JP6649448B2 - Compressed fluid storage power generation device and power generation method thereof - Google Patents

Description

The present invention relates to a compressed fluid storage power generation device and a power generation method thereof .

  Patent Literature 1 discloses that a compressed gas whose heat is recovered by a heat exchanger disposed downstream of a compressor is stored in a compressed gas storage device, and the gas extracted from the storage device is heated by the recovered heat to generate power. A compressed air energy storage system for supplying a generator is disclosed.

  In this system, the heat of the compressed gas of the compressor is recovered by the high-temperature heat exchanger and the low-temperature heat exchanger, but in each case only the same compressed gas heat is recovered. Heat recovery from the heat source is not considered.

JP-T-2013-536357A

An object of the present invention is to improve power generation efficiency by reusing heat of a low-temperature heat source in a compressed fluid storage power generation device and a power generation method thereof.

According to a first aspect of the present invention, there is provided a compression step of compressing a working fluid, a pressure accumulating step of storing the compressed working fluid, and a low-temperature process of recovering heat generated by power loss, heat dissipation loss or mechanical loss to a low-temperature heat medium. A heat recovery step, a low-temperature heating step of heating the stored working fluid by heat exchange with heat recovered by the low-temperature heat medium, and a power generation step of generating electricity with a generator driven by a driving force of the stored working fluid. And a power generation method for a compressed fluid storage power generation device.

According to this method, the working fluid can be heated in the low-temperature heating step by the heat recovered by the low-temperature heat recovery unit, so that the thermal efficiency can be improved. Therefore, in the power generation method of the compressed fluid storage power generation device, it is possible to improve the power generation efficiency by reusing the heat of the low-temperature heat source. That is, in the power generation method of the compressed fluid storage power generation device, it is possible to minimize heat dissipated due to power loss, heat radiation loss, or mechanical loss without being used for power generation, thereby improving thermal efficiency and power generation efficiency.

  The method further includes: a high-temperature heat recovery step of recovering heat from the compressed working fluid to a high-temperature heat medium; and a high-temperature heating step of heating the stored working fluid by the heat recovered to the high-temperature heat medium. The heating step may heat the working fluid sent to the high-temperature heating step.

  According to this method, the working fluid stored in the pressure accumulator in the high-temperature heating step can be heated by the heat recovered from the working fluid flowing from the compressor body to the pressure accumulating section in the high-temperature heat recovery step, thereby improving thermal efficiency. be able to. Further, since the working fluid sent to the high-temperature heat recovery step is heated (preheated) by the low-temperature heating step, the thermal efficiency can be further improved.

  In the method, the low-temperature heating step may heat the working fluid before compression.

  According to this method, the temperature of the working fluid compressed in the compression step can be increased by heating the working fluid before compression in the low-temperature heating step. Therefore, the temperature of the high-temperature heat medium recovered from the working fluid compressed in the high-temperature heat recovery step can be increased.

  According to a second aspect of the present invention, there is provided a compressor for compressing a working fluid, a pressure accumulator for storing the compressed working fluid, and a low-temperature heat transfer medium for transferring heat generated by power loss, heat radiation loss, or mechanical loss of a low-temperature heating unit. A low-temperature heat recovery unit that recovers the working fluid stored in the pressure accumulating unit, and a low-temperature heating unit that heats the working fluid by heat exchange with a low-temperature heat medium that has recovered heat in the low-temperature heat recovery unit; A generator driven by a driving force of a working fluid.

  According to this configuration, the working fluid can be heated by the low-temperature heating unit by the heat recovered by the low-temperature heat recovery unit, so that the thermal efficiency can be improved. Therefore, in the compressed fluid storage power generation device, the power generation efficiency can be improved by reusing the heat of the low-temperature heat source. That is, in the compressed fluid storage and power generation device, heat that is not used for power generation and is wasted due to power loss, heat radiation loss, or mechanical loss can be minimized, and thermal efficiency can be improved and power generation efficiency can be improved.

  The compressed air storage power generation device includes a high-temperature heat recovery unit that recovers heat from the compressed working fluid that flows toward the pressure storage unit, and a heat that recovers the working fluid stored in the pressure storage unit by the high-temperature heat recovery unit. And a high-temperature heating unit configured to heat the working fluid to be sent to the high-temperature heat recovery unit.

  According to this configuration, the working fluid stored in the pressure accumulating section can be heated by the high temperature heating section with the heat recovered from the working fluid flowing from the compressor body to the pressure accumulating section in the high temperature heat collecting section, so that the thermal efficiency is improved. be able to. Further, since the working fluid sent to the high-temperature heat recovery unit is heated (preheated) by the low-temperature heating unit, the thermal efficiency can be further improved.

  In the compressed air storage power generation device, the low-temperature heating unit may be provided so as to heat the working fluid sucked into the compressor.

According to this configuration, the temperature of the working fluid compressed by the compressor can be increased by heating the working fluid sucked into the compressor by the low-temperature heating unit. Therefore, the temperature of the high-temperature heat medium recovered from the working fluid compressed by the high-temperature heat recovery section can be increased.

According to the present invention, in the compressed fluid storage power generation apparatus and the power generation method, power loss, the heat radiation loss or heat generated by the mechanical loss, it is possible to heat the work moving fluid, by reusing the heat of the low-temperature heat source The power generation efficiency can be improved.

FIG. 1 is a schematic diagram showing a compressed fluid storage power generation device according to a first embodiment of the present invention. FIG. 2 is a diagram showing a low-temperature heat medium system of the compressed fluid storage and power generation device according to the first embodiment. FIG. 2 is a perspective view of a unit including the compressor and the high-temperature heat recovery unit according to the first embodiment. The perspective view of the cooler in which the intercooler and the aftercooler were integrated. The side view of the intercooler and the aftercooler with the cover removed. FIG. 3 is a perspective view of a heater in which a preheater and an interheater are integrated. FIG. 2 is a perspective view of a unit including the generator according to the first embodiment and a high-temperature heating unit. The schematic diagram of the casing of the inverter or the converter provided with the heat sink structure. The top view which shows the cooling jacket of the casing of a motor or a generator main body. Sectional drawing which shows the cooling jacket of the compressor main body or the casing of an air turbine. The schematic diagram showing the compression fluid storage power generation device concerning a 2nd embodiment of the present invention. The figure showing the low-temperature heat carrier system of the compressed fluid storage power generator concerning a 2nd embodiment. The schematic diagram showing the compression fluid storage power generator concerning a 3rd embodiment. The figure showing the low-temperature heat carrier system of the compressed fluid storage power generator concerning a 3rd embodiment. The top view showing the heat storage tank group of the compressed fluid storage power generator concerning a 4th embodiment. The front view showing the heat storage tank group of the compressed fluid storage power generator concerning a 4th embodiment. The top view showing the modification of the heat storage tank group of the compressed fluid storage power generator concerning a 4th embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(1st Embodiment)
FIG. 1 shows a compressed fluid storage power generation device 10 according to a first embodiment of the present invention. FIG. 2 shows a low-temperature heat medium system of the compressed fluid storage power generation device 10 according to the first embodiment. The compressed fluid storage and power generation device 10 compresses air, which is a working fluid, when the working fluid is compressed by the compressor 11, stores the compressed air in the pressure storage tank (pressure storage unit) 12, and stores the compressed air when the power is generated by the power generator 13. This is a power generator that supplies compressed air stored in the tank 12 to the generator 13 to generate power. In the compressed fluid storage and power generation device 10, heat is recovered by the high-temperature heat recovery unit (intercooler 23, aftercooler 25) from the air flowing from the compressor main bodies 22 and 24 to the pressure accumulator tank 12, and the heat thus recovered is used. Then, the air flowing into the expanders 28 and 32 is heated by the high-temperature heating unit (the pre-heater 27 and the inter-heater 31). In addition, compression is performed by heat from the low-temperature heat generating portion, which is heat (recovery heat) such as power loss, heat radiation loss, or mechanical loss recovered by the low-temperature heat recovery portion in each of the compressor 11 and the generator 13. The working fluid flowing through the fluid storage and power generation device 10 is heated by a low-temperature heating unit (the intake preheater 21, the loss recovery heat preheater 26, and the loss recovery heat interheater 29). As a result, heat of the compressed working fluid and heat from a low-temperature heat source other than the compressed working fluid are recovered to improve thermal efficiency and power generation efficiency.

  The compressed fluid storage power generation device 10 includes an air system 20, a first high-temperature heat medium system 40, a second high-temperature heat medium system 50, and a low-temperature heat medium system 60.

(Air system)
Referring to FIG. 1, an air preheater (first low-temperature preheater) 21, a low-pressure stage compressor main body 22, an intercooler 23, a high-pressure stage compressor main body 24, an aftercooler 25 are provided along an air flow in an air system 20. , Pressure accumulation tank 12, loss recovery heat preheater (second low temperature preheater) 26, preheater 27, high pressure stage expander 28, loss recovery heat interheater (third low temperature preheater) 29, interheater 31, low pressure stage expander 32, and An aftercooler (generator-side aftercooler) 36 is arranged in order.

The intake preheater 21 is provided upstream of the low-pressure stage compressor main body 22. The intake pre-heater 21 is provided with a low-temperature heat, such as a power loss, a heat radiation loss, or a mechanical loss , which has been recovered by the low-temperature heat recovery unit of the compressor 11 and the generator 13 from the air sucked into the low-pressure stage compressor body 22 from the outside. This is a heat exchanger for exchanging heat with the low-temperature heat medium (oil flowing from the oil circulation passages 70a and 80a) of the medium system 60. The intake preheater 21 forms a low-temperature heating unit.

  In the present embodiment, the low-pressure stage compressor main body 22 is a positive displacement screw compressor main body. The low-pressure stage compressor body 22 is driven by an electric motor (drive source) 34 under the control of a control device (not shown), and sucks and compresses air heated by the intake preheater 21. The low-pressure stage compressor main body 22 of the unit shown in FIG. 3 is a component of the compressor 11. The compressor 11 includes an electric motor 34 including an inverter (not shown) for controlling the rotation speed of the low-pressure stage compressor main body 22.

  The intercooler 23 is, as shown in FIGS. 1 and 3 to 5, a compressed air introduced from an air inlet 23 a of the air system 20 and led out from an air outlet 23 b, and a heat medium inlet of a first high-temperature heat medium system 40. This is a heat exchanger that exchanges heat with the first high-temperature heat medium (oil) introduced from the heat medium outlet 23d and introduced from the heat medium outlet 23d. The intercooler 23 forms a high-temperature heat recovery unit.

