JP4016882B2 - Rankine cycle - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a Rankine cycle for extracting power from superheated steam, and is effective when applied to a system for extracting power from waste heat generated in a vehicle such as cooling water for an engine (internal combustion engine).
[0002]
[Prior art]
Rankine cycle is a steam generator that generates superheated steam by heating a liquid phase fluid, an expander that expands superheated steam isentropically to extract power, and liquefies steam that has been expanded by the expander. Radiator , And a liquid pump for sending a liquid phase fluid to a steam generator (see, for example, Patent Document 1).
[0003]
[Patent Document 1]
Japanese Patent No. 2540738
[0004]
[Problems to be solved by the invention]
By the way, in the invention according to Patent Document 1, a liquid pump that sends a fluid to the steam generator is required. However, when the liquid pump sucks the fluid, the suction-side pressure decreases, so the sucked fluid evaporates. As a result, the pump efficiency (volumetric efficiency) is reduced, and the fluid pressure is locally reduced near the surface of the impeller such as an impeller, resulting in boiling of the fluid and cavitation.
[0005]
When the fluid sucked by cavitation or the like is vaporized, the flow rate of the liquid discharged from the pump decreases. Therefore, the discharge flow rate does not increase even if the number of revolutions of the pump, that is, the impeller is increased. There arises a problem that the flow rate cannot be secured and a problem that the impeller is eroded by cavitation.
[0006]
In view of the above points, the present invention firstly provides a novel Rankine cycle different from the conventional one, and secondly, the pump efficiency of the pump is prevented from being lowered and the Rankine cycle is operated efficiently. The purpose is to do.
[0007]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides a steam generator (30) for heating a liquid phase fluid to generate superheated steam and an isentropic expansion of the superheated steam. An expander (33a) for extracting power and a radiator (11) for liquefying the steam that has been expanded by the expander (33a), Liquefied by radiator (11) A pump (32) for delivering liquid phase fluid to the steam generator (30), and a suction side of the pump (32); Radiator (11) A refrigerator that is provided in a fluid circuit that connects the outlet side of the fluid circuit and cools the fluid in the fluid circuit ( 10, 11, 13 , 36 , 39 ) Before starting the pump (32), when the refrigerator (10, 11, 13, 36, 39) is operated and power is taken out from the expander (33a), the refrigerator (10, 11, 13, 36) is used. , 39) It is characterized by that.
[0008]
As a result, the fluid in the fluid circuit (hereinafter referred to as suction fluid) is cooled, so that the fluid sucked into the pump (32) can be surely made into a liquid-phase fluid, and its excess The degree of cooling can be increased.
[0009]
Accordingly, it is possible to reliably prevent the suction fluid from evaporating (boiling) on the suction side of the pump (32), so that the pump (32) pump efficiency is prevented from being lowered and the Rankine cycle is operated efficiently. can do.
[0011]
Furthermore, since the refrigerators (10, 11, 13, 36, 39) are operated before starting the pump (32), When the Rankine cycle is started, since the liquid phase fluid having a large degree of supercooling can be reliably supplied to the suction side of the pump (32), the suction fluid is vaporized (boiling) on the suction side of the pump (32). Can be reliably prevented.
[0012]
Claim 2 In the invention described in Refrigerator ( 10, 11, 13 , 36 , 39 ) Is operated for a predetermined time, and then the pump (32) is started.
[0013]
Claim 3 In the invention described in (1), the pump (32) is started when the amount of the liquid-phase fluid existing in the fluid circuit becomes a predetermined amount or more.
[0014]
As a result, the liquid-phase suction fluid can be secured reliably, and the refrigerator ( 10, 11, 13 , 36 , 39 ) Is not operated, so that the heat recovery amount can be increased.
[0015]
Claim 4 In the invention described in Sucked into pump (32) The pump (32) is started when the degree of supercooling of the liquid phase fluid exceeds a predetermined value.
[0016]
As a result, the liquid-phase suction fluid can be secured reliably, and the refrigerator ( 10, 11, 13 , 36 , 39 ) Is not operated, so that the heat recovery amount can be increased.
