DE102005024685A1 - heat circuit - Google Patents

Abstract

The waste heat recovery operation mode (a Rankine cycle) is started and operated for a certain period T1 (S430 to S450). If the difference (P2-P1) between the upstream pressure (P1) and the downstream pressure (P2) of the liquid pump is higher than the predetermined pressure (P), the waste heat recovery operation mode is continued. If the difference (P2-P1) is not greater than the predetermined pressure (P) after the air conditioning operation mode is started (S480 to S500), the waste heat recovery operation mode is restarted (S430 to S450). Due to this, it is possible to provide a heating circuit provided with a refrigerating cycle and a Rankine cycle, which are interchangeable, and in which an incomplete start at the time of a Rankine cycle can be reduced and a deterioration of the Circular efficiency can be reduced.

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

The The present invention relates to a Clausius-Rankine cycle, in The energy from a heat energy given to a refrigerant receives.

2. Description of others designs

traditionally, is a heat circuit device known as a refrigeration cycle device is referred to, and it is also known a heat-circulating device, referred to as a Rankine Rankine Circular Device. According to the refrigeration cycle device can if a refrigerant compressed by giving it energy to transfer heat, a high or a low temperature can be provided. According to one Clausius Rankine Circular Device can give you energy from one refrigerant given heat energy receive. For example, a Rankine Rankine cycle device in granted Japanese Patent Publication No. 3356449 and the unaudited Japanese Utility Model Publication No. 63-92021. This Clausius-Rankine circular device can be used as an electric generator device in which Thermal energy is recovered, so as to generate electrical energy. alternative For example, this Rankine cycle device can be used as a drive power generation device be used in the waste heat an internal combustion engine of a motor vehicle is recovered, so as to generate a drive energy.

In Japanese Patent Application No. 2003-390893 proposed the inventors an air conditioning system (cooling circuit) to use the vehicle with a Clausius Rankine circle to recover of heat energy from an engine-out of a vehicle-mounted engine waste heat in front. This air conditioner for vehicle use is given as an example the former Registration designated.

This example of the earlier application will now be referred to 1 explained. The example of the earlier application includes components for constructing a refrigeration cycle device to provide an air conditioning operation mode (refrigeration cycle mode) in which the refrigerant is arranged in the order of the reciprocating rotary machine 10 → of the radiator 11 → the gas / liquid separator 12 → of the decompressor 13 → of the evaporator 14 flows.

Furthermore, this earlier application contains a liquid phase tube 31 for connecting the tube forming the cooling circuit to the steam generator 30 ; and a liquid pump 32 in the liquid phase tube 31 is arranged to move the liquid-phase refrigerant to the steam generator 30 , The earlier application further includes components to construct a Rankine Rankine cycle apparatus to provide a waste heat recovery mode (Rankine cycle operation) in which the refrigerant is in the order of the liquid pump 32 → of the steam generator 30 → the reversible lathe 10 → of the radiator 11 flows.

Therefore, at the time of the air conditioning operation mode, the vehicle compartment can be conditioned, and at the time of the waste heat recovery operation mode, that of the engine 20 discharged waste heat through the reversible lathe 10 be recovered in the form of energy.

However, in the example of the earlier application, the following cases may occur. If any of the amount in the gas / liquid separator 12 remaining refrigerant is small on the basis of an operating condition of the air conditioner (the refrigerating cycle) for vehicle use or if the liquid-phase refrigerant in the liquid pump 32 by an increase in the temperature in the liquid pump 32 vaporizes, bubbles of the gas-phase refrigerant inside the liquid pump 32 and the liquid phase refrigerant can not become a steam generator 30 be moved, even if the liquid pump 32 is operated. Due to this, there is a possibility that it becomes impossible to normally operate the waste heat recovery operation mode (Clausius-Rankine cycle).

Even if the liquid pump 32 the liquid phase refrigerant still to the steam generator 30 is the operating power of the liquid pump 32 through the into the liquid pump 32 reduced mixed bubbles of the gas-phase refrigerant. In other words, an amount of the refrigerant to be transported is reduced in terms of the power consumption of the pump. That is, one to the steam generator 30 The amount of refrigerant to be conducted is reduced, and there is a possibility that the efficiency of a Rankine cycle can be lowered.

A Object of the present invention is the possibility of the occurrence of a incomplete Starts a Clausius Rankine circle device to reduce.

It is a further object of the present invention to reduce the possibility of deterioration To reduce the efficiency of a Rankine Rankine cycle device.

It is a still further object of the present invention, it is possible to to operate a Clausius-Rankine cycle device stably, by the function of a refrigeration cycle device in the heat circuit device, the for both the Rankine Rankine cycle apparatus and the refrigeration cycle apparatus can be used.

SUMMARY OF THE INVENTION

Around to solve the above tasks, The present invention sets the following technical measures one.

The invention described in Aspect 1 uses a heat-circulating device with a fluid lathe ( 10 . 10b . 10c ) for mutually converting between fluid energy of a refrigerant and mechanical rotational energy; a capacitor ( 11 ) for condensing the from the fluid lathe ( 10 . 10b . 10c ) supplied refrigerant; a Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) with a fluid pump ( 32 . 300 ) for moving the from the capacitor ( 11 ) supplied refrigerant and also with a steam generator ( 30 ) for heating the refrigerant, which has been moved by the fluid pump, by the heat of a heat generating body ( 20 ); a refrigeration cycle system ( 10 . 11 . 13 . 14 ) with an evaporator ( 14 ) for vaporizing the of the capacitor ( 11 ) supplied refrigerant; and a control unit ( 40 ) for performing a refrigerant condensation operation in which the refrigerant in the refrigeration cycle system ( 10 . 11 . 13 . 14 ) through the fluid lathe ( 10 . 10b . 10c ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) and the compressed refrigerant through the condenser ( 11 ) is condensed.

According to this Invention is operated when a Rankine Rankine system will, the refrigerant in the refrigeration cycle system compressed by the fluid lathe and by the condenser condensed. Therefore, the liquid-phase refrigerant can be a Rankine Ranking system supplied become. As a result, it is possible that Occurrence of an incomplete Starts a Rankine cycle system to suppress. Further Is it possible, to suppress the deterioration of efficiency during operation.

The invention described in aspect 2 employs a thermal circuit device according to aspect 1, wherein the control unit ( 40 ) comprises: judging means for judging whether the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) operates normally or not after the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) was started; and a control device for continuing the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) if it is judged that the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ), and performing the refrigerant condensation operation if it is judged that the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) does not work normally.

According to this The invention becomes when it is judged that the Rankine cycle system is not normal works, the refrigerant condensation operation executed. Therefore may be the liquid phase refrigerant fed to the Rankine cycle system. Accordingly, it is possible, the occurrence of a lack of the liquid-phase refrigerant caused abnormal condition to suppress.

According to one embodiment According to the present invention, the refrigerant condensation operation accomplished when the operation of the Rankine cycle system is temporarily stopped. According to one another embodiment According to the present invention, the refrigerant condensation operation executed simultaneously be while the operation of the Rankine cycle system is continued.

The invention described in aspect 3 employs a heat circuit device according to aspect 2, further comprising an upstream refrigerant pressure sensor (US Pat. 42 ) for measuring a pressure of the refrigerant that is in an upstream portion of the refrigerant flow of the fluid pump ( 32 . 300 ) is arranged; and a downstream refrigerant pressure sensor ( 43 ) for measuring a pressure of the refrigerant that is in a downstream portion of the refrigerant flow of the fluid pump ( 32 . 300 ), wherein the judging means judges that the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) operates normally, if a difference (P2 - P1) between the detected pressure (P2) of the downstream refrigerant pressure sensor ( 43 ) and the detected pressure (P1) of the upstream refrigerant pressure sensor (FIG. 42 ) is greater than a predetermined pressure (P), and the judging means judges that the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) does not operate normally, if the difference (P2 - P1) between the detected pressure (P2) of the downstream refrigerant pressure sensor ( 43 ) and the detected pressure (P1) of the upstream refrigerant pressure sensor (FIG. 42 ) is not larger than the predetermined pressure (P).

According to this invention, it is possible to have a Anomaly of the Rankine cycle system caused by a lack of liquid-phase refrigerant to judge correctly.

The invention described in Aspect 4 employs a thermal circuit device according to claim 2, wherein the judging means judges that the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) works normally, if an operating load of the liquid pump ( 32 . 300 ) is heavier than a predetermined operating load, and the judging means at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) judges that the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) does not work normally if the operating load of the liquid pump ( 32 . 300 ) is not more than the predetermined operating load.

According to this Invention it is possible an anomaly of the Rankine cycle system, which is characterized by a Lack of liquid phase refrigerant caused will judge correctly.

The invention described in Aspect 5 employs a heat circuit device according to Claim 4, in which the liquid pump is an electric liquid pump ( 32 ) and the operating load through a through the electric fluid pump ( 32 ) consumed electrical energy is displayed.

According to this Invention it is possible an anomaly of the Rankine cycle system by a simple Structure to judge.

The invention described in Aspect 6 uses a thermal circuit device according to any one of aspects 1 to 5, further comprising an air blowing device ( 14a ) for blowing air, the temperature of which through the refrigeration cycle system ( 10 . 11 . 13 . 14 ), the control unit ( 40 ) performs the refrigerant condensation operation under the condition that the air blowing device ( 14a ) is not operated.

According to this Invention may be the refrigerant condensation operation be provided when the cooling device or the refrigeration device in the refrigeration cycle system is operated, and a state in which the blower device is not operated will be through the measure for providing the operation in which the liquid-phase refrigerant is increased, provided. As a result, the liquid-phase refrigerant positively fed become.

The invention described in aspect 7 employs a thermal circuit device according to any one of aspects 1 to 6, further comprising a sensor ( 46 . 47 ) for measuring a physical value having a correlation with the temperature of the refrigerant in the liquid pump ( 32 . 300 ), the control unit ( 40 ) determines the time since the start of the refrigerant condensation operation until when the sensor ( 46 . 47 ) shows that the refrigerant in the refrigerant pump ( 32 ) in the supercooled state has elapsed to be the continuation time for continuing the refrigerant condensation operation.

According to this Invention it is possible excessive refrigerant condensation operation too suppress.

The invention described in aspect 8 employs a thermal circuit device according to any one of aspects 1 to 6, wherein the capacitor ( 11 ) is a heat exchanger for condensing the refrigerant by heat exchange between the outside air and the refrigerant, the heat cycle device further comprising: an outside air temperature sensor ( 45 ) for measuring the temperature of the outside air; and a sensor ( 46 . 47 ) for measuring a physical value having a correlation with the temperature of the refrigerant in the liquid pump ( 32 . 300 ), the control unit ( 40 ) according to the by the outside air temperature sensor ( 45 ) measured outside air temperature, a target temperature at which the refrigerant in the refrigerant pump ( 32 ) is in the supercooled state, and further the control unit ( 40 ) determines the time since the start of the refrigerant condensation operation until when the sensor ( 46 . 47 ) measured physical value to the target temperature has elapsed to be the continuation time to continue the refrigerant condensation operation.

According to this Invention it is possible excessive refrigerant condensation operation too suppress.

The invention described in aspect 9 employs a heat-cycle device according to aspect 7 or 8, in which the sensor is a temperature sensor ( 46 ) for measuring the temperature of the housing of the refrigerant pump.

According to this Invention it is possible to provide a simple structure of the heat circuit device.

The invention described in Aspect 10 uses a thermal circuit device according to Aspect 7 or 8, in which the sensor is a temperature sensor ( 47 ) for measuring the temperature of an air immediately after a heat exchange with the refrigerant in the evaporator ( 14 ).

According to this Invention it is possible to provide a simple structure of the heat circuit device.

The invention described in Aspect 11 uses a thermal circuit device according to one of the aspects 1 to 6, in which the capacitor ( 11 ) is a heat exchanger for condensing the refrigerant by heat exchange between the outside air and the refrigerant, further comprising an outside air temperature sensor ( 45 ) for measuring the outside air temperature, the control unit ( 40 ) Continuation time setting means for determining the continuation time (T21) in which the refrigerant condensation operation is continued in accordance with the flow rate by the outside air temperature sensor (FIG. 45 ) measured temperature.

According to this Invention it is possible excessive refrigerant condensation operation too suppress.

The invention described in aspect 12 employs a thermal cycle device according to any one of aspects 1 to 11, wherein the fluid lathe is a reversible lathe ( 10 ) which can be operated reversely as an expansion machine for obtaining energy when the refrigerant is expanded, or can be operated as a compressor for compressing the refrigerant when power is supplied to the compressor.

According to this Invention may be reversible as the fluid rotary machine Expansion machine or as a compressor can be used is the refrigerant condensation operation accomplished when the fluid lathe at the time of operation of the Rankine cycle system as a compressor works.

The invention described in aspect 13 employs a thermal circuit device according to aspect 12, in which the control unit ( 40 ) performs the refrigerant condensation operation by operating the fluid rotating machine as a compressor before the fluid rotating machine is operated as an expansion machine, and the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is started.

According to this Invention can, if the fluid lathe works in reverse, the refrigerant condensation operation be realized before the operation of the Rankine cycle system is started.

The invention described in Aspect 14 uses a heat-cycle device according to aspect 12 or 13, in which the reversing lathe ( 10 ) with the fluid pump ( 32 . 300 ) is integrated into a body and the fluid pump ( 32 . 300 ) is arranged so that by the in the reversing lathe ( 10 ) sucked gas phase refrigerant at the time of operation of the refrigeration cycle system ( 10 . 11 . 13 . 14 ) can be cooled.

According to this Invention, the temperature of the liquid pump can be reduced if the cooling circuit system is operated.

The invention described in Aspect 15 employs a thermal circuit device according to any one of aspects 1 to 11, wherein the fluid lathe is an expansion machine ( 10c ) for expanding the refrigerant to obtain energy, and a compressor ( 10b ) for compressing the refrigerant when power is supplied to the compressor.