  Referring to FIG. 1, in the present embodiment, the high-pressure stage compressor main body 24 is a positive displacement screw compressor main body. The high-pressure stage compressor main body 24 is driven by the electric motor 34 under the control of a control device (not shown), and sucks and compresses the compressed air cooled by the intercooler 23. The high-pressure compressor body 24 of the unit shown in FIG. 3 is a component of the compressor 11. On the discharge side of the high-pressure compressor body 24 of the air system 20, a compressed air temperature sensor 37 for detecting the temperature T of the discharged compressed air is provided.

  As shown in FIGS. 1, 3 and 4, the aftercooler 25 heats the compressed air introduced from the air inlet 25a of the air system 20 and led out from the air outlet 25b, and the second high-temperature heat medium (oil). It is a heat exchanger to be exchanged. The second high-temperature heat medium (oil) is introduced from a heat medium inlet 25c of a second high-temperature heat medium system 50 branched from a first high-temperature heat medium system 40 between a heat medium supply pump 41 and a three-way valve 46, which will be described later. You. The second high-temperature heat medium (oil) is led out from the heat medium outlet 25d. The temperature of the second high-temperature heat medium (oil) of the aftercooler 25 is higher than the temperature of the first high-temperature heat medium (oil). The aftercooler 25 constitutes a high-temperature heat recovery unit.

  Referring to FIG. 1, the pressure storage tank 12 stores air compressed by the low-pressure stage compressor main body 22 and the high-pressure stage compressor main body 24 when the working fluid is compressed by the compressor 11. That is, in the pressure accumulating tank 12, the pressure is accumulated by the air compressed by the low-pressure stage compressor main body 22 and the high-pressure stage compressor main body 24. In addition, the compressed air stored in the pressure accumulating tank 12 is supplied to the generator 13 when the power is generated by the generator 13. An inlet valve (not shown) and an outlet valve (not shown) are provided at an inlet (not shown) and an outlet (not shown) of the accumulator tank 12, respectively. When the working fluid is compressed by the compressor 11, the control device (not shown) opens the inlet valve (not shown) of the accumulator tank 12. During power generation by the generator 13, an outlet valve (not shown) of the accumulator tank 12 is opened. Except when the working fluid is compressed and when power is generated, both the inlet valve (not shown) and the outlet valve (not shown) of the accumulator tank 12 are closed.

  The loss recovery heat preheater 26 is connected to the compressed air introduced from the air inlet of the air system 20 and led out of the air outlet, and to the heat medium inlet of the low-temperature heat medium system 60 (from the connection point indicated by A2 in FIG. 1). This is a heat exchanger for exchanging heat with a low-temperature heat medium (oil) derived from a heat medium outlet ((connection portion indicated by B2 in FIG. 1).) The loss recovery heat preheater 26 constitutes a low-temperature heating section. .

  As shown in FIGS. 1, 6, and 7, the preheater 27 is configured to supply compressed air introduced from the air inlet 27 a of the air system 20 and led out of the air outlet 27 b to the first high-temperature heat medium of the first high-temperature heat medium system 40. This is a heat exchanger for exchanging heat with a medium (oil). The first high-temperature heat medium (oil) is introduced from the heat medium inlet 27c of the first high-temperature heat medium system 40. The first high-temperature heat medium (oil) is led out from the heat medium outlet 27d of the first high-temperature heat medium system 40. The pre-heater 27 forms a high-temperature heating unit.

  Referring to FIGS. 1 and 7, in the present embodiment, the high-pressure stage expander 28 is a positive displacement screw turbine. The high-pressure stage expander 28 is driven by the compressed air supplied from the pressure accumulation tank 12. When the high-pressure stage expander 28 is driven, the generator body 35 is driven. The high-pressure stage expander 28 is a component of the generator 13.

  Referring to FIG. 1, the loss recovery heat inter-heater 29 includes compressed air introduced from an air inlet of the air system 20 and led out of the air outlet, and a heat medium inlet of a low-temperature heat medium system 60 (indicated by A3 in FIG. 1). This is a heat exchanger that exchanges heat with a low-temperature heat medium that is introduced from a heat medium outlet (the connection part indicated by B3 in FIG. 1) that is introduced from the connected part). The loss recovery heat inter-heater 29 forms a low-temperature heating unit.

  As shown in FIGS. 1, 6, and 7, the inter-heater 31 includes a compressed air introduced from an air inlet 31 a of the air system 20 and derived from an air outlet 31 b, and a heat medium of the second high-temperature heat medium system 50. This is a heat exchanger that exchanges heat with the second high-temperature heat medium (oil) introduced from the inlet 31c and drawn out from the heat medium outlet 31d. In the inter-heater 31, the heat recovered by the after cooler 25 is transferred to the compressed air heated by the loss recovery heat inter-heater 29 via the second high-temperature heat medium (oil), and the compressed air is further heated. Is done. The inter-heater 31 forms a high-temperature heating unit.

  Referring to FIGS. 1 and 7, in the present embodiment, the low-pressure stage expander 32 is a positive displacement screw turbine. The low-pressure stage expander 32 is driven by compressed air supplied from the pressure accumulation tank 12. When the low-pressure stage expander 32 is driven, the generator body 35 is driven. The low-pressure stage expander 32 constitutes the generator 13.

  The aftercooler 36 is provided downstream of the low-pressure stage expander 32. The aftercooler 36 is a heat exchanger for exchanging heat between the air flowing from the low-pressure stage expander 32 and the low-temperature heat medium flowing through the point A4 from the point B (see FIG. 1) which is the inlet of the low-temperature heat medium system 60. It is a vessel. The air system (working fluid flow path) 20 inside the aftercooler 36 forms a low-temperature heating unit. The low-temperature heat medium system (low-temperature heat medium passage) 60 inside the aftercooler 36 constitutes a low-temperature heat recovery unit.

(1st high-temperature heating medium system)
Referring to FIG. 1, the first high-temperature heat medium system 40 includes a heat medium supply pump 41, a three-way valve 46, an intercooler 23, and a first heat medium tank (oil) along the flow of the first high-temperature heat medium (oil). A first high-temperature heat storage section) 42, a preheater 27, a first heat medium recovery pump 43, a heat medium return tank 44, and a first heat exchanger 45 are arranged. The first high-temperature heat medium (oil) that has passed through the first heat exchanger 45 is returned to the heat medium supply pump 41 and circulates through the first high-temperature heat medium system 40.

  The heat medium supply pump 41 sends the first high-temperature heat medium (oil) sent from the first heat exchanger 45. The heat medium supply pump 41 operates when the working fluid is compressed by the compressor 11. The rotation speed of the heat medium supply pump 41 is controlled by a control device (not shown) in proportion to the electric motor input power.

  The three-way valve 46 is disposed so as to be able to switch between a flow path leading from the heat medium supply pump 41 to the intercooler 23 and a flow path leading from the heat medium supply pump 41 to the first heat medium tank 42 bypassing the intercooler 23. ing. A flow path connecting the three-way valve 46 and the first high-temperature heat medium system 40 between the intercooler 23 and the first heat medium tank 42 is a bypass flow path 47. The communication of the three-way valve 46 is switched according to the detection value of the compressed air temperature sensor 37. That is, the three-way valve 46 switches the flow path so that the allowable set value Td ° C. of the discharge temperature of the high-pressure stage compressor main body 24 is controlled to be constant.

  As shown in FIGS. 1, 3 and 4, in the above-described intercooler 23, the first high-temperature heat medium (which is introduced from the heat medium inlet 23 c of the first high-temperature heat medium system 40 and drawn out from the heat medium outlet 23 d). Oil) is heated by heat exchange with the compressed air in the air system 20.

  Referring to FIG. 1, the first heat medium tank 42 stores the first high-temperature heat medium (oil) heated by the intercooler 23. That is, the first heat medium tank 42 stores heat recovered by the intercooler 23.

  In the above-described preheater 27, since the heat recovered by the intercooler 23 is transferred to the compressed air via the first high-temperature heat medium (oil), the first high-temperature heat medium (oil) is cooled.

  The first heat medium recovery pump 43 sends the first high-temperature heat medium (oil) from the preheater 27 to the heat medium return tank 44. The first heat medium recovery pump 43 is operated by the control device (not shown) at the time of power generation by the generator 13. The rotation speed of the first heat medium recovery pump 43 is controlled by a control device (not shown) in proportion to the generator output power.

  The heat medium return tank 44 stores the first high-temperature heat medium (oil) sent by the first heat medium recovery pump 43.

  As shown in FIGS. 1 and 3, the first heat exchanger 45 connects a cooling water passage through which cooling water supplied from the outside flows, and the first high-temperature heat medium (oil) of the first high-temperature heat medium system 40. This is a heat exchanger for heat exchange. In the first heat exchanger 45, the first high-temperature heat medium (oil) is cooled by heat exchange with the cooling water, and the temperature of the first high-temperature heat medium (oil) flowing to the heat medium supply pump 41 is kept constant. ing.

(Second high-temperature heating medium system)
Referring to FIG. 1, the second high-temperature heat medium system 50 includes a heat medium supply pump 41, an aftercooler 25, and a second heat medium tank (second high-temperature heat storage) along the flow of the second high-temperature heat medium (oil). Section) 51, an inter-heater (high-temperature heating section) 31, a second heat medium recovery pump 52, a heat medium return tank 44, and a first heat exchanger 45. The second high-temperature heat medium (oil) that has passed through the first heat exchanger 45 is returned to the heat medium supply pump 41, and circulates through the second high-temperature heat medium system 50. In the present embodiment, the heat medium supply pump 41 of the second high-temperature heat medium system 50, the heat medium return tank 44, and the first heat exchanger 45 are connected to the heat medium supply pump 41 of the first high-temperature heat medium system 40, It is common to the return tank 44 and the first heat exchanger 45. That is, the second high-temperature heat medium system 50 branches off from the first high-temperature heat medium system 40 between the heat medium supply pump 41 and the three-way valve 46, and is connected to the first heat medium recovery pump 43 and the heat medium return tank 44. And joins the first high-temperature heat medium system 40 between the two.

  The heat medium supply pump 41 is common to the heat medium supply pump 41 of the first high-temperature heat medium system 40.

