JP2012202369A - Heat pump integrated with evaporator and rankine cycle system - Google Patents

Abstract

An evaporator-integrated heat pump and Rankine cycle device capable of eliminating a cold heat source and reducing power consumption are provided.
The evaporator-integrated heat pump 4 evaporates by opening an evaporation chamber 40, a heat input element 43, a gas discharge port 45, a liquid suction port 107, a gas discharge port 45, and a gas discharge port 45. The gaseous fluid in the chamber 40 is discharged to an external gas receiving portion to lower the pressure of the evaporation chamber 40, and the liquid fluid is supplied to the evaporation chamber 40 whose pressure has been reduced by opening the gas discharge valve 46. A liquid suction valve 47 for sucking the evaporation chamber 40 through the suction port 107 and a gas discharge valve 48 for discharging the fluid in the evaporation chamber 41 to the gas receiving portion are provided.
[Selection] Figure 1

Description

  The present invention relates to an evaporator-integrated heat pump and a Rankine cycle device.

  In Patent Document 1, a heat pump composed of an expansion tank, a check valve a1 for suction, a pressure regulating valve a2 on the discharge side, and a pressure equalizing valve s for the expansion tank and the condenser is used for the condenser and collector of the Rankine cycle. An apparatus constructed in between is disclosed. Here, the expansion tank and the condenser are pressure-equalized by opening the pressure equalizing valve s, and further, the inside of the expansion tank is depressurized by flowing cold water through the piping c of the expansion tank, and the liquid is allowed to flow from the check valve a1. . By flowing warm water through the piping H of the expansion tank, the liquid evaporates and the tank internal pressure increases. When the tank internal pressure exceeds the set value of the pressure regulating valve a2, the pressure regulating valve a2 on the discharge side is opened and the liquid is discharged to the heat collector.

  Patent Document 2 discloses a Rankine cycle apparatus characterized by utilizing the capillary force in the evaporator for the Rankine cycle pump function. A Rankine cycle device that utilizes capillary force includes an expander, a condenser, and an evaporator, and the evaporator has a function of evaporating the fluid and simultaneously imparting a circulation driving force to the fluid. Further, the evaporator includes a capillary structure for driving the liquid-phase working fluid by capillary force on the entire cross-section of the flow path of the working fluid, and a heating unit for evaporating the working fluid in the capillary structure. Has been.

Japanese Patent Application No. 2006-535145 JP 2009-150251 A

  In patent document 1, in order to drive a heat pump, both a heat source and a cold heat source are required. In particular, the cold heat source requires energy for producing cold heat, which causes a reduction in the overall efficiency of the apparatus. In Patent Document 2, since the pressure at which the liquid is sent out by the capillary force depends on the surface tension of the fluid in the capillary part and the flow path radius, it is necessary to reduce the flow path radius of the capillary trunk part when obtaining high pressure. is there. For example, in order to obtain a pressure increase of 500 kPa with the refrigerant R134a, a very small flow path diameter of 0.1 μm or less is required. In this case, it is difficult to select a capillary structure that forms the capillary. Furthermore, there is a high possibility that problems such as blockage of the flow path will occur due to impurities or lubricating oil.

  This invention is made | formed in view of the above-mentioned actual condition, and makes it a subject to provide the evaporator integrated heat pump and Rankine cycle apparatus which can abolish a cold heat source and can reduce power consumption.

(1) The evaporator integrated heat pump according to the present invention of aspect 1 is
(I) an evaporation chamber that contains a fluid capable of phase change from a liquid phase to a gas phase, a heat input element that evaporates a liquid fluid in the evaporation chamber in accordance with external heat input, and promotes gasification, and an evaporation chamber The gas discharge port for discharging the gaseous fluid to the low pressure source, the liquid suction port for sucking the liquid fluid from the external liquid fluid supply source to the evaporation chamber, and the evaporation increased in pressure by the heat input to the heat input element An evaporation pump unit comprising a gas discharge port for supplying a gaseous fluid in the evaporation chamber to an external gas receiving unit based on the pressure of the chamber;
(Ii) a gas release valve that is provided to open and close the gas discharge port of the evaporation pump unit and releases the gaseous fluid in the evaporation chamber to a low-pressure source by opening the gas discharge port, thereby reducing the pressure of the evaporation chamber;
(Iii) a liquid suction valve for sucking liquid fluid from an external liquid fluid supply source into the evaporation chamber through the liquid suction port into the evaporation chamber whose pressure has been reduced by opening the gas release valve;
(Iv) a gas discharge valve that supplies the fluid in the evaporation chamber to an external gas receiving section by opening.