According to this Invention, when both the expansion machine and the Compressor are provided, at the time of operation of the Rankine cycle system the refrigerant condensation operation be carried out by means of the compressor function.

The invention described in aspect 16 employs a thermal circuit device according to aspect 15, in which the control unit ( 40 ) the refrigerant condensation operation by operating the compressor ( 10b ) before the expansion machine ( 10c ) and the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is started.

According to this Invention it is possible the refrigerant condensation operation to realize before the operation of the Rankine cycle system accomplished becomes.

The invention described in aspect 17 employs a thermal circuit device according to aspect 15, in which the control unit ( 40 ) the refrigerant condensation operation by operating the compressor ( 10b ) at the same time, when the expansion machine ( 10c ) and the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is started.

According to this The invention may be at the time of starting the Rankine cycle system the refrigerant condensation operation will be realized. The refrigerant condensation operation can be performed in parallel with the operation of the Rankine cycle system.

The invention described in aspect 18 employs a heat circuit device having a Rankine Ranking circuit system ( 10 . 11 . 30 . 32 . 300 ) with a fluid pump ( 32 . 300 ) for moving a refrigerant and also with a steam generator ( 30 ) for heating the refrigerant, which has been moved by the fluid pump, by the heat of a heat generating body ( 20 ); a Kühlkreissys tem ( 10 . 11 . 13 . 14 ) with an evaporator ( 14 ) for vaporizing the refrigerant; and a control unit ( 40 ) for performing the cooling operation for cooling the fluid pump by operating the refrigeration cycle system ( 10 . 11 . 13 . 14 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ).

According to this Invention can operate when the Rankine Ranking system will, the liquid pump chilled become. That's why it's possible the occurrence of a problem caused by the gas-phase refrigerant to prevent.

The invention described in aspect 19 employs a heat circuit device according to aspect 18, in which the refrigeration cycle system comprises a compressor ( 10 . 10b ) and the fluid pump ( 32 . 300 ) is arranged so that through the in the compressor ( 10 . 10b ) sucked gas-phase refrigerant can be cooled.

According to this Invention, the lathe can be arranged integrated. Further is it possible with this construction, the liquid pump to cool.

The invention described in aspect 20 employs a heat-cycle device according to aspect 18 or 19, in which the control unit ( 40 ) performs the cooling operation before the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) and / or during the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is operated.

According to this Invention, the fluid pump can be cooled. That's why it is possible, the occurrence of a problem caused by the gas-phase refrigerant to prevent. When the cooling process accomplished is started before the operation of the Rankine cycle system it will be possible the gas phase refrigerant in the liquid pump to reduce. Therefore, the occurrence of an incomplete start of the Rankine cycle system can be suppressed. When the cooling process is performed at the beginning of the start of the Rankine cycle system, i. e. when the cooling process accomplished immediately after the Rankine cycle system is started, Is it possible, the occurrence of an incomplete Starts the Clausius-Rankine circle system to suppress. If the cooling process while operation of the Rankine cycle system, it is possible to have a Deterioration of the efficiency of the Rankine cycle system to suppress.

The present invention has been devised to solve the above objects. The invention described in aspect 21 provides a heat circuit with a cooling circuit ( 10 . 11 . 13 . 14 ) in which a low-pressure refrigerant is evaporated so as to absorb heat from a low-temperature side, and the evaporated gas-phase refrigerant is compressed so as to raise the temperature, and the heat absorbed from the low-temperature side is radiated to a high-temperature side, so condensing the gas phase refrigerant into the liquid phase refrigerant; a Rankine Ranking Circle ( 10 . 11 . 30 . 32 ) with a steam generator ( 30 ) for generating the gas-phase refrigerant by heating the liquid-phase refrigerant of the refrigeration cycle ( 10 . 11 . 12 . 14 ) by the waste heat of a heat generating body ( 20 ), as well as with a liquid phase tube ( 31 ) for connecting a liquid phase extraction section ( 12 . 52 ) for removing the liquid-phase refrigerant from the refrigeration cycle ( 10 . 11 . 13 . 14 ) with the steam generator ( 30 ), as well as with one in the liquid phase tube ( 31 ) arranged liquid pump ( 32 . 300 ) for moving the liquid phase refrigerant to the steam generator ( 30 ), as well as with an expansion machine ( 10 ) for obtaining energy by expanding the gas-phase refrigerant, and also with a condenser ( 11 ) for condensing the gas-phase refrigerant generated by the expander ( 10 ) has been extended; a control device ( 40 ) for controlling an operating state of the cooling circuit ( 10 . 11 . 13 . 14 ) and also for controlling an operating state of the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ); and a switching device ( 35a . 36 ) for switching between a case where a Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) and a case where the refrigeration cycle ( 10 . 11 . 13 . 14 ) by one of the control device ( 40 ), the control device ( 40 ) the Clausius-Rankine-Kreis ( 10 . 11 . 30 . 32 . 300 ) operates in such a way that the cooling circuit ( 10 . 11 . 13 . 14 ) is operated by the refrigerant condensing operation so as to condense the gas-phase refrigerant into the liquid-phase refrigerant, and then the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) is operated.

Because of this, if the cooling circuit ( 10 . 11 . 13 . 14 ) before the Clausius-Rankine cycle ( 10 . 11 . 30 . 32 . 300 ), the gas phase refrigerant is condensed to the liquid phase refrigerant. As a result, the liquid pump ( 32 . 300 ) the liquid-phase refrigerant positively from the liquid-phase refrigerant extraction portion ( 12 . 52 ) and suck it to the steam generator ( 30 ) move. Accordingly, the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) are started normally.

In addition, it is possible to deteriorate the operating efficiency of the liquid pump (FIG. 32 . 300 ) caused by bubbles in the gas-phase refrigerant. Therefore, it is possible to prevent deterioration of the efficiency of the Rankine cycle.

The invention described in aspect 22 provides a heat circuit with a cooling circuit ( 10 . 11 . 13 . 14 ) in which a refrigerant is evaporated at a low pressure so as to absorb heat from a low-temperature side, and the vaporized gas-phase refrigerant is compressed so as to elevate the temperature, and the heat absorbed by the low-temperature side is radiated to a high-temperature side, so as to condense the gas-phase refrigerant into the liquid-phase refrigerant; a Rankine Ranking Circle ( 10 . 11 . 30 . 32 . 300 ) with a steam generator ( 30 ) for generating the gas-phase refrigerant by heating the liquid-phase refrigerant of the refrigeration cycle ( 10 . 11 . 13 . 14 ) by the waste heat of a heat generating body ( 20 ), as well as with a liquid phase tube ( 31 ) for connecting a liquid phase extraction section ( 12 . 52 ) for removing the liquid-phase refrigerant from the refrigeration cycle ( 10 . 11 . 13 . 14 ) with the steam generator ( 30 ), as well as with one in the liquid phase tube ( 31 ) arranged liquid pump ( 32 . 300 ) for moving the liquid phase refrigerant to the steam generator ( 30 ), as well as with an expansion machine ( 10 ) for obtaining energy by expanding the gas phase refrigerant, and also with a condenser ( 11 ) for condensing the gas-phase refrigerant generated by the expander ( 10 ) has been extended; a control device ( 40 ) for controlling an operating state of the cooling circuit ( 10 . 11 . 13 . 14 ) and also for controlling an operating state of the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ); and a switching device ( 35a . 36 ) for switching between the case where the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) and the case where the refrigeration cycle ( 10 . 11 . 13 . 14 ) by one of the control device ( 40 ), the control device ( 40 ) after the Clausius-Rankine cycle ( 10 . 11 . 30 . 32 . 300 ), assesses whether the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) is working normally or not, the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) is kept in operation if the operation of the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) has been judged normal and the control device ( 40 ) in the case when the operation of the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) has been assessed as abnormal, works in such a way that it controls the operation of the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) stops and the cooling circuit ( 10 . 11 . 13 . 14 ), so as to perform the refrigerant condensation process for recovering the liquid-phase refrigerant, and the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) operates again after the refrigerant condensation process.

Because of this, and only if the Rankine Ranking Circle ( 10 . 11 . 30 . 32 . 300 ) works abnormally, the cooling circuit ( 10 . 11 . 13 . 14 ) and the same effect as in Aspect 1 can be exhibited. Therefore, it is possible to prevent occurrence of a case where the refrigeration cycle is unnecessarily operated before the Rankine cycle (FIG. 10 . 11 . 30 . 32 . 300 ) is operated.

The invention described in aspect 23 provides a heat circuit according to aspect 22, further comprising an upstream refrigerant pressure sensor ( 42 ) in a portion on the upstream flow side of the refrigerant of the liquid pump ( 32 . 300 ) is arranged, wherein the upstream refrigerant pressure sensor ( 42 ) a signal of the refrigerant pressure to the control device ( 40 ) outputs; and a downstream refrigerant pressure sensor ( 43 ) in a section on the downstream flow side of the refrigerant of the liquid pump ( 32 . 300 ), wherein the downstream coolant pressure sensor ( 43 ) a signal of the refrigerant pressure to the control device ( 40 ), the control device ( 40 ) in the case where a value (P2 - P1) obtained when a detected pressure value (P1) of the upstream refrigerant pressure sensor (FIG. 429 from a detected pressure value (P2) of the downstream refrigerant pressure sensor (FIG. 43 ) is higher than a predetermined pressure value (P) when the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ), judges that the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) operates normally, and the control device ( 40 ) in the case where the value (P2 - P1) obtained when the detected pressure value (P1) of the upstream refrigerant pressure sensor (FIG. 42 ) of the detected pressure value (P2) of the downstream refrigerant pressure sensor (FIG. 43 ) is not greater than the predetermined pressure value (P), judges that the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) does not work normally.

In this context, if the liquid pump ( 32 . 300 ) is normal, the detected pressure (P1) of the upstream refrigerant pressure sensor ( 42 ) lower than the detected pressure (P2) of the downstream refrigerant pressure sensor (FIG. 43 ). Therefore, and especially when the difference (P2 - P1) is not larger than the predetermined pressure (P), it is possible to judge that the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) does not work normally.

According to the invention described in aspect 24, a thermal circuit according to aspect 22 is provided, in which the control device ( 40 ) judges that the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) works normally, if an operating load of Flüs pump ( 32 . 300 ) is greater than a certain operating load when the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ), and the control device ( 40 ) judges that the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) does not work normally if the operating load of the liquid pump ( 32 . 300 ) is not greater than the specified operating load when the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) is working.

The invention described in aspect 25 provides a heat circuit according to aspect 24, wherein the liquid pump is an electricity driven electric liquid pump ( 32 ) and the operating load by a power consumption of the electrically driven liquid pump ( 32 ) is shown. Thus, the operating load can be calculated specifically.

According to the invention described in aspect 26, there is provided a heat circuit according to any one of aspects 22 to 25, wherein the expansion machine comprises a reversing lathe ( 10 ) with the function of a compressor for compressing the gas-phase refrigerant in the refrigeration cycle ( 10 . 11 . 13 . 14 ), the reverse lathe ( 10 ) integrated with the liquid pump ( 32 . 300 ), and the liquid pump ( 32 . 300 ) at the time of operation of the cooling circuit ( 10 . 11 . 13 . 14 ) by the in the reversing lathe ( 10 ) is sucked gas-phase refrigerant is cooled.

Because of this, the liquid pump ( 32 . 300 cooled by the low-temperature gas-phase refrigerant which is sucked when the reversing lathe ( 10 ) works as a compressor. Therefore, the liquid phase refrigerant in the liquid pump ( 32 . 300 ) and an evaporation of the refrigerant in the liquid pump ( 32 . 300 ) can be prevented. Therefore, the liquid-phase refrigerant can be positively moved to the steam generator.

Since the liquid pump ( 32 . 300 ) and the expansion machine ( 10 ) are integrated with each other in a body, the fluid pump ( 32 . 300 ) and the expansion machine ( 10 ) forming parts, which makes the fluid machine smaller in size.

The invention described in aspect 27 provides a heat circuit according to one of the aspects 21 to 26, further comprising an air blowing device ( 14a ) for blowing conditioned air through the cooling circuit ( 10 . 11 . 13 . 14 ); and an operation command device ( 41 ) for commanding the operation of the refrigeration cycle ( 10 . 11 . 13 . 14 In the case of performing the refrigerant condensing operation, the control device (FIG. 40 ) carries out the refrigerant condensation process without the air blowing device ( 14a ) when the operation of the cooling circuit ( 10 . 11 . 13 . 14 ) by the operation command device ( 41 ) is not ordered.

Due to this, in the refrigerant condensation process in which the refrigeration cycle ( 10 . 11 . 13 . 14 ), even if an operator of the heating circuit does not control the operation of the refrigeration cycle ( 10 . 11 . 13 . 14 ), no air jet whose temperature and humidity are set sent. Therefore, the refrigerant condensation process can be carried out without causing inconvenience to the operator. In this connection, in the present invention, the term of air conditioning includes temperature adjustment and humidity adjustment.

The invention described in aspect 28 provides a heat circuit according to one of the aspects 21 to 27, wherein the capacitor ( 11 ) is a heat exchanger for condensing the gas phase refrigerant by heat exchange between the outside air and the refrigerant, the heat circuit further includes an outside air temperature sensor ( 45 ) for measuring the temperature of the outside air, the control device ( 40 ) determines the continuation time (T21) to continue the refrigerant condensation operation, and the continuation time (T21) is determined based on the outside air temperature.

In In this context, the condensation temperature in the cooling circuit and the refrigerant pressure, where the gas-phase refrigerant in the liquid phase refrigerant condensed, by the outside air temperature certainly. This means, if the outside air temperature is high, the refrigerant pressure elevated, to increase the condensation temperature. On the other hand, the temperature is on the the liquid-phase refrigerant supercooled becomes, the higher, The higher the condensation temperature is.