[0018]
Claim 5 In the invention described in, the refrigerator is an electronic refrigerator using the Peltier effect. (39) It is characterized by being.
[0025]
Claim 6 In the invention described in Furthermore, a compressor (10) for sucking and compressing the gas phase fluid, a decompression means (13) for decompressing the high-pressure fluid to generate a low-pressure fluid, and a liquid-phase fluid sucked into the pump (32) An internal heat exchanger (36) that evaporates by heat exchange and flows out to the suction side of the compressor (10), and a fluid that flows into the radiator (11) the steam that has been expanded by the expander (33a) Fluid that causes the compressor (10) discharge fluid to flow into the flow path and the radiator (11), and also flows the radiator (11) outflow fluid into the internal heat exchanger (36) via the decompression means (13). The refrigerator is provided with a flow path switching valve (35a, 35b, 35c, 37) for switching the flow path, and the refrigerator is connected to the radiator (11) by means of the flow path switching valve (35a, 35b, 35c, 37). 10) While letting the discharged fluid flow in, the radiator (11) The output fluid through the pressure reducing means (13) is the internal heat exchanger (36) vapor compression type refrigerator composed by being switched to the fluid flow path for flowing into (10,11,13,36) It is characterized by that.
[0026]
As a result, the suction fluid is cooled, so that the fluid sucked into the pump (32) can be surely made into a liquid phase fluid and the degree of supercooling can be increased.
[0027]
Accordingly, it is possible to reliably prevent the suction fluid from evaporating (boiling) on the suction side of the pump (32), so that the pump (32) pump efficiency is prevented from being lowered and the Rankine cycle is operated efficiently. can do.
[0028]
Claim 7 In the invention described in item 1, the compressor (10) is operated before starting the pump (32).
[0029]
Accordingly, when the Rankine cycle is started, the liquid phase fluid having a large degree of supercooling can be reliably supplied to the suction side of the pump (32), so that the suction fluid is vaporized on the suction side of the pump (32). (Boiling) can be reliably prevented.
[0030]
Claim 8 In the invention described in (1), the pump (32) is started after at least the compressor (10) has been operated for a predetermined time.
[0031]
Claim 9 In the invention described in Further, the radiator (11) includes a gas-liquid separator (12) for separating the gas-liquid of the outflow fluid, and the gas-liquid separator (12) The pump (32) is started when the amount of the liquid phase fluid present therein becomes a predetermined amount or more.
[0032]
As a result, the liquid-phase suction fluid can be secured reliably, and the refrigerator ( 10, 11, 13, 36 ) Is not operated, so that the heat recovery amount can be increased.
[0033]
Claim 10 In the invention described in Further, the radiator (11) includes a gas-liquid separator (12) for separating the gas-liquid of the outflow fluid, and the pump (32) sucks the liquid-phase fluid separated by the gas-liquid separator (12). Gas-liquid separator (12) The pump (32) is started when the degree of supercooling of the liquid phase fluid existing therein becomes a predetermined value or more.
[0034]
As a result, the liquid-phase suction fluid can be secured reliably, and the refrigerator ( 10, 11, 13, 36 ) Is not operated, so that the heat recovery amount can be increased.
[0035]
Claim 11 In the invention described in (1), the steam generator (30) is started before the pump (32) is started.
[0036]
Thereby, the refrigerant staying in the steam generator (30) can be pushed away and the liquid phase fluid can be reliably stored on the suction side of the pump (32), so that the suction fluid is vaporized on the suction side of the pump (32) ( It is possible to reliably prevent boiling).
[0037]
Incidentally, the reference numerals in parentheses of each means described above are an example showing the correspondence with the specific means described in the embodiments described later.
[0038]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
In this embodiment, the Rankine cycle according to the present invention is applied to a vehicle, and FIG. 1 is a schematic diagram of the Rankine cycle according to the present embodiment.
[0039]
In the Rankine cycle according to the present embodiment, energy is recovered from waste heat generated in the engine 20 that constitutes a heat engine that generates driving power, and cold energy and thermal energy generated in the vapor compression refrigerator are used for air conditioning. To do. Hereinafter, the Rankine cycle will be described.