  In the above-mentioned aftercooler 25, the second high-temperature heat medium (oil) of the second high-temperature heat medium system 50 is heated by heat exchange with the compressed air of the air system 20.

  The second heat medium tank 51 stores the second high-temperature heat medium (oil) heated by the aftercooler 25. That is, the second heat medium tank 51 stores heat recovered by the aftercooler 25.

  In the above-described inter-heater 31, since the heat recovered by the aftercooler 25 is transferred to the compressed air via the second high-temperature heat medium (oil), the second high-temperature heat medium (oil) is cooled.

  The second heat medium recovery pump 52 sends the second high-temperature heat medium (oil) from the inter heater 31 to the heat medium return tank 44. The second heat medium recovery pump 52 is operated by the control device (not shown) at the time of power generation by the power generator 13. The rotation speed of the second heat medium recovery pump 52 is controlled by a control device (not shown) in proportion to the generator output power.

  The heat medium return tank 44 is common to the heat medium return tank 44 of the first high-temperature heat medium system 40.

  The first heat exchanger 45 is common to the first heat exchanger 45 of the first high-temperature heat medium system 40.

(Low-temperature heating medium system)
Referring to FIGS. 1 and 2, the low-temperature heat medium system 60 includes a compressor-side low-temperature heat medium system 70 and a generator-side low-temperature heat medium system 80. In the present embodiment, the low-temperature heat medium system 60 is oil circulation channels 70a and 80a that circulate the low-temperature heat medium (oil) between the low-temperature heat recovery unit and the low-temperature heating units 21, 26, and 29. Here, the low-temperature heat recovery unit includes a range in which low-temperature heat generation units 72A, 72B, 73, 74, 75A, 75B, 81A, 81B, 82, 83, 84, 85A, and 85B described later are arranged and an oil pump 77, The oil circulation passages 70a and 80a and the after cooler 36 are arranged in a range in which 87 is arranged. The low-temperature heat medium system 60 is provided with a bypass flow passage 104 that branches off from an upstream of a second heat exchanger 71 described below and merges downstream of a three-way valve 78 described below. A valve 105 is provided in the bypass flow passage 104. The opening and closing of the valve 105 is controlled according to the oil level detected by an oil level sensor 108 of a turbine lubricating oil tank 86 described later.

  As shown in FIG. 2, in the compressor-side low-temperature heat medium system 70, the second heat exchanger 71, the low-pressure stage compressor body frictional heat generating portion 72 </ b> A, the high-pressure stage compression are performed along the flow of the low-temperature heat medium (oil). Machine body friction heat generating section 72B, inverter heating section 73, electric motor heating section 74, high pressure stage compressor main body casing heating section 75A, low pressure stage compressor main body casing heating section 75B, compressor lubricating oil tank (low temperature heat storage section) 76 , An oil pump 77 and a three-way valve 78 are arranged in this order. In the present embodiment, the second heat exchanger 71 and the three-way valve 78 of the compressor-side low-temperature heat medium system 70 are common to the second heat exchanger 71 and the three-way valve 78 of the generator-side low-temperature heat medium system 80. is there. That is, the generator-side low-temperature heat medium system 80 branches from the compressor-side low-temperature heat medium system 70 between the second heat exchanger 71 and the low-pressure stage compressor main body frictional heat generating section 72A, and is compressed by the three-way valve 78. Merges with the machine-side low-temperature heat medium system 70.

  In the low-temperature heat medium system 60, the flow path on the downstream side of the three-way valve 78 is branched into three. The ends of each channel are A1 to A3 shown in FIG. A1 to A3 are provided with valves 102, 111, and 112, respectively. As shown in FIGS. 1 and 2, the low-temperature heat medium system 60 is connected between the upstream side B and the heat medium inlet A4 of the aftercooler 36, and is connected to the heat medium outlet B4 of the aftercooler 36 and the turbine. A flow path 106 that connects the lubricating oil tank 86 to B4 is provided. The compressor-side low-temperature heat medium system 70 is connected to heat medium inlets (A1 to A4 in FIG. 1) of the low-temperature heating units 21, 26, 29, and 36.

  A valve 102 is provided between the three-way valve 78 and the intake preheater 21. The valve 102 opens when the working fluid is compressed (including when the working fluid is compressed and when power is generated) and when the amount of heat recovered by the low-temperature heat medium is excessive.

  As shown in FIG. 1, in the low-temperature heat medium system 60, a flow path on the upstream side of a second heat exchanger 71 described later is branched into three. The ends of each flow path are B1 to B3. The low-temperature heat medium system 70 is connected to heat medium outlets (B1 to B3 in FIG. 1) of the low-temperature heating units 21, 26, and 29.

  As shown in FIG. 2, the second heat exchanger 71 is a cooling water flow path through which cooling water supplied from the outside flows, and a compressor-side low-temperature heating medium system 70 from the low-temperature heating units 21, 26, and 29. Further, the heat exchanger is a heat exchanger that internally exchanges heat with the low-temperature heat medium (oil) of the generator-side low-temperature heat medium system 80. In the second heat exchanger 71, the low-temperature heat medium (oil) is cooled by heat exchange with the cooling water, and the temperature of the low-temperature heat medium (oil) flowing to the low-temperature heat generating sections 72A, 72B, 73, 74, 75A, 75B. Is maintained at a constant value (40 ° C. in the present embodiment).

  The low-pressure stage compressor body frictional heat generating section 72A constitutes a low-temperature heating section. The low-pressure stage compressor body frictional heat generating portion 72A is a portion that generates heat by friction generated in each of the bearings and gears (compressor body speed-up gear) of the electric motor 34 and the compressor body 22. The heat generated by the friction is a mechanical loss. The outer surface of the low-pressure stage compressor main body frictional heat generating section 72A constitutes a low-temperature heat recovery section.

  The high-pressure compressor body frictional heat-generating portion 72B constitutes a low-temperature heat-generating portion. The high-pressure stage compressor main body frictional heat generating portion 72B is a portion that generates heat by friction generated in each of a bearing and a gear (compressor main body speed increasing gear) of the electric motor 34 and the compressor main body 24. The heat generated by the friction is a mechanical loss. The outer surface of the high-pressure compressor body frictional heat generating section 72B constitutes a low-temperature heat recovery section.

  The inverter heating section 73 forms a low-temperature heating section. As shown in FIG. 8, the inverter heating section 73 is a heat sink provided on a casing 73a of the inverter having an IGBT element for controlling the rotation speed of the electric motor 34. The heat sink of the casing 73a of the inverter is disposed adjacent to the oil circulation passage 70a of the low-temperature heat medium system 70 through which the low-temperature heat medium flows. In the heat sink, the heat transferred from the inside of the casing 73a of the inverter and the low-temperature heat medium (oil) in the oil circulation passage 70a exchange heat. The heat sink constitutes a low-temperature heat recovery unit.

  The motor heating section 74 forms a low-temperature heating section. As shown in FIG. 9, the motor heating section 74 is a cooling jacket 34 b provided on a casing 34 a of the motor 34. The cooling jacket 34b of the casing 34a of the electric motor 34 is disposed so that the low-temperature heat medium (oil) in the oil circulation flow path 70a flows inside. In the cooling jacket 34b, heat transferred from the inside of the casing 34a of the electric motor 34 exchanges heat with the low-temperature heat medium (oil) in the oil circulation passage 70a. The cooling jacket 34b forms a low-temperature heat recovery unit.

  The high-pressure compressor body casing heat-generating section 75A constitutes a low-temperature heat-generating section. As shown in FIG. 10, the high-pressure stage compressor main body casing heat generating portion 75 </ b> A is a cooling jacket 24 b provided on the casing 24 a of the high-pressure stage compressor main body 24. The cooling jacket 24b of the casing 24a of the high-pressure stage compressor main body 24 is arranged so that the low-temperature heat medium (oil) in the oil circulation flow path 70a flows inside. In the cooling jacket 24b, heat transferred from the inside of the casing 24a of the high-pressure stage compressor main body 24 and heat exchange between the low-temperature heat medium (oil) in the oil circulation passage 70a. The cooling jacket 24b forms a low-temperature heat recovery unit.

  The low-pressure compressor body casing heat-generating portion 75B constitutes a low-temperature heat-generating portion. As shown in FIG. 10, the low pressure stage compressor main body casing heat generating portion 75 </ b> B is a cooling jacket 22 b provided on the casing 22 a of the low pressure stage compressor main body 22. The cooling jacket 22b of the casing 22a of the low-pressure stage compressor main body 22 is arranged so that the low-temperature heat medium (oil) in the oil circulation passage 70a flows inside. In the cooling jacket 22b, heat transferred from the inside of the casing 22a of the low-pressure stage compressor main body 22 exchanges heat with the low-temperature heat medium (oil) in the oil circulation passage 70a. The cooling jacket 22b forms a low-temperature heat recovery unit.

  The compressor lubricating oil tank 76 stores the low-temperature heat medium (oil) after recovering the heat in each low-temperature heating section of the compressor-side low-temperature heat medium system 70. That is, the compressor lubricating oil tank 76 stores the heat recovered in each of the low-temperature heating sections 72A, 72B, 73, 74, 75A, and 75B of the compressor-side low-temperature heating medium system 70. In the present embodiment, the temperature of the low-temperature heat medium (oil) stored in the compressor lubricant oil tank 76 is 75 ° C.

  A communication passage 79 is provided between the compressor lubricant oil tank 76 and the turbine lubricant oil tank 86. The communication passage 79 is provided with a check valve 79a that allows only the flow from the compressor lubricant tank 76 to the turbine lubricant tank 86.

  The rotation speed of the oil pump 77 is controlled by a control device (not shown) based on the input power to the electric motor 34 and the oil temperature. The oil pump 77 operates when the compressor 11 compresses the working fluid, and sends the low-temperature heat medium (oil) from the compressor lubricating oil tank 76 to the low-temperature heating units 21, 26, and 29 through the three-way valve 78. The oil pump 77 stops after a certain time has elapsed after the end of the working fluid compression.

  The three-way valve 78 is a valve that communicates one or both of the compressor-side low-temperature heating medium system 70 and the generator-side low-temperature heating medium system 80 with a flow path to the low-temperature heating units 21, 26, and 29. The three-way valve 78 opens the valve on the compressor side low-temperature heat medium system 70 side and the valve on the flow path side when the working fluid is compressed, and the valve on the generator side low temperature heat medium system 80 side and the flow path side on the power generation side during power generation. And the valve to open.

