JP2006017108A - Heat cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat cycle device provided with refrigeration cycle and Rankine cycle capable of reduction of start error at a time of Rankine cycle operation and drop of cycle efficiency. <P>SOLUTION: Exhaust heat collection operation mode (Rankine cycle) is started and is operated foe a predetermined time T1 (S430-S450). When difference P2-P1 between upstream pressure P1 and downstream pressure P2 of a liquid pump is greater than predetermined pressure P, exhaust heat collection operation mode is continued. When the same is the predetermined pressure P or less, exhaust heat collection operation mode is restarted (S430-S450) after starting air conditioning operation mode is started (S480-S500). <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a Rankine cycle that obtains power from thermal energy applied to a refrigerant.

Conventionally, what is called a refrigeration cycle apparatus and what is called a Rankine cycle apparatus are known as thermal cycle apparatuses. The refrigeration cycle apparatus is an apparatus that provides high or low temperature by compressing a refrigerant by power and conveying heat. A Rankine cycle device is a device that obtains power from thermal energy applied to a refrigerant. As Rankine cycle devices, for example, those disclosed in Patent Document 1 and Patent Document 2 are known. Such a Rankine cycle device can be used, for example, as a device that recovers waste heat and obtains power for power generation, or as a device that recovers waste heat of an internal combustion engine of a vehicle and obtains power of the vehicle.
Japanese Patent No. 3356449 Japanese Utility Model Publication No. 63-92021

  In the patent application of Japanese Patent Application No. 2003-390893, the present inventors have proposed a vehicle air conditioner (refrigeration cycle) including a Rankine cycle for recovering thermal energy from waste heat of an engine mounted on a vehicle ( Hereinafter referred to as a prior application example).

  The prior application example will be described with reference to FIG. 1. The prior application example includes an air conditioning operation mode in which the refrigerant flows in the order of the reversible rotating machine 10 → the radiator 11 → the gas-liquid separator 12 → the decompressor 13 → the evaporator 14. A component as a refrigeration cycle apparatus providing refrigeration cycle operation) is provided.

  Furthermore, the liquid phase piping 31 which connects the piping which comprises the refrigerating cycle for providing an air-conditioning operation mode, and the steam generator 30, and the liquid which arrange | positions in the liquid phase piping 31 and sends a liquid phase refrigerant | coolant to the steam generator 30 And a component as a Rankine cycle device that provides a waste heat recovery operation mode (Rankine cycle operation) that includes a pump 32 and flows the refrigerant in the order of the liquid pump 32 → the steam generator 30 → the reversible rotary machine 10 → the radiator 11. Is provided.

  Thus, the vehicle interior space can be air-conditioned during the air-conditioning operation mode, and the waste heat of the engine 20 can be recovered as power by the reversible rotary machine 10 during the waste heat recovery operation mode.

  However, in the heat cycle device of the prior application example, when the liquid refrigerant stored in the gas-liquid separator 12 is small due to the operating state of the vehicle air conditioner (refrigeration cycle) or the temperature inside the liquid pump 32 increases. When the liquid phase refrigerant in the liquid pump 32 is vaporized, the gas phase refrigerant bubbles may enter the liquid pump 32 and the liquid phase refrigerant may not be sent to the vapor generator 30 even if the liquid pump 32 is activated. is there. As a result, the waste heat recovery operation mode (Rankine cycle) may not start normally.

  Even if the liquid pump 32 can send the liquid-phase refrigerant to the vapor generator 30, if the gas-phase refrigerant bubbles are mixed in the liquid pump 32, the operation efficiency of the liquid pump 32 (power consumption of the pump) The transport amount of the refrigerant with respect to the refrigerant decreases. That is, there is a possibility that the amount of the liquid phase refrigerant sent to the steam generator 30 is reduced and the efficiency of the Rankine cycle is lowered.

  One object of the present invention is to reduce the risk of poor start-up of the Rankine cycle device.

  Another object of the present invention is to reduce the risk of a decrease in efficiency of the Rankine cycle apparatus.

  Still another object of the present invention is to stabilize the Rankine cycle apparatus by utilizing the function as the refrigeration cycle apparatus in a thermal cycle apparatus that can be used for both the operation as the Rankine cycle apparatus and the operation as the refrigeration cycle apparatus. Is to enable efficient driving.

  In order to achieve the above object, the present invention employs the following technical means.

  According to the first aspect of the present invention, the rotary fluid machine (10, 10b, 10c) that mutually converts the fluid energy and mechanical rotational energy of the refrigerant, and the rotary fluid machine (10, 10b, 10c). The condenser (11) for condensing the refrigerant supplied from the liquid, the liquid pump (32, 300) for sending the refrigerant supplied from the condenser (11), and the refrigerant sent by the liquid pump as the heating element (20). ) A Rankine cycle system (10, 11, 30, 32, 300) including a steam generator (30) that is heated by the heat of) and an evaporator (14) that evaporates the refrigerant supplied from the condenser (11). In the operation of the refrigeration cycle system (10, 11, 13, 14) including the Rankine cycle system (10, 11, 30, 32, 300), the refrigeration cycle system (10, 11, And a control device (40) for performing a refrigerant condensation operation in which the refrigerant of (3, 14) is compressed by the rotary fluid machine (10, 10b, 10c) and condensed by the condenser (11). Adopt a heat cycle device.

  According to the present invention, when the Rankine cycle system is operated, the refrigerant in the refrigeration cycle system is compressed by the rotary fluid machine and condensed by the condenser, so that the liquid phase refrigerant can be supplied to the Rankine cycle system. . As a result, it is possible to suppress a start-up failure of the Rankine cycle system or a decrease in efficiency during operation.

  In the invention according to claim 2, the control device (40) starts the operation of the Rankine cycle system (10, 11, 30, 32, 300), and then the Rankine cycle system (10, 11, 30). , 32, 300) determining means for determining whether the operation is normal or abnormal, and if it is determined normal, the operation of the Rankine cycle system (10, 11, 30, 32, 300) is continued, When it determines, it has a control means which performs the refrigerant condensation operation, The heat cycle device according to claim 1 is adopted.

  According to the present invention, when the abnormality of the Rankine cycle system is determined, the refrigerant condensing operation is executed. Therefore, the liquid phase refrigerant can be supplied to the Rankine cycle system, and the abnormal state caused by the shortage of the liquid phase refrigerant is suppressed. be able to.

  In one embodiment of the present invention, the refrigerant condensing operation can be executed by temporarily stopping the operation of the Rankine cycle system. In other embodiments, the refrigerant condensing operation can be performed in parallel while continuing operation of the Rankine cycle system.

  In the invention according to claim 3, further, an upstream refrigerant pressure sensor (42) that is disposed at a refrigerant flow upstream side portion of the liquid pump (32, 300) and measures the pressure of the refrigerant, and the liquid pump (32, 300). 300) and a downstream refrigerant pressure sensor (43) for measuring the pressure of the refrigerant. The determination means includes the Rankine cycle system (10, 11, 30, 32, 300). During operation, the difference value (P2−P1) between the detected pressure value (P2) of the downstream refrigerant pressure sensor (43) and the detected pressure value (P1) of the upstream refrigerant pressure sensor (42) is a predetermined pressure value (P ), The operation of the Rankine cycle (10, 11, 30, 32, 300) is determined to be normal, and the detected pressure value (P2) of the downstream refrigerant pressure sensor (43) and the upstream refrigerant pressure are determined. SE When the difference value (P2−P1) from the detected pressure value (P1) of the spring (42) is equal to or less than the predetermined pressure value (P), the Rankine cycle (10, 11, 30, 32, 300) is operated. The heat cycle apparatus according to claim 2 is employed.

  According to the present invention, it is possible to accurately determine an abnormality of the Rankine cycle system resulting from a shortage of liquid phase refrigerant.

  In the invention according to claim 4, the determination means is configured such that the work of the liquid pump (32, 300) is larger than a predetermined work during the Rankine cycle system (10, 11, 30, 32, 300) operation. In this case, it is determined that the operation of the Rankine cycle system (10, 11, 30, 32, 300) is normal, and when the work of the liquid pump (32, 300) is equal to or less than a predetermined work, the Rankine The heat cycle device according to claim 2, wherein the operation of the cycle system (10, 11, 30, 32, 300) is determined to be abnormal.

  According to the present invention, it is possible to accurately determine an abnormality of the Rankine cycle system resulting from a shortage of liquid phase refrigerant.

  The invention according to claim 5 is characterized in that the liquid pump is an electric liquid pump (32), and the work amount is indicated by an amount of electric power consumed by the electric liquid pump (32). 4 is adopted.

  According to the present invention, an abnormality of the Rankine cycle system can be determined with a simple configuration.

  In the invention described in claim 6, the air conditioner further includes air blowing means (14 a) for blowing air whose temperature is adjusted by the refrigeration cycle system (10, 11, 13, 14), and the control device (40) The heat cycle apparatus according to any one of claims 1 to 5, wherein the refrigerant condensing operation is performed in a state where the air blowing means (14a) is not operated.

  According to the present invention, the refrigerant condensing operation is provided by the operation as a cooling device or a refrigeration device of the refrigeration cycle system, and the state in which the blowing unit is not operated is provided by the means for providing the operation of increasing the liquid phase refrigerant. . As a result, liquid phase refrigerant can be reliably supplied.

  The invention according to claim 7 further includes a sensor (46, 47) that measures a physical quantity having a correlation with the temperature of the refrigerant inside the liquid pump (32, 300), and the control device (40) includes the controller (40). The time from when the refrigerant condensing operation is started until the physical quantity measured by the sensors (46, 47) reaches a value indicating that the refrigerant inside the refrigerant pump (32) is in a supercooled state, The heat cycle device according to any one of claims 1 to 6, wherein a duration time for continuing the refrigerant condensation operation is employed.

  According to the present invention, excessive refrigerant condensation operation can be suppressed.

  In the invention according to claim 8, the condenser (11) is a heat exchanger that condenses the refrigerant by exchanging heat between the outside air and the refrigerant, and further includes an outside air temperature sensor that measures the temperature of the outside air ( 45) and sensors (46, 47) for measuring physical quantities having a correlation with the temperature of the refrigerant inside the liquid pump (32, 300), and the control device (40) includes the outside air temperature sensor (45). The target temperature at which the refrigerant inside the refrigerant pump (32) is in a supercooled state is determined based on the outside air temperature measured by the above, and after the refrigerant condensation operation is started, the sensors (46, 47) The heat cycle apparatus according to any one of claims 1 to 6, wherein a time until the measured physical quantity reaches a value indicating the target temperature is set as a continuation time for continuing the refrigerant condensation operation. adopt.

  According to the present invention, excessive refrigerant condensation operation can be suppressed.

  In a ninth aspect of the invention, the thermal cycle device according to the seventh or eighth aspect is employed, wherein the sensor is a temperature sensor (46) for measuring a temperature of the housing of the refrigerant pump.

  According to the present invention, a simple configuration can be provided.

  The invention according to claim 10 is characterized in that the sensor is a temperature sensor (47) for measuring the temperature of air immediately after heat exchange with the refrigerant in the evaporator (14). 8 is adopted.

  According to the present invention, a simple configuration can be provided.

  In the invention according to claim 11, the condenser (11) is a heat exchanger that condenses the refrigerant by exchanging heat between the outside air and the refrigerant, and further includes an outside air temperature sensor that measures the temperature of the outside air ( 45), and the control device (40) includes duration setting means for determining a duration (T21) for continuing the refrigerant condensing operation according to the temperature measured by the outside air temperature sensor (45). The heat cycle apparatus according to any one of claims 1 to 6 is employed.

  According to the present invention, excessive refrigerant condensation operation can be suppressed.

  In the invention according to claim 12, the rotary fluid machine is a reversible rotary machine (10) that can be reversibly operated as an expander that expands the refrigerant to extract power, or a compressor that compresses the refrigerant by receiving power. The heat cycle apparatus according to any one of claims 1 to 11 is employed.

  According to the present invention, by using a rotary fluid machine that can reversibly function as an expander or compressor, the refrigerant condensation operation is performed by causing the rotary fluid machine to function as a compressor when operating the Rankine cycle system. can do.