Therefore, the controller determines ( 40 ) the continuation time (T21) according to a relationship between the outside air temperature and the time period in which the liquid-phase refrigerant is undercooled by the continuous operation of the refrigeration cycle. As a result, the liquid-phase refrigerant can be positively cooled. Therefore, the liquid pump ( 32 . 300 ) the liquid phase refrigerant positive to the steam generator ( 30 ) conduct.

The invention described in aspect 29 provides a thermal circuit according to any one of aspects 21 to 27, further comprising a sensor ( 46 . 47 ) for measuring a physical value having a correlation with the temperature of the refrigerant in the liquid pump ( 32 . 300 ), wherein the control device ( 40 ) determines the continuation time, in which the refrigerant condensation process is continued, and the continuation time, the time from the start of the refrigerant condensation process until when the by the sensor ( 46 . 47 ) is the physical value measured at the temperature at which the refrigerant in the refrigerant pump ( 32 ) is undercooled is.

Due to this, the refrigerant in the refrigerant pump ( 32 ) is positively placed in the liquid phase. Therefore, the liquid pump ( 32 . 300 ) the liquid phase refrigerant positive to the steam generator ( 30 ) conduct.

For example, when the refrigerant condensation process continues until the refrigerant temperature in the refrigerant pump (FIG. 32 ) becomes lower than the minimum refrigerant condensation temperature determined by the minimum outside air temperature in the environment-utilizing heat circuit, the above effect can be exhibited.

The invention described in aspect 30 provides a heat circuit according to one of the aspects 21 to 27, wherein the capacitor ( 11 ) is a heat exchanger for condensing the gas-phase refrigerant by heat exchange between the outside air and the refrigerant, the heat circuit further comprises an outside air temperature sensor ( 45 ) for measuring the temperature of the outside air and also a sensor ( 46 . 47 ) for measuring a physical value having a correlation with the temperature of the refrigerant in the liquid pump ( 32 . 300 ), the control device ( 40 ) determines the temperature at which the refrigerant in the refrigerant pump ( 32 is supercooled by the outside air temperature, and also determines the continuation time in which the refrigerant condensing operation is continued, and the continuation time determines the time from the start of the refrigerant condensing operation to when the time passed by the sensor (FIG. 46 . 47 ) is the physical value measured at the temperature at which the refrigerant in the refrigerant pump ( 32 ) is undercooled is.

Because of this, the invention provides the same effect as in Aspect 29, and further, the temperature to which the refrigerant in the liquid pump (FIG. 32 . 300 ) is undercooled, determined by the outside air temperature. Therefore, the continuation time of the refrigerant condensation process can be reduced.

As described in aspect 31, in a thermal circuit according to aspect 29 or 30, the sensor for measuring the physical value may be a temperature sensor (FIG. 46 ) for measuring the temperature of the housing of the refrigerant pump.

As described in aspect 32, in a heat circuit according to aspect 29 or 30, the cooling circuit ( 10 . 11 . 13 . 14 ) an evaporator ( 14 ) for evaporating the low-pressure refrigerant by heat exchange between the low-pressure refrigerant and air, and the physical-value sensor may include a temperature sensor ( 47 ) for measuring the temperature of the air immediately after heat exchange with the low pressure refrigerant.

In In this context correspond to those stated at each institution Reference numerals in parentheses in the embodiment described later shown special facilities.

These and other objects, features and advantages of the present invention will be exemplary in view of the detailed description embodiments of which, as represented by the drawings, can be better understood.

BRIEF DESCRIPTION OF THE DRAWINGS

1 Fig. 10 is an overall arrangement diagram of the first embodiment. 1 is also a schematic representation for explaining the earlier application.

2A and 2 B FIG. 12 are schematic diagrams for explaining a reverse rotary machine of the first embodiment. FIG.

3 FIG. 10 is a flowchart of a control operation of the electronic control unit of the first embodiment. FIG.

4 FIG. 12 is a flowchart of a main portion of the control operation of the electronic control unit of the first embodiment. FIG.

5 Fig. 10 is an overall arrangement diagram of the second embodiment.

6 FIG. 10 is a flowchart of a main portion of the control operation of the electronic control unit of the second embodiment. FIG.

7 FIG. 10 is a flowchart of a main portion of the control operation of the electronic control unit of the third embodiment. FIG.

8th Fig. 10 is an overall arrangement diagram of a fourth embodiment.

9 FIG. 14 is a flowchart of a main portion of the control operation of the electronic control unit of the fourth embodiment. FIG.

10 Fig. 10 is an overall arrangement diagram of a fifth embodiment.

11 is a sectional view of a reversal Lathe of the fifth embodiment.

12 Fig. 10 is a flowchart of a main portion of the control operation of the electronic control unit of the fifth embodiment.

13 Fig. 10 is an overall arrangement diagram of a sixth embodiment.

14 Fig. 10 is a flowchart of a main portion of the control operation of the electronic control unit of the sixth embodiment.

15 Fig. 10 is an overall arrangement diagram of a seventh embodiment.

16 Fig. 10 is an overall arrangement diagram of a modification of the vapor compression refrigerator of the first embodiment.

17 Fig. 10 is an overall arrangement diagram of another modification of the vapor compression refrigerator of the first embodiment.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In an embodiment The present invention is made at the time of operation of a Rankine cycle system the cooling circuit system operated. According to one the features of the embodiment is in the refrigeration cycle system a refrigerant condensation process executed in which the refrigerant compressed by a fluid lathe and by a condenser is condensed. When this refrigerant condensation process is carried out, For example, the liquid-phase refrigerant can positively contribute to the Rankine cycle system be forwarded. The refrigerant condensation process can accomplished before the Rankine cycle system is started, or at the beginning of starting the Rankine Ranking system immediately after the start of the Rankine cycle system, or while the operation of the Rankine cycle system. The refrigerant condensation process may be according to a signal for indicating the start of the Rankine cycle system to be started. When the refrigerant condensation process accomplished before the operation of the Rankine cycle system is started, the Liquid phase refrigerant positively fed at the time of starting the Rankine cycle system become. When the refrigerant condensation process executed simultaneously becomes, if the Rankine cycle system or immediately after the Rankine cycle system is started, the liquid-phase refrigerant at the time of starting the Clausius-Rankine cycle or at the beginning Starting the Clausius Rankine Circle be forwarded positively. When the refrigerant condensation process while operating the Rankine cycle system, may be the liquid phase refrigerant while be positively fed to the operation of the Rankine cycle system. The refrigerant condensation process can be started by judging whether the liquid-phase refrigerant must be forwarded to the Rankine cycle system or not. For example, a trial run of the Rankine cycle system carried out and it is judged from the behavior of the Rankine cycle, whether the liquid-phase refrigerant needed will or not. If it is judged that the supply of the liquid-phase refrigerant is needed the refrigerant condensation process started. Alternatively, according to the collection of experimental data set an environmental condition in which it reacts on the liquid-phase refrigerant lacks, and if this condition is met, the refrigerant condensation process to be started. The refrigerant condensation process can be stopped after being executed for a predetermined period of time or after being for executed a variable period of time has been. For example, after a fixed constant period of time has passed, the refrigerant condensation process being stopped. Alternatively, the refrigerant condensation process be stopped when it is detected that the condition becomes a condition has become, in which the liquid-phase refrigerant supplied or when it detects that the liquid-phase refrigerant stably fed to the Rankine cycle system. The refrigerant condensation process can be executed be when the refrigeration cycle system as a cooling device or as a cold device is operated. In this case, means for increasing the Amount of liquid phase refrigerant be provided. For example, a means may be provided a state in which an air blower for blowing Air to the evaporator in the cooling circuit is not operated, be arranged. Alternatively, means for providing a Condition in which a volume of forced air is pressed, be arranged.

The fluid lathe may be provided by a device having both the function of an expansion machine and the function of a compressor. The fluid lathe can translate energy between fluid energy and mechanical energy generated by rotation. When the fluid rotating machine is rotated, the fluid is compressed from a low pressure to a high pressure. When the fluid is moved from the high pressure side to the low pressure side, rotation is generated. The fluid lathe may be a displacement type machine or a non-displacement type machine. For example it is it is possible to use a reversible lathe which can reversibly function as an expansion machine or a compressor. In this case, the operation of the Rankine cycle system and the operation of the refrigeration cycle system can be selectively performed. With this structure, the refrigerant condensation process can be performed by the refrigeration cycle system prior to the operation of the Rankine cycle system. The fluid lathe may be provided with both the expander and the compressor. In this case, the expansion machine and the compressor can be selectively operated. In addition, the expansion machine and the compressor can be operated simultaneously.

following another feature is described. When operating the cooling circuit system becomes the cooling process for cooling the liquid pump executed. If the liquid pump is cooled, Is it possible, to prevent the occurrence of a problem caused by existence the gas phase refrigerant is caused. The cooling process can accomplished be started before the operation of the Rankine cycle system, and during the Operation of the Rankine cycle system. When the cooling process accomplished is started before the operation of the Rankine cycle system is started, Is it possible, the gas phase refrigerant in the liquid pump and the occurrence of an incomplete start of the Rankine cycle system can be suppressed become. When the cooling process is executed at the beginning of the start of the Rankine cycle system, immediately after the operation of the Rankine cycle system is started, it is possible the occurrence of an incomplete Starts the Clausius Rankine circle system to suppress. When the cooling process while operating the Rankine cycle system, Is it possible, a deterioration in the efficiency of the Rankine cycle system to prevent. The Rankine cycle system forming liquid pump can close the suction channel of the cooling circuit system be arranged forming compressor.

(First embodiment)

In this embodiment, the heat circuit of the present invention is applied to a vapor pressure compression refrigerating cycle having a Rankine cycle. 1 is a schematic representation of a model of this embodiment. The vapor compression refrigerator with a Rankine cycle of this embodiment extracts energy from the engine 20 , which is a heat engine for generating energy used to drive a vehicle, recovered waste heat again. At the same time, the Clausius-Rankine cycle vapor compression refrigerator of this embodiment uses cold heat ("cold", which is analogous hereinafter) and hot heat ("heat", which is hereafter analogous) generated by the vapor compression refrigerator, for air conditioning a vehicle compartment.

In the 1 illustrated reverse lathe 10 is a rotary-type fluid machine having both the function of a compressor for sucking and compressing the refrigerant and the function of an expansion machine for isotropically expanding a superheated steam to obtain energy. The reversible lathe 10 is a rotary-type fluid machine reversibly as an expansion machine for obtaining energy by expanding the refrigerant or as a compressor for compressing the refrigerant when the engine 10 Energy is supplied, can be operated. The reversible lathe 10 may be referred to as a compressor integrated with an expansion engine.

The motor generator 10a is used as an energy source for supplying energy (torque) to the reverse lathe 10 operated, if the reverse lathe 10 as a compressor works. On the other hand, the motor generator 10a a dynamo-electric machine serving as a generator for generating electric power from energy recovered by the expansion machine, that is, as a generator for generating electric power by the reciprocating rotary machine 10 is operated, if the reverse lathe 10 is operated as an expansion machine. In this connection, the construction of the reversible lathe 10 described later.

The cooler 11 is with the output side of the reversible lathe 10 connected when the reverse lathe 10 operates as a compressor, and heat is radiated from the refrigerant to the outside air. That is, the radiator 11 is a radiator for cooling the refrigerant by the outside air. That of the radiator 11 escaping refrigerant flows into the gas / liquid separator 12 (Collecting vessel) for separating the gas-phase refrigerant and the liquid-phase refrigerant from each other.

The decompressor 13 decompresses and expands the liquid phase refrigerant passing through the gas / liquid separator 12 has been separated. This embodiment employs a temperature-type expansion valve which decompresses the refrigerant isentropically and controls the opening degree of the valve so that the degree of superheating of the refrigerant into the reverse rotary machine 10 sucked refrigerant to a certain value when the reverse lathe 10 as a compressor is working.

The evaporator 14 is a heat absorbing device for absorbing heat from the refrigerant when passing through the decompressor 13 decompressed refrigerant is evaporated. That from the evaporator 14 escaping refrigerant flows back into the reversible lathe 10 , As described above, the vapor compression refrigerator (the refrigerant cycle) for moving the heat from the low-temperature side to the high-temperature side from the compressor (the reverse rotary machine 10 ), the radiator 11 , the gas / liquid separator 12 , the decompressor 13 and the evaporator 14 built up. In this context, the evaporator 14 with a fan 14a for sending an air flow, which has been conditioned, when the refrigerant evaporates and absorbs heat, provided in a vehicle compartment. This fan 14a is through the electronic control unit 40 controlled.

In this connection, this embodiment includes an engine cooling circuit for circulating the cooling water around the engine 20 which is a heat generating body to cool. The arranged in the engine cooling circuit water pump 22 circulates the engine cooling water, and the radiator 23 is a heat exchanger for cooling the engine cooling water by heat exchange between the engine cooling water and the outside air. The bypass circuit 24 is a bypass circuit through which the cooling water to the radiator 23 can flow past, and the thermostat 25 is a flow control valve for adjusting a quantity of cooling water entering the bypass circuit 24 flows, and a lot of water, which is in the cooler 23 flows.

In this context, the water pump 22 one by the energy of the engine 20 driven pump of mechanical type. The water pump 22 However, of course, it may also be an electric pump driven by an electric motor.

It is a steam generator 30 in a section on the downstream side of the refrigerant flow of the engine 20 in the engine cooling circuit and in the cooling circuit for connecting the reverse rotary machine 10 with the radiator 11 provided in the cooling circuit. In this steam generator 30 The refrigerant is heated when heat between the refrigerant flowing in the refrigerant cycle and the engine cooling water, the waste heat from the engine 20 has been exchanged.

The arranged in the engine cooling circuit three-way valve 21 Switches between a case in which the engine 20 escaping engine cooling water into the steam generator 30 is circulated, and a case in which the engine 20 Outgoing engine cooling water not in the steam generator 30 is circulated to. In this embodiment, the operation of the three-way valve 21 through the electronic control unit 40 controlled.