  As shown in FIG. 2, in the generator-side low-temperature heat medium system 80, the second heat exchanger 71, the high-pressure turbine friction heat generation section 81A, and the low-pressure turbine friction heat generation section 81B follow the flow of the low-temperature heat medium. , A converter heating section 82, an inverter heating section 83, a generator body heating section 84, a high-pressure turbine casing heating section 85A, a low-pressure turbine casing heating section 85B, a turbine lubricating oil tank 86, an oil pump 87, and a three-way valve 78 in this order. Are located.

  As described above, the second heat exchanger 71 is common to the second heat exchanger 71 of the compressor-side low-temperature heat medium system 70.

  The high-pressure stage turbine frictional heating section 81A constitutes a low-temperature heating section. The high-pressure turbine frictional heat generating portion 81A is a portion that generates heat by friction generated in the bearings and gears of the generator body 35 and the expander 28, respectively. The heat generated by the friction is a mechanical loss. The outer surface of the high-pressure turbine frictional heating section 81A constitutes a low-temperature heat recovery section.

  The low-pressure stage turbine frictional heat generating portion 81B constitutes a low-temperature heat generating portion. The low pressure stage turbine frictional heat generating portion 81B is a portion that generates heat due to friction generated in each of the bearings and gears of the generator body 35 and the expander 32. The heat generated by the friction is a mechanical loss. The outer surface of the low pressure stage turbine frictional heat generating portion 81B constitutes a low temperature heat recovery portion.

  Converter heating section 82 constitutes a low-temperature heating section. As shown in FIG. 8, converter heat generating portion 82 is a heat sink provided on casing 82 a of the converter of generator body 35. The heat sink of the converter casing 82a is arranged adjacent to the oil circulation passage 80a through which the low-temperature heat medium flows. In the heat sink, heat transferred from the inside of the casing 82a of the converter and the low-temperature heat medium (oil) in the oil circulation channel 80a exchange heat. The heat sink constitutes a low-temperature heat recovery unit.

  The inverter heating section 83 forms a low-temperature heating section. As shown in FIG. 8, the inverter heating section 83 is a heat sink provided on a casing 83a of the inverter that reconverts the generated power converted by the converter. The heat sink of the casing 83a of the inverter is disposed adjacent to the oil circulation passage 70a through which the low-temperature heat medium flows. In the heat sink, the heat transferred from the inside of the casing 83a of the inverter and the low-temperature heat medium (oil) in the oil circulation passage 70a exchange heat. The heat sink constitutes a low-temperature heat recovery unit.

  The generator main body heating section 84 constitutes a low temperature heating section. As shown in FIG. 9, the generator main body heat generating portion 84 is a cooling jacket 35 b provided on the casing 35 a of the generator main body 35. The cooling jacket 35b of the casing 35a of the generator main body 35 is disposed so that the low-temperature heat medium (oil) of the oil circulation channel 80a flows inside. In the cooling jacket 35b, heat transferred from the inside of the casing 35a of the generator body 35 and heat exchange with the low-temperature heat medium (oil) in the oil circulation passage 80a. The cooling jacket 35b forms a low-temperature heat recovery unit.

  The high-pressure stage turbine casing heat-generating portion 85A constitutes a low-temperature heat-generating portion. As shown in FIG. 10, the high-pressure stage turbine casing heat generating portion 85A is a cooling jacket 28b provided on a casing 28a of the high-pressure stage expander 28. The cooling jacket 28b of the casing 28a of the high-pressure stage expander 28 is disposed so that the low-temperature heat medium (oil) of the oil circulation flow path 80a flows inside. In the cooling jacket 28b, heat transferred from the inside of the casing 28a of the high-pressure stage expander 28 exchanges heat with the low-temperature heat medium (oil) in the oil circulation passage 80a. The cooling jacket 28b forms a low-temperature heat recovery unit.

  The low-pressure stage turbine casing heat-generating portion 85B constitutes a low-temperature heat-generating portion. As shown in FIG. 10, the low-pressure stage turbine casing heat generating portion 85 </ b> B is a cooling jacket 32 b provided on the casing 32 a of the low-pressure stage expander 32. The cooling jacket 32b of the casing 32a of the low-pressure stage expander 32 is arranged so that the low-temperature heat medium (oil) of the oil circulation flow path 80a flows inside. In the cooling jacket 32b, heat transferred from the inside of the casing 32a of the low-pressure stage expander 32 exchanges heat with the low-temperature heat medium (oil) in the oil circulation passage 80a. The cooling jacket 32b forms a low-temperature heat recovery unit.

  The turbine lubricating oil tank 86 stores the low-temperature heat medium (oil) after recovering the heat in each low-temperature heating section of the generator-side low-temperature heat medium system 80. That is, the turbine lubricating oil tank 86 stores the heat recovered in the low-temperature heating sections 81A, 81B, 82, 83, 84, 85A, 85B of the generator-side low-temperature heating medium system 80. In the present embodiment, the temperature of the low-temperature heat medium (oil) stored in the turbine lubricating oil tank 86 is 81 ° C. The turbine lubricating oil tank 86 is provided with a flow path through which a low-temperature heat medium flows from the heat medium outlet of the aftercooler 36 through B4. The turbine lubricating oil tank 86 is provided with an oil level sensor 108 for detecting an oil level. When the oil level sensor 108 detects that the oil level of the turbine lubricating oil tank 86 has reached a predetermined lower limit, the control device (not shown) opens the valve 105 of the bypass flow passage 104.

  The rotation speed of the oil pump 87 is controlled by a control device (not shown) based on the power generated by the generator 13 and the oil temperature. The oil pump 87 operates at the time of power generation by the generator 13, and sends the low-temperature heat medium (oil) from the turbine lubricating oil tank 86 to the low-temperature heating units 21, 26, and 29 through the three-way valve 78. The oil pump 87 stops after a certain period of time has elapsed after the end of power generation.

  As described above, the three-way valve 78 is common to the three-way valve 78 of the compressor-side low-temperature heat medium system 70.

  The operation of the compressed fluid storage and power generation device 10 having the above configuration will be described.

  Referring to FIG. 1, at the time of compressing the working fluid, the electric motor 34 is operated by the control of the oil temperature or the input power of the control device (not shown) to move the low-pressure stage compressor main body 22 and the high-pressure stage compressor main body 24. Driven. An inlet valve (not shown) of the accumulator tank 12 opens. The heat medium supply pump 41 operates, and the oil pump 77 of the compressor side low-temperature heat medium system 70 operates. The three-way valve 78 is opened so that the compressor-side low-temperature heat medium system 70 communicates with the three-way valve 78.

  By driving the low-pressure stage compressor main body 22, the low-pressure stage compressor main body 22 sucks air from outside through the intake preheater 21. At this time, in the intake preheater 21, the air is heated by heat exchange with the low-temperature heat medium (oil) from the compressor lubricating oil tank 76 sent from the oil circulation passage 70a by the oil pump 77 (compressed air temperature: 70 ° C). The air sucked into the low-pressure stage compressor main body 22 is compressed by the low-pressure stage compressor main body 22 and sent to the air inlet 23a of the intercooler 23 (compressed air temperature: 176 to 210 ° C).

  The compressed air flowing from the air inlet 23a of the intercooler 23 exchanges heat with the first high-temperature heat medium (oil) sent by the heat medium supply pump 41 inside the intercooler 23 to be cooled (compressed air temperature: 115 ° C.), flows out of the air outlet 23 b and is sent to the high-pressure stage compressor main body 24. When passing through the first heat exchanger 45, the first high-temperature heat medium (oil) sent to the intercooler 23 by the heat medium supply pump 41 exchanges heat with the cooling water in the cooling water flow path and is cooled. . The first high-temperature heat medium (oil) recovered from the compressed air by the intercooler 23 is heated (165 ° C. to 200 ° C.), stored in the first heat medium tank 42, and stored.

  In the high-pressure stage compressor main body 24, the compressed air from the intercooler 23 is compressed and discharged at a higher temperature and higher pressure than the compressed air on the discharge side of the low-pressure stage compressor main body 22 (compressed air temperature, pressure: 250 ° C, 0.6 MPa). The compressed air discharged from the high-pressure stage compressor main body 24 is sent to an aftercooler 25.

  The compressed air flowing from the air inlet 25 a of the aftercooler 25 exchanges heat with the second high-temperature heat medium (oil) of the second high-temperature heat medium system 50 sent by the heat medium supply pump 41 inside the aftercooler 25. Then, the air is cooled (compressed air temperature: 90 ° C.), flows out from the air outlet 25b, and is sent to the accumulator tank 12. The compressed air compressed by the compressor 11 at the time of compressing the working fluid is supplied to the accumulator tank 12. In the compressed fluid storage and power generation device 10, the inlet valve (not shown) and the outlet valve (not shown) of the accumulator tank 12 are closed until the power generation after the end of the working fluid compression, and the compressed air is stored and accumulated. Is done. The second high-temperature heat medium (oil) recovered from the compressed air by the aftercooler 25 is heated to 240 ° C., stored in the second heat medium tank 51, and stored therein. The electric motor 34 stops, and the low-pressure stage compressor main body 22 and the high-pressure stage compressor main body 24 stop. The inlet valve (not shown) of the accumulator tank 12 is closed. The heat medium supply pump 41 stops, and the oil pump 77 of the compressor-side low-temperature heat medium system 70 stops after a certain period of time. The compressed air in the accumulator tank 12 is cooled to an ambient temperature of 30 ° C. by heat radiation.

  On the other hand, in the compressor-side low-temperature heat medium system 70 of the compressor 11, the low-temperature heat medium is sent from the compressor lubricating oil tank (low-temperature heat storage unit) 76 by the operation of the oil pump 77 and the opening of the valve 102. It flows to the intake preheater 21 through the three-way valve 78. The low-temperature heat medium does not flow to the loss recovery heat pre-heater (second low-temperature pre-heater) 26 and the recovery heat inter-heater (third low-temperature pre-heater) 29 by closing the valves 111 and 112. In this state, since the low-temperature heat medium has excess heat recovery, the valve 102 is opened. In the intake preheater 21, the air sucked into the low-pressure stage compressor main body 22 exchanges heat with the low-temperature heat medium of the compressor-side low-temperature heat medium system 70. Thereby, the air is heated and the low-temperature heat medium is cooled.