  In the invention according to claim 13, the control device (40) operates the rotary fluid machine as the expander to start operation of the Rankine cycle system (10, 11, 30, 32, 300). The heat cycle apparatus according to claim 12, wherein the refrigerant condensation operation is performed by operating the rotary fluid machine as the compressor before.

  According to the present invention, the refrigerant fluid operation can be realized prior to the operation of the Rankine cycle system by reversibly functioning the rotary fluid machine.

  In the invention according to claim 14, the reversible rotating machine (10) is configured as an integral structure with the liquid pump (32, 300), and the liquid pump (32, 300) is configured with the refrigeration cycle system ( The heat according to claim 12 or 13, characterized in that it is arranged to be cooled by a gaseous refrigerant sucked into the reversible rotary machine (10) during operation of 10, 11, 13, 14). Cycle equipment is adopted.

  According to this invention, the temperature of the liquid pump can be lowered by operating the refrigeration cycle system.

  The invention according to claim 15 is characterized in that the rotary fluid machine includes an expander (10) for extracting power by expanding a refrigerant and a compressor (10b) for compressing the refrigerant by receiving power. The heat cycle apparatus according to any one of claims 1 to 11 is employed.

  According to this invention, by providing the expander and the compressor, the refrigerant condensing operation can be executed by causing the compressor to function during the operation of the Rankine cycle system.

  In invention of Claim 16, before the said control apparatus (40) operates the said expander (10c) and starts the driving | operation of the said Rankine cycle system (10, 11, 30, 32, 300), The heat cycle device according to claim 15, wherein the refrigerant condensing operation is performed by operating the compressor (10b).

  According to this invention, the refrigerant condensing operation prior to the operation of the Rankine cycle system can be realized.

  In invention of Claim 17, when the said control apparatus (40) operates the said expander (10c) and starts the driving | operation of the said Rankine cycle system (10, 11, 30, 32, 300), At the same time, the compressor (10b) is operated to perform the refrigerant condensing operation, and the heat cycle device according to claim 15 is adopted.

  According to the present invention, the refrigerant condensing operation can be realized at the start of the operation of the Rankine cycle system. The refrigerant condensing operation can be executed in parallel with the operation of the Rankine cycle system.

  In the invention according to claim 18, a Rankine cycle including a liquid pump (32, 300) for sending a refrigerant and a steam generator (30) for heating the refrigerant sent by the liquid pump by heat of a heating element (20). A refrigeration cycle system (10, 11, 13, 14) including a system (10, 11, 30, 32, 300), an evaporator (14) for evaporating the refrigerant, and the Rankine cycle system (10, 11, 30, And a control device (40) for performing a cooling operation for cooling the liquid pump by operating the refrigeration cycle system (10, 11, 13, 14). Cycle equipment is adopted.

  According to this invention, when the Rankine cycle system is operated, the liquid pump (32, 300) can be cooled, and the occurrence of problems due to the gas-phase refrigerant can be suppressed.

  In the invention described in claim 19, the refrigeration cycle system includes a compressor (10, 10b), and the liquid pump (32, 300) is generated by a gas-phase refrigerant sucked into the compressor (10, 10b). The heat cycle apparatus according to claim 18, wherein the heat cycle apparatus is arranged to be cooled.

  According to the present invention, it is possible to provide a configuration in which rotating machines can be arranged in an integrated manner and the liquid pump is cooled under the configuration.

  In the invention according to claim 20, the control device (40) is configured to start the operation of the Rankine cycle system (10, 11, 30, 32, 300) and / or the Rankine cycle system (10, The heat cycle apparatus according to claim 18 or 19, wherein the cooling operation is performed during the operation of 11, 30, 32, 300).

  According to this invention, the liquid pump can be cooled, and the occurrence of problems due to the gas-phase refrigerant can be suppressed. By performing the cooling operation before starting the operation of the Rankine cycle system, it is possible to reduce the gas-phase refrigerant in the liquid pump and suppress the start-up failure of the Rankine cycle system. Further, the start-up failure of the Rankine cycle system can also be suppressed by performing the cooling operation in the initial start-up period immediately after the start of operation of the Rankine cycle system. Further, by performing the cooling operation during the operation of the Rankine cycle system, it is possible to suppress a decrease in the efficiency of the Rankine cycle system.

  In the invention according to claim 21, in the heat cycle device, the low-pressure refrigerant is evaporated to absorb heat from the low temperature side, and the evaporated gas phase refrigerant is compressed to increase the temperature to absorb heat from the low temperature side. Refrigeration cycle (10, 11, 13, 14) that condenses the gas-phase refrigerant to a liquid phase refrigerant by radiating heat to the high temperature side, and the refrigeration cycle (10, 11, 13 and 14) a vapor generator (30) for generating a gas-phase refrigerant by heating the liquid-phase refrigerant, and a liquid-phase refrigerant take-out section (12) for taking out the liquid-phase refrigerant from the refrigeration cycle (10, 11, 13, 14). , 52) and a liquid phase pipe (31) connecting the steam generator (30) and a liquid pump (32, 300) arranged in the liquid phase pipe (31) and sending a liquid phase refrigerant to the steam generator (30). ) And an expander (1 ) And a condenser (11) for condensing the gas-phase refrigerant that has been expanded in the expander (10), a Rankine cycle (10, 11, 30, 32, 300), and a refrigeration cycle (10, 11, 13, 14) and the Rankine cycle (10, 11, 30, 32, 300), and the Rankine cycle (10, 11, 30, 32, 300) and switching means (35a, 36) for switching between the operation of the refrigeration cycle (10, 11, 13, 14), and the control means (40) includes a Rankine cycle (10 , 11, 30, 32, 300), the refrigerant condensation operation is performed by operating the refrigeration cycle (10, 11, 13, 14) to condense the vapor-phase refrigerant into a liquid-phase refrigerant. After contraction operation, characterized in that is adapted to operate the Rankine cycle (10,11,30,32,300).

  According to this, by operating the refrigeration cycle (10, 11, 13, 14) before operating the Rankine cycle (10, 11, 30, 32, 300), the vapor-phase refrigerant is condensed and the liquid-phase refrigerant is condensed. Can be. As a result, the liquid pump (32, 300) can reliably suck the liquid refrigerant from the liquid refrigerant extraction part (12, 52) and send it to the steam generator 30, so the Rankine cycle (10, 11, 30) 32, 300) is suppressed.

  Moreover, since the fall of the operating efficiency of a liquid pump (32, 300) by mixing of the bubble of a gaseous-phase refrigerant | coolant can also be suppressed, the efficiency fall of Rankine cycle can be reduced.

  In the invention according to claim 22, in the heat cycle device, the low-pressure refrigerant is evaporated to absorb heat from the low temperature side, and the evaporated gas phase refrigerant is compressed to increase the temperature to absorb heat from the low temperature side. Refrigeration cycle (10, 11, 13, 14) that condenses the gas-phase refrigerant to a liquid phase refrigerant by radiating heat to the high temperature side, and the refrigeration cycle (10, 11, 13 and 14) a vapor generator (30) for generating a gas-phase refrigerant by heating the liquid-phase refrigerant, and a liquid-phase refrigerant take-out section (12) for taking out the liquid-phase refrigerant from the refrigeration cycle (10, 11, 13, 14). , 52) and a liquid phase pipe (31) connecting the steam generator (30) and a liquid pump (32, 300) arranged in the liquid phase pipe (31) and sending a liquid phase refrigerant to the steam generator (30). ) And an expander (1 ) And a condenser (11) for condensing the gas-phase refrigerant that has been expanded in the expander (10), a Rankine cycle (10, 11, 30, 32, 300), and a refrigeration cycle (10, 11, 13, 14) and the Rankine cycle (10, 11, 30, 32, 300), and the Rankine cycle (10, 11, 30, 32, 300) and switching means (35a, 36) for switching between the operation of the refrigeration cycle (10, 11, 13, 14), and the control means (40) includes a Rankine cycle (10 11, 30, 32, 300) after the operation, it is determined whether the operation of the Rankine cycle (10, 11, 30, 32, 300) is normal or abnormal. If the operation of the cycle (10, 11, 30, 32, 300) is continued and determined to be abnormal, the operation of the Rankine cycle (10, 11, 30, 32, 300) is stopped, and the refrigeration cycle (10, 11, 13, 14) is operated to perform a refrigerant condensation operation for recovering the liquid phase refrigerant, and after the refrigerant condensation operation, the Rankine cycle (10, 11, 30, 32, 300) is operated again. It is characterized by that.

  According to this, only when the operation of the Rankine cycle (10, 11, 30, 32, 300) is abnormal, the refrigeration cycle (10, 11, 13, 14) is operated, and the same effect as in claim 1 is achieved. Therefore, it is possible to prevent unnecessary operation of the refrigeration cycle before operating the Rankine cycle (10, 11, 30, 32, 300).

  According to a twenty-third aspect of the present invention, in the thermal cycle device according to the twenty-second aspect, the upstream of the liquid pump (32, 300) disposed upstream of the refrigerant flow and outputting the refrigerant pressure to the control means (40). A refrigerant pressure sensor (42), and a downstream refrigerant pressure sensor (43) that is disposed at a downstream side of the refrigerant flow of the liquid pump (32, 300) and outputs the refrigerant pressure to the control means (40). (40) indicates the detected pressure value (P1) of the upstream refrigerant pressure sensor (42) from the detected pressure value (P2) of the downstream refrigerant pressure sensor (43) during the Rankine cycle (10, 11, 30, 32, 300) operation. ) Is larger than the predetermined pressure value (P), the Rankine cycle (10, 11, 30, 32, 300) is operated normally, and the downstream refrigerant pressure sensor (43 When the value (P2-P1) obtained by subtracting the detected pressure value (P1) of the upstream refrigerant pressure sensor (42) from the detected pressure value (P2) of the engine is equal to or less than the predetermined pressure value (P), the Rankine cycle (011, 30 , 32) is determined to be abnormal.

  By the way, when the liquid pump (32, 300) is operating normally, the detected pressure value (P1) of the upstream refrigerant pressure sensor (42) is higher than the detected pressure value (P2) of the downstream refrigerant pressure sensor (43). Get smaller. Thereby, when the differential value (P2-P1) is specifically equal to or less than the predetermined pressure value (P), it is possible to determine that the operation of the Rankine cycle (10, 11, 30, 32, 300) is abnormal.

  According to a twenty-fourth aspect of the present invention, in the thermal cycle device according to the twenty-second aspect, the control means (40) is configured so that the liquid pump is operated during the Rankine cycle (10, 11, 30, 32, 300) operation. When the work amount of (32, 300) is larger than the predetermined work amount, the Rankine cycle (10, 11, 30, 32, 300) is operated normally, and the work amount of the liquid pump (32, 300) is the predetermined work amount. If the amount is less than or equal to the amount, the operation of the Rankine cycle (10, 11, 30, 32, 300) may be determined to be abnormal.

  As in the invention described in claim 25, in the heat cycle apparatus according to claim 24, the liquid pump is an electric liquid pump (32) operated by electricity, and the electric liquid pump (32) consumes work. If the amount of electric power is used, the amount of work can be calculated specifically.

  According to a twenty-sixth aspect of the present invention, in the thermal cycle device according to any one of the twenty-first to twenty-fifth aspects, the expander compresses the gas-phase refrigerant in the refrigeration cycle (10, 11, 13, 14). The reversible rotating machine (10) has the function of a machine, and the reversible rotating machine (10) is configured as an integral structure with the liquid pump (32, 300). The liquid pump (32, 300) 10, 11, 13, 14), and is cooled by a gas-phase refrigerant sucked into the reversible rotating machine (10).

  According to this, the liquid pump (32, 300) is cooled by the low-temperature gas-phase refrigerant sucked when the reversible rotating machine (10) functions as a compressor, and the liquid phase inside the liquid pump (32, 300). Since the refrigerant is supercooled and the vaporization of the refrigerant inside the liquid pump (32, 300) can be prevented, the liquid phase refrigerant can be reliably sent to the steam generator 30.

  Moreover, since the liquid pump (32, 300) and the expander (10) are integrated, the fluid machine can be downsized by sharing the components constituting the liquid pump (32, 300) and the expander (10). You can also plan.