[0040]
The compressor 10 obtains power from the electric motor or the engine 20 and sucks and compresses the refrigerant, and the radiator 11 is a cooler that cools the refrigerant by exchanging heat between the flowing refrigerant and the outside air.
[0041]
The gas-liquid separator 12 is a receiver that separates the refrigerant that has flowed out of the radiator 11 into a gas-phase refrigerant and a liquid-phase refrigerant, and the decompressor 13 expands the liquid-phase refrigerant separated by the gas-liquid separator 12 under reduced pressure. Thus, in the present embodiment, a temperature type expansion valve is used that decompresses the refrigerant in an enthalpy manner and controls the throttle opening so that the degree of superheat of the refrigerant sucked into the compressor 10 becomes a predetermined value. .
[0042]
The evaporator 14 is a heat absorber that evaporates the refrigerant decompressed by the decompressor 13 and exerts an endothermic effect. The evaporator 10, the radiator 11, the gas-liquid separator 12, the decompressor 13, the evaporator 14, and the like. Constitutes a vapor compression refrigerator that moves the heat on the low temperature side to the high temperature side.
[0043]
The heater 30 is provided in a refrigerant circuit connecting the compressor 10 and the radiator 11, and heats the refrigerant flowing through the refrigerant circuit and the engine cooling water to heat the refrigerant and generate superheated vapor refrigerant. It is a steam generator, and the case where the engine cooling water flowing out from the engine 20 by the three-way valve 21 is circulated to the heater 30 is switched to the case where it is not circulated.
[0044]
The first bypass circuit 31 is a refrigerant passage that guides the liquid-phase refrigerant separated by the gas-liquid separator 12 to the refrigerant inlet / outlet side of the radiator 11 in the heater 30. A liquid pump 32 for circulating the phase refrigerant and a check valve 31a that allows the refrigerant to flow only from the gas-liquid separator 12 side to the heater 30 side are provided. Note that the suction side of the liquid pump 32 is disposed below the gas-liquid separator 12. Incidentally, the liquid pump 32 is an electric pump in this embodiment.
[0045]
The refrigerant circuit in parallel with the compressor 10 is provided with an energy recovery unit 33 that expands the superheated steam flowing out from the heater 30 and recovers the thermal energy given to the heater 30 as mechanical (rotational) energy. It has been.
[0046]
In the present embodiment, the energy recovery machine 33 is configured by the expander 33a and the generator 33b driven by the mechanical output output from the expander 33a, and the electric power generated by the generator 33b is a battery. 33c is stored.
[0047]
The second bypass circuit 34 is a refrigerant passage that connects the refrigerant outlet side of the expander 33a and the refrigerant inlet side of the radiator 11, and the second bypass circuit 34 radiates heat from the refrigerant outlet side of the expander 33a. A check valve 34 a that allows the refrigerant to flow only on the refrigerant inlet side of the vessel 11 is provided.
[0048]
The check valve 14a allows the refrigerant to flow only from the refrigerant outlet side of the evaporator 14 to the suction side of the compressor 10, and the on-off valves 35a to 35c are electromagnetic valves that open and close the refrigerant passage. .
[0049]
Further, a refrigerant circuit that connects the refrigerant outlet side of the radiator 11 and the suction side of the liquid pump 32, that is, the liquid pump 32 side of the liquid phase refrigerant outlet side of the gas-liquid separator 12 is connected to the suction side of the liquid pump 32. The refrigerant circuit is provided with an internal heat exchanger 36 for exchanging heat with the refrigerant existing in the refrigerant circuit and the low-pressure refrigerant decompressed by the decompressor 13, and the refrigerant heated by the internal heat exchanger 36 is And returned to the refrigerant outlet side of the evaporator 14.
[0050]
The three-way valve 37 switches between the case where the low-pressure refrigerant flowing out from the pressure reducer 13 flows to the evaporator 14 and the case where it flows to the internal heat exchanger 36. The on-off valves 35a to 35c, the three-way valves 21, 37, etc. It is controlled by the control device.
