure in the heat tanks. Maintaining a constant temperature in the heat tanks makes it possible to increase the yield. The additional means of heating and cooling can for example use an additional heat transfer fluid to exchange heat with the second fluid. Advantageously, the additional heat transfer fluid is the first fluid, so that the device is economical. In this case, the additional heating and cooling means is for example crossed by an additional duct providing the fluidic connection between the portions of the heat reservoirs containing the first heat transfer fluid, so as to ensure a heat exchange in the additional heating means and cooling between the first fluid and the second fluid. As a variant, the additional means of heating and cooling are combined with the main heating and cooling means allowing the heat exchange between the installation and the first heat transfer fluid. It is thus realized the economy of a heat exchanger, reducing the costs of the device.
    [0006] According to one embodiment, the regulating means comprises a hydraulic pump, using a regulating fluid compatible with the first fluid of a source to maintain the constant pressure in the heat tanks. For this purpose, for example, the regulating means comprises a regulator reservoir containing regulating fluid and the second fluid under the second pressure and at low temperature, said regulator reservoir being maintained under substantially constant pressure by the hydraulic pump using the regulating fluid. According to a second aspect, the invention proposes a heat recovery system comprising a device as presented above and an installation, such as an installation for producing electrical energy. The installation then comprises a compressed air energy storage unit comprising compressed air compression means, a compressed air storage tank, compressed air expansion means and compressed air storage means. fluidic connection means between firstly the compression and expansion means and secondly the storage tank for the compressed air, and in that the expansion means of the compressed air and the compression means pass through main means of heating and cooling for the heat exchange between the installation and the second fluid.
    [0007] The storage tank may include a portion containing first fluid in fluid connection with the third fluid containing portion of the regulator reservoir. According to a third aspect, the invention proposes a method for storing and restoring heat energy by a heat transfer fluid according to the device as presented above, connected to an installation, which in turn yields calories to the heat transfer fluid and then takes heat transfer fluid, characterized in that: in the heat energy storage phase: - the pumping means circulates the heat transfer fluid from the second reservoir to the first reservoir, - the first heat transfer fluid captures the heat of the installation during its passage in the main heating and cooling means for the heat exchange between the installation and the coolant, - the second compressed fluid contained in the first tank is discharged concomitantly with the first heat transfer fluid inlet in this first reservoir to maintain it at first pressure, - second compressed fluid at low temperature rature is introduced into the second tank concomitantly with the first coolant outlet of said second tank to maintain it at the second pressure; in the heat energy return phase: the pumping means circulates the first heat transfer fluid from the first reservoir to the second reservoir, the first heat transfer fluid delivers its heat to the installation during its passage in the main heating means. and cooling for the heat exchange between the installation and the first heat transfer fluid, - the second compressed fluid of the second tank is discharged concomitantly with the inlet of the first heat transfer fluid in the second tank to maintain it at the second pressure - The second fluid compressed at a high temperature is introduced into the first reservoir concomitantly with the first heat transfer fluid outlet of the first reservoir to maintain it at the first pressure. According to one embodiment, the pressure in the heat tanks is kept constant in the device by the introduction or the evacuation of the second fluid compressed by the regulating means and by the circulation between the heat reservoirs of the second compressed fluid placed in temperature by means of heating and cooling.
    [0008] The features and advantages of the invention will appear on reading the description which follows, given solely by way of example, and not by way of limitation, with reference to the following appended figures: FIG. 1 is a schematic representation of the device according to a first exemplary embodiment of the invention, - Figure 2 is a schematic representation of the device according to a second embodiment of the invention comprising a single source of gas, - Figure 3 is a schematic representation of an alternative embodiment. of the device shown in FIG. 2, - FIG. 4 is a representation of another variant embodiment of the invention in which the calories of the device are used to vary the temperature of the gas; FIG. 5 represents an embodiment of the invention with a single heat exchanger, - Figure 6 shows a closed circuit embodiment according to the invention, - Figure 7 is a representation of an embodiment of the invention using a fluid as a pressure variator, and - the Figure 8 shows a general diagram of the invention combined with a compressed air energy storage facility.