  According to a twenty-seventh aspect of the present invention, in the heat cycle apparatus according to any one of the twenty-first to twenty-sixth aspects, the air blowing means (14a) for blowing the air conditioned by the refrigeration cycle (10, 11, 13, 14). ) And operation requesting means (41) for requesting operation of the refrigeration cycle, and the control means (40), when performing the refrigerant condensation operation, is operated by the operation requesting means (41) by the refrigeration cycle (10, 11, 13). , 14) when the operation is not required, the refrigerant condensing operation is performed without operating the air blowing means (14a).

  According to this, the refrigeration cycle (10, 11, 13, 14) is operated even though the operator of the heat cycle device does not request the operation of the refrigeration cycle (10, 11, 13, 14). In the refrigerant condensing operation, since the air whose temperature and humidity are adjusted is not blown, the refrigerant condensing operation can be performed without giving an uncomfortable feeling to the operator. The air conditioning in the present invention means at least temperature adjustment or humidity adjustment.

  According to a twenty-eighth aspect of the present invention, in the heat cycle device according to any one of the twenty-first to twenty-seventh aspects, the condenser (11) heats the vapor phase refrigerant by exchanging heat between the outside air and the refrigerant. The exchanger is provided with an outside air temperature sensor (45) for measuring the temperature of the outside air, and the control means (40) is configured to determine a duration (T21) for continuing the refrigerant condensing operation. (T21) is a time determined by the outside air temperature.

  By the way, in the refrigeration cycle, the condensation temperature and the refrigerant pressure that the vapor phase refrigerant condenses to become a liquid phase refrigerant are determined by the outside air temperature. That is, when the outside air temperature is high, the refrigerant pressure is increased and the condensation temperature is also increased. On the other hand, the higher the condensation temperature, the higher the temperature of the liquid refrigerant becomes supercooled.

  Therefore, the control means (40) is allowed to determine the duration (T21) based on the relationship between the outside air temperature and the time until the liquid refrigerant is supercooled by the continuous operation of the refrigeration cycle. As a result, since the liquid phase refrigerant can be reliably subcooled, the liquid pump (32, 300) can reliably send the liquid phase refrigerant to the vapor generator 30.

  According to a twenty-ninth aspect of the present invention, in the heat cycle device according to any one of the twenty-first to twenty-seventh aspects, the sensor (46) measures a physical quantity having a correlation with the temperature of the refrigerant inside the liquid pump (32, 300). 47), and the control means (40) determines the duration for which the refrigerant condensing operation is continued, and the duration is measured by the sensors (46, 47) after the refrigerant condensing operation is started. The measured physical value is a time until the temperature of the refrigerant inside the refrigerant pump (32) becomes a value indicating that the refrigerant is in a supercooled state.

  According to this, since the refrigerant inside the refrigerant pump (32) is surely in the liquid phase, the liquid pump (32, 300) can reliably send the liquid phase refrigerant to the vapor generator 30.

  For example, the above-described effect can be exhibited by continuing the refrigerant condensation operation until the refrigerant temperature inside the refrigerant pump (32) becomes lower than the lowest refrigerant condensation temperature determined by the lowest outside air temperature in the environment where the heat cycle device is used. .

  According to a thirty-third aspect of the present invention, in the heat cycle apparatus according to any one of the twenty-first to twenty-seventh aspects, the condenser (11) condenses the gas-phase refrigerant by exchanging heat between the outside air and the refrigerant. An outside air temperature sensor (45) that measures the temperature of the outside air, and a sensor (46, 47) that measures a physical quantity correlated with the temperature of the refrigerant inside the liquid pump (32, 300). The control means (40) determines the temperature at which the refrigerant temperature in the refrigerant pump (32, 300) becomes supercooled according to the outside air temperature, and further determines the duration for continuing the refrigerant condensation operation. The duration is a value indicating that the physical value measured by the sensors (46, 47) after starting the refrigerant condensing operation indicates that the temperature of the refrigerant inside the refrigerant pump (32) is in an overcooled state. Time to become Characterized in that there.

  According to this, in addition to having the same effect as that of the twenty-ninth aspect, the temperature at which the refrigerant inside the liquid pump (32, 300) is in a supercooled state is determined by the outside air temperature. Time can be shortened.

  As in the invention described in claim 31, in the heat cycle device according to claim 29 or 30, the sensor for measuring the physical quantity may be a temperature sensor (46) for measuring the temperature of the housing of the refrigerant pump.

  As in the invention described in claim 32, in the heat cycle device according to claim 29 or 30, the refrigeration cycle (10, 11, 13, 14) evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant and air. The sensor that includes the evaporator (14) that measures the physical quantity may be a temperature sensor (47) that measures the temperature of the air immediately after passing through the evaporator (14).

  In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

  In one embodiment of the present invention, the refrigeration cycle system is operated when the Rankine cycle system is operated. In one feature, the operation of the refrigeration cycle system performs a refrigerant condensing operation in which the refrigerant is compressed by a rotary fluid machine and condensed by a condenser. This refrigerant condensing operation makes it possible to reliably supply liquid phase refrigerant to the Rankine cycle system. The refrigerant condensing operation can be performed before starting the Rankine cycle system, during an initial startup period immediately after startup, or during an operation period of the Rankine cycle system. The refrigerant condensing operation can be started in association with a signal instructing activation of the Rankine cycle system.

  If the refrigerant condensing operation is executed before the operation of the Rankine cycle system is started, liquid phase refrigerant can be reliably supplied when the Rankine cycle system is started. The refrigerant condensing operation can also be executed as a normal air conditioning operation before starting the Rankine cycle system. In this case, the operation of the Rankine cycle system is started from the state where the refrigeration cycle system is operated as a normal air conditioning operation.

  When the refrigerant condensing operation is executed simultaneously with the start of the Rankine cycle system or after a slight delay after the start of the Rankine cycle system, the liquid phase refrigerant is reliably supplied at the start or immediately after the start. it can.

  When the refrigerant condensing operation is executed during the operation period of the Rankine cycle system, the liquid phase refrigerant can be reliably supplied during the operation period of the Rankine cycle system. The refrigerant condensing operation can be started by determining whether or not it is necessary to supply the liquid phase refrigerant to the Rankine cycle system. For example, the Rankine cycle system is trial run, the necessity of the liquid phase refrigerant is determined from the behavior of the Rankine cycle system, and the refrigerant condensation operation is started when it is determined that the supply of the liquid phase refrigerant is necessary. Can do. Further, it is possible to set a condition such as an environmental condition in which the liquid phase refrigerant is insufficient based on the accumulation of empirical data, and start the refrigerant condensation operation when this condition is satisfied.

  The refrigerant condensing operation can be stopped after a certain time or variable time operation. For example, the refrigerant condensing operation can be stopped after the fixed fixed time operation.

  Further, the refrigerant condensing operation can be stopped by detecting that the liquid phase refrigerant can be supplied or that the liquid phase refrigerant is stably supplied to the Rankine cycle system. .

  The refrigerant condensing operation can be provided by an operation as a cooling device or a refrigeration device of the refrigeration cycle system, and can be accompanied by means for providing an operation for increasing the liquid phase refrigerant. For example, it is possible to provide a means for providing a state in which the air blowing means to the evaporator of the refrigeration cycle system is not operated or the air blowing amount is suppressed.

  The rotary fluid machine can be provided by a device that provides a function as an expander and a function as a compressor.

  A rotary fluid machine mutually converts fluid energy and mechanical energy by rotation, compresses the fluid from a low pressure to a high pressure by receiving a rotational force, and generates a rotation by moving the fluid from a high pressure to a low pressure. . The rotary fluid machine can be provided by a positive displacement type or a non positive displacement type machine. For example, a reversible rotary fluid machine that can reversibly function as an expander or a compressor can be used. In this case, the operation of the Rankine cycle system and the operation of the refrigeration cycle system are selectively performed. Under this configuration, the refrigerant condensing operation can be executed by the refrigeration cycle system prior to the operation of the Rankine cycle system.

  The rotary fluid machine can include both an expander and a compressor. In this case, in addition to the selective operation of the expander and the compressor, the expander and the compressor can be operated simultaneously.

  In other features, the operation of the refrigeration cycle system performs a cooling operation to cool the liquid pump. By cooling the liquid pump, it is possible to suppress the occurrence of problems due to the gas-phase refrigerant. The cooling operation can be performed before and / or during the operation of the Rankine cycle system. By performing the cooling operation before starting the operation of the Rankine cycle system, it is possible to reduce the gas-phase refrigerant in the liquid pump and suppress the start-up failure of the Rankine cycle system.

  In addition, the start-up failure of the Rankine cycle system can also be suppressed by performing the cooling operation in the initial startup period immediately after the start of the operation of the Rankine cycle system. Moreover, the efficiency fall of a Rankine cycle system can be suppressed by performing a cooling operation during the operation of the Rankine cycle system.

The liquid pump constituting the Rankine cycle system can be disposed in the vicinity of the suction path of the compressor constituting the refrigeration cycle system.
(First embodiment)
In the present embodiment, the thermal cycle device according to the present invention is applied to a vehicular vapor compression refrigerator (refrigeration cycle) having a Rankine cycle, and FIG. 1 is an overall configuration diagram of the present embodiment. The vapor compression refrigerator having the Rankine cycle of the present embodiment recovers energy from waste heat generated in the engine 20 that is a heat engine that generates driving power, and also generates cold and hot heat generated in the vapor compression refrigerator. Is used for air conditioning of the passenger compartment space.

  A reversible rotating machine 10 shown in FIG. 1 is a fluid machine that has both a function as a compressor that sucks and compresses a refrigerant and a function as an expander that expands superheated steam isentropically to extract power. The reversible rotary machine 10 is a rotary fluid machine that can be reversibly operated as an expander that expands a refrigerant to extract power or a compressor that compresses a refrigerant by receiving power. The reversible rotary machine 10 can also be referred to as an expander-integrated compressor.

  When the reversible rotary machine 10 is operated as a compressor, the motor generator 10a operates as a power source that gives power (rotational force) to the reversible rotary machine 10. On the other hand, when the reversible rotary machine 10 is operated as an expander, it is a rotating electrical machine that operates as an expander, that is, a generator that generates electric power with the power recovered by the reversible rotary machine 10. The structure of the reversible rotating machine 10 will be described later.

  The radiator 11 is connected to the discharge side when the reversible rotary machine 10 operates as a compressor, and is a cooler that radiates the refrigerant to the outside air, that is, cools the refrigerant with the outside air. The refrigerant that has flowed out of the radiator 11 flows into the gas-liquid separator 12 (receiver) that separates the gas-phase refrigerant and the liquid-phase refrigerant.

  The decompressor 13 decompresses and expands the liquid phase refrigerant separated by the gas-liquid separator 12. In this embodiment, the decompressor 13 decompresses the refrigerant in an enthalpy manner and operates the reversible rotary machine 10 as a compressor. A temperature-type expansion valve is used that controls the throttle opening so that the degree of superheat of the refrigerant sucked into the reversible rotating machine 10 becomes a predetermined value.

  The evaporator 14 is a heat absorber that evaporates the refrigerant depressurized by the pressure reducer 13 and exhibits an endothermic effect. The refrigerant that has flowed out of the evaporator 14 flows into the reversible rotary machine 10 again. In this way, a vapor compression refrigerator (refrigeration) that moves the heat on the low temperature side to the high temperature side in the compressor (reversible rotating machine 10), the radiator 11, the gas-liquid separator 12, the decompressor 13, the evaporator 14, and the like. Cycle). The evaporator 14 is provided with a blower 14a for blowing air conditioned by evaporating the refrigerant and absorbing heat, and the blower 14a is controlled by the electronic control unit 40.

  By the way, in this embodiment, the engine cooling circuit in which the cooling water for cooling the engine 20 which is a heat generating body circulates is provided. The water pump 22 arranged in the engine cooling circuit circulates the 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 the outside air. The bypass circuit 24 is a bypass circuit that bypasses the radiator 23 and flows cooling water, and the thermostat 25 is a flow rate adjustment valve that adjusts the amount of cooling water that flows to the bypass circuit 24 and the amount of cooling water that flows to the radiator 23.

  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.