  Thereafter, the low-temperature heat medium (oil) in the oil circulation passage 70a cooled by the intake preheater 21 flows into the second heat exchanger 71 through B1 and B, and exchanges heat with the cooling water in the cooling water passage. It is cooled by the second heat exchanger 71. Thereafter, the low-temperature heat medium (oil) passes through the second heat exchanger 71, and the frictional heat generated by the rotation is generated in the low-pressure stage compressor body frictional heat generation section 72A and the high-pressure stage compressor body frictional heat generation section 72B. Recovers heat from bearings and gears. The low-temperature heat medium (oil) that has recovered heat from the bearings and gears in the low-pressure stage compressor main body frictional heat generation section 72A and the high-pressure stage compressor main body frictional heat generation section 72B is a heat sink, which is an inverter heat generation section 73 shown in FIG. And heat exchange with the casing 73a of the inverter. Thereafter, the low-temperature heat medium (oil) flows into the cooling jacket 34b of the casing 34a of the electric motor 34 shown in FIG. 9 and recovers heat from the casing 34a of the electric motor 34 via the cooling jacket 34b at the electric motor heating section 74. Thereafter, the low-temperature heat medium (oil) is supplied to the cooling jackets 22b and 24b of the casings 22a and 24a of the compressor bodies 22 and 24, which are the high-pressure compressor body casing heat-generating portion 75A and the low-pressure compressor body casing heat-generating portion 75B. The refrigerant flows into the casing and recovers heat from the casings 22a, 24a of the compressor bodies 22, 24 via the cooling jackets 22b, 24b. The low-temperature heat medium (oil) recovered from the casings 22a and 24a of the compressor main bodies 22 and 24 flows into the compressor lubricating oil tank 76 and is stored therein. That is, by storing the low-temperature heat medium (oil) in the compressor lubricating oil tank 76, the heat of the low-temperature heat medium (oil) is stored. The low-temperature heat medium (oil) circulates in the compressor-side low-temperature heat medium system 70. After the working fluid is compressed, the oil pump 77 is stopped after a certain period of time, and the circulation of the low-temperature heat medium is terminated.

  At the time of power generation, a valve (not shown) on the outlet side of the pressure accumulation tank 12 is opened by rotation speed control according to the generated power transmitted to the system of the control device (not shown), and Is supplied with compressed air (compressed air temperature: 30 ° C.). The first heat medium recovery pump 43 operates, and the second heat medium recovery pump 52 operates. The oil pump 87 of the generator-side low-temperature heat medium system 80 operates. The three-way valve 78 opens so that the generator-side low-temperature heat medium system 80 communicates.

  The compressed air flowing from the pressure accumulation tank 12 by opening an outlet valve (not shown) of the pressure accumulation tank 12 is sent to the loss recovery heat preheater 26. In the loss recovery heat preheater 26, the compressed air exchanges heat with the low-temperature heat medium (oil) from the turbine lubricating oil tank 86 sent by the oil pump 87 from the oil circulation passage 80a of the generator-side low-temperature heat medium system 80. Heated by On the other hand, the low-temperature heat medium (oil) is cooled and flows to the low-temperature heat generating section of the generator-side low-temperature heat medium system 80. The compressed air heated by the loss recovery heat preheater 26 is sent to the preheater 27 (compressed air temperature: 70 ° C.).

  In the preheater 27, the compressed air is heated by exchanging heat with the first high-temperature heat medium (oil) of the first high-temperature heat medium system 40 flowing by the operation of the first heat medium recovery pump 43 (compressed air temperature: 155). ° C). On the other hand, the first high-temperature heat medium (oil) is cooled and flows to the heat medium return tank 44. The compressed air heated by the preheater 27 is sent to a high-pressure stage expander 28.

  The high-pressure stage expander 28 is driven by the compressed air sent from the preheater 27, and the generator body 35 is driven. By driving the generator main body 35, power is generated in the generator 13, and the generated power is transmitted to a system (not shown). The compressed air that has passed through the high-pressure stage expander 28 is sent to the loss recovery heat interheater 29 (compressed air temperature, pressure: 25 ° C., 0.2 MPa).

  In the loss recovery heat inter-heater 29, the compressed air is transferred to the low-temperature heat medium (oil) from the turbine lubricating oil tank 86 sent by the oil pump 87 from the oil circulation passage 80a of the generator-side low-temperature heat medium system 80. Heated by replacement. On the other hand, the low-temperature heat medium (oil) is cooled and flows to the low-temperature heat generating portion of the generator-side low-temperature heat medium system 80 through B3 and B. The compressed air heated by the loss recovery heat inter-heater 29 is sent to the inter-heater 31 (compressed air temperature: 71 ° C.).

  In the inter-heater 31, the compressed air is heated by exchanging heat with the second high-temperature heat medium (oil) of the second high-temperature heat medium system 50 flowing by the operation of the second heat medium recovery pump 52. On the other hand, the second high-temperature heat medium (oil) is cooled (oil temperature: 80 ° C.) and flows to the heat medium return tank 44. The compressed air heated by the inter-heater 31 is sent to the low-pressure stage expander 32 (compressed air temperature: 230 ° C.).

  The low-pressure stage expander 32 is driven by the compressed air sent from the inter-heater 31, and the generator body 35 is driven. By driving the generator main body 35, power is generated in the generator 13, and the generated power is transmitted to a system (not shown). The compressed air that has passed through the low-pressure stage expander 32 flows to the aftercooler 36.

  In the aftercooler 36, the compressed air is cooled by exchanging heat with a low-temperature heat medium (oil) flowing from B through A4, and is discharged to the atmosphere at a temperature of about 45 ° C. On the other hand, the low-temperature heat medium (oil) is heated by exchanging heat with the compressed air. The heated low-temperature heat medium (oil) at about 80 ° C. returns to the turbine lubricating oil tank 86 through B4 (see FIGS. 1 and 2).

  On the other hand, in the generator-side low-temperature heat medium system 80 of the generator 13, the low-temperature heat medium is sent from the turbine lubricating oil tank (low-temperature heat storage unit) 86 by the operation of the oil pump 87 and the opening of the valves 111 and 112. , Through a three-way valve 78, to a loss recovery heat preheater (second low temperature preheater) 26 and a recovery heat interheater (third low temperature preheater) 29. In both the loss recovery heat preheater 26 and the recovery heat interheater 29, the compressed air is heated and the low-temperature heat medium is cooled. Note that the valve 102 is closed, and the low-temperature heat medium is not sent to the intake preheater (first low-temperature preheater) 21.

  Thereafter, the low-temperature heat medium (oil) in the oil circulation channel 80a cooled by the loss recovery heat pre-heater 26 and the recovery heat inter-heater 29 flows into the second heat exchanger 71 through B2 and B3, and flows through the cooling water flow. The heat is exchanged with the cooling water of the road and cooled by the second heat exchanger 71. After that, the low-temperature heat medium (oil) passes through the second heat exchanger 71, and the bearing having frictional heat generated by rotation in the high-pressure stage turbine frictional heat generation portion 81A and the low-pressure stage turbine frictional heat generation portion 81B. Recovers heat from gears. The low-temperature heat medium (oil) that has recovered heat from the bearings and gears in the high-pressure stage turbine frictional heat generating portion 81A and the low-pressure stage turbine frictional heat generating portion 81B includes a heat sink and an inverter heat generating portion that are the converter heat generating portion 82 shown in FIG. When passing through the heat sink 83, the heat exchange is performed between the casing 82 a of the converter heating section 82 and the casing 83 a of the inverter heating section 83.

  Thereafter, the low-temperature heat medium (oil) flows into the cooling jacket 35b of the casing 35a of the generator main body 35 shown in FIG. 9 at the generator main body heating section 84, and passes through the cooling jacket 35b to the casing 35a of the generator main body 35. From the heat. Thereafter, the low-temperature heat medium (oil) flows into the cooling jackets 28b and 32b of the casings 28a and 32a of the expanders 28 and 32, which are the high-pressure stage turbine casing heat-generating portion 85A and the low-pressure stage turbine casing heat-generating portion 85B. Heat is recovered from the casings 28a, 32a of the expanders 28, 32 via the tubes 28b, 32b. The low-temperature heat medium (oil) recovered from the casings 28a and 32a of the expanders 28 and 32 flows into the turbine lubricating oil tank 86 and is stored therein. That is, by storing the low-temperature heat medium (oil) in the turbine lubricating oil tank 86, the heat of the low-temperature heat medium (oil) recovered by the low-temperature heat recovery unit is stored. The low-temperature heat medium (oil) circulates in the generator-side low-temperature heat medium system 80. After power generation, the oil pump 87 is stopped after a certain period of time, and the circulation of the low-temperature heat medium is terminated.

  In the above, each of the operation at the time of compression of the working fluid and the operation at the time of power generation has been described.

  In any of the execution of only the working fluid compression, the execution of only the power generation, the execution of the working fluid compression and the power generation, and the stop of the working fluid compression and the power generation, the oil level sensor 108 controls the oil level of the turbine lubricating oil tank 86. When it is detected that the predetermined lower limit has been reached, the control device (not shown) opens the valve 105 of the bypass flow passage 104.

  According to the present invention, the pre-heater 27 and the inter-heater 31 cause the compressed air flowing from the pressure accumulation tank 12 to the expanders 28 and 32 in the pre-heater 27 and the inter-heater 31 by the heat recovered from the compressed air flowing to the pressure accumulation tank 12 in the inter cooler 23 and the after cooler 25. Since heating can be performed, thermal efficiency can be improved. In addition, at least one of the low-temperature heating sections 36, 72A, 72B, 73, 74, 75A, 75B, 77, 81A, 81B, 82, 83, 84, 85A, 85B, 87 of the compressor 11 and the generator 13 The compressed air can be heated by the intake preheater 21, the loss recovery heat preheater 26, and the loss recovery heat interheater 29 by the heat recovered by the low-temperature heat recovery unit, so that the thermal efficiency can be further improved. Therefore, in the compressed fluid storage power generation device 10, improvement in power generation efficiency by reusing heat of the low-temperature heat source can be realized. That is, in the compressed fluid storage power generation device 10, the low-temperature heating parts 36, 72 A, 72 B, 73, 74, 75 A, 75 B, 77, 81 A, 81 B, 82, 83, 84, 85 A, 85 B, 87 are not used for power generation. In this way, the amount of heat that is wasted can be minimized, and the heat efficiency can be improved and the power generation efficiency can be improved.