    [0009] Hereinafter a detailed description of several embodiments of the invention with examples and references to the drawings. Figure 1 shows a first example of implementation of the invention of a heat recovery system. The energy storage and return device 1 is composed of two heat reservoirs 4, 5, namely a first heat reservoir 4 and a second heat reservoir 5. Each tank 4, 5 of heat comprises a portion containing a first fluid 2 and a portion containing a second fluid 6. The first fluid 2 is heat-carrying, and is intended to store heat. This is for example a liquid. The second fluid 6 is preferably compressible and may be, as in the example shown, a gas. In what follows, we will speak of storage liquid 2 to designate the first fluid and gas 6 to designate the second fluid. The two heat tanks 4, 5 are in fluid connection by a conduit 7 said main located at the parts of the tanks containing the storage liquid 2, so that the parts of the tanks 4, 5 of heat containing the liquid 2 storage communicate with each other. A first means 18 for heating and cooling, said main, is placed on the main conduit 7, between the two tanks 4, 5, heat so that the storage liquid 2 flowing in the main conduit 7 between the two tanks 4 5 heat passes through the main heat exchanger 18. The main means 18 is for example a heat exchanger, and will be considered as such in the following description. The main heat exchanger 18 is connected to an installation 3, to allow to give heat or take heat to the installation 3. The storage liquid 2 of the first tank 4 is at a first so-called high temperature T1 of the order of 250 ° C and the gas 6 contained in the first tank 4 is compressed at a pressure P1 of the order of 40 bar. The storage liquid 2 of the second tank 5 is at a second so-called low temperature T2, lower than the high temperature T1 of the first tank 4, of the order of 25 ° C and the gas 6 contained in this tank is compressed at a pressure P2 of the order of 40 bars, substantially equal to the pressure P1 of the first tank 4. For the sake of representation in the figures, the angled hatches represent the storage liquid 2 at the high temperature T1 and the horizontal hatches represent the storage liquid 2 at a low temperature T2. The placing of the coolant 2 under a constant pressure P1 makes it possible to keep it in the first tank 4 in liquid form even at high temperatures T1. The storage liquid 2 flows between the tanks 4 and 5 of heat by means of a pumping means 8 of the hydraulic pump type, preferably positioned between the main heat exchanger 18 and the second tank 5, on the fluid side at the low end. temperature T2 the lowest. Indeed, the low temperature operating constraints are more favorable for the pump 8 than at high temperature. The hydraulic pump 8 is indifferently a two-way pump or two pumps having an opposite direction of flow positioned on two separate ducts (not shown). According to the example of FIG. 1, each part of the tanks 4, 5 of heat containing the compressed gas 6 is in fluidic connection via a conduit, respectively 9 and 11, of gas to a means, respectively 10 and 12, regulator providing gas 6 at a given pressure, respectively P1 and P2, and at a temperature compatible with the internal environment of each tank 4 and 5 of heat. The temperature of the gas 6 can be adapted by means of heating and cooling 131 and 132 arranged the conduits 9 and 11 of gas. A first regulating means 10 can supply the first reservoir 4 with gas 6 under pressure P1 and preferably with a high temperature T1. The second regulator means 12 can supply the second reservoir 5 with pressurized gas 6 and preferably with a low temperature T2. If necessary, and depending on the temperature of the gas 6 delivered by the means 9 and 10, the gas 6 is heated or cooled to reach a temperature close to the temperature inside the tanks 4 and 5. When the installation 3 needs to cool and therefore to give calories, the low temperature storage liquid T2 of the second tank 5 is sent by the pump 8 to the main heat exchanger 18. The calories of the plant 3 are transmitted to the low temperature storage liquid T2 in the main heat exchanger 18. The storage liquid 2 thus passes to the high temperature T1 and fills the first tank 4. The gas 6 of the first tank 4 is discharged to the first regulator means 10 in order to maintain a pressure P1 in the first tank 4. On the contrary, the gas 6 under pressure P2 and at a low temperature T2 is introduced into the second tank 5 to compensate the flow of the storage liquid 2 from the second tank 5 to the first tank 4. The pressure of the two tanks 4, 5 of heat remains maintained pressure, P1 and P2 respectively, constant through the presence of means 10 and 12 regulators that can alternate injection or withdrawal of gas 6.