  In addition, a steam generator 30 is disposed in the refrigerant flow downstream portion of the engine 20 in the engine cooling circuit and in the refrigerant circuit that connects the reversible rotating machine 10 and the radiator 11 in the refrigeration cycle. The steam generator 30 heats the refrigerant by exchanging heat between the refrigerant flowing through the refrigerant circuit and the engine coolant that has recovered the waste heat of the engine 20.

  Further, in the engine cooling circuit, the three-way valve 21 switches between the case where the engine cooling water flowing out from the engine 20 is circulated to the steam generator 30 and the case where it is not circulated. In the present embodiment, the operation of the three-way valve 21 is controlled by the electronic control device 40.

  By the way, the 1st bypass circuit 31 which is liquid phase piping is a refrigerant path which guide | induces the liquid phase refrigerant | coolant isolate | separated by the gas-liquid separator 12 to the refrigerant | coolant inlet / outlet side by the side of the radiator 11 among the steam generators 30. FIG. The first bypass circuit 31 is provided with a liquid pump 32 for circulating the liquid-phase refrigerant and a check valve 33a that allows the refrigerant to flow only from the gas-liquid separator 12 side to the steam generator 30 side. Yes. In the present embodiment, the liquid pump 32 is an electric pump, and the operation of the liquid pump 32 is controlled by the electronic control unit 40.

  The second bypass circuit 34 is a refrigerant passage that connects the refrigerant outlet side when the reversible rotary machine 10 operates with the expander and the refrigerant inlet side of the radiator 11. A check valve 33b is provided that allows the refrigerant to flow only from the refrigerant outlet side to the refrigerant inlet side of the radiator 11 when the rotary machine 10 operates with the expander.

  The check valve 33 c allows the refrigerant to flow only from the refrigerant outlet side of the evaporator 14 to the suction side of the compressor 10. The opening / closing valve 35 a disposed between the steam generator 30 and the radiator 11 is controlled by the electronic control device 40. Furthermore, the control valve 36 functions as a discharge valve when the reversible rotary machine 10 operates as a compressor, that is, as a check valve that allows the refrigerant to flow only from the reversible rotary machine 10 side to the steam generator 30 side, The valve is opened when operating as an expander. The operation of the control valve 36 is also controlled by the electronic control unit 40. In this way, a Rankine cycle is configured in which the refrigerant flows through the reversible rotating machine 10, the condenser 11, the gas-liquid separator 12, the liquid pump 32, and the like.

  The electronic control unit 40 also includes a detection temperature TW of a water temperature sensor 44 that detects the temperature of engine cooling water after absorbing heat from the engine 20, an air conditioner operation signal (A / C operation) issued from the air conditioning electronic control unit 41. Request signal), the detected pressure P1 of the upstream refrigerant pressure sensor 42 for detecting the pressure on the upstream side of the liquid pump 32, and the detected pressure P2 of the downstream refrigerant pressure sensor 43 for detecting the pressure on the downstream side of the liquid pump 32. Is provided.

  The electronic control unit 40 controls the control valve 36, the liquid pump 32, the three-way valve 21 and the like according to a program stored in advance based on the temperature detected by the water temperature sensor 44, that is, the waste heat temperature Tw and the presence / absence of an A / C operation request signal. Control operation.

  Next, a schematic structure of the reversible rotating machine 10 and its operation will be described.

  FIG. 2A shows a case where the reversible rotating machine 10 operates as a compressor, and FIG. 2B shows a case where the reversible rotating machine 10 operates as an expander. The reversible rotating machine 10 is constituted by a vane type fluid machine.

  When the reversible rotary machine 10 is operated as a compressor, the motor generator 10a rotates the rotor 10b to suck and compress the refrigerant, and the high-pressure refrigerant discharged from the control valve 36 flows back to the rotor 10b side. To be prevented.

  Further, when the reversible rotating machine 10 is operated as an expander, the control valve 36 is opened and superheated steam generated by the steam generator 30 is introduced into the reversible rotating machine 10 to rotate the rotor 10b to generate heat. Convert energy into mechanical energy.

  Next, the operation of the vapor compression refrigerator (air conditioner) including the Rankine cycle according to the present embodiment will be described. In the vapor compression refrigerator having the Rankine cycle of this embodiment, the control means 40 switches and controls the following operation modes based on the presence / absence of an A / C operation request signal and the waste heat temperature Tw. The operation mode and the waste heat recovery operation mode will be described.

  1. Air-conditioning operation mode This operation mode is an operation mode in which the refrigerant is allowed to cool by the radiator 11 while the refrigeration ability is exhibited by the evaporator 14. In this embodiment, the vapor compression refrigerator is operated only for the cooling generated by the vapor compression refrigerator, that is, for the cooling operation and the dehumidification operation using the endothermic effect, and the 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.

  Specifically, with the liquid pump 32 stopped, the on-off valve 35a is opened, and the motor generator 10a is energized with the control valve 36 functioning as a discharge valve to rotate the rotor 10b. The valve 21 is operated as shown by the broken line in FIG. 1 to bypass the steam generator 30 and circulate the cooling water.

  Accordingly, the refrigerant circulates in the order of the reversible rotating machine (compressor) 10 → the steam generator 30 → the radiator 11 → the gas-liquid separator 12 → the decompressor 13 → the evaporator 14 → the reversible rotating machine (compressor) 10. . In addition, since engine cooling water does not circulate through the steam generator 30, the refrigerant is not heated by the steam generator 30, and the steam generator 30 functions as a simple refrigerant passage.

  Therefore, the low-pressure refrigerant decompressed by the decompressor 13 absorbs heat from the air blown into the room by the blower 14a and evaporates, and the evaporated gas-phase refrigerant is compressed by the reversible rotating machine 10 and becomes a high temperature. 11 is cooled by outdoor air and condensed.

  In the present embodiment, alternative chlorofluorocarbon (HFC-134a) is used as the refrigerant. However, the refrigerant is not limited to HFC-134a as long as the refrigerant condenses on the high pressure side.

  2. Waste heat recovery operation mode This operation mode is a mode in which the air conditioner, that is, the reversible rotary machine 10 is stopped and the waste heat of the engine 20 is recovered as usable energy.

  Specifically, the on-off valve 35a is closed, the control valve 36 is opened, the liquid pump 32 is operated, and the three-way valve 21 is operated as shown by the solid line in FIG. The cooling water is circulated to the steam generator 30.

  Thereby, the refrigerant circulates in the order of the gas-liquid separator 12 → the first bypass circuit 31 → the steam generator 30 → the reversible rotating machine (expander) 10 → the second bypass circuit 34 → the radiator 11 → the gas-liquid separator 12. To do.

  Therefore, the superheated steam heated by the steam generator 30 flows into the reversible rotating machine 10, and the vapor refrigerant that flows into the reversible rotating machine 10 expands in the reversible rotating machine 10 in an isentropic manner while enthalpy. Will decrease. For this reason, the reversible rotating machine 10 gives mechanical energy corresponding to the reduced enthalpy to the motor generator 10a, and the electric power generated by the motor generator 10a is stored in a battery or a capacitor such as a capacitor.

  The refrigerant flowing out of the reversible rotating machine 10 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 vaporized by the liquid pump 32. It is sent to the generator 30 side.

  As described above, in the waste heat recovery operation mode, the heat energy discarded in the atmosphere as heat by the radiator 23 is converted into energy that can be easily used, such as electric power. That is, the fuel consumption of the engine 20 can be reduced.

  Further, in the waste heat recovery operation mode, power is generated by the waste heat of the engine 20, so that the necessity of driving a generator such as an alternator with the engine 20 is reduced, and the fuel consumption of the engine 20 can be further reduced. .

  Next, the control in the electronic control unit 40 will be described. In this embodiment, when the A / C operation request signal is issued from the air conditioning electronic control unit 41 to the electronic control unit 40, the reversible rotating machine 10 is used. Is operated as a compressor, and supply of engine cooling water to the steam generator 30 is stopped to prioritize the air conditioning operation mode.

  On the contrary, when the A / C operation request signal is not issued from the air-conditioning electronic control device 41 to the electronic control device 40 and the waste heat temperature Tw is equal to or higher than a predetermined temperature, the engine is sent to the steam generator 30. While supplying the cooling water, the reversible rotating machine 10 is operated as an expander to perform the waste heat recovery operation mode.

  Further, when the A / C operation request signal is not issued from the air-conditioning electronic control device 41 to the electronic control device 40 and the waste heat temperature Tw is equal to or lower than the predetermined temperature, the engine to the steam generator 30 is In the state where the supply of the cooling water is stopped, the energization to the reversible rotary machine 10, that is, the motor generator 10a is stopped.

  Incidentally, FIG. 3 is an example of a flowchart showing the above-described control operation, and the outline of this flowchart will be described below. The control program shown in FIG. 3 is started at the same time when the vehicle start signal is input. First, it is determined whether or not an A / C operation request signal is issued from the air conditioning electronic control device 41 to the electronic control device 40. It is determined (S1).

  When the A / C operation request signal is issued from the air conditioning electronic control device 41 to the electronic control device 40, the Rankine cycle is not operated and the air conditioning operation mode is activated (S2).

  When the A / C operation request signal is not issued from the air conditioning electronic control device 41 to the electronic control device 40, whether or not the Rankine cycle is operated based on the waste heat temperature Tw, that is, waste heat. It is determined whether or not the recovery operation mode is performed (S3). When the waste heat temperature Tw is equal to or higher than a predetermined temperature, the determination result is set to 1. When the Rankine cycle is operated (S4), the waste heat temperature Tw is lower than the predetermined temperature. The judgment result is set to 0 and the Rankine cycle is not operated.

  In the present embodiment, in determining whether or not to operate the Rankine cycle based on the waste heat temperature Tw, when the waste heat temperature Tw is in the descending process, the determination result is set to 1 when the temperature is equal to or higher than the predetermined temperature Tw1. The Rankine cycle is operated. When the temperature is lower than the predetermined temperature Tw1, the determination result is set to 0 and the Rankine cycle is not operated. In addition, when the waste heat temperature Tw is in the process of rising, the Rankine cycle is operated with a determination result of 1 when the temperature is equal to or higher than the predetermined temperature Tw2 higher than the predetermined temperature Tw1, and when the temperature is lower than the predetermined temperature Tw2, the determination result is A constant hysteresis control determination is made such that the Rankine cycle is not operated as 0.

  Next, the control when the electronic control unit 40 operates the Rankine cycle (S4) will be described in more detail with reference to FIG. First, the counter value is reset (S410). This counter value stores how many times the refrigerant condensation operation (S470 to S500) that comes out later is performed.

  Next, the timer is reset (S420). This timer stores how many seconds have elapsed since the start of the waste heat recovery operation mode and the air conditioning operation mode. Thereafter, the electronic control unit 40 activates the liquid pump 32 to activate the waste heat recovery operation mode (S430). Thereafter, the waste heat recovery operation mode is operated until a predetermined time T1 (s) (20 seconds in the present embodiment) elapses in S440 and S450.

  Thereafter, the electronic control unit 40 determines whether the differential pressure P2-P1 between the detection pressure P1 of the upstream refrigerant pressure sensor 42 and the detection pressure P2 of the downstream refrigerant pressure sensor 43 is greater than the set pressure P (0.3 MPa in this embodiment). It is determined whether or not (S460). When the differential pressure P2-P1 is greater than the set pressure P (0.3 MPa in this embodiment), that is, when the liquid pump 32 is applying pressure to the liquid phase refrigerant, the process flows to S5 in FIG. .

  When the differential pressure P2-P1 is smaller than the set pressure P (0.3 MPa in the present embodiment), the liquid pump 32 cannot apply pressure to the liquid phase refrigerant. It is determined that the phase refrigerant is mixed and the liquid pump 32 cannot apply pressure to the refrigerant, and the refrigerant condensing operation (S470 to S500) is performed.

  In the refrigerant condensing operation (S470 to S500), the air conditioning operation mode is activated (S480) after the waste heat recovery operation mode is stopped (S470). Thereafter, the air-conditioning operation mode is operated until a predetermined time T2 (s) (10 seconds in the present embodiment) elapses in S490 and S500. Then, after the refrigerant condensing operation (S470 to S500), the counter value is set to the counter value +1.

  In S520, it is determined whether or not the counter value is greater than the specified number C (three times in the present embodiment). If the counter value is equal to or less than the specified number C, the process returns to S420. If it is larger than the specified value C, it is determined that an abnormality has occurred in the Rankine cycle, and the system is stopped.