  According to the above configuration, it is possible to cope with charging of fluctuating power and transmission of fluctuating necessary power. In other words, it is possible to smooth the fluctuating power generated by solar power and wind power, which are renewable energy.

Oil circulation passages 70a for circulating oil between the compressor-side low-temperature heating medium system 70 and the generator-side low-temperature heating medium system 80, and the intake preheater 21, the loss recovery heat preheater 26, and the loss recovery heat interheater 29. 80a. Therefore, heat of the heat generating parts 72A, 72B, 73, 74, 75A, 75B, 77 of the compressor 11 and heat of the heat generating parts 36, 81A, 81B, 82, 83, 84, 85A, 85B, 87 of the generator 13 are obtained. Can be reliably recovered via the oil in the oil circulation channels 70a and 80a. In addition, due to the recovered heat of power loss, heat radiation loss, and mechanical loss, it is possible to raise the compressed air, whose temperature has dropped to near the ambient temperature in the power generation process, to a higher temperature, for example, about 70 ° C., thereby increasing the enthalpy of the compressed air. This makes it possible to increase the amount of heating heat as compared with A-CAES in which reheating is performed only with the accumulated compression heat, so that more air turbine expansion work can be obtained, and higher charge and discharge efficiency can be obtained.

  The low-temperature heat recovery part of the low-temperature heat recovery part is a friction heat generation part (bearing friction heat generation part, gear friction heat generation) that generates frictional heat in rotating parts of the compressor body, expanders 28 and 32, electric motor 34, and generator body 35. Part). By providing the low-temperature heat recovery sections 72A, 72B, 73, 74, 75A, 75B, 77, 81A, 81B, 82, 83, 84, 85A, 85B, 87, the compressor bodies 22, 24 and the expanders 28, 32 are provided. The waste heat released to the atmosphere as frictional heat from the electric motor 34 and the generator main body 35 can be recovered, and the thermal efficiency can be improved.

  The driving source is an electric motor 34 having an inverter for controlling the number of rotations. The heat generating portion includes a motor heat generating portion 74 which is a heat generating portion of the electric motor 34 and an inverter heat generating portion 73 which is a heat generating portion of the inverter. Therefore, the waste heat released to the atmosphere from the casing 34a of the electric motor 34 and the casing 73a of the inverter can be recovered, and the thermal efficiency can be improved.

  The low-temperature heat medium (oil) flows into the cooling jackets 22b and 24b of the casings 22a and 24a of the compressor bodies 22 and 24, so that the casings 22a and 24a of the compressor bodies 22 and 24 pass through the cooling jackets 22b and 24b. From the heat.

  The low-temperature heat medium (oil) flows into the cooling jacket 35b of the casing 35a of the generator main body 35, so that heat can be recovered from the casing 35a of the generator main body 35 via the cooling jacket 35b.

  It includes a converter for converting the power generated by the generator body 35, and an inverter for re-converting the power converted by the converter. Further, the low-temperature heat generating portion includes a generator main body heat generating portion 84 as a heat generating portion of the generator main body 35, a converter heat generating portion 82 as a converter heat generating portion, and an inverter heat generating portion as an inverter heat generating portion. 83. Therefore, waste heat released to the atmosphere from the generator body 35, the converter, and the inverter can be recovered, and the thermal efficiency can be improved.

  The low-temperature heat medium (oil) flows into the cooling jackets 28b, 32b of the casings 28a, 32a of the expanders 28, 32, so that the heat from the casings 28a, 32a of the expanders 28, 32 passes through the cooling jackets 28b, 32b. Can be recovered.

  The inverter heating section 73 is a casing 73a of the inverter, and the compressor-side low-temperature heating medium system 70 has a heat sink provided in the casing 73a of the inverter. Thereby, the heat of the casing 73a of the inverter can be recovered through the heat sink, and the thermal efficiency can be improved.

  The converter heating section 82 is a converter casing 82a, the inverter heating section 83 is an inverter casing 83a, and the generator-side low-temperature heating medium system 80 is a heat sink provided on each of the converter casing 82a and the inverter casing 83a. Having. Therefore, the heat of the converter and the casings 82a and 83a of the inverter can be recovered through the heat sink, and the thermal efficiency can be improved.

  The compressor bodies 22 and 24 include a low-pressure stage compressor body 22 and a high-pressure stage compressor body 24, and the expanders 28 and 32 include a high-pressure stage expander 28 and a low-pressure stage expander 32. The low-temperature heating unit includes at least one of a first low-temperature preheater 21, a second low-temperature preheater 26, and a third low-temperature preheater 29. According to this configuration, the driving force of the high-pressure stage expander 28 and the low-pressure stage expander 32 can be increased. Thereby, the power generation efficiency can be improved.

  Since the first heat medium tank 42, the second heat medium tank 51, and the low-temperature heat storage units 76 and 86 are provided, heat mediums having three different temperatures can be used as heating sources. Thereby, the power generation efficiency can be increased.

  Generator loss, inverter loss for generator, and converter loss are recovered as heat in the lubricating oil cooling structure, and the power consumption of the lubricating oil pump is raised to increase the lubricating oil temperature. Can be heated.

The effect of power loss on charge / discharge efficiency exceeds 20%, and heat recovery can greatly improve charge / discharge efficiency. The mechanical loss affects the charging / discharging efficiency by 5 to 10% depending on the model. The heat loss affects the charge / discharge efficiency by about 5%. If these low-temperature heat losses are recovered and can be used for pre-air supply to the turbine, the charge / discharge efficiency can be improved by up to about 30%.

  In the present invention, since the lubricating oil or cooling water, which is a liquid, is used as the low-temperature heat medium, the temperature difference between the casings 22a, 24a, and 35a can be reduced. Therefore, it is possible to prevent the casings 22a, 24a, and 35a from being deformed due to a temperature difference between the compressor bodies 22, 24 and the casing 35a of the generator body 35.

  The heat generation temperature differs depending on the heat generating part for heat recovery. When heat is stored with lubricating oil, the limit is about 80 ° C. The low-pressure stage air compressor 22 has a temperature zone of about 160 ° C. unless the intake air is heated. The discharge temperature of the high pressure stage can be raised to about 250 ° C. by adjusting the cooling degree of the intercooler. Depending on the temperature zone, three types of heat storage tanks 42, 51, 76 (86) are used to selectively use heating sources according to the required temperature conditions for air turbine power supply heating and intermediate exhaust heating, thereby increasing power generation efficiency. Can be improved.

(2nd Embodiment)
FIG. 11 shows a compressed fluid storage power generation device 10 according to a second embodiment of the present invention. FIG. 12 shows a low-temperature heat medium system 60 of the compressed fluid storage power generation device 10 according to the second embodiment of the present invention. The configuration other than the low-temperature heat recovery unit using the cooling water as the low-temperature heat medium and the low-temperature heat medium system 60 is substantially the same as that of the first embodiment.

  The low-temperature heat medium system 60 has a cooling water system 60a that recovers the heat of the low-temperature heating section with cooling water, and a lubricating oil system 60d that recovers the heat of the low-temperature heating section with lubricating oil.

  The cooling water system 60a is a water circulation channel of the cooling water passing through the low-temperature heat recovery unit and the low-temperature heating units 21, 26, 29, and 36. The cooling water system 60a branches to the compressor 11 at an intermediate portion and is connected to the three-way valve 97. The compressor includes a compressor-side cooling water system 60b and a generator-side cooling water system 60c branched to the generator 13 and connected to the three-way valve 97.

  The compressor-side cooling water system 60b includes a second heat exchanger 71, a third heat exchanger (oil-water heat exchanger) 91, an inverter heating unit 73, a motor heating unit 74, a high-pressure compressor body casing heating unit 75A, A low pressure stage compressor main body casing heat generating portion 75B, a hot water tank 92, a water pump 93, and a three-way valve 97 are arranged in this order. The low-temperature heating section of the compressor-side cooling water system 60b is an inverter heating section 73, a motor heating section 74, a high-pressure compressor body casing heating section 75A, a low-pressure compressor body casing heating section 75B, and a water pump 93. The inverter heating section 73, the motor heating section 74, the high-pressure compressor body casing heating section 75A, and the low-pressure compressor body casing heating section 75B of the present embodiment are the same as those of the first embodiment.

  The second heat exchanger 71 is the same as the second heat exchanger 71 of the first embodiment.

  The third heat exchanger (oil-water heat exchanger) 91 is a heat exchanger that exchanges heat between the cooling water in the cooling water system 60a and the lubricating oil in the lubricating oil system 60d.

  The hot water tank 92 corresponds to the compressor lubricating oil tank 76 of the first embodiment.

  The water pump 93 corresponds to the oil pump 77 of the first embodiment.

  The three-way valve 97 is the same as the three-way valve 78 of the first embodiment.

  The generator-side cooling water system 60c includes a second heat exchanger 71, a third heat exchanger (oil-water heat exchanger) 91, a converter heating section 82, an inverter heating section 83, a generator body heating section 84, a high-pressure stage turbine casing. A heating section 85A, a low-pressure stage turbine casing heating section 85B, a hot water tank 94, a water pump 95, and a three-way valve 97 are arranged in this order. The low-temperature heating section of the generator-side cooling water system 60c is a converter heating section 82, an inverter heating section 83, a generator body heating section 84, a high-pressure stage turbine casing heating section 85A, and a low-pressure stage turbine casing heating section 85B. The converter heating section 82, the inverter heating section 83, the generator body heating section 84, the high pressure stage turbine casing heating section 85A, and the low pressure stage turbine casing heating section 85B of the present embodiment are the same as those of the first embodiment.

  The second heat exchanger 71 is common to the second heat exchanger 71 of the compressor-side cooling water system 60b.

  The third heat exchanger (oil-water heat exchanger) 91 is common to the third heat exchanger (oil-water heat exchanger) 91 of the compressor-side cooling water system 60b.

  The hot water tank 94 corresponds to the turbine lubricating oil tank 86 of the first embodiment.

  The water pump 95 corresponds to the oil pump 87 of the first embodiment.