  According to this aspect, when the gas discharge valve is opened, the gas discharge port is opened, and the gaseous fluid in the evaporation chamber is discharged to the low-pressure source outside the evaporator-integrated heat pump. The pressure is reduced compared to before opening the valve. Since the evaporation chamber is reduced in pressure by opening the gas release valve in this way, when the liquid intake valve is opened, external heat (for example, waste heat from the engine or fuel cell, solar heat, geothermal heat, etc.) is liquid from the liquid fluid supply source. This fluid is sucked into the evaporation chamber through the liquid suction port. At this time, since heat is input to the evaporation chamber from the outside through the heat input element, the liquid fluid in the evaporation chamber is heated to evaporate. Since the pressure in the evaporation chamber increases due to the progress of evaporation, the gas discharge valve is opened, and the evaporated high-pressure gaseous fluid is supplied from the gas discharge valve and the gas discharge port to the external gas receiving unit. In the present specification, the low pressure source means a portion having a lower pressure than the liquid suction port of the evaporation chamber.

  (2) According to the evaporator-integrated heat pump according to the present invention of aspect 2, in the above aspect, the evaporation pump unit forms a passage-like evaporation chamber that accommodates a fluid capable of phase change from the liquid phase to the gas phase. The heat input element is formed of heat exchange fins provided on the outer wall of the evaporation pipe. When heat is input to the heat exchange fins, the liquid fluid in the evaporation pipe is heated and evaporated. Accordingly, the pressure in the evaporation chamber is increased, and the gaseous fluid in the evaporation chamber is supplied to the external gas receiving portion.

  (3) According to the evaporator-integrated heat pump according to the present invention of aspect 3, in the above aspect, the evaporation pump unit forms a passage-shaped evaporation chamber that accommodates a fluid capable of phase change from the liquid phase to the gas phase. The heat input element has a heat exchange container that forms a heat exchange chamber that covers the plurality of evaporation pipes. When a heat exchange fluid heated by external heat (for example, waste heat of an engine or fuel cell, solar heat, geothermal heat, etc.) is supplied to the heat exchange chamber, the liquid fluid in the evaporation pipe is heated and evaporated. Accordingly, the pressure in the evaporation chamber is increased, and the high-pressure gaseous fluid in the evaporation chamber is supplied to the external gas receiver.

(4) A Rankine cycle device according to the present invention of aspect 4 includes an expander having a first suction port and a first discharge port, and condensation that advances condensation of gaseous refrigerant returned from the first discharge port of the expander. In the Rankine cycle device having an evaporator and an evaporator that evaporates the refrigerant that has been condensed in the condenser, the evaporator is composed of an evaporator-integrated heat pump,
The evaporator-integrated heat pump
(I) an evaporation chamber that contains a fluid capable of phase change from a liquid phase to a gas phase, a heat input element that evaporates a liquid fluid in the evaporation chamber in accordance with external heat input, and promotes gasification, and an evaporation chamber The gas discharge port for discharging the gaseous fluid toward the external low pressure source, the liquid intake port for sucking the liquid fluid from the external liquid fluid supply source into the evaporation chamber, and the high pressure by heat input to the heat input element An evaporation pump unit including a gas discharge port for supplying a gaseous fluid in the evaporation chamber to an external gas receiving unit based on the pressure of the converted evaporation chamber;
(Ii) a gas release valve provided to open and close the gas discharge port of the evaporation pump unit and to release the gaseous fluid in the evaporator chamber to a low-pressure source by opening the gas discharge port, thereby reducing the pressure of the evaporation chamber;
(Iii) a liquid suction valve for sucking liquid fluid from an external liquid fluid supply source into the evaporation chamber through the liquid suction port into the evaporation chamber whose pressure has been reduced by opening the gas release valve;
(Iv) a gas discharge valve that supplies the fluid in the evaporation chamber to an external gas receiving section by opening.