In this context, the first bypass circuit 31 which is a liquid phase pipe, a refrigerant passage for introducing the liquid-phase refrigerant passing through the gas-liquid separator 12 has been disconnected to the refrigerant inlet and outlet side of the steam generator 30 on the side of the radiator 11 , This first bypass circuit 31 contains a liquid pump 32 for circulating the liquid phase refrigerant and a check valve 33a to remove the refrigerant only from the side of the gas / liquid separator 12 to the side of the steam generator 30 to flow. In this connection, in this embodiment, the liquid pump 32 an electrically driven pump and is powered by the electronic control unit 40 controlled.

The second bypass circuit 34 is a refrigerant passage to the refrigerant outlet side with the refrigerant inlet side of the radiator 11 to connect when the reverse lathe 10 as an expansion machine works. This second bypass circuit 34 contains a check valve 33b to transfer the refrigerant only from the refrigerant outlet side to the refrigerant inlet side of the radiator 11 to flow when the reverse lathe 10 is operated as an expansion machine.

In this context, the check valve leaves 33c the refrigerant only from the refrigerant outlet side of the evaporator 14 to the suction side of the compressor 10 stream. The opening and closing valve 35a that between the steam generator 30 and the radiator 11 is arranged, is under the control of the electronic control unit 40 opened and closed. The control valve 36 works as a dispensing valve when the reverse lathe 10 is operated as a compressor, ie the control valve 36 works as a check valve to the refrigerant only from the side of the reversible lathe 10 to the side of the steam generator 30 to flow. If the reverse lathe 10 is operated as an expansion engine, the control valve 36 open. An operation of this control valve 36 is through the electronic control unit 40 controlled. As described above, a Rankine cycle is constructed in which the refrigerant in the reverse rotary machine 10 , the capacitor 11 , the gas / liquid separator 12 and the liquid pump 32 flows.

The electronic control unit 40 includes an input section in which the measuring temperature T _{W of} the water temperature sensor 44 for detecting the temperature of the engine cooling water after the heat absorption of the engine cooling water from the engine 20 , the environmental operation signal (environmental operation command signal) from the electronic control unit 41 for an air conditioner, the measuring pressure P1 of the upstream refrigerant pressure sensor 42 for detecting the pressure on the upstream side of the liquid pump 32 and the gauge pressure P2 of the downstream refrigerant pressure sensor 43 for detecting the pressure on the downstream side of the liquid pump 32 be entered.

The electronic control unit 40 controls the operations of the control valve 36 , the fluid pump 32 and the three-way valve 21 according to the program stored in advance based on the measuring temperature of the water temperature sensor 44 that is, on the basis of the waste heat temperature T _W , and also on the basis of the existing or nonexistent air conditioning operation command signal.

The structure and operation of the reversible lathe 10 are briefly explained as follows.

2a is an illustration of a case in which the reversible lathe 10 is operated as a compressor, and 2 B is an illustration of a case in which the reversible lathe 10 is operated as an expansion machine. In this embodiment, the reversible lathe is 10 built from a well-known rotary vane type fluid machine.

If the reverse lathe 10 is operated as a compressor, the rotor 10b through the motor generator 10a rotated, so that the refrigerant can be sucked and compressed. At the same time, the control valve 36 prevents the refrigerant discharged high pressure on the side of the rotor 10b flows back.

If the reverse lathe 10 is operated as an expansion engine, the control valve 36 opened and a through the steam generator 30 Overheated steam generated is transferred to the reverse lathe 10 initiated, so that the rotor 10b rotated and heat energy can be converted into mechanical energy.

When next Now, an operation of the vapor compression refrigerator (the air conditioner) with a Clausius Rankine circle according to this embodiment described.

In the Clausius-Rankine cycle type vapor compression refrigerator of this embodiment, the operation mode is controlled by the controller 40 is switched in accordance with the existing or non-existent Klimabetriebsbefehlssignal and the waste heat temperature T _W. First, the air conditioning mode and the waste heat recovery mode will be explained as follows.

1. Air conditioning mode

In this climate mode of operation is while the evaporator 14 a cooling performance shows the refrigerant through the radiator 11 cooled. In this connection, in this embodiment, the vapor compression refrigerator is operated only for the cooling operation and the dehumidifying operation in which the cold generated by the vapor compression refrigerator is utilized, ie, the heat absorbing effect is utilized. The vapor compression chiller is not operated for the heating process in which the through the radiator 11 generated heat is used. However, even at the time of heating, the operation of the vapor compression refrigerator is the same as that of the cooling operation and the dehumidifying operation.

In particular, the process is carried out as follows. On the condition that the liquid pump 32 is stopped, the opening and closing valve 35a opened and the control valve 36 works as an output valve, the motor generator 10a is energized to the rotor 10b to turn, and the three-way valve 21 is operated as indicated by the dashed line in 1 shown so that the cooling water is circulated while it is on the steam generator 30 flows past.

Because of this, the refrigerant circulates in the order of the reversing lathe (compressor) 10 → of the steam generator 30 → of the radiator 11 → the gas / liquid separator 12 → of the decompressor 13 → of the evaporator 14 → reversing lathe (compressor) 10 , In this regard, since the engine cooling water is not in the steam generator 30 the refrigerant is not circulated through the steam generator 30 heated, and the steam generator 30 works alone as a refrigerant channel.

Accordingly, the low pressure refrigerant that passes through the decompressor 13 has been decompressed, heat from the in the vehicle compartment through the blower 14a blow-out air, and the vaporized gas-phase refrigerant is passed through the reverse rotary machine 10 compressed and the temperature of the refrigerant is increased. The high temperature refrigerant is due to the outside air in the radiator 11 cooled and condensed.

In this connection, in the present embodiment, the refrigerant is alternative Fleon (HFC-134a). However, if the refrigerant can be liquefied on the high pressure side, is the refrigerant is not restricted to HFC-134a.

2. Waste heat recovery mode

In this operating mode, the air conditioning, ie the reverse lathe 10 stopped, and waste heat of the engine 20 is recovered so that it can be used as useful energy.

In particular, the liquid pump becomes 32 operated under the condition that the opening and closing valve 35a is closed and that the control valve 36 is open, and the three-way valve 21 becomes like through the solid line in 1 operated, so that from the engine 20 escaping engine cooling water into the steam generator 30 is circulated.

Due to this, the refrigerant circulates in the order of the gas-liquid separator 12 → of the first bypass circuit 31 → of the steam generator 30 → reversing lathe (expansion machine) 10 → of the second bypass circuit 34 → of the radiator 11 → the gas / liquid separator 12 ,

Accordingly, flows through the steam generator 30 heated superheated steam in the reverse lathe 10 , While the vapor refrigerant entering the reverse lathe 10 has flowed in the reverse lathe 10 isentropically expanded, the enthalpy is reduced. That's why the reverse lathe gives 10 mechanical energy, which corresponds to a reduced enthalpy, to the motor generator 10a from. The through the motor generator 10a generated electrical energy is stored in a capacity or a battery.

That from the reversible lathe 10 escaping refrigerant is through the radiator 11 cooled and condensed and in the gas / liquid separator 12 saved. The liquid-phase refrigerant in the gas-liquid separator 12 is through the liquid pump 32 to the side of the steam generator 30 emotional.

As described above, the heat energy coming from the radiator 23 is lost in the atmosphere as waste heat, in the waste heat recovery mode of operation is converted into energy, such as electrical energy, which can be easily used. Therefore, the fuel consumption of the vehicle, ie the fuel consumption of the engine 20 be reduced.

Further, in the waste heat recovery operation mode, electric power is generated by the waste heat of the engine 20 generated. Therefore, it becomes unnecessary for a generator, such as an alternator, by the engine 20 drive. Accordingly, the fuel consumption of the engine 20 be further reduced.

Next is the by the electronic control unit 40 executed control is described as follows. In this embodiment, when an environmental command signal from the electronic control unit 41 for the air conditioning to the electronic control unit 40 is sent, the compressor integrated with the expansion machine 10 operated as a compressor, and the supply of engine cooling water to the steam generator 30 is stopped so that the priority is given to the climatic operation mode.

In contrast, even if no Klimabetriebsbefehlsignal from the electronic control unit 41 for the air conditioning to the electronic control unit 40 is sent and when the waste heat temperature T _{W is} not less than a predetermined temperature, the engine cooling water to the steam generator 30 fed, and the reverse lathe 10 is operated as an expansion engine, so that the waste heat recovery operation mode can be executed.

If no environmental operation command signal from the electronic control unit 41 for the air conditioning to the electronic control unit 40 is sent and when the waste heat temperature T _{W is} not greater than a predetermined temperature, under the condition that the supply of the engine cooling water to the steam generator 30 stopped, one of the reversible lathe 10 supplied electric power switched off, ie a motor generator 10a supplied electric power is turned off.

In this context is 3 an example of the flowchart of the above-described control operation. A draft of this flowchart will be explained as follows. Simultaneously with the input of the start signal for starting a vehicle, the in 3 presented control program started. First, it is judged whether the environmental operation command signal from the electronic control unit 41 for the air conditioning to the electronic control unit 40 has been sent or not (S1).

If the environmental operation command signal from the electronic control unit 41 for the air conditioning to the electronic control unit 40 has been sent, the Clausius-Rankine cycle is not operated, and the air conditioning operation mode is executed (S2).

In contrast, if no Klimabetriebsbefehlsignal from the electronic control unit 41 for the air conditioning to the electronic control unit 40 has been sent, it is judged according to the waste heat temperature T _W , whether the Rankine cycle Clausius is operated or not, that is, it is judged whether the waste heat recovery operation mode is executed or not (S3). When the waste heat temperature T _{W is} not less than the predetermined temperature, the result of the determination is determined to be 1, and the Rankine cycle is executed (S4). When the waste heat temperature T _{W is} lower than the predetermined temperature, the result of the determination is determined to be 0, and the Rankine cycle is not executed.

In this connection, in this embodiment, according to the following predetermined hysteresis control judgment, it is judged whether or not the Rankine cycle is being operated according to the waste heat temperature. When the waste heat temperature decreases, if the waste heat temperature is not lower than the predetermined temperature T _W1 , the judgment result of 1 is determined, and the Rankine cycle is executed. If the waste heat temperature T _{W is} lower than the predetermined temperature T _W1 , the judgment result is determined to be 0, and the Rankine cycle is not executed. When the waste heat temperature T _W increases, if the waste heat temperature T _{W is} not lower than the predetermined temperature T _W2 which is higher than the predetermined temperature T _W1 by a predetermined temperature, the judgment result is determined to be 1 and the Rankine cycle is running. If the waste heat temperature T _{W is} lower than the predetermined temperature T _{W 2} , the judgment result is determined to be 0, and the Rankine cycle is not executed. In this way, a predetermined hysteresis control judgment is executed.

Next, referring to FIG 4 the controller in which the electronic control unit 40 operates the Clausius-Rankine circle (S4), explained in more detail. First, the counter value is reset (S410). This counter value represents the number of refrigerant condensation operations (S470 to S500) which will be described later.

Next, the timer is reset (S420). This timer stores the elapsed time (in seconds) from the start of the waste heat recovery operation mode and the air conditioning operation mode. After that puts the electronic control unit 40 the liquid pump 32 and starts the waste heat recovery operation mode (S430). Thereafter, in S440 and S450, the waste heat recovery operation mode is operated until the predetermined time T ₁ (20 seconds in this embodiment) elapses.

After that, the electronic control unit judges 40 whether the pressure difference (P2 - P1) between the measuring pressure P1 of the upstream refrigerant pressure sensor 42 and the measuring pressure P2 of the downstream refrigerant pressure sensor 43 is higher than the set pressure P (0.3 MPa in this embodiment) or not (S460). If the pressure difference (P2-P1) is higher than the set pressure P (0.3 MPa in this embodiment), that is, if the liquid pump 32 When the liquid phase refrigerant is pressurized and the refrigerant is being delivered, the program goes to S5 3 ,

If the pressure difference (P2-P1) is lower than the set pressure P (0.3 MPa in this embodiment), it is judged that the liquid pump 32 on the liquid-phase refrigerant can not exert pressure. More specifically, it is judged that the gas-phase refrigerant in the liquid-phase refrigerant is mixed, so that the liquid pump 32 can not exert pressure on the refrigerant. Therefore, the refrigerant condensation process (S470 to S500) is performed.

In the refrigerant condensation process (S470 to S500), after stopping the waste heat recovery operation mode (S470), the air conditioning operation mode is started S480. Thereafter, in S490 and S500, the air conditioning operation mode is operated until the predetermined time T ₂ (10 seconds in this embodiment) elapses. Then, after the refrigerant condensation process (S470 to S500) has been executed, the counter value is set to (counter value + 1).

In S520 is judged whether the counter value higher than the standard value C (3 times in this embodiment) is or not. If the counter value is not greater than If the standard value is C, the program returns to S420. If the counter value higher than the normal value is C, it is judged that the Rankine cycle is in an abnormal state, and an operation of the system is stopped.

In this connection, in the refrigerant condensation process (S470 to S500), no air conditioning operation command signal is output. That's why the blower 14a not operated. Due to this, no conditioned air is blown into the passenger compartment. Therefore, the refrigerant condensation process can be carried out without being uncomfortable to the passenger.