[0051]
Meanwhile, the water pump 22 circulates engine cooling water, and the radiator 23 is a heat exchanger that cools the engine cooling water by exchanging heat between the engine cooling water and outside air.
[0052]
In FIG. 1, a bypass circuit that bypasses the radiator 23 and flows cooling water, and a flow rate adjustment valve that adjusts the cooling water amount flowing through the bypass circuit and the cooling water amount flowing through the radiator 23 are omitted.
[0053]
Incidentally, although the water pump 22 is a mechanical pump that operates by obtaining power from the engine 20, it goes without saying that an electric pump driven by an electric motor may be used.
[0054]
Next, Rankine cycle operation according to this embodiment will be described.
[0055]
1. Air conditioning operation mode (see Fig. 2)
This operation mode is an operation mode in which the refrigerant is allowed to cool by the radiator 11 while the refrigerating capacity is exhibited by the evaporator 14.
[0056]
In this embodiment, the vapor compression refrigerator is operated only for the cooling generated by the vapor compression refrigerator, that is, the cooling operation and the dehumidifying operation using the endothermic effect, and the warm heat generated by the radiator 11 is used. Although the heating operation is not performed, the operation of the vapor compression refrigerator is the same as that during the cooling operation and the dehumidifying operation even during the heating operation.
[0057]
Specifically, the on-off valves 35a and 35c are opened with the liquid pump 32 stopped, the on-off valve 35b is closed and the compressor 10 is operated, and the three-way valve 21 is operated as shown in FIG. Then, the cooling water is circulated by bypassing the heater 30.
[0058]
Accordingly, the refrigerant circulates in the order of the compressor 10 → the heater 30 → the radiator 11 → the gas-liquid separator 12 → the decompressor 13 → the evaporator 14 → the compressor 10. In addition, since engine cooling water does not circulate through the heater 30, the refrigerant is not heated by the heater 30, and the heater 30 functions as a mere refrigerant passage.
[0059]
Therefore, the low-pressure refrigerant decompressed by the decompressor 13 absorbs heat from the air blown into the room and evaporates, and the evaporated gas-phase refrigerant is compressed by the compressor 10 and becomes a high temperature, and the heat radiator 11 Cools with air and condenses.
[0060]
In the present embodiment, chlorofluorocarbon (HFC134a) is used as the refrigerant. However, the refrigerant is not limited to HFC134a as long as the refrigerant is liquefied on the high-pressure side.
[0061]
2. Waste heat recovery operation mode
This operation mode is a mode in which the air conditioner, that is, the compressor 10 is stopped and the waste heat of the engine 20 is recovered as usable energy, and is activated before the transition to the steady operation mode in which energy recovery is performed and the steady operation mode. There is a mode.
[0062]
Then, the start mode is executed for a predetermined time from the time when the waste heat recovery start signal is issued from a switch or the like for starting the waste heat recovery operation mode, and when the predetermined time has elapsed, the operation mode is shifted to the steady operation mode.
[0063]
Hereinafter, the operation will be described in order from the start mode.
[0064]
2.1 Startup mode (see Fig. 3)
In this operation mode, the on-off valves 35a and 35c are opened with the liquid pump 32 stopped, the on-off valve 35b is closed and the compressor 10 is operated, and the three-way valve 37 is switched as shown in FIG. The low-pressure refrigerant decompressed by the decompressor 13 is circulated to the internal heat exchanger 36.
[0065]
The engine coolant is circulated by bypassing the heater 30 as in the air conditioning operation mode.
[0066]
Accordingly, the refrigerant circulates in the order of the compressor 10 → the heater 30 → the radiator 11 → the gas-liquid separator 12 → the decompressor 13 → the internal heat exchanger 36 → the compressor 10. In addition, since engine cooling water does not circulate through the heater 30, the refrigerant is not heated by the heater 30, and the heater 30 functions as a mere refrigerant passage.