  According to this aspect, when the gas discharge valve is opened, the gas discharge port is opened, and the gaseous fluid in the evaporation chamber is discharged to an external low-pressure source. The pressure is reduced. Since the evaporation chamber is reduced in pressure by opening the gas release valve in this way, when the liquid suction valve is opened, the liquid fluid from the external liquid fluid supply source enters the evaporation chamber via the liquid suction valve and the liquid suction port. Inhaled. At this time, since heat is input to the evaporation chamber from the outside through the heat input element, the liquid fluid in the evaporation chamber is heated to evaporate. Since the pressure in the evaporation chamber increases as the evaporation proceeds, the gas discharge valve is opened, and the gaseous fluid evaporated in the evaporation chamber is supplied from the gas discharge valve and the gas discharge port to the external gas receiving unit.

(5) According to the Rankine cycle device according to the present invention of aspect 5, in the above aspect, the expander is compressed by the expansion action of the expansion chamber in addition to the first intake port and the first discharge port for Rankine cycle. An expansion compressor having a second suction port and a second discharge port for a vapor compression cycle communicated with the compression chamber.
An expansion element that is connected to the outlet side of the condenser and expands the liquid refrigerant condensed in the condenser, and the refrigerant that is connected to the expansion element and expanded by the expansion element is evaporated and the evaporated gaseous refrigerant is expanded and compressed. A vapor compression heat pump device including a heat pump evaporator that is sucked into a second suction port of the machine is integrally provided.

  ADVANTAGE OF THE INVENTION According to this invention, the evaporator integrated heat pump with which the evaporator and the heat drive type pump were integrated can be provided. In this case, external heat such as waste heat from the engine and fuel cell, solar heat, geothermal heat, etc. is used as the drive source for the evaporator-integrated heat pump. Since external heat such as waste heat, solar heat, and geothermal heat is used, power consumption can be reduced.

  According to the present invention, when the gas discharge valve is opened, the gas discharge port is opened, and the gaseous fluid in the evaporation chamber is discharged to the low-pressure source outside the evaporator-integrated heat pump. The pressure is reduced compared to before opening the valve. Since the evaporation chamber is reduced in pressure by opening the gas release valve in this way, when the liquid suction valve is opened, the liquid fluid is sucked into the evaporation chamber from the external liquid fluid supply source through the liquid suction port. At this time, since external heat is input into the evaporation chamber via the heat input element, the liquid fluid in the evaporation chamber is heated and evaporation proceeds. Since the pressure in the evaporation chamber increases due to the progress of evaporation, the gas discharge valve is opened, and the evaporated gaseous fluid is supplied from the gas discharge valve and the gas discharge port to the external gas receiving unit.

1 is a circuit diagram showing a Rankine cycle device according to Embodiment 1. FIG. It is a figure explaining the action | operation of an evaporator integrated heat pump. It is a side view which concerns on Embodiment 2 and shows an evaporator integrated heat pump typically. FIG. 6 is a side view schematically showing an evaporator-integrated heat pump according to a third embodiment. It is a side view which concerns on Embodiment 4 and shows an evaporator integrated heat pump typically. (A) (B) is a side view which shows typically an evaporator integrated heat pump concerning Embodiment 5. FIG. It is a circuit diagram which shows the Rankine cycle apparatus which concerns on Embodiment 6 and incorporated the vapor compression heat pump apparatus. (A) is a circuit diagram showing a Rankine cycle device incorporating a vapor compression heat pump device according to Embodiment 7, and (B) and (C) are diagrams each schematically showing the structure of a liquid storage tank. It is a circuit diagram which shows the Rankine-cycle apparatus which concerns on Embodiment 8 and integrated the vapor compression heat pump apparatus. It is a ph diagram which shows the state of a refrigerant. It is a figure which concerns on Embodiment 8 and shows the Rankine cycle apparatus incorporating the vapor compression heat pump apparatus. It is a circuit diagram which shows the Rankine cycle apparatus which concerns on Embodiment 9 and incorporated the vapor compression heat pump apparatus. It is a circuit diagram which shows the Rankine cycle apparatus which concerns on Embodiment 10 and incorporating the vapor compression heat pump apparatus.