• (1) Es ist möglich, ein Mischen von Blasen in das Flüssigphasenrohr 31 und die Flüssigkeitspumpe 32 zu verhindern. Deshalb kann das Auftreten eines solchen Problems, dass das Kältemittel durch die Flüssigkeitspumpe 32 nicht zugeführt werden kann, verhindert werden, und eine Verschlechterung der Betriebseffizienz des Kältemittels kann verhindert werden. Gemäß diesem Ausführungsbeispiel wird, falls der Clausius-Rankine-Kreis als in einem anormalen Zustand befindlich beurteilt wird, der Klimabetriebsmodus (Kühlkreis) betrieben, sodass das Gasphasen-Kältemittel zu dem Flüssigphasen-Kältemittel kondensiert werden kann. Ferner kann das in einem komplizierten Teil des Kältemittelkanals in dem Kühlkreis bleibende Kältemittel, zum Beispiel das in dem Verdampfapparat 14 bleibende Kältemittel, in der Gas/Flüssigkeit-Trennvorrichtung 12 in Form von flüssigem Kältemittel gespeichert werden. Danach ist es durch Betreiben des Abwärmewiedergewinnungsbetriebsmodus (des Clausius-Rankine-Kreises) möglich, ein Mischen von Blasen in das Flüssigphasenrohr 31 zu verhindern, was von dem herkömmlichen Beispiel verschieden ist. Demgemäß kann die Flüssigkeitspumpe 32 das Flüssigphasen-Kältemittel dem Dampfgenerator 30 positiv zuführen. Demgemäß kann der Abwärmewiedergewinnungsbetriebsmodus (der Clausius-Rankine-Kreis) normal gestartet und betrieben werden. Außerdem ist es möglich, die Verschlechterung der Betriebseffizienz der Flüssigkeitspumpe 32 zu verhindern, welche verursacht wird, wenn Blasen des Gasphasen-Kältemittels in das Flüssigphasenrohr 31 und die Flüssigkeitspumpe 32 gemischt werden. Das heißt, es ist möglich, das Auftreten des Problems zu verhindern, dass die Effizienz des Clausius-Rankine-Kreises verschlechtert ist.
• (2) Die Steuereinrichtung 40 beurteilt, ob der Abwärmewiedergewinnungsbetriebsmodus (der Clausius-Rankine-Kreis) normal oder anormal ist. Falls der Abwärmewiedergewinnungsbetriebsmodus (der Clausius-Rankine-Kreis) normal ist, wird der Abwärmewiedergewinnungsbetriebsmodus fortgesetzt. Falls der Abwärmewiedergewinnungsbetriebsmodus (der Clausius-Rankine-Kreis) anormal ist, wird der Klimabetriebsmodus betrieben. Demgemäß ist es möglich, eine unnötige Ausführung des Klimamodus zu verhindern.
• (3) Da der Differenzwert (P2 – P1) zwischen dem stromaufwärtigen Druckwert P1 und dem stromabwärtigen Druckwert P2 der Flüssigkeitspumpe 32 mit dem vorbestimmten Druckwert P verglichen wird, ist es möglich, speziell zu beurteilen, ob der Abwärmewiedergewinnungsbetriebsmodus normal oder anormal ist. In diesem Zusammenhang wird, wenn die Flüssigkeitspumpe 32 normal betrieben wird, der durch den stromaufwärtigen Kältemitteldrucksensor 42 erfasste Druckwert P1 niedriger als der durch den stromabwärtigen Kältemitteldrucksensor 43 erfasste Druckwert P2. Aufgrund dessen ist es möglich, zu beurteilen, dass ein Betrieb des Abwärmewiedergewinnungsbetriebsmodus anormal ist, falls der Differenzwert (P2 – P1) speziell nicht größer als der vorbestimmte Druckwert P ist.
• (4) Durch den Abwärmewiedergewinnungsbetriebsmodus ist es möglich, die Wärmeenergie, die üblicherweise von dem Kühler 23 in die Atmosphäre verloren geht, in Energie, wie beispielsweise elektrische Energie, die einfach in praktische Nutzung umgesetzt werden kann, umzusetzen. Deshalb ist es möglich, den Kraftstoffverbrauch des Fahrzeugs zu reduzieren, d.h. es ist möglich, den Kraftstoffverbrauch des Motors 20 zu reduzieren. Genauer ist es, da elektrische Energie durch die Abwärme des Motors 20 erzeugt wird, möglich, die Notwendigkeit zu reduzieren, den Generator, wie beispielsweise einen Drehstromgenerator, durch den Motor 20 anzutreiben. Demgemäß kann der Kraftstoffverbrauch des Motors 20 reduziert werden.

Next, the functional effects of the first embodiment will be enumerated as follows.

• (1) It is possible to mix bubbles into the liquid phase tube 31 and the liquid pump 32 to prevent. Therefore, the occurrence of such a problem that the refrigerant through the liquid pump 32 can not be fed, prevented, and a worsening tion of the operating efficiency of the refrigerant can be prevented. According to this embodiment, if the Rankine cycle is judged to be in an abnormal state, the air conditioning operation mode (refrigeration cycle) is operated, so that the gas-phase refrigerant can be condensed to the liquid-phase refrigerant. Further, the refrigerant remaining in a complicated part of the refrigerant passage in the refrigeration cycle, for example, in the evaporator 14 permanent refrigerant, in the gas / liquid separator 12 stored in the form of liquid refrigerant. Thereafter, by operating the waste heat recovery mode (the Rankine cycle), it is possible to mix bubbles into the liquid phase tube 31 to prevent what is different from the conventional example. Accordingly, the liquid pump can 32 the liquid phase refrigerant to the steam generator 30 positively. Accordingly, the waste heat recovery operation mode (the Rankine cycle) can be normally started and operated. In addition, it is possible to deteriorate the operating efficiency of the liquid pump 32 to prevent which is caused when bubbles of the gas-phase refrigerant in the liquid phase pipe 31 and the liquid pump 32 be mixed. That is, it is possible to prevent the occurrence of the problem that the efficiency of the Rankine cycle is deteriorated.
• (2) The controller 40 judges whether the waste heat recovery operation mode (the Clausius-Rankine cycle) is normal or abnormal. If the waste heat recovery operation mode (the Rankine cycle) is normal, the waste heat recovery operation mode is continued. If the waste heat recovery operation mode (the Rankine cycle) is abnormal, the air conditioning operation mode is operated. Accordingly, it is possible to prevent unnecessary execution of the climate mode.
• (3) Since the difference value (P2 - P1) between the upstream pressure value P1 and the downstream pressure value P2 of the liquid pump 32 is compared with the predetermined pressure value P, it is possible to specifically judge whether the waste heat recovery operation mode is normal or abnormal. In this connection, when the liquid pump 32 operated normally by the upstream refrigerant pressure sensor 42 detected pressure value P1 lower than that by the downstream refrigerant pressure sensor 43 detected pressure value P2. Due to this, it is possible to judge that an operation of the waste heat recovery operation mode is abnormal if the difference value (P2 - P1) is specifically not larger than the predetermined pressure value P.
• (4) By the waste heat recovery operation mode, it is possible to reduce the heat energy that is usually emitted from the radiator 23 is lost to the atmosphere, into energy, such as electrical energy, which can be easily converted into practical use implement. Therefore, it is possible to reduce the fuel consumption of the vehicle, that is, it is possible to reduce the fuel consumption of the engine 20 to reduce. Specifically, it is because electrical energy due to the heat of the engine 20 is possible to reduce the need for the generator, such as a three-phase generator, by the motor 20 drive. Accordingly, the fuel consumption of the engine 20 be reduced.

In this context, the pressure in the evaporator is at the time of the air conditioning mode, ie, the pressure at the check valve 33c on the evaporator side, which is about 0.3 MPa in this embodiment, lower than the pressure at the check valve 33c on the side facing away from the evaporator, which in this embodiment is about 1 MPa, in the case of recovery of energy by the compressor integrated in an expansion machine. The check valve 33c prevents backflow of the refrigerant to the evaporator by this pressure difference at the time of the waste heat recovery operation mode. However, at the time of the waste heat recovery operation mode, when the radiator and the evaporator communicate with each other, the pressure on the evaporator side, ie, the pressure in the evaporator, which is about 0.3 MPa in this embodiment, may be at the pressure of the check valve 33c on the side facing away from the evaporator, which is about 1 MPa in this embodiment, rise and malfunction of the check valve 33c may be caused and the energy recovery mode of operation (Clausius-Rankine cycle) may fail.

Therefore, this embodiment includes a temperature-type expansion valve in which the flow rate adjusting portion and the decompressing portion for decompressing the passing refrigerant are integrated with each other in a body. In this case, if the degree of superheating of the refrigerant at the outlet of the evaporator is low, the flow rate setting portion also sets the opening degree of the refrigerant passage to the full opening side if the degree of superheat of the refrigerant at the outlet of the evaporatingap is high. This temperature-type expansion valve functions as a refrigerant lock means for blocking a flow of the refrigerant into the evaporator at the time of recovering energy.

Due to this, when the compressor stops the suction of the refrigerant, the pressure at the outlet of the evaporator becomes the saturation pressure of the evaporator temperature in a very short period of time. Here, the expansion device 12 of the temperature type completely closes and shuts off the refrigerant passage, and therefore an increase in the pressure in the evaporator can be prevented if energy is recovered by the energy recovery machine. Therefore, the pressure in the evaporator does not increase even if the energy recovery operation is continuously performed, so that damage of the pipe can be prevented and malfunction of the backflow prevention device can be prevented.

Second Embodiment

The structure of this embodiment is the same as that of the first embodiment except that the upstream refrigerant pressure sensor 42 and the downstream refrigerant pressure sensor 43 that are provided in the first embodiment are omitted, and further except that a through the liquid pump 32 Consumed electricity through the electronic control unit 40 is measured (shown in 5 ). In the 3 The control shown is the same as that of the first embodiment.

Regarding the detail of S4 of 3 , in the 6 is shown, however, the following point is different. Whether the Clausius-Rankine cycle is normally operated or not, in this embodiment, by the power consumption of the liquid pump 32 assessed. That is, if the liquid pump 32 works normally and the liquid refrigerant to the steam generator 30 can be supplied, is the power consumption of the liquid pump 32 higher than the predetermined value increases. Therefore, if the liquid pump 32 consumes more electric power than the predetermined electric power consumption W (50 watts in this embodiment), judges it normal. In this context, the electrical energy consumption of the liquid pump 32 measured in this embodiment by a current sensor.

If on the other hand, the electrical energy is not more than the predetermined one electrical energy consumption is W, the program continues to S470. An afterwards to be executed Operation is the same as that of the first embodiment.

Because of this, it is without provision of the upstream refrigerant pressure sensor 42 and the downstream refrigerant pressure sensor 43 which are indispensable components for the first embodiment, it is possible to judge whether the waste heat recovery operation mode (the Rankine cycle) is normal or abnormal. Therefore, the cost of the entire heat circuit can be reduced.

In this connection can in this embodiment in the first embodiment described functional effects (1) to (4) are also shown.

(Third Embodiment)

The construction of this embodiment is the same as that of the first embodiment, but part of the control in S4 (shown in FIG 4 ) is different, as in 7 shown. The difference is explained in more detail as follows. After the electronic control unit 40 has started the air conditioning mode in S480, it is judged whether the counter value is 0 or not (S485). If the counter value is 0, the program proceeds to S495 and S505, and the air conditioning operation mode is operated until the time T3 elapses. This predetermined time T3 is shorter than the predetermined time T2. In this embodiment, the predetermined period of time T3 is 2 seconds. On the other hand, if the counter value is not 0, the air conditioning operation mode is continued until the time T2 elapses, which is 10 seconds as described above (S490, S500). Then the program continues to S510. An operation to be executed thereafter is the same as that of the first embodiment.

In this context, in a section of low pressure in the liquid pump 32 if the liquid refrigerant is in the gas / liquid separator 12 is a saturated liquid, although the liquid refrigerant in the gas / liquid separator 12 remains, causing a cavitation. In this case, when the air conditioning mode is started for a short period of time and pressure in the gas / liquid separator 12 is increased so as to change the liquid-phase refrigerant into a supercooled liquid, the generation of cavitation is reduced.

In this embodiment, when the counter value is 0, that is, after it has been judged that the waste heat recovery operation mode is in an abnormal state (S460 in FIG 4 ), the first time climate mode of operation shorter than the second time mode of air mode and thereafter. Because of this, without running egg In a useless climate mode of operation, the waste heat recovery mode of operation can be quickly put into normal operation.

In this connection can in the first embodiment described functional effects (1) to (4) also in this embodiment to be shown.

(Fourth Embodiment)

in the first, second and third embodiments is the time T2, in which the refrigerant condensation process accomplished is set to a predetermined period of time (10 seconds). In this embodiment However, the time T2 is corresponding to the operating state of the air conditioning mode changed. This is one of the first, second and third embodiments different point.

8th Fig. 10 is an overall construction diagram of a vapor compression refrigerator of this embodiment. The only different point of this arrangement of the in 1 illustrated arrangement is that the outside air temperature sensor 45 on the upstream side in the air flow direction of the condenser 11 is provided. The output values Tam of the outside air temperature sensor 45 gets into the electronic control unit 40 entered. In the electronic control unit 40 becomes the continuation time T21 for continuing the refrigerant condensation operation in accordance with the output value Tam of the outside air temperature sensor 45 certainly.

In this embodiment, it is determined so that T21 can be extended as the value of Tam becomes larger. When the outside air temperature is high, the condensation temperature is made high. Therefore, the temperature at which the liquid-phase refrigerant can be supercooled is also made high. However, the time for cooling the refrigerant is prolonged by the heat capacities of the other parts forming the heat circuit. Therefore, the relationship between the outside air temperature, which was previously measured, and the time at which the liquid-phase refrigerant can be supercooled, in the electronic control unit 40 stored and T21 is determined by the value of Tam.

The control sequence of the electronic control unit 40 This embodiment differs as follows. As in 9 is shown with respect to the first embodiment (shown in FIG 4 ) in step S415 Tam and T21 determined. In steps S490 and S501, the air conditioning operation mode is operated until the continuation time T21 elapses.

by virtue of of which it is possible to ensure the operating time of the air conditioning operating mode necessary is to the liquid-phase refrigerant in the supercooled state to put. Therefore, the operating time of the air conditioning operation mode in the unnecessary Refrigerant condensing operation be reduced. Furthermore, can in the first embodiment described functional effects (1) to (4) are shown.

(Fifth Embodiment)

In the first to fourth embodiments, the reverse rotary machine 10 and the liquid pump 32 built separately from each other. In the present invention, as shown in the overall arrangement diagram of 10 is shown, however, contains the reverse lathe 10 an expansion and compression section 100 , a generator and motor section 200 a liquid pump section 300 and a valve mechanism section 107 , etc., which are integrated with each other in a body. Accordingly, the liquid pump 32 and the control valve 36 not independently provided.