    [0010] Alternatively, when the installation 3 has a need for heat, the pump 8 circulates the liquid storage 2 from the first tank 4 to the second tank 5 through the main heat exchanger 18. In the main heat exchanger, the storage liquid 2 transmits its calories to the installation 3. The high temperature T1 at the inlet of the main heat exchanger 18 disappears in favor of the low temperature T2 at the outlet of the heat exchanger 18 Main. By flowing from the first tank 4, the storage liquid 2 fills the second tank 5 pushing the gas 6 under pressure to the second means 12 regulator. In the first tank 4, a supply of gas from the first regulating means 10 keeps a pressure P1 after the flow of the storage liquid 2. The pressure of the two tanks 4, 5 of heat is maintained at pressure P1 and P2 thanks to the presence of the means 10 and 12 regulators which can alternate injection or withdrawal of gas. Figure 2 illustrates another non-limiting example of implementation of the invention. The device 1 is composed as before of two tanks 4 and 5 of heat, a main heat exchanger 18 itself in connection with the installation 3, a hydraulic pump 8 and a main conduit 7 to make alternately circulating the storage liquid 2 contained in the tanks 4 and 5 of heat. The heat tanks 4 and 5 also contain compressed gas 6. The heat transfer fluid 2 and the compressed gas 6 of the first heat reservoir 4 are at a high temperature T1 of the order of 250 ° C. and a pressure P1 of order of 40 bars. The storage liquid 2 and the compressed gas 6 of the second heat reservoir 5 are at a low temperature T2 of the order of 25 ° C. and a pressure P2 of the order of 40 bars. According to the example of FIG. 2, a conduit 9 'of gas provides the fluidic connection between an additional means 13 for heating and cooling and the parts of each of the tanks 4 and 5 of heat containing the compressed gas 6. The means 13 additional heating and cooling is for example a heat exchanger, and will be considered as such in the following description. The additional heat exchanger 13, specific to the gas 6, is traversed by an additional heat transfer fluid 14 via an additional duct 15. A regulator means 12 ', which may be unique according to the example of FIG. 2, is connected to the conduit 9' of gas via a regulator conduit 110 between the additional heat exchanger 13 and the second reservoir 5. The means 12 ' In the injection mode, it delivers gas 6 under pressure P2 and low temperature T2, via a pipe 110, to the part of the second tank 5 containing the gas 6. During the recovery of the heat coming from the installation 3 at the main heat exchanger 18, the storage liquid 2 flows from the second tank 5 to the first tank 4. The gas 6 of the first tank 4 is sent to the second tank 5 through the conduit 9 'of gas. Since the gas coming from the first tank 4 is at a high temperature T1, it is necessary to cool it in the additional heat exchanger 13 by virtue of the additional heat transfer medium 14 so that it reaches a temperature close to the gas 6 at the low temperature T2 of the second tank 5. According to Charles' law, at constant pressure, the volume occupied by a certain mass of perfect gas varies proportionally with the absolute temperature. Thus, the gas 6 occupies more volume in the first tank 4 with a high temperature T1 than in the second tank 5 with a low temperature T2. During the passage of the gas 6 in the additional heat exchanger 13, its volume will decrease and it will be necessary to compensate for this loss of volume by the addition of gas 6 to the low temperature T2 from the means 12 'regulator. Conversely, during the return of heat to the installation 3, the heat transfer fluid 2 passes from the first tank 4 to the second tank 5 via the main heat exchanger 18 and the pump 8. that the density of gas is greater at low temperature, only a part of the low temperature gas 6 T2 is transferred to the first tank 4 after being carried, thanks to the exchanger 13 and the heat transfer fluid 14, at a temperature close to the high temperature T1 compatible with the temperature of the first tank 4. The other part of the gas 6 is expelled from the second tank 5 to the means 12 'regulator to maintain a constant pressure P1, P2 in the two tanks 4, 5 heat.