  According to the present invention, when the gas release valve is opened, the low pressure source to which the gas released from the evaporation chamber is supplied means a portion having a lower pressure than the liquid suction port of the evaporation chamber. When a condenser or a reservoir tank is provided, examples of the low pressure source include a portion having a pressure level lower than the pressure of the condenser or the reservoir tank. When the vapor compression cycle is provided, the low pressure source is exemplified by a low pressure circuit in the vapor compression cycle (for example, a passage downstream from the outlet of the expansion valve). Further, an example is shown in which an ejector is provided instead of the expansion valve in the vapor compression cycle, and the suction port of the ejector is used as the low pressure source. The use of the evaporator-integrated heat pump is not limited to the Rankine cycle apparatus, or is not limited to the Rankine cycle apparatus having the vapor compression heat pump apparatus, and can be widely applied to the pump apparatus. Therefore, the fluid is not limited to the refrigerant, and any fluid can be used as long as it can change into a liquid phase and a gas phase.

(Embodiment 1)
Hereinafter, Embodiment 1 of the present invention will be described with reference to FIG. FIG. 1 shows a Rankine cycle apparatus 1 having an evaporator-integrated heat pump 4. The Rankine cycle device 1 includes a first suction port 25 and a first discharge port 26 for Rankine cycle, and an expander 21 that performs refrigerant expansion work, and a first discharge port 26 of the expander 21 that is connected to the expander 21. The condenser 3 for condensing the gaseous refrigerant returned from the condenser 3 and the outlet 3p side of the condenser 3 are connected to the outlet 3p side to evaporate the liquid refrigerant into a gaseous refrigerant, which is then supplied to the first suction port 25 of the expander 21 And an evaporator-integrated heat pump 4 that performs the pumping action.

  The evaporator-integrated heat pump 4 (hereinafter, also referred to as a heat pump 4) is an integrated evaporator and heat pump, and the internal pressure is increased by evaporating the liquid by external heat input to increase the internal pressure. A pressure increasing discharge step for discharging the gas, and reducing the pressure in the evaporation chamber by releasing the gas in the evaporation chamber toward the low pressure source, and liquid refrigerant is supplied to the evaporation chamber from the liquid fluid supply source (condenser or reservoir tank). Pumping is repeated with the inhalation process.

  Here, according to the present embodiment, the inlet 3i side of the condenser 3 functions as a low-pressure source that can be lower in pressure than the liquid suction port 107 of the evaporation chamber 41 when the evaporation chamber 41 discharges gas. Positionally, the condenser 3 is arranged above the evaporation chamber 41 in the height direction, and in particular, the bottom of the condenser 3 is arranged above the evaporation chamber 41 in the height direction. By utilizing the head difference of the liquid refrigerant due to this height difference, the liquid suction valve 47 is passed from the outlet 3p of the condenser 3 to the evaporation chamber 41 in the suction process shown in (4) to (1) described later. And inhale.

  As shown in FIG. 1, the heat pump 4 integrates an evaporator and a heat pump that evaporate liquid refrigerant into a gaseous refrigerant, and includes an evaporation chamber 41, a gas release valve 46, and a liquid. A suction valve 47 and a gas discharge valve 48 are provided. The heat pump 4 promotes gasification by evaporating the liquid refrigerant in the evaporation chamber 41 in accordance with heat input from the outside and the evaporation chamber 41 that stores the refrigerant as a fluid capable of phase change from the liquid phase to the gas phase. A heat input element 43 to be discharged, a gas discharge passage 460 having a gas discharge port 49 for discharging the gaseous refrigerant in the evaporation chamber 41 toward the inlet 3i side (external second gas receiving portion) of the condenser 3, and condensation The liquid suction port 107 through which the liquid refrigerant is sucked into the evaporation chamber 41 through the suction passage 470 from the outlet 3p of the vessel 3 (external liquid refrigerant supply source), and the evaporation increased in pressure by the heat input to the heat input element 43 Via an electrically operated first suction on-off valve 91i for supplying the gaseous refrigerant in the evaporation chamber 41 to the first suction port 25 (external first gas receiving portion) of the expander 21 based on the pressure in the chamber 41. A gas discharge passage 450 having a gas discharge port 45.