[0067]
Therefore, the low-pressure refrigerant decompressed by the decompressor 13 absorbs heat from a refrigerant (hereinafter referred to as suction refrigerant) existing in a refrigerant circuit connecting the liquid-phase refrigerant outlet side of the gas-liquid separator 12 and the suction side of the liquid pump 32. The vapor phase refrigerant thus evaporated is compressed by the compressor 10 to become a high temperature, cooled by the outdoor air in the radiator 11, and condensed.
[0068]
2.2 Steady operation mode (see Fig. 4)
The liquid pump 32 is operated with the on-off valves 35a and 35c closed, and the on-off valve 35b is opened to stop the compressor 10, and the three-way valve 21 is operated as shown in FIG. The engine cooling water thus obtained is circulated to the heater 30.
[0069]
Thereby, the refrigerant circulates in the order of gas-liquid separator 12 → first bypass circuit 31 → heater 30 → energy recovery machine 33 (expansion machine 33 a) → second bypass circuit 34 → heat radiator 11 → gas-liquid separator 12. To do.
[0070]
Therefore, the superheated steam heated by the heater 30 flows into the expander 33a, and the vapor refrigerant flowing into the expander 33a reduces its enthalpy while expanding isentropically in the expander 33a. Go. For this reason, the expander 33a gives mechanical energy corresponding to the lowered enthalpy to the generator 33b, and the electric power generated by the generator 33b is stored in a battery 33c or a capacitor such as a capacitor.
[0071]
The refrigerant flowing out of the expander 33 a is cooled and condensed by the radiator 11 and stored in the gas-liquid separator 12. The liquid-phase refrigerant in the gas-liquid separator 12 is heated by the liquid pump 32. 30 side.
[0072]
The liquid pump 32 sends the liquid-phase refrigerant to the heater 30 at such a pressure that the superheated steam generated by being heated by the heater 30 does not flow backward to the gas-liquid separator 12 side.
[0073]
Next, the effect of this embodiment is described.
[0074]
In the present embodiment, the refrigerant sucked by the vapor compression refrigerator is cooled before the Rankine cycle is actually started, so that the refrigerant sucked into the liquid pump 32 can be reliably made into a liquid phase refrigerant. The degree of supercooling can be increased.
[0075]
Accordingly, it is possible to reliably prevent the suction refrigerant from evaporating (boiling) on the suction side of the liquid pump 32, so that the pump efficiency of the liquid pump 32 is prevented from being lowered and the Rankine cycle is operated efficiently. Can do.
[0076]
Further, before the Rankine cycle is actually started, the refrigerant sucked in the refrigerant circuit is condensed by cooling the sucked refrigerant in the vapor compression refrigerator, so that the waste heat is collected. It is possible to prevent the refrigerant from staying in the refrigerant circuit that is not used during the recovery operation. As a result, the amount of refrigerant that can be effectively utilized during the waste heat recovery operation increases, so that the amount of refrigerant to be charged during the Rankine cycle can be minimized.
[0077]
In addition, since the suction side of the liquid pump 32 is disposed below the gas-liquid separator 12, the pressure due to the weight of the refrigerant acts on the suction side of the liquid pump 32, so that the suction side refrigerant pressure boils due to the suction pressure. It can prevent that it falls below pressure, and can prevent that the liquid pump 32 pump efficiency falls.
[0078]
(Second Embodiment)
In the present embodiment, as shown in FIG. 5, the liquid pump 32, the gas-liquid separator 12 and the internal heat exchanger 36 are integrated, or the liquid pump 32 and the gas-liquid separator 12 are brought close to the internal heat exchanger 36. As a result, not only the refrigerant sucked but also the liquid pump 32 and the gas-liquid separator 12 can be cooled at the start-up in the internal heat exchanger 36.
[0079]
As a result, since the liquid pump 32 and the gas-liquid separator 12 having a relatively large heat capacity can be cooled, the degree of supercooling of the suction refrigerant can be reliably increased, and the pump efficiency of the liquid pump 32 is reduced. And the Rankine cycle can be operated efficiently.
[0080]
(Third embodiment)
In the present embodiment, as shown in FIG. 6, a supercooler 38 that cools the liquid-phase refrigerant with outside air is provided between the gas-liquid separator 12 and the internal heat exchanger 36.