  In the refrigerant condensation operation (S470 to S500), since the A / C operation request signal is not issued, the blower 14a is not operated. Thereby, since the air-conditioned air is not blown into the vehicle interior, the refrigerant condensing operation can be performed without giving the passenger a sense of incongruity.

  Next, the actions and effects of the first embodiment are listed. (1) Since it is possible to prevent bubbles of the gas-phase refrigerant from being mixed into the liquid-phase piping 31 and the liquid pump 32, A decrease in the operating efficiency of the refrigerant can be reduced.

  In this embodiment, when it is determined that the Rankine cycle is abnormal, the air-conditioning operation mode (refrigeration cycle) is operated to condense the gas-phase refrigerant into the liquid-phase refrigerant, and further, the refrigerant passage in the refrigeration cycle A complicated portion, for example, a refrigerant stored in the evaporator 14 can be stored in the gas-liquid separator 12. Thereafter, if the waste heat recovery operation mode (Rankine cycle) is operated, it is possible to reduce the mixing of bubbles into the liquid phase pipe 31 as in the conventional example.

  Therefore, since the liquid pump 32 can reliably send the liquid phase refrigerant to the steam generator 30, the waste heat recovery operation mode (Rankine cycle) can be normally started and operated.

  Moreover, since the fall of the operation efficiency of the liquid pump 32 by mixing of the bubble of the gaseous-phase refrigerant | coolant to the liquid phase piping 31 and the liquid pump 32 can also be suppressed, the fall of the Rankine cycle efficiency can be reduced.

  (2) The control means 40 determines whether the waste heat recovery operation mode (Rankine cycle) is normal or abnormal. If it is normal, the waste heat recovery operation mode is continued, and if it is abnormal, the air conditioning operation mode is executed. To do. Therefore, it is possible to prevent the air conditioning operation mode from being executed unnecessarily.

  (3) In order to compare the difference value P2-P1 between the upstream pressure value P1 and the downstream pressure value P2 of the liquid pump 32 and the predetermined pressure value P, specifically determine whether the waste heat recovery operation mode is normal or abnormal. it can.

  By the way, when the liquid pump 32 is operating normally, the detected pressure value P1 of the upstream refrigerant pressure sensor 42 becomes smaller than the detected pressure value P2 of the downstream refrigerant pressure sensor 43. Thereby, when the difference value P2-P1 is specifically equal to or less than the predetermined pressure value P, it is possible to determine that the operation in the waste heat recovery operation mode is abnormal.

  (4) The waste heat recovery operation mode converts the heat energy discarded in the atmosphere as heat by the radiator 23 into energy that can be easily used, such as electric power. Fuel consumption can be reduced. More specifically, since power is generated by waste heat of the engine 20, the necessity of driving a generator such as an alternator with the engine 20 is reduced, and the fuel consumption of the engine 20 can be reduced.

(Second Embodiment)
The present embodiment has the same configuration as the first embodiment except that the upstream refrigerant pressure sensor 42 and the downstream refrigerant pressure sensor 43 of the first embodiment are eliminated and the current consumption of the liquid pump 32 is measured by the electronic control device 40. (See FIG. 5). Also, the control shown in FIG. 3 is the same as in the first embodiment.

  However, with respect to the details of S4 in FIG. 3 shown in FIG. 6, in this embodiment, whether or not the Rankine cycle operation is normal is determined by the power consumption of the liquid pump 32 (S465). To do. That is, when the liquid pump 32 operates normally and the liquid refrigerant can be sent to the steam generator 30, the power consumption of the liquid pump 32 is greater than a predetermined value, so that the liquid pump 32 has a predetermined value. A case in which more power than the power consumption amount W (50 W in the present embodiment) is consumed is determined as normal. In the present embodiment, the power consumption of the liquid pump 32 is measured using a current sensor.

  On the other hand, if the power consumption is less than or equal to the predetermined power consumption W, the process proceeds to S470. The following operations are the same as in the first embodiment.

  According to this, since it is possible to determine whether the waste heat rotation operation mode (Rankine cycle) is normal or abnormal without the upstream refrigerant pressure sensor 42 and the downstream refrigerant pressure sensor 43 which are essential components in the first embodiment, the thermal cycle device The overall cost can be reduced.

  In the present embodiment, the effects (1) to (4) described in the first embodiment can be exhibited.

(Third embodiment)
This embodiment has the same configuration as the first embodiment, but a part of the control in S4 (see FIG. 4) is different as shown in FIG. More specifically, after starting the air conditioning operation mode in S480, the electronic control unit 40 determines whether the counter value is 0 (S485). When the counter value is 0, the process proceeds to S495 and S505, and the air conditioning operation mode is operated until T3 (s) has elapsed. This T3 (s) is a predetermined time shorter than T2 (s), and is 2 seconds in this embodiment. On the other hand, when the counter value is other than 0, the air-conditioning operation mode is operated until T2 (s) (10 seconds as described above) has elapsed (S490, S500), and then the process proceeds to S510. The following operations are the same as in the first embodiment.

  By the way, when the liquid refrigerant of the gas-liquid separator 12 is a saturated liquid, cavitation occurs at a portion where the pressure in the liquid pump 32 is low, although the liquid-phase refrigerant is accumulated in the gas-liquid separator 12. End up. In such a case, cavitation can be reduced by starting the air-conditioning operation mode for a short time to increase the pressure in the gas-liquid separator 12 and using the liquid refrigerant as the supercooled liquid.

  In the present embodiment, the counter value is 0, that is, after the waste heat recovery operation mode is determined to be abnormal (S460 in FIG. 4), the first air conditioning operation mode is made shorter than the second and subsequent times. Thereby, the waste heat recovery operation mode can be normally operated promptly without wastefully operating the air conditioning operation mode.

  In the present embodiment, the effects (1) to (4) described in the first embodiment can be exhibited.

(Fourth embodiment)
In the first embodiment, the second embodiment, and the third embodiment, the time T2 (s) for performing the refrigerant condensation operation is set to a predetermined time (10 seconds), but in this embodiment, T2 is air-conditioned. The difference is that the operation mode is changed according to the operation status.

  FIG. 8 is an overall configuration diagram of the vapor compression refrigerator in the present embodiment, which differs from FIG. 1 only in that an outside air temperature sensor 45 is provided on the upstream side of the condenser 11 in the air flow direction. The output value Tam of the outside air temperature sensor 45 is input to the electronic control device 40, and the electronic control device 40 determines the duration T21 (s) for continuing the refrigerant condensing operation based on the output value Tam of the outside air temperature sensor 45.

  In this embodiment, it is determined that T21 becomes longer as the value of Tam becomes larger. When the outside air temperature is high, the condensing temperature is also high, so that the temperature at which the liquid refrigerant can be brought into a supercooled state is also high. However, it takes a long time to cool the refrigerant due to the heat capacities of other components constituting the cycle. Therefore, the relationship between the external temperature measured in advance and the time during which the liquid-phase refrigerant can be brought into the supercooled state is stored in the electronic control unit 40, and T21 is determined by the value of Tam.

  Further, in the control flow of the electronic control unit 40 in the present embodiment, as shown in FIG. 9, Tam is read and T21 is determined in step S415 with respect to the first embodiment (FIG. 4). S501 is different in that the air-conditioning operation mode operates until the continuation time T21 (s) elapses.

  Thereby, since the operation time of the air-conditioning operation mode required for making a liquid phase refrigerant into a supercooled state can be ensured, the operation time of the air-conditioning operation mode in an unnecessary refrigerant condensing operation can be shortened. Furthermore, the operational effects (1) to (4) described in the first embodiment can be exhibited.

(Fifth embodiment)
In the first to fourth embodiments, the embodiment in which the reversible rotary machine 10 and the liquid pump 32 are configured separately has been described. However, in this embodiment, as shown in the overall configuration diagram of FIG. The machine 10 is configured such that the expansion / compression unit 100, the generator motor unit 200, the liquid pump unit 300, the valve mechanism unit 107, and the like are integrated. Therefore, the liquid pump 32 and the control valve 36 are not provided independently.

  Further, the reversible rotary machine 10 is provided with a liquid pump housing temperature sensor 46 for measuring the temperature of the pump housing of the liquid pump 300, and the output value Twp of the liquid pump housing temperature sensor 46 is input to the electronic control unit 40. Is different. Other configurations are the same as those of the fourth embodiment.

  Next, the reversible rotary machine 10 according to the present embodiment will be described with reference to the cross-sectional view of FIG. The reversible rotating machine 10 includes a compression / expansion unit 100 that compresses or expands a gas-phase refrigerant, a generator motor 200 that outputs electric energy when rotational energy is input, and outputs rotational energy when electric power is input, When operating the waste heat recovery operation mode, it is configured by a liquid pump unit 300 that pumps liquid refrigerant to the compression / expansion unit 100 side.

  The compression / expansion unit 100 has the same structure as a known scroll-type compression mechanism, and specifically, a fixed scroll (shell) fixed to the stator housing 230 of the generator motor unit 200 via the middle housing 101. 102, a movable scroll 103 that forms a movable member that pivots and displaces in the space between the middle housing 101 and the fixed scroll 102, and a valve mechanism 107 that opens and closes the communication passages 105 and 106 that connect the working chamber V1 and the high-pressure chamber 104. Etc.

  Here, the fixed scroll 102 is configured to have a plate-like substrate portion 102a and a spiral tooth portion 102b protruding from the substrate portion 102a toward the movable scroll 103, while the movable scroll 103 is formed on the tooth portion 102b. It is configured to have a spiral tooth portion 103b that contacts and meshes, and a base plate portion 103a on which the tooth portion 103b is formed, and the movable scroll 103 is swung while the both tooth portions 102b and 103b are in contact with each other. The volume of the working chamber V1 constituted by the scrolls 102 and 103 is enlarged or reduced.

  The shaft 108 is rotatably supported on the middle housing 101 by the bearing 108b and on the stator housing 230 by the bearing 108c, and one end portion in the longitudinal direction thereof has an eccentric portion 108a that is eccentric with respect to the rotation center axis. It is a crankshaft. The lip seal 108 d is a shaft seal device that prevents the refrigerant from leaking out of the stator housing 230 from the gap between the shaft 108 and the stator housing 230. In addition, the movable scroll 103 is rotatably connected to the eccentric portion 108a via a bearing 103c.

  The rotation prevention mechanism 109 makes the movable scroll 103 rotate once around the eccentric portion 108a while the shaft 108 rotates once. Therefore, when the shaft 108 rotates, the movable scroll 103 does not rotate and revolves around the rotation center axis of the shaft 108, and the working chamber V1 is displaced from the outer diameter side of the movable scroll 103 to the center side. Its volume changes so as to shrink. In the present embodiment, a pin-ring (pin-hole) type is adopted as the rotation prevention mechanism 109.

  The communication path 105 is a discharge port that discharges the compressed refrigerant by communicating the working chamber V1 and the high pressure chamber 104 that have a minimum volume in the pump mode, and the communication path 106 has a minimum volume in the waste heat recovery operation mode. This is an inflow port that connects the working chamber V1 and the high-pressure chamber 104, and guides the high-temperature and high-pressure superheated steam (that is, the gas-phase refrigerant) introduced into the high-pressure chamber 104 to the working chamber V1.

  The high-pressure chamber 104 is a space formed by a gap between the valve mechanism housing 107i and the surface opposite to the surface formed by the tooth portion 102b of the base plate portion 102a of the operating scroll 102. This port has a function of smoothing the pulsation of the refrigerant discharged from the port 105. The high pressure chamber 104 is provided with a high pressure port 110 connected to the heater 30 and the radiator 11 side. Yes.

  The low pressure port 111 connected to the evaporator 14 and the second bypass circuit 34 side is provided in the stator housing 230 and passes through the internal space 230a in the generator motor section 200 and the middle housing 101 to the working chamber V1. It communicates with the outermost diameter part.

  Next, the details of the valve mechanism 107 will be described. In the high-pressure chamber 104, a discharge valve 107a and a valve stop plate 107b are provided on the surface of the working scroll 102 opposite to the surface on which the teeth 102b of the base plate 102a are formed. It is fixed with bolts 107c. The discharge valve 107a is a reed valve-like check valve that prevents the refrigerant discharged from the discharge port 105 from flowing back from the high-pressure chamber 104 to the working chamber V1, and the stopper 107b regulates the maximum opening of the discharge valve 107a. It is a valve stop plate.