  As shown in FIG. 1, the evaporator includes a plurality of evaporation pipes 410 arranged substantially in parallel so as to form a passage-shaped evaporation chamber 41 that contains a fluid that can change in phase from a liquid phase to a gas phase. The heat input element 43 includes a heat exchanger 431 that forms a heat exchange chamber 430 that covers the outer wall of the evaporation pipe 410. When the external heat Q is input to the heat input element 43, the liquid refrigerant in the evaporation chamber 41 is heated and evaporated to become a gaseous refrigerant. Examples of the external heat Q include waste heat of equipment such as engines and fuel cells, solar heat, and geothermal heat.

  According to the apparatus shown in FIG. 1, since the liquid refrigerant is heated and evaporated by the external heat Q in the evaporation chamber 41 of the heat pump 4, the evaporation chamber 41 is increased in pressure. When the gas discharge valve 48 and the first discharge opening / closing valve 91p are closed and the electric gas discharge valve 46 is opened, the gas in the evaporation chamber 41 is discharged from the gas discharge port 49, the gas discharge port 45, and the gas discharge passage. 460 is supplied to the inlet 3 i (low pressure source) side of the condenser 3. For this reason, the pressure in the evaporation chamber 41 decreases, and the pressure-responsive liquid suction valve 47 is automatically opened based on the head difference as described above, and the outlet of the condenser 3 (external liquid refrigerant supply source). From the 3p side, the refrigerant liquefied by the condenser 3 is sucked into the evaporation chamber 41 through the liquid suction valve 47 and the liquid suction port 107. When the refrigerant is sucked into the evaporation chamber 41 by a predetermined amount, the gas release valve 46 is closed. Here, since the heat input from the external heat Q continues, the evaporation in the evaporation chamber 41 continues and the evaporation chamber 41 is increased in pressure (for example, 0.8 MPa), and the relief pressure of the gas discharge valve 48 is increased. Also gets higher. For this reason, the pressure-responsive gas discharge valve 48 is opened. At this time, since the first open / close valve 91i that is electrically open / closed is opened, the gaseous high-pressure refrigerant in the evaporation chamber 41 passes through the gas discharge port 45 and the gas discharge passage 450, so that the first Supplyed to the suction port 25 (external first gas receiving portion), the expander 21 performs expansion work. Therefore, it can be said that the Rankine cycle apparatus 1 gives expansion work to the expander 21.

  Thus, the gaseous refrigerant in the evaporation chamber 41 is sucked into the first suction port 25 (gas receiving portion) of the expander 21 via the gas discharge valve 48, the gas discharge passage 450, and the first suction opening / closing valve 91i. Is done. This gas expands in the expander 21 and performs expansion work on the piston 24. After that, the gaseous refrigerant supplied to the first suction port 25 of the expander 21 is discharged from the first discharge port 26 of the expander 21 and is in an intermediate pressure state (for example, through the electric first discharge opening / closing valve 91p). 0.25 MPa) and supplied to the condenser 3 from the inlet 3i. Since the condenser 3 radiates heat to the outside, the gaseous refrigerant undergoes a phase change in the condenser 3 and liquefaction of the refrigerant proceeds. Further, the refrigerant that has been liquefied in the condenser 3 is discharged from the outlet 3p of the condenser 3 and is sucked into the evaporation chamber 41 of the heat pump 4 via the liquid suction port 107 through the suction passage 470.

  As described above, the heat input element 43 of the heat pump 4 is continuously input with external heat Q (waste heat of devices such as engines and fuel cells, solar heat, geothermal heat). The evaporation chamber 41 evaporates and gasifies the liquid refrigerant. In this way, the heat pump 4 functions as an evaporator that evaporates the liquid refrigerant into a gaseous refrigerant, and the first refrigerant intake port 25 (external first port) of the expanded gaseous refrigerant. 1 gas receiving section) and a pump suction function for sucking liquid refrigerant into the evaporation chamber 41.