    [0011] The regulator means 12 'operating here with a gas at low temperature T2 and at pressure P2 can be replaced by means 10' regulator operating with a gas pressure P1 and high temperature T1. In this case, the means 10 'regulator will be connected to the first tank 4 of heat in its portion containing the gas 6. This embodiment is visible in Figure 3. The choice of one or the other embodiments corresponding to Figures 2 and 3 is determined by resources available at the facility site that will facilitate one or the other configuration. FIG. 4 illustrates an alternative embodiment of the invention for which the additional heat transfer fluid 14 is the first storage liquid 2 used to heat or cool the gas 6 in the additional heat exchanger 13. The additional duct 15 on which the additional heat exchanger 13 is placed puts in fluid connection the tanks 4 and 5 of heat in their parts containing the storage liquid 2, ensuring the circulation of the storage liquid 2 through the exchanger 13 additional thermal. Means (not shown) of the hydraulic pump type make it possible to circulate the storage liquid 2 in one direction or another in the additional duct 15. During the accumulation of heat in the first heat reservoir 4, a portion of the low temperature storage liquid T2 from the second heat reservoir 5 passes into the additional conduit to the additional exchanger 13. The gas 6 at high temperature T1 pushed by the storage liquid 2 in the accumulation phase passes through the additional heat exchanger 13 and transmits its heat to the low temperature storage liquid T2 from the second heat reservoir 5. The heated storage liquid 2 is reintroduced into the first heat reservoir 4. The gas 6 from the first heat reservoir 4 is cooled in the additional heat exchanger 13 and is introduced into the second low temperature heat reservoir T2. Conversely, in the calorie recovery phase, the cycle is reversed and the storage liquid 2 from the first tank 4 is used to heat the gas 6 from the second tank 5. In each case, a means 12 'low temperature regulator T2 and at pressure P2, as shown, makes it possible to compensate for the losses or the excess pressure in tanks 4 and 5. As a variant, as previously, a regulating means at high temperature T1 and at pressure P1 can replace the means 12 'regulator at low temperature T2 and at pressure P2. Another alternative embodiment of the invention, wherein the additional exchanger 13 is merged with the main exchanger 18, allows the economy of a specific heat exchanger for the gas. In this advantageous variant illustrated in FIG. 5, the conduit 9 'of gas is connected to the part of the tanks 4, 5 containing the gas 6 and passes through the main heat exchanger 18. During the accumulation of heat in the first tank 4, the gas 6 expelled at high temperature T1 cools by passing through the main heat exchanger 18 before compensating for the lack of gas 6 at low temperature T2 in the second tank 5 The means 12 'low temperature regulator T2 low pressure P2 also maintains the pressure by adding gas 6 at low temperature T2. The means for maintaining the pressure of the gas 6 can also be a means at high temperature T1 and pressure P1 (not shown in Figure 5) connected to the first tank 4. The cycle is reversed in the energy recovery phase at the same time. 3. This implementation makes it possible to increase the efficiency of the installation by exploiting all the calories stored in the storage liquid 2 and the gas 6. According to one embodiment, as illustrated in FIG. the means 12 'low temperature regulator T2 and P2 pressure consists of a pressure regulator tank 16 P1, P2 of the order of 40 bar (identical to the pressure of the tanks 4 and 5 of heat) and low temperature T2, containing gas 6 and a fluid 200 regulator. An additional hydraulic pump 17 makes it possible to pressurize the reservoir 16 with the control fluid 200 drawn from a source 19 of fluid at atmospheric pressure or at any pressure. Advantageously, the fluid 200 regulator of the source 19 is compatible with the storage liquid 2 contained in the tanks 4 and 5 of heat due to the exchange of saturating vapors between the second tank 5 and the tank 16 regulator. In other words, the regulating fluid 200 behaves similarly to the storage liquid 2 with respect to temperatures and phase change pressures. For example, the fluid 200 regulator is of the same nature as the liquid 2 storage.