Further, this embodiment differs in the following points. At the reversible lathe 10 is a liquid pump portion housing temperature sensor 46 for measuring the temperature of the pump housing of the liquid pump section 300 attached, and the output value Twp of the liquid pump portion housing temperature sensor 46 gets into the electronic control unit 40 entered. The other points of the construction of this embodiment are the same as those of the fourth embodiment.

Next, referring to the sectional view of FIG 11 the reverse lathe 10 This embodiment explains. The reversible lathe 10 contains a compression and expansion section 100 for compressing and expanding the gas phase refrigerant; a generator and motor section 200 from which electrical energy is output when a rotational energy is input to it, and rotational energy is output when electrical energy is input thereto; and a liquid pump section 300 for supplying the liquid phase refrigerant to the compression and expansion section 100 with pressure when the waste heat recovery operation mode is operated.

The compression and expansion section 100 has the same structure as that of the well-known spiral-type compression mechanism. In particular, the compression and expansion section contains 100 a stationary spiral (Casing) 102 attached to the stator housing 230 of the generator and motor section 200 over the middle housing 101 is attached; a movable scroll forming a movable element 103 that in between the middle housing 101 and the stationary spiral 102 turned space is turned; and a valve mechanism section 107 for opening and closing the connection channel 105 . 106 to the working chamber V with the high pressure chamber 104 connect to.

In this case contains the stationary spiral 102 a plate-shaped base plate portion 102 and one of the base plate portion 102 to the side of the movable spiral 103 projecting spiral tooth section 102b , On the other hand, contains the movable spiral 103a one the tooth section 102b contacting and engaging in this spiral tooth section 103b and a base plate portion 103a in which the tooth section 103b is trained. When the movable spiral 103 is rotated under the condition that the two tooth sections 102b and 103b In contact with each other, the volume of the working chamber V1, which consists of two spirals 102 and 103 is formed, expanded and reduced.

The wave 108 is through the middle case 101 through the camp 108b rotatably supported and also by the stator housing 230 over the camp 108c rotatably held. An end portion in the longitudinal direction of the shaft 108 is a crankshaft with an eccentric section 108a which is eccentric with respect to the rotational center axis. The lip seal 108d is a shaft sealing device for preventing leakage of the refrigerant from the stator housing 230 from a gap between the shaft 108 and the stator housing 230 , The movable spiral 103 is about the camp 103c rotatably on the eccentric portion 108a appropriate.

The anti-rotation mechanism 109 is constructed so that the movable spiral 103 around the eccentric section 108a can rotate one turn while the shaft 108 is rotated by one turn. Therefore, when the wave 108 is rotated, the movable spiral 103 about the rotational center axis of the shaft 108 turned without rotation. Further, since the working chamber V1 becomes from the outer diameter side of the movable scroll 103 is moved to the center side, the volume of the working chamber V1 reduced. In this connection, in this embodiment, a rotation preventing mechanism 109 of the pin-ring (pin-hole) type.

The connection channel 105 provides a connection of the working chamber V1, whose volume is minimal at the time of the pump mode, with the high-pressure chamber 104 her, ie the connection channel 105 is an output port for discharging the compressed refrigerant. The connection channel 106 makes communication of the working chamber V1 whose volume becomes minimum at the time of the waste heat recovery operation mode with the high-pressure chamber 104 her, ie the connection channel 106 is an inflow port for passing the superheated steam (the gas phase refrigerant) of high temperature and high pressure from the high pressure chamber 104 into the working chamber V1.

The high pressure chamber 104 is a space in a gap between the valve mechanism housing 107i and that of the surface on which the tooth portion 102b of the base plate section 102 the movable spiral 102 is formed, the opposite surface is formed. The high pressure chamber 104 has a function of smoothing a pulsation of that of the connection channel 105 (hereinafter referred to as a dispensing opening 105 designated) discharged refrigerant. In this high pressure chamber 104 is the high pressure opening 110 with the side of the heater 30 and the radiator 11 is connected, provided.

The with the side of the evaporator 14 and the second bypass circuit 34 connected low-pressure opening 111 is in the stator housing 230 provided and communicates with the outermost diameter portion of the working chamber V1 via the interior 230 in the generator and motor section 200 and over the middle case 101 in connection.

Next, the valve mechanism section 107 explained in detail as follows. In the high pressure chamber 104 are on the side on which the tooth section 102b of the base plate section 102 the movable spiral 102 is formed, opposite side of the dispensing valve 107a and the valve stopper plate or the valve stopper 107b through the screws 107c attached. The dispensing valve 107a is a leaf-valve-shaped check valve for preventing the backflow of the refrigerant from the discharge port 105 has been issued from the high pressure chamber 104 into the working chamber V1. The stop 107b is a valve stopper plate for regulating the maximum opening degree of the discharge valve 107a ,

The sink 107d is a valve body for opening and closing the connection channel 106 (hereinafter referred to as an inflow port 106 designated). The electromagnetic valve 107e is a control valve for controlling a pressure in the back pressure chamber 107f by controlling the connection state of the low pressure port side 111 with the back pressure chamber 107f , The feather 107g is a spring means for giving a spring force to the spool 107d so that the inflow opening 106 can be closed. The throttle 107h is a resistance device for connecting the back pressure chamber 107f with the high pressure chamber 104 , where the throttle 107h has a certain channel resistance. In this context, the coil 107d , the electromagnetic valve 107e and the spring 107g in the valve mechanism housing 107i arranged, and the back pressure chamber 107f and the throttle 107h are with the valve mechanism housing 107i integrated in one body.

When the electromagnetic valve 107e is open, the pressure in the back pressure chamber 107f lower than the pressure in the high pressure chamber 107f reduced. That's why the coil is made 107d when through the spring 107g is compressed in the drawing shifted to the right, so that the inflow opening 106 can be opened. In this context, there is a pressure loss in the throttle 107h very large. That is why the amount of the high pressure chamber 104 in the back pressure chamber 107f flowing refrigerant negligible.

If, on the other hand, the electromagnetic valve 107e closed, the pressure in the back pressure chamber 107 and the pressure in the high pressure chamber 104 equal to each other. Accordingly, the coil becomes 107d through one through the spring 107g generated force in the drawing moved down. Therefore, the inflow opening 106 getting closed. Accordingly, an electric opening and closing valve of the servo type for opening and closing the inflow port 106 out of the coil 107d , the electromagnetic valve 107i , the back pressure chamber 107f , the feather 107g and the throttle 107h , etc. are built. In this context, the electromagnetic valve 107e through the electronic control unit 40 controlled.

The generator and motor section 200 is a brushless DC motor with a stator 210 and one on the inner peripheral side of the stator 210 rotating rotor 220 , The stator 210 is a stator winding in which a winding is wound around an iron core made of a magnetic material such as steel. This stator 210 is in the inner peripheral portion of the stator housing 230 attached.

The rotor 220 is a magnetic rotor in which a permanent magnet is embedded. On the inner peripheral side of the rotor 220 a not-shown keyway is formed, so that the rotor 220 integral with the shaft through this keyway 108 can be attached.

The liquid pump section 300 has the same construction as a well-known scroll-type compressor mechanism. In particular, the liquid pump section contains 300 one on the stator housing 230 of the generator and motor section 200 over the pump housing 301 fixed stationary spiral (housing) 302 ; a movable spiral 303 one in a room between the pump housing 301 and the stationary spiral 302 is formed, rotatable movable element is; and a working chamber V2, etc.

In this case contains the stationary spiral 302 a plate-shaped base plate portion 302a and a spiral tooth portion 302b that of the base plate section 302a to the side of the movable spiral 303 protrudes. On the other hand, contains the movable spiral 303 a spiral tooth section 303b that with the tooth section 302b is in contact and engages in this, and a base plate section 303a in which the tooth section 303b is trained. When the movable spiral 303 is rotated while both tooth sections 302b . 303b are in contact with each other, which is made up of two spirals 302 . 303 formed working chamber V2 from the side of the refrigerant suction port described later 309 to the side of the refrigerant discharge port 308 emotional.

In this connection, the compression ratio of the scroll compression mechanism of the liquid pump section is 300 1. Therefore, even when the liquid-phase refrigerant is drawn into the working chamber V2, the liquid-phase refrigerant is not compressed. Accordingly, compression of the liquid phase refrigerant does not malfunction the liquid pump portion 300 causes.

The pump shaft 304 is through the pump housing 301 over the camp 304b rotatably held. An end portion of the pump shaft 304 in the longitudinal direction is a crankshaft with an eccentric portion 304a which is eccentric with respect to the rotational center axis. The pump shaft 304 is about the one-way clutch 305 on the side on which the eccentric section 108a is provided, opposite side with an end portion of the shaft 108 which includes the compression and expansion section 100 and the generator and motor section 200 forming element is connected.

The one-way clutch 305 is a power transmission device having a function of transmitting a rotational driving force of the shaft 108 on the pump shaft 304 only in the waste heat recovery mode of operation. The movable spiral 303 is about the camp 303c with the eccentric section 304a rotatably connected.

Through the rotation prevention mechanism 306 . 307 becomes the movable spiral 303 , while the pump shaft 304 is rotated by one turn, one turn around the eccentric section 304a turned. That is why the movable spiral 303 when the pump shaft 304 is rotated without rotation about the rotational center axis of the pump shaft 304 turned. Further, the working chamber V2 is gradually shifted from the outer diameter side to the center side. In this connection, in this embodiment, the pin-ring-type mechanism (pin-hole type) is a rotation-preventing mechanism 306 . 307 used.

The refrigerant discharge opening 308 is an opening from which the liquid-phase refrigerant is discharged. The refrigerant discharge opening 308 is disposed at such a position that the refrigerant discharge port 308 can be in communication with the working chamber V2, when the working chamber V2 to the center side of the liquid pump section 200 is moved. The refrigerant suction port 309 is an opening from which the liquid-phase refrigerant is sucked. The refrigerant suction port 309 is disposed at such a position that the refrigerant suction port 309 can be in communication with the working chamber V2, when the working chamber V2 to the outer diameter side of the liquid pump section 200 is moved.

In this connection, the liquid pump portion housing temperature sensor is 46 on the pump housing 301 attached, and the output value Twp of the liquid pump portion housing temperature sensor 46 gets into the electronic control unit 40 entered.

When next Now the operation of the vapor compression chiller with a Rankine cycle of this embodiment.

In the air conditioning mode, the generator and motor section 200 the reversible lathe 10 supplied electrical energy, and by the electronic control unit 40 becomes the electromagnetic valve 107e closed and the three-way valve 21 switched as indicated by the dashed line in 10 shown.

If the generator and motor section 200 electrical energy is supplied to the rotor 220 and the wave 108 turned integrally with each other. Through this rotation, the reverse lathe sucks 10 the gas phase refrigerant from the low pressure port 111 , compresses the gas-phase refrigerant in the working chamber V1, and outputs the gas-phase refrigerant from the high-pressure port 110 out.

When the electromagnetic valve 107c is closed, the valve mechanism section works 107 as a check valve, the refrigerant only from the side of the reversible lathe 10 to the side of the steam generator 30 to flow. In the air conditioning mode transmits the one-way clutch 305 not the rotational drive force from the shaft 108 on the pump shaft 304 , Therefore, the liquid pump section becomes 300 not operated.

Due to this, in the air conditioning mode, the same refrigeration cycle as in the first embodiment can be constructed. Further, the low pressure gas phase refrigerant cools from the low pressure port 111 the compression and expansion section 100 is sucked when it is in the evaporator 14 is evaporated and the temperature of the gas-phase refrigerant is lowered, when the gas-phase refrigerant, the interior 230a happens, the liquid pump section 300 over the contact surface 230b the liquid pump section 300 of the stator housing 230 , Due to this, the liquid-phase refrigerant becomes in the liquid pumping section 300 supercooled. Accordingly, when the waste heat recovery operation mode is executed after the air conditioning operation mode, the liquid pumping section 300 the liquid phase refrigerant to the steam generator 30 pass positively.

Next, in the waste heat recovery operation mode, the electromagnetic valve becomes 107e opened and the three-way valve 21 is through the electronic control unit 40 switched as indicated by the solid line in

10 shown. In this case, the wave becomes 108 although the electronic control unit 40 the liquid pump section 300 does not drive, rotated when the refrigerant in the compression and expansion section 100 is extended. Accordingly, the rotational driving force generated at this time becomes over the one-way clutch 305 on the pump shaft 304 transfer. Therefore, the liquid pump section becomes 300 operated.

by virtue of this may be in the waste heat recovery mode the same Clausius Rankine circle as formed in the first embodiment become.

In this connection, in the waste heat recovery operation mode, the low-pressure gas-phase refrigerant coming out of the low-pressure opening becomes 111 the compression and expansion section 100 flows out, through the steam generator 30 overheated. Thus, the temperature of the gas-phase refrigerant is greatly increased. Therefore, the following problems may occur. Because the gas phase refrigerant high temperature also through the interior 230 flows, the liquid can pump section 300 by the gas-phase refrigerant of high temperature over the contact surface 230b are heated, and the liquid-phase refrigerant in the liquid pumping section 300 can be heated and evaporated.

In the waste heat recovery operation mode, however, the liquid pump section becomes 300 operated and the liquid-phase refrigerant does not remain in the liquid pump section 300 , which is different from the air conditioning mode, but flows through the interior of the liquid pump section 300 , Since the liquid-phase refrigerant to the steam generator 30 is sent before it evaporates, therefore, there is no possibility that the refrigerant in the liquid pump 300 evaporated.

Next, by the electronic control unit 40 executed control process described as follows. In this embodiment, the electronic control unit controls 40 in the same manner as in the first embodiment, the air conditioning operation mode and the waste heat recovery mode. In this embodiment, however, in the case of the operation of the Rankine cycle (S4), the control is different from that of the first embodiment.