  The spool 107d is a valve body that opens and closes the communication passage 106 (hereinafter referred to as the inflow port 106), and the electromagnetic valve 107e controls the communication state between the low pressure port 111 side and the back pressure chamber 107f, thereby controlling the back pressure chamber. It is a control valve which controls the pressure in 107f. The spring 107g is an elastic means for applying an elastic force in a direction to close the inflow port 106 to the spool 107d, and the throttle 107h is a resistance means having a predetermined passage resistance to communicate the back pressure chamber 107f and the high pressure chamber 104. . The spool 107d, the electromagnetic valve 107e, and the spring 107g are disposed in the valve mechanism housing 107i, and the back pressure chamber 107f and the throttle 107h are configured integrally with the valve mechanism housing 107i.

  When the electromagnetic valve 107e is opened, the pressure in the back pressure chamber 107f is lower than that in the high pressure chamber 104, and the spool 107d is displaced to the right side of the sheet while pressing and contracting the spring 107g, so that the inflow port 106 is opened. Since the pressure loss at the throttle 107h is very large, the amount of refrigerant flowing from the high pressure chamber 104 into the back pressure chamber 107f is negligibly small.

  Conversely, when the electromagnetic valve 107e is closed, the pressure in the back pressure chamber 107f and the pressure in the high pressure chamber 104 become equal, and the spool 107d is displaced downward by the force of the spring 107g, so the inflow port 106 is closed. That is, a pilot type electric on-off valve that opens and closes the inflow port 106 is configured by the spool 107d, the electromagnetic valve 107e, the back pressure chamber 107f, the spring 107g, the throttle 107h, and the like. The electromagnetic valve 107e is controlled by the electronic control unit 40.

  The generator motor unit 200 is a brushless DC motor including a stator 210 and a rotor 220 that rotates on the inner peripheral side of the stator 210. The stator 210 is a stator coil in which a winding is wound around an iron core formed of a magnetic material, such as steel, and is fixed to the inner peripheral portion of the stator housing 230.

  The rotor 220 is a magnet rotor in which a permanent magnet is embedded, and has a key groove (not shown) on the inner peripheral side, and is fixed integrally with the shaft 108 by a key.

  The liquid pump unit 300 has the same structure as a well-known scroll-type compression mechanism. Specifically, the liquid pump unit 300 is a fixed scroll (shell) 302 fixed to the stator housing 230 of the generator motor unit 200 via the pump housing 301. The movable scroll 303 is a movable member that is pivotally displaced in the space between the pump housing 301 and the fixed scroll 302, the working chamber V2, and the like.

Here, the fixed scroll 302 is configured to have a plate-like substrate portion 302a and a spiral tooth portion 302b protruding from the substrate portion 302a to the movable scroll 303 side, while the movable scroll 303 is formed on the tooth portion 302b. It is configured to have a spiral tooth portion 303b that contacts and meshes, and a base plate portion 303a on which the tooth portion 303b is formed. The working chamber V2 constituted by the scrolls 302 and 303 moves from the refrigerant suction port 309 side described later to the refrigerant discharge port 308 side. The compression ratio of the scroll type compression mechanism of the liquid pump unit 300 is 1, and even if the liquid phase refrigerant is sucked into the working chamber V2, the liquid phase refrigerant is not compressed. There is no malfunction.

  The pump shaft 304 is rotatably supported by the pump housing 301 by a bearing 304b, and one end portion in the longitudinal direction is a crankshaft having an eccentric portion 304a that is eccentric with respect to the rotation center axis. The pump shaft 304 is coupled to an end portion of the shaft 108 that is also a constituent member of the compression / expansion portion 100 and the generator-motor portion 200 on the opposite side to the eccentric portion 108a via a one-way clutch 305.

  The one-way clutch 305 is power transmission means having a function of transmitting the rotational driving force of the shaft 108 to the pump shaft 304 only in the waste heat recovery operation mode. The movable scroll 303 is rotatably connected to the eccentric portion 304a via a bearing 303c.

  The anti-rotation mechanisms 306 and 307 make the movable scroll 303 rotate once around the eccentric portion 304a while the pump shaft 304 rotates once. Therefore, when the pump shaft 304 rotates, the movable scroll 303 does not rotate and revolves around the rotation center axis of the pump shaft 304, and the working chamber V2 is displaced from the outer diameter side of the movable scroll 103 to the center side. To go. In this embodiment, a pin-ring (pin-hole) type is adopted as the rotation prevention mechanisms 306 and 307.

  The refrigerant discharge port 308 is a port for discharging a liquid phase refrigerant, and is disposed at a position where the working chamber V2 communicates with the working chamber V2 when the working chamber V2 moves to the center side of the liquid pump unit 200. The refrigerant suction port 309 is a port for sucking the liquid phase refrigerant, and is disposed at a position where the working chamber V2 communicates with the working chamber V2 when the working chamber V2 moves to the outer diameter side of the liquid pump unit 200.

  The pump housing 301 is provided with a liquid pump unit housing temperature sensor 46, and the output value Twp of the liquid pump unit housing temperature sensor 46 is input to the electronic control unit 40.

  Next, the operation of the vapor compression refrigerator having the Rankine cycle in this embodiment will be described.

  In the air conditioning operation mode, power is supplied to the generator motor 200 of the reversible rotary machine 10 by the electronic control unit 40, the electromagnetic valve 107e is closed, and the three-way valve 21 is switched as indicated by the broken line in FIG. .

  When power is supplied to the generator motor 200, the rotor 220 and the shaft 108 rotate together. By this rotation, the reversible rotary machine 10 sucks the gas phase refrigerant from the low pressure port 111, compresses the gas phase refrigerant in the working chamber V <b> 1, and discharges it from the high pressure port 110.

  Further, since the solenoid valve 107e is closed, the valve mechanism 107 functions as a check valve that allows the refrigerant to flow only from the reversible rotary machine 10 side to the steam generator 30 side. Further, since the one-way clutch 305 does not transmit the rotational driving force of the shaft 108 to the pump shaft 304 in the air conditioning operation mode, the liquid pump unit 300 does not operate.

  Therefore, in the air conditioning operation mode, the same refrigeration cycle as in the first embodiment can be configured. Furthermore, since the low-pressure gas-phase refrigerant sucked from the low-pressure port 111 of the compression / expansion unit 100 is evaporated by the evaporator 14 and has a low temperature, the liquid pump unit 300 of the stator housing 230 is passed when passing through the internal space 230a. The liquid pump unit 300 is cooled via the contact surface 230b. As a result, the liquid phase refrigerant in the liquid pump unit 300 is supercooled. Therefore, when the waste heat recovery operation mode is operated after the air conditioning operation mode, the liquid pump unit 300 reliably transfers the liquid phase refrigerant to the steam generator. 30 can be sent.

  Next, in the waste heat recovery operation mode, the electromagnetic valve 107e is opened by the electronic control unit 40, and the three-way valve 21 is switched as shown by the solid line in FIG. Here, the electronic control unit 40 does not drive the liquid pump unit 300, but rotates the shaft 108 when the refrigerant expands in the compression / expansion unit 100, so that the rotational driving force is applied to the pump shaft 304 via the one-way clutch 305. As a result, the liquid pump unit 300 operates.

  Therefore, in the waste heat recovery operation mode, a Rankine cycle similar to that of the first embodiment can be configured.

  By the way, in the waste heat recovery operation mode, the low-pressure gas-phase refrigerant flowing out from the low-pressure port 111 of the compression / expansion unit 100 is overheated by the steam generator 30 and has a high temperature. Since this high-temperature gas-phase refrigerant also passes through the internal space 230a, there is a concern that the liquid pump unit 300 is heated via the contact surface 230b and the liquid phase refrigerant in the liquid pump unit 300 is heated and vaporized.

  However, in the waste heat recovery operation mode, the liquid pump unit 300 is operating, and the liquid phase refrigerant does not stay in the liquid pump unit 300 as in the air conditioning operation mode, but passes through the liquid pump unit 300. Therefore, since the liquid phase refrigerant is sent to the steam generator 30 before being vaporized, there is no concern that the refrigerant inside the liquid pump unit 300 vaporizes.

  Next, the control in the electronic control unit 40 will be described. In the present embodiment, the air conditioning operation mode and the waste heat recovery mode are controlled as in the first embodiment, but the control in the case of operating the Rankine cycle (S4) is performed. Is different.

  Specifically, as shown in FIG. 12, in step S416, the outside air temperature Tam and the liquid pump unit housing temperature Twp are read, and the operation in the air conditioning operation mode for performing the refrigerant condensing operation is performed as shown in step S502. The temperature is continued until Tam + α ≧ β × liquid pump unit housing temperature Twp.

  Here, the refrigerant condensing temperature can be grasped from the outside air temperature Tam, and the liquid pump part housing temperature Twp has a correlation with the refrigerant temperature inside the liquid pump part 300. Therefore, the refrigerant temperature inside the liquid pump part 300 Can be grasped. Furthermore, if the temperature of the refrigerant inside the liquid pump unit 300 becomes lower than the refrigerant condensation temperature, it can be determined that the refrigerant inside the liquid pump unit 300 is a supercooled liquid phase refrigerant.

  Therefore, in the present embodiment, the refrigerant condensing operation is performed until the refrigerant condensing temperature is the outside air temperature Tam + α (α = 15 ° C. in the present embodiment) and the β × liquid pump housing temperature Twp is equal to or lower than the outside air temperature Tam + α. . β is a multiplier for control. Therefore, when the waste heat recovery mode is operated after the refrigerant condensing operation, since the refrigerant inside the liquid pump unit is in a supercooled state, the liquid pump unit 300 can reliably send the liquid phase refrigerant to the steam generator 30. it can.

  Of course, even when the outside air temperature Tam is not measured, the lowest refrigerant condensing temperature (for example, 10 ° C.) is determined in advance from the lowest outside air temperature in the environment in which the heat cycle device is used, and β × liquid pump housing temperature Twp is The refrigerant condensing operation may be performed until the refrigerant condensing temperature is lower than the minimum. According to this, since the outside air temperature sensor 45 can be made unnecessary, the cost of the entire heat cycle device can be reduced.

  In the present embodiment, the effects (1) to (4) described in the first embodiment can be exhibited.

(Sixth embodiment)
In the fifth embodiment, the liquid pump unit housing temperature sensor 46 for measuring the temperature of the pump housing of the liquid pump unit 300 has been described. However, in the present embodiment, as shown in FIG. In place of the housing temperature sensor 46, an evaporator outlet temperature sensor 47 for measuring the temperature of the air heat-exchanged by the evaporator 14 is provided. Other configurations are the same as those of the fifth embodiment.

  The evaporator outlet temperature Te output from the evaporator outlet temperature sensor 47 is the temperature of the low-pressure gas-phase refrigerant in the air-conditioning operation mode, and is the temperature of the low-pressure gas-phase refrigerant sucked into the reversible rotary machine 10. That is, since it is the same as the temperature of the gas-phase refrigerant that cools the liquid pump unit 300, it has a correlation with the temperature inside the liquid pump unit 300. Therefore, the same effect as that of the fifth embodiment can be obtained by using the evaporator outlet temperature Te instead of the liquid pump housing temperature Twp as in steps S417 and S503 of FIG.

(Seventh embodiment)
In the embodiments from the first embodiment to the sixth embodiment, the reversible rotating machine 10 that functions as a compressor in the refrigeration cycle and functions as an expander in the Rankine cycle is used. In the present embodiment, FIG. As shown, a vapor compression refrigerator having a Rankine cycle is constituted by the compressor 10b dedicated to the refrigeration cycle and the expander 10c dedicated to the Rankine cycle without using the reversible rotating machine 10.

  The compressor 10b has a function of sucking in refrigerant, compressing it, and discharging it. The electromagnetic clutch 48 controlled by the electronic control unit 40 causes the engine 20 to pass through the engine side pulley 49, the belt 50, and the compressor side pulley 51. Operates under driving force.