[0081]
In the present embodiment, the radiator 11, the gas-liquid separator 12, and the supercooler 38 are integrated by brazing or the like.
[0082]
Thereby, since the degree of supercooling of the suction refrigerant can be increased in the steady operation mode, it is possible to stably prevent the liquid pump 32 from being lowered and to efficiently operate the Rankine cycle. .
[0083]
(Fourth embodiment)
In the above-described embodiment, the startup mode is executed for a predetermined time. The Thereafter, the operation mode is shifted to the steady operation mode. In the present embodiment, as shown in FIG. 7, the gas-liquid separator 12 is provided with a liquid level sensor 12a for detecting the liquid level position of the liquid-phase refrigerant. The start-up mode is executed until the liquid level in the inside exceeds a predetermined value, that is, until the amount of refrigerant sucked in the liquid phase exceeds a predetermined amount.
[0084]
As a result, the liquid-phase suction refrigerant can be reliably ensured, and the start-up mode is not executed more than necessary, so that the amount of waste heat recovery can be increased.
[0085]
In addition, although FIG. 7 applied this embodiment to 1st Embodiment, this embodiment is not limited to this.
[0086]
(Fifth embodiment)
In the above-described embodiment, the startup mode is executed for a predetermined time. The Thereafter, the operation mode is shifted to the steady operation mode. In this embodiment, as shown in FIG. 8, the gas-liquid separator 12 is provided with a first temperature sensor 12b for detecting the temperature of the liquid phase refrigerant, and the internal heat exchanger is provided. A second temperature sensor 12c for detecting the temperature of the suction refrigerant is provided on the refrigerant outlet side of 36, and the temperature difference between the two temperature sensors 12b and 12c, that is, the degree of supercooling of the liquid-phase refrigerant is calculated. The activation mode is executed until the value exceeds a predetermined value.
[0087]
As a result, the liquid-phase suction refrigerant can be reliably ensured, and the start-up mode is not executed more than necessary, so that the amount of waste heat recovery can be increased.
[0088]
In addition, although FIG. 8 applied this embodiment to 1st Embodiment, this embodiment is not limited to this.
[0089]
(Sixth embodiment)
In the above-described embodiment, the suction refrigerant is cooled by the vapor compression refrigerator, but in this embodiment, as shown in FIG. 9, the suction refrigerant is cooled by the electronic refrigerator 39 using the Peltier effect. It is.
[0090]
Thereby, since the suction refrigerant is cooled by the electronic refrigerator 39 that is smaller than the vapor compression refrigerator, it is possible to improve the mountability of the Rankine cycle on the vehicle.
[0091]
In the present embodiment, similarly to the above-described embodiment, the suction refrigerant is cooled by the electronic refrigerator 39 in the start-up mode before the steady operation mode. However, the present embodiment is not limited to this. For example, the suction refrigerant may be cooled by the electronic refrigerator 39 even in the steady operation mode.
[0092]
Moreover, when the refrigerant | coolant suck | inhaled at the time of restart after a stop etc. has sufficient supercooling degree, you may stop the electronic refrigerator 39 even at the time of start-up.
[0093]
( Reference example )
In the above-described embodiment, the boiling of the suction refrigerant is suppressed by cooling the suction refrigerant. Reference example As shown in FIG. 10, the feed pump 32a is arranged on the suction side of the liquid pump 32 to prevent the suction side pressure of the liquid pump 32 from dropping below the boiling pressure. This is to prevent the pump efficiency from decreasing.
[0094]
The feed pump 32a is housed in the gas-liquid separator 12 so that the suction port of the feed pump 32a is positioned below the liquid level in the gas-liquid separator 12, and the suction side of the liquid pump 32 and the feed pump 32a The pumps 32 and 32a are integrated by directly connecting to the discharge side.
[0095]
Book Reference example In this case, the liquid pump 32 and the feed pump 32a are started (operated) or stopped at the same time. However, when the Rankine cycle is started, there is no liquid phase refrigerant on the suction side of the feed pump 32a, that is, the gas-liquid separator 12 When the vapor compression refrigerator is operated as a start-up mode and the liquid-phase refrigerant is accumulated in the gas-liquid separator 12, and when a predetermined amount or more of the liquid-phase refrigerant is accumulated in the gas-liquid separator 12, the vapor compression type The refrigerator is stopped and the liquid pump 32 and the feed pump 32a are operated.