    [0012] Depending on the case, the source 19 is oxygen-tight or open to the open air. The additional hydraulic pump 17 is indifferently a two-way pump or two pumps having an opposite direction of circulation placed on two separate ducts (not shown). In the heat accumulation phase, the gas compensation 6 in the second tank 5 during the flow of the low temperature storage liquid T2 is performed by the injection of gas 6 from the tank 16. The pump 17 additional fills the tank 16 regulator with the fluid 200 regulator pumped into the source 19 to maintain a pressure P2 in said tank 16 regulator and push the gas 6 to the second tank 5 via a conduit 110 regulator. The temperature being the same in the second tank 5 and in the tank 16 regulator, it is therefore not necessary to pass the fluid 200 regulator in a heat exchanger. In the heat recovery phase, the gas 6 expelled from the second tank 5 is distributed on the one hand to the first tank 4 after being heated and on the other hand to the tank 16 regulator. In this reservoir, a portion of the fluid 200 regulator will be discharged to the source 19 to maintain a pressure P2 in the tank 16 regulator.
    [0013] The sizing of the tank 16 regulator is proportional to the size of the tanks 4 and 5 of heat. Advantageously, the regulator tank 16 must make it possible to contain at least the volume of gas 6 of the second tank 5 at low temperature T2 minus the volume of gas 6 of the first tank 4 at high temperature T1, at constant pressure. By passing from the first tank 4 at high temperature T1 to the second T2 tank 5 at low temperature T2, the gas 6 decreases its volume ratio (Ti). T2 must be compensated for this loss of volume by adding a volume (1- T1). The minimum volume of the regulator tank 16 will be (Cr - T2 Ti) * V, where V is the volume of the tanks 4 and 5. The regulator tank 16 is about two times smaller than the tanks 4 and 5.
    [0014] This implementation is particularly advantageous because it makes it possible to turn the device 1 in a closed circuit of gas and fluid. This makes sense when the tanks 4, 5 and 16 are made of steel, the gas 6 is air containing a portion of oxygen and the storage liquid 2 is water. Indeed, the dissolution of oxygen in water remains substantial in hot water at high pressure which increases the phenomenon of corrosion. In the case of an open system, the supply of oxygen is renewed at each cycle. In a closed circuit as shown in FIG. 6, the oxygen, initially introduced with the air into the tanks 4, 5 and 16, will be exhausted by slightly oxidizing the steel of the tanks. No longer having outside air supply since the system is in a closed circuit, the oxygen disappears, thus stopping the corrosion. It is also possible to use air / water separators (not shown) in the regulator tank 16 to prevent the contamination of the air of the hot water circuit with dissolved oxygen in the water. According to another embodiment of the invention visible in FIG. 7, the regulator means 12 'consists of an additional hydraulic pump 17 in fluid connection with a source 19 of storage liquid 2 and connected by a regulator conduit 110 to the second reservoir 5. During the various phases of storage and return of heat energy, the means 12 'regulator regulates the pressure of the tanks 4 and 5 of heat by injection or withdrawal of liquid 2 storage. In the storage phase or heat capture from the installation 3, the storage liquid 2 passes from the second tank 5 to the first tank 4 pushing the gas 6 towards the second tank 5. This gas 6 initially at high temperature T1 is cooled in the additional heat exchanger 13, losing its volume and not being able to compensate for the volume of storage liquid 2 discharged from the second tank 5. To compensate for this lack of volume and therefore the drop in pressure, the pump 17 injects liquid 2 storage in the second tank 5 and maintains the pressure P2. Conversely, in the heat destocking phase, the high temperature storage liquid T1 of the first tank 4 flows towards the second tank 5 through the main heat exchanger 18. The low temperature gas 6 of the second tank 5 is expelled to the first tank 4. By passing through the heat exchanger 13, the gas 6 heats up and expands. To compensate for the expansion of the gas 6 during its heating and maintain a pressure P1 and P2 in the tanks 4 and 5 of heat, a portion of the cooled storage liquid 2 is withdrawn by the means 12 'regulator. The storage liquid 2 withdrawn from the tanks 4, 5 of heat is released into the source 19.