In particular, the control is carried out as follows. As in 12 11, the outside air temperature Tam and the liquid pump portion housing temperature Twp are read in at step S416. Regarding the operation of the air conditioning operation mode for performing the refrigerant condensing operation as shown in step S502, the operation is continued until the following relationship is reached: (outside air temperature Tam + α) ≥ (β × liquid pump portion casing temperature Twp).

In this case, it is possible to take the refrigerant condensation temperature from the outside air temperature Tam. Since the liquid pump portion housing temperature Twp correlates with the refrigerant temperature in the liquid pumping section 300 has, it is possible, the refrigerant temperature in the liquid keitspumpenabschnitts 300 to grab. When the refrigerant temperature in the liquid pumping section 300 is lower than the refrigerant condensation temperature, it can further be judged that the refrigerant is in the liquid pumping section 300 in the supercooled state.

Therefore, in this embodiment, the refrigerant condensation temperature is set to (outside air temperature Tam + α), where α = 15 ° C in this embodiment, and the refrigerant condensation process is carried out until (β × liquid pump portion casing temperature Twp) is not higher than (outside air temperature Tam + α) decreases. In this case, β is a multiplier for control. Therefore, when the waste heat recovery mode is operated after completion of the refrigerant condensation operation, because the refrigerant in the liquid pump is in the supercooled state, the liquid pump portion 300 the liquid phase refrigerant positive to the steam generator 30 move.

Of course, the process can also be performed as follows. Even if the outside air temperature Tam is not measured, the minimum refrigerant condensation temperature (for example, 10 ° C.) is determined in advance from the minimum outside air temperature in the environment in which the heat circuit is used, and the refrigerant condensation process is performed until (β × liquid pumping section Housing temperature Twp) to a value not higher than the minimum refrigerant condensation temperature decreases. Due to this, it is possible to affect the outside air temperature sensor 45 to renounce. Accordingly, the manufacturing cost of the entire heat circuit can be reduced.

In this connection can also in this embodiment in the first embodiment described functional effects (1) to (4) are shown.

(Sixth Embodiment)

The above explanations are made for the fifth embodiment in which the liquid pump portion housing temperature sensor 46 for measuring the pump housing temperature of the liquid pump section 300 is provided. however, in this embodiment, instead of the liquid pump portion housing temperature sensor 46 , as in 13 shown, the evaporator blow-out temperature sensor 47 provided that measures the temperature of the air passing through the evaporator 14 is in heat exchange. The other points of the construction are the same as the fifth embodiment.

That of the evaporator exhaust temperature sensor 47 The output evaporator temperature Te is a temperature of the low-pressure gas-phase refrigerant in the air-conditioning mode and a temperature of the reverse-rotation machine 10 That is, that of the evaporator blow-off temperature sensor 47 output evaporator temperature Te is the same temperature as that of the gas phase refrigerant for cooling the liquid pump portion 300 , Therefore, the one of the evaporator blow-out temperature sensor has 47 output Evaporator blow-off temperature Te correlates to the temperature in the liquid pump section 300 , Accordingly, as shown in FIGS 14 As shown in steps S417 and S503, using the evaporator blow-out temperature Te instead of the liquid pump portion case temperature Twp, the same effects as those of the fifth embodiment can be obtained.

(Seventh Embodiment)

In the first to sixth embodiments, a reversing lathe 10 which functions as a compressor in a refrigeration cycle and also functions as an expansion engine in a Rankine cycle. In this embodiment, however, as in 15 shown, a reverse lathe 10 not used, but a compressor used exclusively for the cooling circuit 10b and an expansion machine used exclusively for the Rankine cycle 10c are used to build up the vapor compression type chiller.

The compressor 10b has a function of sucking, compressing and discharging the refrigerant. This compressor 10b is by the engine 20 via the motor-side pulley 49 , the belt 50 and the compressor-side pulley 51 through the electromagnetic clutch 48 , which by the electronic control unit 40 is driven, driven.

The construction of the expansion machine 10c is equal to that of the reversible lathe 10 of the fifth embodiment. In the expansion machine 10c are the expansion section 100 , the generator section 200 and the liquid pump section 300 integrated with each other in one body. However, there is no possibility that the expansion machine works as a compressor. That's why the wave 108 and the pump shaft 30 connected together in a body without using a one-way clutch or other devices.

When a driving force through the electronic control unit 40 is transferred to the compressor, the refrigerant is in the order of the compressor 10b → of the radiator 11 → the gas / liquid separator 12 → of the decompressor 13 → of the evaporator 14 → of the compressor 10b circulated. Due to this, the same cooling circuit as in the first embodiment can be constructed.

If the electronic control unit 40 the three-way valve 21 switches so that the engine coolant through the steam generator 30 can flow, the refrigerant, which flows through the steam generator 30 has been overheated in the expansion section 100 so that the generator section 200 and the liquid pump section 300 operate. Through the generator section 200 generated electrical energy is via the electronic control unit 40 stored in the battery. The liquid pump section 300 further moves the liquid-phase refrigerant to the steam generator 30 ,

That from the expansion section 100 effluent gas phase refrigerant is in the order of the expansion machine 10c → of the radiator 11 → the gas / liquid separator 12 → of the liquid pump section 300 → of the steam generator 30 → the expansion machine 10c circulated. Due to this, the same Rankine cycle can be constructed as in the first embodiment.

In this case, the high-pressure refrigerant discharge port of the compressor 10b and the low pressure discharge port of the expansion machine 10c connected to each other at the pipe confluence portion X. However, because the compressor 10b has a dispensing valve flows out of the expansion machine 10c low pressure refrigerant does not leak from the high pressure refrigerant discharge port of the compressor 10b back to the compressor 10b , Furthermore, this flows from the compressor 10b high-pressure refrigerant discharged from the low-pressure refrigerant outflow port of the expansion machine 10c back to the expansion machine 10c because the check valve 33b is provided.

The upstream refrigerant pressure sensor 42 , the downstream refrigerant pressure sensor 43 and the water temperature sensor 44 measure the same physical values as in the first embodiment, and the measured values become the electronic control unit 40 entered.

Accordingly, according to this embodiment, it is possible to carry out control in the same manner as in the first embodiment. Further, it is possible to carry out a control in which the refrigerating cycle and the Rankine cycle are independent of each other. That is, when the refrigerant condensation process is performed by the refrigeration cycle before the waste heat recovery operation mode is operated by a Rankine cycle, the same effects as in the first embodiment can be provided. When the refrigeration cycle is operated simultaneously when a Rankine cycle is being run, the refrigeration cycle in the gas / liquid separator may be used 12 a sufficiently large amount of the liquid-phase refrigerant can be stored. Therefore, bubbles of the gas-phase refrigerant do not leak into the liquid pump cut 300 , Accordingly, the liquid-phase refrigerant can be positive to the steam generator 30 sent.

(Further embodiment)

The Clausius-Rankine cycle type vapor compression refrigerating machine to which the present invention can be applied is not limited to the specific structure described in the above embodiments. The vapor compression refrigeration machine can also be used in 16 in which the evaporator is used as a condenser in a Rankine cycle and the liquid-phase refrigerant in the gas-liquid separator 52 downstream of the evaporator 14 the steam generator 30 through the liquid pump 32 is forwarded. Alternatively, as in 17 shown, the capacitor 53 in a Rankine cycle separate from the radiator 11 and the evaporator 14 , which are arranged in the cooling circuit, be arranged.

In the control executed in the third to seventh embodiments, the refrigerant pressure sensor becomes 42 . 43 of the first embodiment. Of course, the same effect can also be provided if the control performed according to the power consumption of the liquid pump of the second embodiment can be applied. The control of the third embodiment can be applied to the fourth to seventh embodiments.

The heat transfer rib temperature of the evaporator 14 or the pressure of the low-pressure opening 111 of the compressor can be considered physical values with a correlation to the refrigerant temperature in the liquid pump 32 and the liquid pumping section 300 used in the fifth or sixth embodiment.

In the embodiments described above The recovered energy is stored in a capacity. However, the recovered energy can also be considered as mechanical energy, such as a kinetic stored by a flywheel Energy or as a stored by a spring elastic energy get saved.

In the above embodiments, the reversing lathe becomes 10 used, that is, the rotary shifter type and spiral type fluid machine are used as a compressor and as an expansion machine. It should be noted, however, that the present invention is not limited to the above specific embodiment.

In the above embodiments a certain hysteresis is provided when the waste heat recovery mode is controlled. However, it should be noted that the present Invention is not limited to the above specific embodiments.

It It should be noted that the application of the present invention is not limited to one vehicle is.

Of the Heat generating body is not limited to an internal combustion engine, i. the heat generating body can be changed differently For example, the heat generating body may have a Be fuel cell (FC).

An opening and closing valve (For example, an electromagnetic valve for opening and closing, when it is energized) and a capillary tube can act as a refrigerant barrier device be arranged.

Due to this, since the electromagnetic valve positively blocks the refrigerant passage, the type of the decompression device is not limited to the temperature-type expansion valve, but an inexpensive capillary tube may be used. Further, it is possible to form a storage circuit in which a memory on the downstream side of the refrigerant flow of the evaporator 14 at the time of the air conditioning operation mode, instead of the downstream side of the refrigerant flow of the radiator 11 disposed at the time of the air-conditioning operation mode gas / liquid separation device (collecting vessel) is arranged to show the above functional effects.

in the above embodiment the heater is in series between the radiator and the one with an expansion engine integrated compressor arranged. It is possible, however, the Clausius Rankine circle to operate, even if the heater is in parallel between the radiator and the compressor integrated with an expansion machine is.

The waste heat generated by various devices on a vehicle, for For example, the suction heat generated by a turbine from an inverter generated heat and the accessories generated waste heat, Can be used as a heat source Heating the refrigerant be used. Only a heat source Can be used to cool the refrigerant to heat. Alternatively you can several heat sources be used to the refrigerant to heat.

The application of the present invention is not limited to an air conditioner for vehicle use. It is possible the present Invention apply to a stationary cooling circuit (chiller).

in the above embodiment the expansion valve of the temperature type is shown by way of example, in that a flow rate of the refrigerant accordingly the temperature of a temperature sensing cylinder and the temperature is set at the outlet of the evaporator. The expansion valve however, the temperature type is not limited to the above type. To the Example, it is possible to enter electronic expansion valve with a flow rate adjustment section in which a thermistor for the temperature detecting section is used and the opening degree a refrigerant channel adjusted by an actuator according to the detected temperature becomes.

Provided it with the concept of the invention, as it is within the scope of the patent described, agrees can be any embodiment be included in the present invention. It should be noted that the present invention is not limited to the above specific embodiments limited is.

Claims (32)