  The expander 10c has the same structure as that of the fifth embodiment and the reversible rotary machine 10, and the expansion unit 100, the power generation unit 200, and the liquid pump unit 300 are integrally configured. However, since the expander 10c does not function as a compressor, the shaft 108 and the pump shaft 30 are integrally coupled without a one-way clutch or the like.

  When driving force is transmitted to the compressor by the electronic control unit 40, the refrigerant circulates in the order of the compressor 10b → the radiator 11 → the gas-liquid separator 12 → the decompressor 13 → the evaporator 14 → the compressor 10b. Thus, the same refrigeration cycle as in the first embodiment can be configured.

  When the electronic control unit 40 switches the three-way valve 21 so that the engine coolant passes through the steam generator 30, the refrigerant superheated by the steam generator 30 expands in the expansion unit 100, and the power generation unit 200 and the liquid pump The part 300 is operated. The electric power generated by the power generation unit 200 is stored in the battery via the electronic control device 40. Further, the liquid pump unit 300 further sends the liquid phase refrigerant to the vapor generator 30.

  The gas-phase refrigerant flowing out from the expansion unit 100 circulates in the order of the expander 10c → the radiator 11 → the gas-liquid separator 12 → the liquid pump unit 300 → the steam generator 30 → the expander 10c. A Rankine cycle similar to the embodiment can be configured.

  Here, the high-pressure refrigerant discharge port of the compressor 10b and the low-pressure refrigerant outlet of the expander 10c merge at the pipe junction, but since the compressor 10b includes a discharge valve, the low-pressure refrigerant flowing out of the expander 10c There is no reverse flow from the high-pressure refrigerant outlet of the compressor 10b into the compressor 10b. Furthermore, the high-pressure refrigerant discharged from the compressor 10b does not flow back from the low-pressure refrigerant outlet of the expander 10c into the expander 10c by the check valve 33b.

  Further, the upstream refrigerant pressure sensor 42, the downstream refrigerant pressure sensor 43, and the water temperature sensor 44 measure the same physical quantity as in the first embodiment, and the measured value is input to the electronic control unit 40.

  Therefore, in the present embodiment, control similar to that in the first embodiment can be performed. Further, in this embodiment, the refrigeration cycle and the Rankine cycle can be operated simultaneously. That is, the same effect as that of the first embodiment can be obtained by performing the refrigerant condensation operation by the refrigeration cycle before operating the waste heat recovery operation mode by the Rankine cycle. Furthermore, if the refrigeration cycle is operated simultaneously with the Rankine cycle, a sufficient amount of liquid phase refrigerant can be stored in the gas-liquid separator 12 by the refrigeration cycle, and gas phase refrigerant bubbles may enter the liquid pump unit 300. Therefore, the liquid-phase refrigerant can be reliably sent to the steam generator 30.

  The electronic control unit 40 of this embodiment operates the refrigeration cycle before the Rankine cycle. This refrigeration cycle operation provides refrigerant condensation operation. The operation of the refrigeration cycle before the Rankine cycle is operated can be set to a time necessary for accumulating a predetermined amount of liquid-phase refrigerant.

  In the electronic control device 40 of this embodiment, when the operation of the Rankine cycle is commanded in a state where the refrigeration cycle is in the normal air conditioning operation, the normal air conditioning operation of the refrigeration cycle is set as the refrigerant condensation operation, and the Rankine cycle Start driving.

  The electronic control unit 40 of this embodiment continues the operation as the refrigeration cycle even after the Rankine cycle starts operation. When the stop of the Rankine cycle is instructed, for example, when the engine coolant temperature as the heat source is excessively lowered, the operation of the Rankine cycle is stopped while the operation as the refrigeration cycle is continued. When the engine coolant temperature rises again, the electronic control unit 40 resumes the Rankine cycle operation. Also at the time of resumption, the refrigerant condensing operation is provided because the refrigeration cycle continues to operate before resumption.

  By such an operation, the start-up failure of the Rankine cycle is suppressed. In addition, stable and highly efficient operation can be realized during Rankine cycle operation.

(Other embodiments)
The vapor compression refrigerator having the Rankine cycle to which the present invention can be applied is not limited to the configuration described in the above embodiment, and the evaporator 14 is used as a refrigerant condenser in the Rankine cycle as shown in FIG. Alternatively, the liquid-phase refrigerant in the gas-liquid separator 52 downstream of the evaporator 14 may be sent to the vapor generator 30 by the liquid pump 32. Moreover, you may arrange | position the condenser 53 in a Rankine cycle separately from the heat radiator 11 and the evaporator 14 which are arrange | positioned at a refrigerating cycle like FIG.

  In the control of the third embodiment to the seventh embodiment, an example in which the control using the refrigerant pressure sensors 42 and 43 of the first embodiment is applied has been described. However, according to the liquid pump power consumption amount of the second embodiment. It is natural that the same effect can be exhibited even if the control is applied. Further, the control of the third embodiment may be applied to the fourth embodiment to the seventh embodiment.

  Further, as physical quantities having a correlation with the refrigerant temperatures inside the liquid pump 32 and the liquid pump unit 300 used in the fifth embodiment or the sixth embodiment, the heat transfer fin temperature of the evaporator 14 and the low pressure port 111 of the compressor Pressure may be used.

  In the above-described embodiment, the collected energy is stored in the capacitor. However, the energy may be stored as mechanical energy such as elastic energy by kinetic energy by a flywheel or a spring.

  In the above-described embodiment, the vane type and scroll type fluid machines are used as the reversible rotary machine 10, the compressor, and the expander. However, the present invention is not limited to this.

  In the above-described embodiment, a certain hysteresis is provided in controlling the waste heat recovery operation mode, but the present invention is not limited to this.

  The application of the present invention is not limited to vehicles.

  Further, the heating element is not limited to the internal combustion engine, and various modifications such as a fuel cell (FC) can be made.

  Further, the present invention is not limited to the above-described embodiment as long as it matches the gist of the invention described in the claims.

It is a whole block diagram of 1st Embodiment, and is also explanatory drawing of the example of a prior application. It is explanatory drawing of the reversible rotary machine of 1st Embodiment. It is a flowchart which shows control of the electronic control apparatus of 1st Embodiment. It is a flowchart which shows the principal part of control of the electronic control apparatus of 1st Embodiment. It is a whole block diagram of 2nd Embodiment. It is a flowchart which shows the principal part of control of the electronic control apparatus of 2nd Embodiment. It is a flowchart which shows the principal part of control of the electronic control apparatus of 3rd Embodiment. It is a whole block diagram of 4th Embodiment. It is a flowchart which shows the principal part of control of the electronic control apparatus of 4th Embodiment. It is a whole block diagram of 5th Embodiment. It is sectional drawing of the reversible rotary machine of 5th Embodiment. It is a flowchart which shows the principal part of control of the electronic control apparatus of 5th Embodiment. It is a whole block diagram of 6th Embodiment. It is a flowchart which shows the principal part of control of the electronic control apparatus of 6th Embodiment. It is a whole block diagram of 7th Embodiment. It is a whole block diagram which shows the modification of the vapor compression refrigerator of 1st Embodiment. It is a whole block diagram which shows another modification of the vapor compression refrigerator of 1st Embodiment.

Explanation of symbols

10: Reversible rotating machine (refrigeration cycle, Rankine cycle, expander),
11 ... radiator (refrigeration cycle, Rankine cycle, condenser),
13 ... decompressor (refrigeration cycle), 14 ... evaporator (refrigeration cycle),
20 ... Engine (heating element), 30 ... Steam generator (Rankine cycle),
31 ... 1st bypass circuit (liquid phase piping),
32 ... Electric liquid pump (liquid pump, Rankine cycle),
35a ... open / close valve (switching means), 36 ... control valve (switching means),
40 ... Electronic control unit (control means), 42 ... Upstream refrigerant pressure sensor,
43 ... Downstream refrigerant pressure sensor, 45 ... Outside air temperature sensor,
46 ... Liquid pump housing temperature sensor, 47 ... Evaporator outlet temperature sensor,
DESCRIPTION OF SYMBOLS 100 ... Compression expansion part, 200 ... Electric power generation motor part, 300 ... Liquid pump part (Rankine cycle).

Claims (32)