  The lubricating oil system 60d is an oil circulation channel, and is a channel for circulating oil through the low-temperature heat generating parts 72A, 72B, 81A, 81B, 98, and 99 of the lubricating oil system 60d. The lubricating oil system 60d includes a compressor-side lubricating oil system 60e and a generator-side lubricating oil system 60f. Each of the compressor-side lubricating oil system 60e and the generator-side lubricating oil system 60f is connected to a channel inlet and a channel outlet of a third heat exchanger (oil-water heat exchanger) 91. That is, the oil of the lubricating oil system 60d circulates in each of the compressor-side lubricating oil system 60e and the generator-side lubricating oil system 60f.

  In the compressor-side lubricating oil system 60e, a third heat exchanger (oil-water heat exchanger) 91, a low-pressure stage compressor main body frictional heat generating portion 72A, a high-pressure stage compressor main body frictional heat generating portion 72B, and an oil pump 98 are arranged in this order. Have been. The low-pressure stage compressor main body frictional heat generation section 72A and the high-pressure stage compressor main body frictional heat generation section 72B of the present embodiment are the same as those of the first embodiment. The third heat exchanger (oil-water heat exchanger) 91 is common to the third heat exchanger (oil-water heat exchanger) 91 of the cooling water system 60a. The oil pump 98 operates when the working fluid is compressed by the compressor 11, and circulates the oil in the compressor-side lubricating oil system 60e.

  In the generator-side lubricating oil system 60f, a third heat exchanger (oil-water heat exchanger) 91, a low-pressure stage turbine frictional heat generation unit 81B, a high-pressure stage turbine frictional heat generation unit 81A, and an oil pump 99 are arranged in this order. The low-pressure turbine frictional heat generation section 81B and the high-pressure turbine frictional heat generation section 81A of the present embodiment are the same as those of the first embodiment. The third heat exchanger (oil-water heat exchanger) 91 is common to the third heat exchanger (oil-water heat exchanger) 91 of the cooling water system 60a. The oil pump 99 operates during power generation by the generator 13, and circulates oil in the generator-side lubricating oil system 60f.

  When the working fluid is compressed by the compressor 11, the control is performed by a control device (not shown) in proportion to the electric power input to the motor. The oil pump 98 of the compressor-side lubricating oil system 60e operates by controlling the number of revolutions according to the electric power input to the motor. Thus, in the compressor-side lubricating oil system 60e, heat is recovered from the low-temperature heat generating sections 72A and 72B by the circulation of the lubricating oil. Further, the heat of the oil pump 98 is recovered by the lubricating oil.

  On the other hand, in the water circulation channel 60 a of the low-temperature heat medium system 60, the valve 102 is opened, the cooling water flows in from the intake preheater 21, and the second heat exchanger 71 exchanges heat with the cooling water in the cooling water channel to perform cooling. Is done. The cooling water that has passed through the second heat exchanger 71 is heated in the third heat exchanger 91 by exchanging heat with the lubricating oil whose heat has already been recovered in the lubricating oil system 60e. At that time, the oil in the lubricating oil system 60e is cooled and flows out of the third heat exchanger 91. In the third heat exchanger 91, the heat recovered by the oil system low-temperature heat recovery units 72A, 72B, 98 via the oil in the oil circulation channel 60e is transferred to the water in the water circulation channel 60a and collected.

  The water that has passed through the third heat exchanger 91 passes through the low-temperature heat recovery section of the compressor-side cooling water system 60b to recover heat, and is stored in the hot water tank (low-temperature heat storage section) 92. The water in the hot water tank 92 passes through the three-way valve 97 and is sent to the intake preheater 21 by the operation of the water pump 93. Since the generators 28 and 32 are not generating power, the low-temperature heat medium is not sent to the loss recovery heat preheater 26 and the loss recovery heat interheater 29 by closing the valves 111 and 112. In this state, since the low-temperature heat medium has excess heat recovery, the valve 102 is opened and the low-temperature heat medium is sent to the intake preheater (first low-temperature preheater) 21 as described above. In the intake preheater 21, the air sucked into the low-pressure stage compressor main body 22 exchanges heat with the low-temperature heat medium of the compressor-side low-temperature heat medium system 70. Thereby, the air is heated and the low-temperature heat medium is cooled.

  At the time of power generation by the generator 13, in the lubricating oil system 60d of the low-temperature heat medium system 60, heat is recovered from the low-pressure stage turbine frictional heat generating portion 81B and the high-pressure stage turbine frictional heat generating portion 81A by the lubricating oil. The heat of the oil pump 99 is recovered by the lubricating oil.

  On the other hand, in the water circulation channel 60 a of the low-temperature heat medium system 60, the cooling water flows from the loss recovery heat preheater 26 and the loss recovery heat interheater 29 by opening the valves 111 and 112, and is cooled by the second heat exchanger 71. It is cooled by exchanging heat with the cooling water in the water channel. The cooling water that has passed through the second heat exchanger 71 is heated in the third heat exchanger 91 by exchanging heat with lubricating oil from which heat has already been recovered in the lubricating oil system 60f. At that time, the oil in the lubricating oil system 60f is cooled and flows out of the third heat exchanger 91. In the third heat exchanger 91, the heat recovered in the oil system low-temperature heat recovery units 81A, 82B, and 99 is transferred to the water in the water circulation channel 60a and recovered via the oil in the lubricating oil system 60f.

  The water that has passed through the third heat exchanger 91 passes through the low-temperature heat recovery sections 82, 83, 84, 85A, and 85B of the water circulation flow channel 60a (the generator-side cooling water system 60c) on the generator 13 side to generate heat. It is collected and stored in a hot water tank (low-temperature storage unit) 94. The water in the hot water tank 94 passes through the three-way valve 97 by the operation of the water pump 95 and is sent to the loss recovery heat pre-heater 26 and the loss recovery heat inter-heater 29. It is cooled by exchanging heat with the compressed air and sent to the low-temperature heat recovery unit side of the low-temperature heat medium system 60. Note that the valve 102 is closed, and the low-temperature heat medium (water) is not sent to the intake preheater (first low-temperature preheater) 21.

  In the above, each of the operation at the time of compression of the working fluid and the operation at the time of power generation has been described.

  In any of the execution of only the working fluid compression, the execution of only the power generation, the execution of the working fluid compression and the power generation, and the stop of the working fluid compression and the power generation, the oil level sensor 108 controls the oil level of the turbine lubricating oil tank 86. When it is detected that the predetermined lower limit has been reached, the control device (not shown) opens the valve 105 of the bypass flow passage 104.

  According to the present invention, the compressor 11 and the low-temperature heating sections 36, 72A, 72B, 73, 74, 75A, 75B, 81A, 81B, 82, 83, 84, 85A, 85B, 93, 95, The heat of 98, 99 can be reliably recovered through the oil in the lubricating oil system 60d and the cooling water in the water circulation channel 60a. Thereby, the thermal efficiency can be improved. Therefore, in the compressed fluid storage power generation device 10, improvement in power generation efficiency by reusing heat of the low-temperature heat source can be realized. That is, in the compressed fluid storage power generation device 10, the low-temperature heat generation parts 36, 72 A, 72 B, 73, 74, 75 A, 75 B, 81 A, 81 B, 82, 83, 84, 85 A, 85 B, 93, 95 are not used for power generation. , 98, and 99, the heat wasted can be minimized, and the heat efficiency can be improved and the power generation efficiency can be improved.

(Third embodiment)
FIG. 13 shows a compressed fluid storage power generation device 10 according to a third embodiment of the present invention. FIG. 14 shows a low-temperature heat medium system 60 of the compressed fluid storage power generation device 10 according to the third embodiment of the present invention. In FIG. 13, the illustration of the low-temperature heat medium system 60 is omitted.

  The configuration according to the present embodiment is configured such that a sub-after-cooler 88 is provided between the after-cooler 25 of the air system 20 and the accumulator tank 12, and the low-temperature heat recovery branching off from the low-temperature heat medium system 60 and joining the low-temperature heat medium system 60. The configuration is the same as that of the first embodiment except that a flow path 101 is provided. One end of the low-temperature heat recovery flow path 101 is connected to a branch portion between the compressor-side low-temperature heat medium system 70 and the generator-side low-temperature heat medium system 80 of the low-temperature heat medium system 60, and the other end is connected to the compressor-side low-temperature heat medium. The system 70 is connected to a compressor lubricating oil tank 76. The connection shown in FIG. 13C and the connection shown in FIG. 14C are connected, and the connection shown in FIG. 13D and the connection shown in FIG. 14D are connected. . )

  The sub-after cooler 88 is a heat exchanger that exchanges heat between the compressed air in the air system 20 and the low-temperature heat medium in the low-temperature heat recovery flow path 101.

  At the time of compressing the working fluid, the compressed air is flowing in the air system 20 as in the first embodiment. On the other hand, in the low-temperature heat medium system 60, the low-temperature heat medium that has passed through the second heat exchanger 71 flows to the compressor-side low-temperature heat medium system 70, the generator-side low-temperature heat medium system 80, and the low-temperature heat recovery flow path 101. .

  The low-temperature heat medium flowing through the low-temperature heat recovery flow path 101 flows in from the heat medium inlet of the sub-after cooler 88 and flows out from the heat medium outlet. In the sub-after cooler 88, the flowing heat medium is heated by heat exchange with the compressed air in the air system 20. The low-temperature heat medium heated by the sub-after cooler 88 passes through the low-temperature heat recovery flow path 101, flows into the compressor lubricating oil tank 76, and is stored. That is, by storing the low-temperature heat medium (oil) in the compressor lubricating oil tank 76, the heat of the low-temperature heat medium (oil) is stored. The compressed air in the air system 20 is cooled to a temperature close to the atmospheric temperature by the heat exchange, and flows into the accumulator tank (accumulator) 12.

  According to this configuration, the temperature of the compressed air supplied to the pressure accumulating tank 12 is brought close to the atmospheric temperature, the heat loss in the pressure accumulating tank 12 is reduced, and the residual compression heat is recovered to the low-temperature heat medium (oil). it can.

  According to the present invention, the compressed air stored in the pressure accumulation tank 12 can be further cooled. As a result, it is possible to prevent the heat of the compressed air from radiating from the pressure accumulation tank 12. In addition, a decrease in the pressure of the compressed air can be suppressed. In the accumulator tank 12, the amount of drain generated due to a decrease in the temperature of the compressed air can be reduced.

(Fourth embodiment)
15A and 15B show a heat storage tank group of the compressed fluid storage and power generation device 10 according to the fourth embodiment of the present invention. FIG. 15A is a plan view, and FIG. 15B is a front view.