    [0015] The invention finds a particularly suitable application when the installation 3 is a unit of energy storage by means of compressed air visible in FIG. 8. According to this embodiment, the storage of energy by means of compressed air is done at constant pressure with liquid storage 2, which is according to the example the same as the fluid 2 for storage tanks 4, 5 of heat, provided by a hydraulic pump 25, other than the hydraulic pump 8 of the device 1 storage and return of energy, in a tank 22 of compressed air. In the energy accumulation phase, a compression means 20 compresses air that heats up at high temperature T1. The hot air conveyed by a pipe 23 transmits its calories by passing through the main heat exchanger 18 and the device 1 stores the heat energy in the first tank 4. The compressed air is then stored at low temperature T2 and at a low temperature. P3 pressure of the order of 60 bars in the tank 22 of compressed air. The liquid 2 for storage of the compressed air reservoir 22 is ejected by ejection ducts 24 and 241 to partially fill the regulator reservoir 16 which retains a pressure P2 and for another part which is discharged into the source 19 of the fluid. The gas 6 of the regulator tank 16 is transferred to the second tank 5 via the regulator pipe 110 to compensate the flow of the storage liquid 2 towards the first tank 4. By filling up with storage liquid 2, the first tank 4 evacuates the gas 6 to the second tank 5. In this example, the heat exchange between the various gas circuits and the fluids is via the main heat exchanger 18 but could also be done in different heat exchangers. The advantage of this solution is that it operates in an isothermal way little or more caloric losses inherent in the equipment used.
    [0016] In the expansion phase of the compressed gas in the reservoir 22 of compressed air, the compressed air is heated through the device 1 before going into a turbine 21 to produce electricity. This reheating makes it possible to compensate for the cooling generated by the decompression and increases the efficiency of the turbine 21. When the liquid 2 for storing the first tank 4 flows to the second tank 5, the storage liquid 2 transmits its calories to the tank 1. compressed air from the reservoir 22 of compressed air and the gas 6 evacuated from the second tank 5 by the effect of filling said second tank 5 in liquid 2 storage. Part of the gas 6 of the second tank 5 is transmitted to the regulator tank 16 which will discharge its own storage liquid 2 preferably towards the tank 22 of compressed air and then towards the source 19 by one of the ejection ducts 241. The pressure of the regulator reservoir 16 thus contributes to maintaining the pressure of the compressed air reservoir 22 by less stressing the hydraulic pump 25 of the installation 3 to obtain a high pressure in the compressed air reservoir 22 compatible with the desired efficiency for the turbine 21.
    [0017] Without limitation, the storage liquid 2 may be oil, water or any other heat transfer fluid remaining liquid at different temperatures defined by the different operating cycles of the invention. In the case of the use of water, it is optionally treated against corrosion, for example with the addition of a calcium-based solution. Water has the advantage of being a good heat transfer vector, available at a lower cost and easily recyclable. The gas 6 is preferably air but may also be a neutral gas or nitrogen in the tanks 4, 5 of heat and the tank 16 regulator. One way to limit corrosion within the heat tanks 4, 5 and the regulator tank 16 is to use nitrogen and to add an oxygen scavenger catalyst (not shown) to the gas pipe 9 '. . This catalyst makes it possible to trap oxygen that has escaped from the water 2. It is also possible to fill the first tank 4 by burning compressed air with a hydrogen burner. The chemical reaction would give water and nitrogen and already at a high temperature. The examples of embodiments above were made with a pressure P1 and P2 of the order of 40 bars in the tanks 4, 5 of heat and the tank 16 regulator. The pressure to be used is a function of the operating temperature of the installation 3. In the case of a storage unit of energy using compressed air, the compression of the air generates a temperature of the order of 250 ° C. A pressure of 40 bar keeps the water heated to around 250 ° C below its boiling point. It is therefore possible to use higher pressures in the tanks 4, 5 of heat and the tank 16 regulator if the installation 3 operates at temperatures above 250 ° C. For example, for operating temperatures of 275 ° C and 324 ° C, the respective pressures will be 60 bar and 120 bar. Similarly, the pressure P3 of the reservoir 22 of compressed air may be more or less important (40, 60, 120 bar) depending on the recommendations of the turbine 21 and the compressor 20 and also for the sake of the cost of purchasing the tank 22 of compressed air. Indeed, a tank for 120 bars is more expensive because of the physical constraints exerted by the pressure. For best performance, the first tank 4 and the main pipe 7 are thermally insulated. Despite this isolation, it is possible to add additional heating means (not shown) to reach or maintain a high temperature in the first tank 4. All the ducts 7, 9, 11, 110, 15, 23, 24, 241 provide the fluid connection between the different equipment, and are equipped with valves or valves to open or close these conduits on demand to let the gas 6 or liquid 2 storage, or stop their flow.