A rotary fluid machine (10, 10b, 10c) that mutually converts the fluid energy of the refrigerant and the mechanical rotational energy;
A condenser (11) for condensing refrigerant supplied from the rotary fluid machine (10, 10b, 10c);
Rankine including a liquid pump (32, 300) for sending refrigerant supplied from the condenser (11), and a steam generator (30) for heating the refrigerant sent by the liquid pump by heat of the heating element (20) Cycle system (10, 11, 30, 32, 300);
A refrigeration cycle system (10, 11, 13, 14) including an evaporator (14) for evaporating the refrigerant supplied from the condenser (11);
During the operation of the Rankine cycle system (10, 11, 30, 32, 300), the refrigerant of the refrigeration cycle system (10, 11, 13, 14) is compressed by the rotary fluid machine (10, 10b, 10c). A heat cycle device comprising: a control device (40) for performing a refrigerant condensation operation for condensing the refrigerant by the condenser (11). After the control device (40) starts the operation of the Rankine cycle system (10, 11, 30, 32, 300), the operation of the Rankine cycle system (10, 11, 30, 32, 300) is normal. Determining means for determining whether or not
A control means for continuing the operation of the Rankine cycle system (10, 11, 30, 32, 300) if determined to be normal, and performing the refrigerant condensation operation if determined to be abnormal. The heat cycle apparatus according to claim 1, wherein Furthermore, an upstream refrigerant pressure sensor (42) that is disposed in the refrigerant flow upstream side portion of the liquid pump (32, 300) and measures the pressure of the refrigerant;
A downstream refrigerant pressure sensor (43) that is disposed in a downstream portion of the refrigerant flow of the liquid pump (32, 300) and measures the pressure of the refrigerant;
The determination means is configured to detect the detected pressure value (P2) of the downstream refrigerant pressure sensor (43) and the upstream refrigerant pressure sensor (42) during operation of the Rankine cycle system (10, 11, 30, 32, 300). When the difference value (P2−P1) from the detected pressure value (P1) is larger than the predetermined pressure value (P), it is determined that the operation of the Rankine cycle (10, 11, 30, 32, 300) is normal. ,
The difference value (P2−P1) between the detected pressure value (P2) of the downstream refrigerant pressure sensor (43) and the detected pressure value (P1) of the upstream refrigerant pressure sensor (42) is equal to or less than the predetermined pressure value (P). In the case, it is determined that the operation of the Rankine cycle (10, 11, 30, 32, 300) is abnormal. When the work of the liquid pump (32, 300) is larger than a predetermined work during the Rankine cycle system (10, 11, 30, 32, 300) operation, 10, 11, 30, 32, 300) is determined to be normal,
The operation of the Rankine cycle system (10, 11, 30, 32, 300) is determined to be abnormal when the work of the liquid pump (32, 300) is less than or equal to a predetermined work. 2. The thermal cycle apparatus according to 2. The liquid pump is an electric liquid pump (32),
The heat cycle apparatus according to claim 4, wherein the work amount is indicated by an amount of electric power consumed by the electric liquid pump (32). Furthermore, it has a blowing means (14a) for blowing the temperature-controlled air by the refrigeration cycle system (10, 11, 13, 14),
The heat cycle device according to any one of claims 1 to 5, wherein the control device (40) performs the refrigerant condensing operation in a state where the air blowing means (14a) is not operated. In addition, sensors (46, 47) for measuring physical quantities having a correlation with the temperature of the refrigerant inside the liquid pump (32, 300) are provided,
The controller (40) indicates that the physical quantity measured by the sensors (46, 47) after starting the refrigerant condensation operation indicates that the refrigerant inside the refrigerant pump (32) is in a supercooled state. The heat cycle device according to any one of claims 1 to 6, wherein a time until the value is reached is a duration time during which the refrigerant condensation operation is continued. The condenser (11) is a heat exchanger that condenses the refrigerant by exchanging heat between the outside air and the refrigerant,
Furthermore, an outside air temperature sensor (45) for measuring the temperature of the outside air,
A sensor (46, 47) for measuring a physical quantity having a correlation with the temperature of the refrigerant inside the liquid pump (32, 300),
The control device (40) determines a target temperature at which the refrigerant inside the refrigerant pump (32) is in a supercooled state based on the outside air temperature measured by the outside air temperature sensor (45), and
The time from the start of the refrigerant condensation operation to the time when the physical quantity measured by the sensors (46, 47) reaches a value indicating the target temperature is defined as the duration for which the refrigerant condensation operation is continued. The thermal cycle device according to any one of claims 1 to 6. The thermal cycle device according to claim 7 or 8, wherein the sensor is a temperature sensor (46) for measuring a temperature of a housing of the refrigerant pump. The thermal cycle device according to claim 7 or 8, wherein the sensor is a temperature sensor (47) that measures the temperature of air immediately after heat exchange with a refrigerant in the evaporator (14). The condenser (11) is a heat exchanger that condenses the refrigerant by exchanging heat between the outside air and the refrigerant,
Furthermore, an outside air temperature sensor (45) for measuring the temperature of the outside air is provided,
The said control apparatus (40) is provided with the continuation time setting means which determines the continuation time (T21) which continues the said refrigerant | coolant condensing operation according to the temperature measured by the said external temperature sensor (45). Item 7. The thermal cycle device according to any one of Items 1 to 6. The rotary fluid machine is a reversible rotary machine (10) that can be reversibly operated as an expander that expands a refrigerant to extract power or a compressor that compresses a refrigerant by receiving power. The heat cycle apparatus according to any one of claims 1 to 11. The control device (40) operates the rotary fluid machine as the expander before starting the operation of the Rankine cycle system (10, 11, 30, 32, 300). The heat cycle apparatus according to claim 12, wherein the refrigerant condensing operation is performed by operating as the compressor. The reversible rotating machine (10) is configured as an integral structure with the liquid pump (32, 300),
The liquid pump (32, 300) is arranged to be cooled by a gas phase refrigerant sucked into the reversible rotating machine (10) when the refrigeration cycle system (10, 11, 13, 14) is operated. The thermal cycle apparatus according to claim 12 or 13, wherein 12. The rotary fluid machine includes: an expander (10c) that expands a refrigerant to take out power; and a compressor (10b) that receives the power to compress the refrigerant. The thermal cycle apparatus as described in any one. The controller (40) operates the compressor (10b) before operating the expander (10c) to start operation of the Rankine cycle system (10, 11, 30, 32, 300). The heat cycle apparatus according to claim 15, wherein the refrigerant condensing operation is performed. The control device (40) operates the expander (10c) to start the operation of the Rankine cycle system (10, 11, 30, 32, 300). At the same time, the control device (40) The heat cycle apparatus according to claim 15, wherein the refrigerant condensing operation is performed by operating. Rankine cycle system (10, 11, 30, 32) including a liquid pump (32, 300) for sending refrigerant and a steam generator (30) for heating the refrigerant sent by the liquid pump by heat of the heating element (20) 300)
A refrigeration cycle system (10, 11, 13, 14) including an evaporator (14) for evaporating the refrigerant;
During the operation of the Rankine cycle system (10, 11, 30, 32, 300), a cooling operation for cooling the liquid pump (32, 300) by operating the refrigeration cycle system (10, 11, 13, 14). And a control device (40) for performing the heat cycle. The refrigeration cycle system includes a compressor (10, 10b), and the liquid pump (32, 300) is arranged to be cooled by a gas phase refrigerant sucked into the compressor (10, 10b). The thermal cycle apparatus according to claim 18, wherein The control device (40) is configured to start operation of the Rankine cycle system (10, 11, 30, 32, 300) and / or of the Rankine cycle system (10, 11, 30, 32, 300). The heat cycle apparatus according to claim 18 or 19, wherein the cooling operation is performed during operation. The low-pressure refrigerant is evaporated to absorb heat from the low-temperature side, and the vapor-phase refrigerant evaporated is compressed to increase the temperature, and the heat absorbed from the low-temperature side is dissipated to the high-temperature side to condense the gas-phase refrigerant. Refrigeration cycle (10, 11, 13, 14) to be a liquid phase refrigerant,
A steam generator (30) for heating the liquid phase refrigerant of the refrigeration cycle (10, 11, 13, 14) with waste heat of the heating element (20) to generate a gas phase refrigerant, and the refrigeration cycle (10 , 11, 13, 14) a liquid phase pipe (31) for connecting the liquid phase refrigerant take-out section (12, 52) for taking out the liquid phase refrigerant from the vapor generator (30), and the liquid phase pipe (31 ), A liquid pump (32, 300) for sending the liquid phase refrigerant to the vapor generator (30), an expander (10) for expanding the gas phase refrigerant to extract power, and the expander ( Rankine cycle (10, 11, 30, 32, 300) having a condenser (11) for condensing the gas-phase refrigerant that has been expanded in 10),
Control means (40) for controlling operating states of the refrigeration cycle (10, 11, 13, 14) and the Rankine cycle (10, 11, 30, 32, 300);
Switching between operating the Rankine cycle (10, 11, 30, 32, 300) and operating the refrigeration cycle (10, 11, 13, 14) according to a signal from the control means (40). Switching means (35a, 36),
When the Rankine cycle (10, 11, 30, 32, 300) is operated, the control means (40) operates the refrigeration cycle (10, 11, 13, 14) to condense the gas-phase refrigerant. A thermal cycle apparatus characterized in that a refrigerant condensing operation for converting to a liquid phase refrigerant is performed, and the Rankine cycle (10, 11, 30, 32, 300) is operated after the refrigerant condensing operation. The low-pressure refrigerant is evaporated to absorb heat from the low-temperature side, and the vapor-phase refrigerant evaporated is compressed to increase the temperature, and the heat absorbed from the low-temperature side is dissipated to the high-temperature side to condense the gas-phase refrigerant. Refrigeration cycle (10, 11, 13, 14) to be a liquid phase refrigerant,
A steam generator (30) for heating the liquid phase refrigerant of the refrigeration cycle (10, 11, 13, 14) with waste heat of the heating element (20) to generate a gas phase refrigerant, and the refrigeration cycle (10 , 11, 13, 14) a liquid phase pipe (31) for connecting the liquid phase refrigerant take-out section (12, 52) for taking out the liquid phase refrigerant from the vapor generator (30), and the liquid phase pipe (31 ), A liquid pump (32, 300) for sending the liquid phase refrigerant to the vapor generator (30), an expander (10) for expanding the gas phase refrigerant to extract power, and the expander ( Rankine cycle (10, 11, 30, 32, 300) having a condenser (11) for condensing the gas-phase refrigerant that has been expanded in 10),
Control means (40) for controlling operating states of the refrigeration cycle (10, 11, 13, 14) and the Rankine cycle (10, 11, 30, 32, 300);
Switching between operating the Rankine cycle (10, 11, 30, 32, 300) and operating the refrigeration cycle (10, 11, 13, 14) according to a signal from the control means (40). Switching means (35a, 36),
The control means (40) determines whether the operation of the Rankine cycle (10, 11, 30, 32, 300) is normal or abnormal after the Rankine cycle (10, 11, 30, 32, 300) is operated. ,
If determined to be normal, the operation of the Rankine cycle (10, 11, 30, 32, 300) is continued,
When it is determined as abnormal, the operation of the Rankine cycle (10, 11, 30, 32, 300) is stopped, and the refrigeration cycle (10, 11, 13, 14) is operated to recover the liquid phase refrigerant. A heat cycle apparatus, wherein a refrigerant condensation operation is performed, and the Rankine cycle (10, 11, 30, 32, 300) is operated again after the refrigerant condensation operation. An upstream refrigerant pressure sensor (42) which is disposed in a refrigerant flow upstream portion of the liquid pump (32, 300) and outputs the pressure of the refrigerant to the control means (40);
A downstream refrigerant pressure sensor (43) disposed at a downstream side of the refrigerant flow of the liquid pump (32, 300) and outputting a refrigerant pressure to the control means (40);
The control means (40) is configured to detect the upstream refrigerant pressure sensor (42) from the detected pressure value (P2) of the downstream refrigerant pressure sensor (43) during the Rankine cycle (10, 11, 30, 32, 300) operation. When the value (P2-P1) obtained by subtracting the detected pressure value (P1) is greater than the predetermined pressure value (P), the Rankine cycle (10, 11, 30, 32, 300) is operated normally.
A value (P2-P1) obtained by subtracting the detected pressure value (P1) of the upstream refrigerant pressure sensor (42) from the detected pressure value (P2) of the downstream refrigerant pressure sensor (43) is equal to or less than the predetermined pressure value (P). In the case, the operation of the Rankine cycle (10, 11, 30, 32, 300) is determined to be abnormal. When the work of the liquid pump (32, 300) is larger than a predetermined work during operation of the Rankine cycle (10, 11, 30, 32, 300), the control means (40) (10, 11, 30, 32, 300) is normal,
When the work of the liquid pump (32, 300) is less than or equal to a predetermined work, the operation of the Rankine cycle (10, 11, 30, 32, 300) is determined to be abnormal. The heat cycle apparatus according to claim 22. The liquid pump is an electric liquid pump (32) operated by electricity,
The thermal cycle apparatus according to claim 24, wherein the work amount is an amount of electric power consumed by the electric liquid pump (32). The expander is a reversible rotating machine (10) having a compressor function of compressing the gas-phase refrigerant in the refrigeration cycle (10, 11, 13, 14),
The reversible rotating machine (10) is configured as an integral structure with the liquid pump (32, 300),
The liquid pump (32, 300) is cooled by a gas phase refrigerant sucked into the reversible rotating machine (10) when the refrigeration cycle (10, 11, 13, 14) is operated. The thermal cycle device according to any one of claims 21 to 25, wherein: A blowing means (14a) for blowing air conditioned by the refrigeration cycle (10, 11, 13, 14);
Operation request means (41) for requesting operation of the refrigeration cycle,
When the refrigerant condensing operation is performed, the control means (40), when the operation requesting means (41) does not require the operation of the refrigeration cycle (10, 11, 13, 14), the air blowing means. The heat cycle apparatus according to any one of claims 21 to 26, wherein the refrigerant condensing operation is performed without operating (14a). The condenser (11) is a heat exchanger that condenses the gas-phase refrigerant by exchanging heat between the outside air and the refrigerant,
An outside air temperature sensor (45) for measuring the temperature of the outside air;
The control means (40) is adapted to determine a duration (T21) for continuing the refrigerant condensation operation,
The thermal cycle device according to any one of claims 21 to 27, wherein the duration (T21) is a time determined by the outside air temperature. A sensor (46, 47) for measuring a physical quantity having a correlation with the temperature of the refrigerant inside the liquid pump (32, 300);
The control means (40) is adapted to determine a duration for which the refrigerant condensation operation is continued,
The duration indicates that the physical value measured by the sensors (46, 47) after the refrigerant condensing operation is started indicates that the temperature of the refrigerant inside the refrigerant pump (32) is in an overcooled state. The heat cycle apparatus according to any one of claims 21 to 27, wherein the time is a time until the value is reached. The condenser (11) is a heat exchanger that condenses the gas-phase refrigerant by exchanging heat between the outside air and the refrigerant,
An outside air temperature sensor (45) for measuring the temperature of the outside air;
A sensor (46, 47) for measuring a physical quantity having a correlation with the temperature of the refrigerant inside the liquid pump (32, 300),
The control means (40) determines a temperature at which the temperature of the refrigerant inside the refrigerant pump (32, 300) becomes a supercooled state according to the outside air temperature, and further determines a duration for continuing the refrigerant condensation operation. And
The duration is a value indicating that the physical value measured by the sensors (46, 47) after starting the refrigerant condensation operation indicates that the refrigerant temperature in the refrigerant pump (32) is in an overcooled state. The heat cycle apparatus according to any one of claims 21 to 27, wherein the heat cycle apparatus is time until The thermal cycle device according to claim 29 or 30, wherein the sensor for measuring the physical quantity is a temperature sensor (46) for measuring a temperature of a housing of the refrigerant pump. The refrigeration cycle (10, 11, 13, 14) includes an evaporator (14) for exchanging heat of the low-pressure refrigerant with air to evaporate the low-pressure refrigerant,
The thermal cycle device according to claim 29 or 30, wherein the sensor for measuring the physical quantity is a temperature sensor (47) for measuring the temperature of air immediately after passing through the evaporator (14).

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