  The compressed fluid storage power generation device 10 of the present embodiment includes a container 120 having a length of, for example, 20 feet. A heat storage tank group, a heat exchanger group, and a pump group are housed in the container 120. Except for this point, the configuration of the present embodiment is substantially the same as the first embodiment (see FIGS. 1 to 10).

  The heat storage tank group includes a first heat medium tank 42, a second heat medium tank 51, a compressor lubricating oil tank 76, a turbine lubricating oil tank 86, and a heat medium return tank 44. The container 120 is preferably a heat insulating container provided with a heat insulating material inside (also referred to as a thermal container).

  The heat exchanger group includes a first heat exchanger 45 and a second heat exchanger 71. Note that the first heat exchanger 45 is not shown in FIGS. 15A and 15B because it is located deeper than the second heat medium recovery pump 52 in FIG. 15B.

  The pump group includes a first heat medium recovery pump 43, a second heat medium recovery pump 52, a heat medium supply pump 41, and oil pumps 77 and 87. The first heat medium recovery pump 43 is not shown in FIG. 15A and FIG. 15B because it is located more deeply than the second heat medium recovery pump 52 in FIG. 15B.

  By accommodating in the container 120, heat loss due to heat radiation in the heat storage tank group can be prevented, and a decrease in power generation efficiency can be prevented. Further, the container type facilitates transportation and on-site construction, and since the heat storage tank group is housed in the container 120, they are not exposed to wind and rain, and can be installed outdoors. Moreover, if it is an insulated container, heat radiation can be prevented more reliably.

  In the present embodiment, the first heat exchanger 45, the first heat medium recovery pump 43, the second heat medium recovery pump 52, the heat medium supply pump 41, the second heat exchanger 71, the oil pump 77, and the oil pump 87 Are stored in a common container 120 with the heat storage tank group. However, these heat exchanger groups and pump groups do not necessarily need to be housed in the same container 120 as the heat storage tank groups. That is, it may be stored in a container different from the container 120 or may be arranged outside. Preferably, it is better to be arranged in the container 120 because transportation and construction on site are easy.

  The piping for connecting the heat medium and the connection configuration for the heat storage tank group are the same as in the first embodiment.

  As shown in FIG. 16, the container 120 of the present embodiment includes a first heat medium tank 42, a second heat medium tank 51, a compressor lubricating oil tank 76, a turbine lubricating oil tank 86, and a heat medium return tank 44. It is preferable that a partition 121 is provided inside so as to store them separately. The temperatures of the heat medium stored in the first heat medium tank 42, the second heat medium tank 51, the compressor lubrication oil tank 76, the turbine lubrication oil tank 86, and the heat medium return tank 44 are different. Specifically, the former temperature is high and the latter temperature is low. Therefore, by providing the partition 121 between them, the space can be divided, and in particular, the former can prevent heat loss due to heat radiation. Further, by forming the partition 121 from a heat insulating material, heat loss can be further prevented. The container 120 houses the first heat medium tank 42, the second heat medium tank 51, the compressor lubricating oil tank 76, the turbine lubricating oil tank 86, the first container 122, and the heat medium return tank 44. A second container 123 may be provided.

  Note that the present invention is not limited to the configuration of the above-described embodiment, but can be modified as exemplified below.

  In the above-described embodiment, the configuration has been described in which the compressor main bodies 22 and 24 are positive displacement screw compressor main bodies and the expanders 28 and 32 are positive displacement screw expanders. However, the present invention is not limited thereto. For example, the compressor bodies 22, 24 may be volumetric screw compressor bodies, and the expanders 28, 32 may be speed type expanders, or the compressor bodies 22, 24 may be speed type compressors. The expanders 28 and 32 may be volumetric screw expanders as the main body.

  The displacement type compressor bodies 22 and 24 may be oil-free screw air compressor bodies, and the displacement type turbines 28 and 32 may be oil-free screw turbines. According to this configuration, the discharge temperature of the oil-free screw air compressor bodies 22 and 24 can be significantly increased as compared with the discharge temperature of the oil-cooled screw air compressor body, and the discharge temperatures of the expanders 28 and 32 can be increased. The heating temperature of the working fluid to be supplied can be greatly increased. Since the possibility that oil is mixed in the working fluid can be eliminated, the possibility that oil can be degraded inside the pressure accumulating unit 12 can be eliminated. That is, it is possible to eliminate the risk of spontaneous ignition caused by the occurrence of an oil oxidation reaction inside the pressure accumulating section 12.

  The low-temperature heat medium system 60 on the compressor 11 side and the low-temperature heat medium system 60 on the generator 13 side may be separately provided. Further, only one of the low-temperature heat recovery unit on the compressor 11 side and the low-temperature heat recovery unit on the generator 13 side may be provided.

  It is sufficient that at least one low-temperature heat generating unit is included in the low-temperature heat recovery unit.

  In the above-described embodiment, the compressed air from the low-pressure stage expander 32 is released to the atmosphere after being recovered by the aftercooler 36 without being directly released to the atmosphere. Heat recovery is not limited to this. By using the compressed air from the low-pressure stage expander 32 instead of the low-temperature heat medium in the loss recovery heat preheater 26, the heat of the compressed air is recovered by the heat exchange between the air flowing from the accumulator tank 12 to the expander 28 and the compressed air. After that, it may be released through an air release silencer. Further, the heat recovery of the compressed air from the low-pressure stage expander may be performed by both the aftercooler 36 and the loss recovery heat preheater 26.

  In the above embodiment, both the air compressor 11 and the air generator 13 employ a two-stage system, but may employ a single-stage system.

  Of the first high-temperature heat medium tank 42, the second high-temperature heat medium tank 51, and the low-temperature heat medium tanks 76 (92), 86 (94), two tanks may be shared by one tank.

  The pressure accumulating tank 12 may be a steel tank, a tank using a tunnel, or a tank of a bag submerged in water. Further, the steel tank may be buried underground.

  In the above-described embodiment, the example in which each of the air compressor and the air generator is one is shown, but a plurality of air compressors and air generators may be connected in parallel. The number may be selected according to the input electric energy and the output electric energy (kW).

  The low-temperature heat medium may be water.

  In the present invention, the low-temperature heating medium system 60 only needs to be connected to at least one of the three low-temperature heating units 21, 26, and 29, and is connected to all of the three low-temperature heating units 21, 26, and 29. It is not necessary.

  In the above-described embodiment, the low-temperature heat storage unit that stores the compressor lubricating oil tank 76 and the turbine lubricating oil tank 86 in the container 120 has been described as an example. However, the low-temperature heat storage unit that is stored in the container 120 is not limited thereto. The low-temperature heat storage units housed in the container 120 may be hot water tanks 92 and 94.

  In the above-described embodiment, the first container that stores the high-temperature heat storage unit and the low-temperature heat storage unit in the same space has been illustrated, but the first container is not limited to this. The first container may be provided with a partition for separating a space for storing the high-temperature heat storage unit and a space for storing the low-temperature heat storage unit, and a plurality of containers for storing the high-temperature heat storage unit and the low-temperature heat storage unit separately. It may be.

DESCRIPTION OF SYMBOLS 10 Compressed fluid storage power generation device 11 Compressor 12 Accumulator tank (accumulator)
13 generator 20 air system 21 intake preheater (first low temperature preheater) (low temperature heating section)
22 Low-pressure compressor body 22a Casing 22b Cooling jacket (low-temperature heat recovery section)
23 Intercooler (High-temperature heat recovery section)
23a Air inlet 23b Air outlet 23c Heat medium inlet 23d Heat medium outlet 24 High-pressure stage compressor main body 24a Casing 24b Cooling jacket (low-temperature heat recovery unit)
25 Aftercooler (High-temperature heat recovery section)
25a Air inlet 25b Air outlet 25c Heat medium inlet 25d Heat medium outlet 26 Loss recovery heat preheater (second low temperature preheater) (low temperature heating unit)
27 Preheater (high temperature heating section)
27a Air inlet 27b Air outlet 27c Heat medium inlet 27d Heat medium outlet 28 High-pressure stage expander 28a Casing 28b Cooling jacket (low-temperature heat recovery unit)
29 Loss recovery heat inter-heater (third low-temperature preheater) (low-temperature heating unit)
31 Inter heater (high temperature heating unit)
31a Air inlet 31b Air outlet 31c Heat medium inlet 31d Heat medium outlet 32 Low pressure stage expander

Claims (4)

A compression step of compressing the working fluid;
A pressure accumulating step of storing the compressed working fluid in a pressure accumulating unit ;
A low-temperature heat recovery step of recovering heat generated by power loss, heat dissipation loss or mechanical loss to a low-temperature heat medium,
A low-temperature heating step of heating the working fluid stored in the pressure accumulating unit by heat exchange with heat recovered in the low-temperature heat medium,
A power generating step of generating power with a generator driven by the driving force of the working fluid from the pressure accumulating unit ,
A high-temperature heat recovery step of recovering heat from a compressed working fluid flowing toward the pressure accumulating section to a high-temperature heat medium,
A high-temperature heating step of heating the working fluid stored in the pressure accumulator with heat recovered in the high-temperature heat medium,
Only including,
The power generation method of the compressed fluid storage power generation device, wherein the low temperature heating step includes heating the working fluid sent to the high temperature heating step . The low temperature heating step comprises heating the working fluid before compressed, electric power generation method of the compressed fluid storage power generating apparatus according to claim 1. A compressor for compressing a working fluid;
A pressure accumulator that stores the compressed working fluid;
A low-temperature heat recovery unit that recovers heat generated by power loss, heat radiation loss or mechanical loss of the low-temperature heating unit to a low-temperature heat medium,
A low-temperature heating unit including a part that heats the working fluid stored in the pressure accumulating unit by heat exchange with a low-temperature heat medium recovered in the low-temperature heat recovery unit; and a driving force by the working fluid supplied from the pressure accumulating unit. A driven generator ,
A high-temperature heat recovery unit that recovers heat from the compressed working fluid flowing toward the pressure accumulation unit;
A high-temperature heating unit that heats the working fluid stored in the pressure accumulating unit with heat recovered by the high-temperature heat recovery unit ,
The compressed fluid storage and power generator , wherein the low temperature heating unit includes a portion provided to heat the working fluid sent to the high temperature heat recovery unit . The compressed fluid storage power generator according to claim 3, wherein the low-temperature heating unit includes a portion provided to heat the working fluid sucked into the compressor.

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