[0096]
(No. 7 Embodiment)
In the above-described embodiment, for the vapor compression refrigerator Radiator And for Rankine cycle Radiator And one Radiator 11, in this embodiment, as shown in FIG. 11, the radiator 11a for the vapor compression refrigerator and the Rankine cycle Radiator 11b are provided so that the vapor compression refrigerator and Rankine cycle can be operated independently.
[0097]
Accordingly, in this embodiment, a gas-liquid separator 40 for a vapor compression refrigerator and a gas-liquid separator 41 for a Rankine cycle are provided, and the expander 33a and the compressor 10 are connected to an electromagnetic clutch 10a or the like. It connects via the power transmission means which transmits power intermittently.
[0098]
And when operating a Rankine cycle at the time of operation of a vapor compression type refrigerator, connecting the electromagnetic clutch 10a, the energy recovered from waste heat is given to the compressor 10, and when not operating a Rankine cycle, a vapor compression type refrigerator When operating the compressor 10, the compressor 10 is operated by the engine 20.
[0099]
In addition, when it is difficult to operate the compressor 10 only with the energy collect | recovered from waste heat, it cannot be overemphasized that the compressor 10 may be operated by both the expansion machine 33a and the engine 20. FIG.
[0100]
Further, in the present embodiment, the radiator 11a for the vapor compression refrigerator and the Rankine cycle Radiator Since it is independent of 11b, high temperature (80 ° C. to 110 ° C.) engine cooling water can be passed through the heater 30 in the start-up mode in which the refrigerant sucked is cooled in the vapor compression refrigerator.
[0101]
Therefore, in the present embodiment, in the start-up mode, the steam generator is operated by flowing high-temperature (80 ° C. to 110 ° C.) engine cooling water to the heater 30 to generate superheated steam, and stays in the heater 30. The cooled refrigerant is forced to flow through the gas-liquid separator 41 and the internal heat exchanger 36 so that the liquid-phase refrigerant can easily accumulate on the suction side of the liquid pump 32.
[0102]
The time for performing the start-up mode is the same as any one of the first embodiment, the fourth embodiment, and the fifth embodiment.
[0103]
Incidentally, the heater 42 heats the air blown into the room using the engine coolant as a heat source, and the air mix door 43 adjusts the amount of hot air passing through the heater 42 and the amount of cold air that bypasses the heater 42 to blow out air into the room. The temperature is adjusted.
[0104]
(Other embodiments)
The present invention is not limited to the above-described embodiment, and at least two of the above-described embodiments may be combined.
[0105]
Further, in the above-described embodiment, the energy recovered by the energy recovery machine 33 is stored in the capacitor, but may be stored as mechanical energy such as elastic energy by kinetic energy by a flywheel or a spring.
[0106]
In the above-described embodiment, the present invention is applied to a vehicle, but the application of the present invention is not limited to this.
[Brief description of the drawings]
FIG. 1 is a schematic diagram of a Rankine cycle according to a first embodiment of the present invention.
FIG. 2 is a schematic diagram of a Rankine cycle according to the first embodiment of the present invention.
FIG. 3 is a schematic diagram of a Rankine cycle according to the first embodiment of the present invention.
FIG. 4 is a schematic diagram of a Rankine cycle according to the first embodiment of the present invention.
FIG. 5 is a schematic diagram of a Rankine cycle according to a second embodiment of the present invention.
FIG. 6 is a schematic diagram of a Rankine cycle according to a third embodiment of the present invention.
FIG. 7 is a schematic view of a Rankine cycle according to a fourth embodiment of the present invention.
FIG. 8 is a schematic view of a Rankine cycle according to a fifth embodiment of the present invention.
FIG. 9 is a schematic view of a Rankine cycle according to a sixth embodiment of the present invention.
FIG. 10 Reference example It is a schematic diagram of the Rankine cycle which concerns on.