    权利要求:
    Claims (12)
    [0001]
    REVENDICATIONS1. Device (1) for storing and returning heat energy by a first heat transfer fluid (2) connected to an installation (3) which in turn transfers calories to the first fluid (2) and then takes calories from the first fluid (2), characterized in that it comprises: A first heat reservoir (4) partially containing first fluid (2) at a high temperature (T1) and partly a second fluid (6) compressed at a first pressure (P1), A second heat reservoir (5) partially containing the first fluid (2) at a low temperature (T2) lower than the high temperature (T1) of the first reservoir (4) and in part the second fluid (6) compressed to a second pressure (P2), means (18) for heating and cooling, in connection with the installation (3), in fluid connection with the portion containing the first fluid (2) of each of the reservoirs (4, 5) heat exchange for the heat exchange between the plant (3) and the first fluid (2) contained in the tanks (4, 5) of heat, means (8) for pumping ensuring the flow of the first fluid (2) between the tanks (4, 5) heat, At least one means (10, 12, 12 ') regulator in fluid connection with the heat reservoirs (4, 5) and for holding the second fluid (6) contained in the first heat reservoir (4) at the first pressure (P1) and in the second tank (5) of heat at the second pressure (P2).
    [0002]
    2. Device (1) according to claim 1, comprising at least one additional means (13) for heating and cooling, in fluid connection with the portion containing the second fluid (6) of each of the tanks (4, 5) of heat , allowing the flow of the second fluid (6) between the heat reservoirs (4, 5) and maintaining the temperature (T1, T2) and the pressure (P1, P2) in the reservoirs (4, 5) of heat.
    [0003]
    3. Device (1) according to claim 2, characterized in that the means (13) additional heating and cooling uses an additional heat transfer fluid (14) for exchanging heat with the second fluid (6).
    [0004]
    4. Device (1) according to claim 3, characterized in that the additional fluid (14) coolant is the first fluid (2).
    [0005]
    5. Device (1) according to claims 4, characterized in that the means (13) additional heating and cooling is traversed by a conduit (15) providing the fluidic connection between the parts of the tanks (4, 5) of heat containing the first fluid (2) coolant, so as to provide heat exchange in the means (13) additional heating and cooling between the first fluid (2) and the second fluid (6).
    [0006]
    6. Device (1) according to claims 4, characterized in that the means (13) additional heating and cooling is merged with the main heat exchanger (18) for heat exchange between the installation (3) and the first heat transfer fluid (2).
    [0007]
    7. Device (1) according to any one of the preceding claims, characterized in that the means (10, 12, 12 ') regulator comprises a hydraulic pump (17), using a fluid (2, 200) regulator compatible with the first fluid (2) of a source (19) for maintaining the constant pressure in the heat tanks (4, 5).
    [0008]
    8. Device (1) according to claim 7 characterized in that the means (10, 12, 12 ') regulator comprises a reservoir (16) containing regulator fluid (200, 2) and the second fluid (6) under the second pressure (P2) and low temperature (T2), said reservoir (16) being maintained under substantially constant pressure by the hydraulic pump (17) using the fluid (200, 2) regulator.
    [0009]
    9. Heat recovery system comprising a device (1) according to any one of the preceding claims and an installation (3), characterized in that the installation (3) comprises an energy storage unit by means of compressed air comprising means (20) for compressing compressed air, a reservoir (22) for storing compressed air, means (21) for expanding the compressed air and means (23, 230, 231 ) of fluid connection between on the one hand the means (20, 21) for compression and expansion and on the other hand the reservoir (22) for storing compressed air, and in that the means (21) for expansion compressed air and the compression means (20) pass through the main heat exchanger (18) allowing the heat exchange between the installation (3) and the second fluid (2).