Heat circuit device, with a fluid lathe ( 10 . 10b . 10c ) for mutually converting between a fluid energy of a refrigerant and a mechanical rotational energy; a capacitor ( 11 ) for condensing the from the fluid lathe ( 10 . 10b . 10c ) supplied refrigerant; a Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) with a fluid pump ( 32 . 300 ) for moving the from the capacitor ( 11 ) supplied refrigerant, and also with a steam generator ( 30 ) for heating the refrigerant, which has been moved by the fluid pump, by the heat of a heat generating body ( 20 ); a refrigeration cycle system ( 10 . 11 . 13 . 14 ) with an evaporator ( 14 ) for vaporizing the of the capacitor ( 11 ) supplied refrigerant; and a control unit ( 40 ) for carrying out a refrigerant condensation process in which the refrigerant in the refrigeration cycle system ( 10 . 11 . 13 . 14 ) through the fluid lathe ( 10 . 10b . 10c ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) and the compressed refrigerant through the condenser ( 11 ) is condensed. Thermal circuit device according to claim 1, in which the control unit ( 40 ) comprises: judging means for judging whether the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) operates normally or not after the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) was started; and a control device for continuing the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) if it is judged that the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) operates normally, and to perform the refrigerant condensation process, if it is judged that the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) does not work normally. A heat circuit device according to claim 2, further comprising an upstream refrigerant pressure sensor (10). 42 ) for measuring a pressure of a refrigerant that is in an upstream portion of the refrigerant flow of the fluid pump ( 32 . 300 ) is arranged; and a downstream refrigerant pressure sensor ( 43 ) for measuring a pressure of the refrigerant that is in a downstream portion of the refrigerant flow of the fluid pump ( 32 . 300 ), wherein the judging means judges that the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) operates normally, if a difference (P2 - P1) between the detected pressure (P2) of the downstream refrigerant pressure sensor ( 43 ) and the detected pressure (P1) of the upstream refrigerant pressure sensor (FIG. 42 ) is greater than the predetermined pressure (P), and the judging means judges that the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) does not operate normally, if the difference (P2 - P1) between the detected pressure (P2) of the downstream refrigerant pressure sensor ( 43 ) and the detected pressure (P1) of the upstream refrigerant pressure sensor (FIG. 42 ) is not greater than the predetermined pressure (P). The thermal cycle device of claim 2, wherein the judging means judges that the Rankine Ranking circuit system ( 10 . 11 . 30 . 32 . 300 ) works normally, if an operating load of the liquid pump ( 32 . 300 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is greater than a certain operating load, and the evaluator judges that the Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) does not work normally if the operating load of the liquid pump ( 32 . 300 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is not greater than the specified operating load. A heat circuit device according to claim 4, wherein the liquid pump is an electric liquid pump ( 32 ) and the operating load by a power consumption by the electric fluid pump ( 32 ) is shown. Heat-circulating device according to one of claims 1 to 5, further comprising an air-blowing device ( 14a ) for blowing air, the temperature of which through the refrigeration cycle system ( 10 . 11 . 13 . 14 ), the control unit ( 40 ) carries out the refrigerant condensation process under the condition that the air blowing device ( 14a ) is not operated. Thermal circuit device according to one of claims 1 to 6, further comprising a sensor ( 46 . 47 ) for measuring a physical value having a correlation with the temperature of the refrigerant in the liquid pump ( 32 . 300 ), the control unit ( 40 ) determines the time which elapses from the start of the refrigerant condensation process to when the time passed by the sensor ( 46 . 47 ) measured physical value shows that the refrigerant in the refrigerant pump ( 32 ) in the supercooled state has elapsed to be the continuation time for continuing the refrigerant condensation process. Thermal circuit device according to one of claims 1 to 6, wherein the capacitor ( 11 ) is a heat exchanger for condensing the refrigerant by heat exchange between the outside air and the refrigerant, the heat cycle device further comprising: an outside air temperature sensor ( 45 ) for measuring the temperature of the outside air; and a sensor ( 46 . 47 ) for measuring a physical value having a correlation with the temperature of the refrigerant in the liquid pump ( 32 . 300 ), whereby a control unit ( 40 ) according to the by the outside air temperature sensor ( 45 ) measured outside air temperature, a target temperature at which the refrigerant in the refrigerant pump ( 32 ) is in the supercooled state, and also the control unit ( 40 ) determines the time which elapses from the start of the refrigerant condensation process to when the time passed by the sensor ( 46 . 47 ) measured physical value to the target temperature has elapsed to be the continuation time to continue the refrigerant condensation process. Thermal circuit device according to claim 7 or 8, wherein the sensor is a temperature sensor ( 46 ) for measuring the temperature of the housing of the refrigerant pump. Thermal circuit device according to claim 7 or 8, wherein the sensor is a temperature sensor ( 47 ) for measuring the temperature immediately after a heat exchange with the refrigerant in the evaporator ( 14 ). Thermal circuit device according to one of claims 1 to 6, wherein the capacitor ( 11 ) is a heat exchanger for condensing the refrigerant by heat exchange between the outside air and the refrigerant, further comprising an outside air temperature sensor ( 45 ) for measuring the outside air temperature, the control unit ( 40 ) Continuation time setting means for determining the continuation time (T21) in which the refrigerant condensing operation is continued, in accordance with the flow rate by the outside air temperature sensor (FIG. 45 ) measured temperature. Thermal cycle device according to one of claims 1 to 11, wherein the fluid lathe is a reversible lathe ( 10 ) which can be operated reversibly as an expansion machine for obtaining energy when the refrigerant is expanded or as a compressor for compressing the refrigerant when power is supplied to the compressor. Thermal circuit device according to claim 12, in which the control unit ( 40 ) performs the refrigerant condensation operation by operating the fluid rotating machine as a compressor before the fluid rotating machine is operated as an expansion machine and the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is started. Thermal circuit device according to claim 12 or 13, wherein the reversible lathe ( 10 ) is formed so that it communicates with the fluid pump ( 32 . 300 ) is integrated in a body, and the fluid pump ( 32 . 300 ) is arranged so that by the in the reversing lathe ( 10 ) sucked gas phase refrigerant at the time of operation of the refrigeration cycle system ( 10 . 11 . 13 . 14 ) can be cooled. A thermal cycle device according to any one of claims 1 to 11, wherein the fluid lathe is an expansion machine ( 10c ) for expanding the refrigerant to obtain energy and a compressor ( 10b ) for compressing the refrigerant when the compressor is supplied with energy. Thermal circuit device according to claim 15, in which the control unit ( 40 ) the refrigerant condensation process by operating the compressor ( 10b ) before the expansion machine ( 10c ) and the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is started. Thermal circuit device according to claim 15, in which the control unit ( 40 ) the refrigerant condensation process by operating the compressor ( 10b ) at the same time, when the expansion machine 110c ) and the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is started. Thermal circuit device with a Rankine Ranking system ( 10 . 11 . 30 . 32 . 300 ) with a fluid pump ( 32 . 300 ) for moving a refrigerant and also with a steam generator ( 30 ) for heating the refrigerant, which has been moved by the fluid pump, by the heat of a heat generating body ( 20 ); a refrigeration cycle system ( 10 . 11 . 13 . 14 ) with an evaporator ( 14 ) for vaporizing the refrigerant; and a control unit ( 40 ) for carrying out the cooling operation for cooling the fluid pump by operating the refrigeration cycle system ( 10 . 11 . 13 . 14 ) at the time of operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ). The heat circuit device according to claim 18, wherein the refrigeration cycle system comprises a compressor ( 10 . 10b ) and the fluid pump ( 32 . 300 ) is arranged so that through the in the compressor ( 10 . 10b ) sucked gas-phase refrigerant can be cooled. Thermal circuit device according to claim 18 or 19, wherein the control unit ( 40 ) performs the cooling operation before the operation of the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) and / or during the Rankine cycle system ( 10 . 11 . 30 . 32 . 300 ) is operated. Heat circuit, with a cooling circuit ( 10 . 11 . 13 . 14 ) in which a low-pressure refrigerant is evaporated so as to absorb heat from a low-temperature side, and the evaporated gas-phase refrigerant is compressed so as to raise the temperature, and the heat absorbed from the low-temperature side is radiated to a high-temperature side, so condensing the gas phase refrigerant into the liquid phase refrigerant; a Rankine Ranking Circle ( 10 . 11 . 30 . 32 ) with a steam generator ( 30 ) for generating the gas-phase refrigerant by heating the liquid-phase refrigerant of the refrigeration cycle ( 10 . 11 . 13 . 14 ) by the waste heat of a heat generating body ( 20 ), also with a liquid phase tube ( 31 ) for connecting a liquid phase extraction section ( 12 . 52 ) for removing the liquid-phase refrigerant from the refrigeration cycle ( 10 . 11 . 13 . 14 ) with the steam generator ( 30 ), also with one in the liquid phase tube ( 31 ) arranged liquid pump ( 32 . 300 ) for moving the liquid phase refrigerant to the steam generator ( 30 ), also with an expansion machine ( 10 ) for obtaining energy by expanding the gas-phase refrigerant, and also with a condenser ( 11 ) for condensing the gas phase refrigerant, which by the expansion machine ( 10 ) has been extended; a control device ( 40 ) for controlling an operating state of the cooling circuit ( 10 . 11 . 13 . 14 ) and also for controlling an operating state of the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ); and a switching device ( 35a . 36 ) for switching between a case in which the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) and a case where the refrigeration cycle ( 10 . 11 . 13 . 14 ) by one of the control device ( 40 ), the control device ( 40 ) the Clausius-Rankine-Kreis ( 10 . 11 . 30 . 32 . 300 ) operates in such a way that the cooling circuit ( 10 . 11 . 13 . 14 ) is operated by the refrigerant condensing operation so as to condense the gas-phase refrigerant into the liquid-phase refrigerant, and then the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) is operated. Heat circuit, with a cooling circuit ( 10 . 11 . 13 . 14 ) in which a low-pressure refrigerant is evaporated so as to absorb heat from a low-temperature side, and the vaporized gas-phase refrigerant is compressed so as to raise the temperature, and the heat absorbed from the low-temperature side is radiated to a high-temperature side, so condensing the gas phase refrigerant into the liquid phase refrigerant; a Rankine Ranking Circle ( 10 . 11 . 30 . 32 . 300 ) with a steam generator ( 30 ) for generating the gas-phase refrigerant by heating the liquid-phase refrigerant of the refrigeration cycle ( 10 . 11 . 13 . 14 ) by the waste heat of a heat generating body ( 20 ), also with a liquid phase tube ( 31 ) for connecting a liquid phase extraction section ( 12 . 52 ) for moving the liquid-phase refrigerant from the refrigeration cycle ( 10 . 11 . 13 . 14 ) with the steam generator ( 30 ), also with one in the liquid phase tube ( 31 ) arranged liquid pump ( 32 . 300 ) for moving the liquid phase refrigerant to the steam generator ( 30 ), also with an expansion machine ( 10 ) for obtaining energy by expanding the gas-phase refrigerant, and also with a condenser ( 11 ) for condensing the gas phase refrigerant, which by the expansion machine ( 10 ) has been extended; a control device ( 40 ) for controlling an operating state of the cooling circuit ( 10 . 11 . 13 . 14 ) and also for controlling an operating state of the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ); and a switching device ( 35a . 36 ) for switching between the case where the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) and the case where the refrigeration cycle ( 10 . 11 . 13 . 14 ) by one of the control device ( 40 ), after which the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ), the control device ( 40 ) judges whether the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) works normally or not if an operation of the Clausius-Rankine-Kreis ( 10 . 11 . 30 . 32 . 300 ) has been judged normal, the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) and if an operation of the Clausius-Rankine 10 . 11 . 30 . 32 . 300 ) has been judged abnormal, the control device ( 40 ) works in such a way that it controls the operation of the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) stops and the cooling circuit ( 10 . 11 . 13 . 14 ), so as to carry out the refrigerant condensation process for recovering the liquid phase refrigerant, and the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) is operated again after the refrigerant condensation process. The heat circuit according to claim 22, further comprising an upstream refrigerant pressure sensor ( 42 ) in a section on the upstream side of the refrigerant flow of the liquid pump ( 32 . 300 ) is arranged, wherein the upstream refrigerant pressure sensor ( 42 ) a signal of the refrigerant pressure to the control device ( 40 ) outputs; and a downstream refrigerant pressure sensor ( 43 ) in a section on the downstream side of the refrigerant flow of the liquid pump ( 32 . 300 ) is arranged, wherein the downstream refrigerant pressure sensor ( 43 ) a signal of the refrigerant pressure to the control device ( 40 ), wherein if a value (P2 - P1) obtained when a detected pressure value (P1) of the upstream refrigerant pressure sensor ( 42 ) from a detected pressure value (P2) of the downstream refrigerant pressure sensor (FIG. 43 ) is higher than a predetermined pressure value (P) when the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ), the control device ( 40 ) judges that the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) is normal, and if the value (P2 - P1) obtained when the detected pressure value (P1) of the upstream refrigerant pressure sensor ( 42 ) from a detected pressure value (P2) of the downstream refrigerant pressure sensor (FIG. 43 ), is not greater than the determined pressure value (P), the control device ( 40 ) judges that the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) does not work normally. Heat circuit according to claim 22, in which the control device ( 40 ) judges that the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) works normally, if an operating load of the liquid pump ( 32 . 300 ) is not greater than a certain operating load when the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) and the control device ( 40 ) judges that the Clausius-Rankine circle ( 10 . 11 . 30 . 32 . 300 ) does not work normally if the operating load of the liquid pump ( 32 . 300 ) is not greater than the specified operating load when the Rankine cycle ( 10 . 11 . 30 . 32 . 300 ) is operated. The heat circuit according to claim 24, wherein the liquid pump is an electricity driven electric liquid pump ( 32 ), and the operating load by a power consumption by the electrically driven liquid pump ( 32 ) is shown. Heat circuit according to one of claims 21 to 25, in which the expansion machine comprises a reversible lathe ( 10 ) having the function of a compressor for compressing the gas-phase refrigerant into the refrigeration cycle ( 10 . 11 . 13 . 14 ), the reverse lathe ( 10 ) with the liquid pump ( 32 . 300 ) and the liquid pump ( 32 . 300 ) by the in the reversing lathe ( 10 ) sucked gas phase refrigerant at the time of operation of the cooling circuit ( 10 . 11 . 13 . 14 ) is cooled. Heat circuit according to one of claims 21 to 26, further comprising an air blowing device ( 14a ) for blowing conditioned air through the cooling circuit ( 10 . 11 . 13 . 14 ); and an operation command device ( 41 ) for commanding the operation of the refrigeration cycle, the control device ( 40 ) in the case of performing the refrigerant condensing operation, the refrigerant condensing operation without operating the air blowing device (FIG. 14a ) when the operation of the refrigeration cycle ( 10 . 11 . 13 . 14 ) not by the operating command facility ( 41 ) is ordered. Heat circuit according to one of Claims 21 to 27, in which the capacitor ( 11 ) is a heat exchanger for condensing the gas phase refrigerant by heat exchange between the outside air and the refrigerant, the heat circuit further includes an outside air temperature sensor ( 45 ) for measuring the temperature of the outside air, the control device ( 40 ) determines a continuation time (T21) to continue the refrigerant condensing operation, and the continuation time (T21) is determined based on the outside air temperature. Thermal circuit according to one of claims 21 to 27, further comprising a sensor ( 46 . 47 ) for measuring a physical value with a correlation to a temperature of the refrigerant in the liquid pump ( 32 . 300 ), wherein the control device ( 40 ), a continuation time in which the refrigerant condensing operation is continued, and the continuation time determines the time from the start of the refrigerant condensing operation to when the time passed by the sensor (FIG. 46 . 47 ) measured physical value to the temperature at which the refrigerant in the refrigerant pump ( 32 ) is undercooled is. Heat circuit according to one of Claims 21 to 27, in which the capacitor ( 11 ) is a heat exchanger for condensing the gas phase refrigerant by a heat exchange between the outside air and the refrigerant, the heat circuit further comprises an outside air temperature sensor ( 45 ) for measuring the temperature of the outside air and also a sensor ( 46 . 47 ) for measuring a physical value correlated to the temperature of the refrigerant in the liquid pump ( 32 . 300 ), the control device ( 40 ) determines by the outside air temperature, the temperature at which the refrigerant in the refrigerant pump ( 32 ), and also the continuation time in which the refrigerant condensation process is continued is determined, and the continuation time is the time from the start of the refrigerant condensation process to when the time passed by the sensor (FIG. 46 . 47 ) is the physical value measured at the temperature at which the refrigerant in the refrigerant pump ( 32 ) is undercooled is. A thermal circuit according to claim 29 or 30, wherein the sensor for measuring the physical value is a temperature sensor ( 46 ) for measuring the temperature of the housing of the refrigerant pump. Heat circuit according to claim 29 or 30, wherein the cooling circuit ( 10 . 11 . 13 . 14 ) an evaporator ( 14 ) for evaporating the low-pressure refrigerant by heat exchange between the low-pressure refrigerant and air, and the physical-value sensor includes a temperature sensor ( 47 ) for measuring the air temperature immediately after the heat exchange with the low pressure refrigerant.