FIG. 11 shows the first of the present invention. 7 It is a mimetic diagram of a Rankine cycle concerning an embodiment.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 10 ... Compressor, 11 ... Radiator, 12 ... Gas-liquid separator, 13 ... Decompressor,
14 ... Evaporator, 20 ... Engine, 30 ... Heater,
31 ... 1st bypass circuit, 32 ... Liquid pump, 33 ... Energy recovery machine,
33a ... expander, 33b ... generator, 36 ... internal heat exchanger.

Claims (11)

A steam generator (30) for heating the liquid phase fluid to generate superheated steam;
An expander (33a) for expanding the superheated steam isentropically to extract power;
A radiator (11) for liquefying the steam that has been expanded in the expander (33a);
A pump (32) for sending the liquid phase fluid liquefied by the radiator (11) to the steam generator (30);
Refrigerators ( 10 , 11 , 13 , 36 , 39 ) provided in a fluid circuit connecting the suction side of the pump (32) and the outlet side of the radiator (11) and cooling the fluid in the fluid circuit; With
Before starting the pump (32), operate the refrigerator (10, 11, 13, 36, 39),
The Rankine cycle characterized in that when the power is taken out from the expander (33a), the operation of the refrigerator (10, 11, 13, 36, 39) is stopped . The refrigerator (10, 11, 13, 36, 39) after the was operated a predetermined time, a Rankine cycle according to claim 1, characterized in that for starting the pump (32). When the liquid phase fluid volume present in the fluid circuit is equal to or larger than a predetermined amount, a Rankine cycle according to claim 1, characterized in that for starting the pump (32). When the degree of supercooling of the liquid phase fluid sucked the pump (32) is equal to or above a predetermined value, a Rankine cycle according to claim 1, characterized in that for starting the pump (32). The Rankine cycle according to any one of claims 1 to 4 , wherein the refrigerator is an electronic refrigerator (39) using a Peltier effect. A compressor (10) for sucking and compressing the gas phase fluid;
Decompression means (13) for depressurizing the high-pressure fluid to produce a low-pressure fluid;
An internal heat exchanger (36) for evaporating the low-pressure fluid by exchanging heat with the liquid-phase fluid sucked into the pump (32) and flowing out to the suction side of the compressor (10);
A fluid flow path for allowing the steam that has been expanded by the expander (33a) to flow into the radiator (11), a fluid discharged from the compressor (10) to the radiator (11), and the heat dissipation (11) a flow path switching valve (35a, 35b, 35c, 37) for switching a fluid flow path for flowing out fluid to the internal heat exchanger (36) via the pressure reducing means (13). ,
The refrigerator causes the compressor (10) discharge fluid to flow into the radiator (11) by the flow path switching valve (35a, 35b, 35c, 37) and the radiator (11) outflow fluid. It is a vapor compression refrigeration machine (10 , 11 , 13, 36) configured by switching to a fluid flow path that flows into the internal heat exchanger (36) via the pressure reducing means (13). The Rankine cycle according to any one of claims 1 to 4 , characterized in that: The Rankine cycle according to claim 6 , wherein the compressor (10) is operated before starting the pump (32). The Rankine cycle according to claim 7 , wherein the pump (32) is started after at least the compressor (10) is operated for a predetermined time. Further, the radiator (11) includes a gas-liquid separator (12) for separating the gas-liquid of the outflow fluid,
The Rankine cycle according to claim 7 , wherein the pump (32) is started when the amount of liquid phase fluid existing in the gas-liquid separator (12) becomes a predetermined amount or more. Further, the radiator (11) includes a gas-liquid separator (12) for separating the gas-liquid of the outflow fluid,
The pump (32) sucks the liquid phase fluid separated by the gas-liquid separator (12),
The Rankine cycle according to claim 7 , wherein the pump (32) is started when the degree of supercooling of the liquid-phase fluid existing in the gas-liquid separator (12) exceeds a predetermined value. . Before starting the pump (32), a Rankine cycle according to any one of claims 1 to 10, characterized in that for starting the steam generator (30).

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