  In FIG. 1, the liquid suction valve 47 is a check valve that closes when the internal pressure of the evaporation chamber 41 becomes higher than the relief pressure, and allows the refrigerant flow from the condenser 3 to the evaporation chamber 41 of the heat pump 4. The reverse flow is prevented. The gas discharge valve 48 is a check valve that opens when the internal pressure of the evaporation chamber 41 becomes higher than the relief pressure and opens the gas discharge passage 450, and allows the refrigerant flow from the evaporation chamber 41 of the heat pump 4 to the expander 21. Allow, but prevent reverse flow.

  Next, the operation of the heat pump 4 of the present embodiment will be further described with reference to FIG. Since FIG. 2 is a schematic diagram, the positions of the valves 46 and 48 are shown as being upside down. Under the influence of heat input from the heat input element 43, gasification of the refrigerant in the evaporation chamber 41 of the heat pump 4 proceeds, and the pressure of the gas layer 42 in the evaporation chamber 41 is maintained at a high pressure (for example, about 0.8 MPa). . (1) in FIG. 2 shows a suction process in which the evaporation chamber 41 sucks a liquid refrigerant. (2) of FIG. 2 shows the pressure | voltage rise discharge process which discharges the pressure | voltage rise of the evaporation chamber 41-> gaseous refrigerant. FIG. 2 (3) shows a discharge process for discharging the gaseous refrigerant in the evaporation chamber 41. (4) of FIG. 2 shows the suction | inhalation process in which the evaporation chamber 41 is pressure-reduced and suck | inhales a liquid refrigerant. Here, as shown in FIG. 2 (1), the gas discharge valve 48 is closed by opening the gas discharge valve 46, and the high-pressure gaseous refrigerant in the gas layer 42 of the evaporation chamber 41 is discharged into the gas discharge port 49 and Via the gas discharge passage 460, the gas is discharged to a low pressure source, that is, to the inlet 3i side of the condenser 3 having a pressure lower than that of the evaporation chamber 41 at this time. As a result, the inside of the evaporation chamber 41 is reduced in pressure (for example, 0.25 MPa or less). Therefore, the liquid suction valve 47 which is a pressure responsive check valve is opened, and the liquid refrigerant on the condenser 3 side passes through the suction passage 470, the liquid suction valve 47 and the liquid suction port 107, and automatically enters the evaporation chamber 41. Inhaled (see (1) in FIG. 2). As described above, in the suction process shown in FIG. 2A, the gas release valve 46 is opened and the liquid suction valve 47 is opened, but the pressure in the evaporation chamber 41 is less than the relief pressure of the gas discharge valve 48. For this reason, the gas discharge valve 48 is closed (see the suction step shown in (1) of FIG. 2).

  Since the liquid refrigerant is sucked into the evaporation chamber 41 as described above, the liquid level 4k of the liquid refrigerant sucked into the evaporation chamber 41 rises as shown in the suction step (1) of FIG. . Then, when the liquid level 4k of the liquid refrigerant reaches the vicinity of the upper limit (full state) of the evaporation chamber 41, the gas release valve 46 is closed (see the pressure increase discharge process shown in (2) of FIG. 2). In this case, since the heat input from the heat input element 43 continues continuously, gasification of the liquid refrigerant in the evaporation chamber 41 proceeds, and the pressure of the gas layer 42 in the evaporation chamber 41 increases. Since the pressure in the evaporation chamber 41 rises in this way, the liquid suction valve 47, which is a pressure-responsive check valve, is automatically closed (see the pressure increase discharge process shown in (2) of FIG. 2). For example, when the pressure in the evaporation chamber 41 increases to 0.25 MPa, the liquid suction valve 47 is automatically closed. As described above, since the heat input from the heat input element 43 continues, the liquid refrigerant in the evaporation chamber 41 evaporates due to the heat input, and the pressure of the gas layer 42 in the evaporation chamber 41 further increases to increase the pressure. Turn into. As described above, when the pressure of the gas layer 42 in the evaporation chamber 41 rises to a high pressure value (for example, 0.8 MPa) or higher, that is, higher than the relief pressure of the gas discharge valve 48 that is a pressure-responsive check valve, the gas discharge valve 48 is automatically opened (see (2) in FIG. 2). Thus, in the state shown in the pressure increasing discharge step of (2) in FIG. 2, the first gas release valve 46 and the liquid suction valve 47 are closed, but the pressure in the evaporation chamber 41 is the relief pressure of the gas discharge valve 48. Therefore, the gas discharge valve 48 is opened (see (2) in FIG. 2).