    [0010]
    10. System according to claim 9, comprising a device according to claim 8, characterized in that the storage tank (22) comprises a portion containing first fluid (2) in fluid connection with the portion containing the third fluid (2, 200 ) of the reservoir (16) regulator.
    [0011]
    11. A method for storing and returning heat energy by a heat transfer fluid (2) pelen-lemis implemented in a device described according to any preceding claim connected to an installation (3) which alternately yields calories to the fluid coolant (2) then takes heat to the coolant (2), characterized in that: In heat storage phase: - the means (8) for pumping circulates the coolant (2) of the second tank (5). ) to the first reservoir (4), - the first heat transfer fluid (2) captures the heat of the installation (3) during its passage through the means (18) main heating and cooling for the heat exchange between the l installation (3) and the coolant (2), - the second compressed fluid (6) contained in the first reservoir (4) is discharged concomitantly with the inlet of the first coolant (2) in this first reservoir (4) to maintain this one at the first pressure (P1), - the second compressed fluid (6) at the low temperature (T2) is introduced into the second reservoir (5) concomitantly with the first heat transfer fluid outlet (2) of the second reservoir (5) to maintain it at the second pressure (P2); In the heat energy recovery phase: the pumping means (8) circulates the first heat transfer fluid (2) from the first reservoir (4) to the second reservoir (5), the first heat transfer fluid (2) delivers its heat to the installation (3) during its passage in the means (18) for heating and cooling allowing the heat exchange between the installation (3) and the first coolant (2), - the second compressed fluid (6) the second tank (5) is discharged concomitantly with the inlet of the first heat transfer fluid (2) in the second tank (5) to maintain it at the second pressure (P2), - the second compressed fluid (6) ) at a high temperature (T1) is introduced into the first reservoir (4) concomitantly with the first heat transfer fluid outlet (2) of the first reservoir (4) to maintain it at the first pressure (P1).
    [0012]
    12. A method according to claim 11 characterized in that the pressure (P1, P2) in the tanks (4, 5) of heat is kept constant in the device by the introduction or discharge of second compressed fluid (6) by the means (10, 12) regulating and circulating between the heat reservoirs (4, 5) of the second compressed fluid (6) which is heated (T1, T2) by means (131, 132, 13, 18) of heating and cooling.
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    同族专利:
    公开号 | 公开日
    FR3019854B1|2019-04-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR1026752A|1950-06-06|1953-05-04|Device for using the heat energy of water|
    NL7708896A|1976-08-13|1978-02-15|Bbc Brown Boveri & Cie|DEVICE FOR STORING AND USING ENERGY.|
    US20120297761A1|2010-03-17|2012-11-29|Alexander Anatolyevich Strognaov|Method of conversion of heat into fluid power and device for its implementation|CN110573714A|2017-04-26|2019-12-13|株式会社神户制钢所|compressed air storage power generation device and compressed air storage power generation method|
    WO2020160635A1|2019-02-08|2020-08-13|Hydrostor Inc.|A compressed gas energy storage system|
    US10760739B2|2017-02-01|2020-09-01|Hydrostor Inc.|Hydrostatically compensated compressed gas energy storage system|
    EP3583321A4|2017-02-14|2020-11-25|Azelio AB|Methods of pumping heat transfer fluid in thermal energy storage systems|
    US11274792B2|2018-01-31|2022-03-15|Hydrostor Inc.|Thermal storage in pressurized fluid for compressed air energy storage systems|
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    2021-03-23| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1453231A|FR3019854B1|2014-04-11|2014-04-11|DEVICE FOR STORING AND RESORTING CALORIFIC ENERGY BY A CONSTANTLY-PRESSURIZED CALOPORATOR FLUID|
    FR1453231|2014-04-11|FR1453231A| FR3019854B1|2014-04-11|2014-04-11|DEVICE FOR STORING AND RESORTING CALORIFIC ENERGY BY A CONSTANTLY-PRESSURIZED CALOPORATOR FLUID|
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