  As a result, the gaseous high-pressure refrigerant in the evaporation chamber 41 passes through the gas discharge port 45, the gas discharge passage 450, the open gas discharge valve 48, and the open first suction on-off valve 91i. It discharges to the 1st suction port 25 (refer the discharge process shown in (3) of Drawing 2). In the discharge step shown in FIG. 2 (3), although the first gas release valve 46 and the liquid suction valve 47 are closed, the pressure in the evaporation chamber 41 exceeds the relief pressure of the gas discharge valve 48. The valve 48 is opened, and the refrigerant is continuously discharged to the first suction port 25 via the gas discharge valve 48 (see (3) in FIG. 2).

  Next, when the refrigerant in the evaporator 41 is almost exhausted, the gas release valve 46 is opened, so that the gas in the evaporation chamber 41 is discharged to the low-pressure source, that is, the inlet 3i of the condenser 3, The pressure is reduced (for example, reduced pressure from 0.8 MPa to 0.25 MPa or less). Thus, in order to further reduce the pressure in the evaporation chamber 41, the gas discharge valve 48 is closed, and the pressure-responsive liquid suction valve 47 is opened. As described above, the liquid refrigerant on the condenser side It is automatically sucked into the evaporation chamber 41 through the suction passage 470 and the liquid suction valve 47 (see (4) and (1) in FIG. 2). Thereafter, similar operations are repeated in the order of (1) → (2) → (3) → (4).

  The opening / closing operation speeds of the first suction opening / closing valve 91i and the first discharge opening / closing valve 91p of the expansion compressor 2 are sufficiently high with respect to the operation speed of the heat pump 4, and are equal to one cycle of the heat pump 4. The first suction on-off valve 91i and the first discharge on-off valve 91p of the expansion compressor 2 can perform several cycles of operation.

  As described above, the heat-driven heat pump 4 has an evaporator function for evaporating liquid refrigerant into gaseous refrigerant in the evaporation chamber 41 when the external heat Q is input to the heat input element 43, and evaporating. Pumping function that automatically discharges the gaseous refrigerant to the first suction port 25 (external first gas receiving portion) of the expander 21 of the Rankine cycle device 1 and the liquid refrigerant is sucked into the evaporation chamber 41. Combined with pump suction function. As described above, the heat pump 4 is a heat drive type driven by heat input to the heat input element 43 and is not an electric motor drive type, so that power consumption can be saved.

  As described above, according to the present embodiment, it is possible to provide the heat pump 4 that is advantageous for suppressing power supply from the outside. A cooling heat source for driving the heat pump 4 is unnecessary, energy for generating the heat pump 4 is not required, and overall efficiency can be increased.

(Embodiment 2)
FIG. 3 shows a second embodiment. The first embodiment basically has the same configuration and the same operation and effect as the first embodiment. As described above, the heat pump 4 is an integrated evaporator and heat pump, and includes an evaporation chamber 41, a gas discharge valve 46, a liquid suction valve 47, and a gas discharge valve 48. The evaporator promotes gasification by evaporating the liquid refrigerant in the evaporation chamber 41 in accordance with heat input from the outside and the evaporation chamber 41 that stores the refrigerant as a fluid capable of phase change from the liquid phase to the gas phase. A heat input element 43, a gas discharge passage 460 having a gas discharge port 49 for discharging the gaseous refrigerant in the evaporation chamber 41 toward the inlet side (external second gas receiving portion) of the condenser, and the outlet of the condenser Based on the liquid suction port 107 for sucking the liquid refrigerant from the (external liquid refrigerant supply source) into the evaporation chamber 41 and the pressure of the evaporation chamber 41 increased in pressure by the heat input to the heat input element 43. And a gas discharge passage 450 having a gas discharge port 45 through which high-pressure gaseous refrigerant is supplied to the first suction port 25 (external first gas receiving portion) of the expander 21.

  As shown in FIG. 3, the evaporator of the heat pump 4 has a plurality of evaporating pipes 410 arranged in parallel to form a passage-like evaporating chamber 41 that accommodates a fluid capable of phase change from a liquid phase to a gas phase. The heat input element 43 is formed by a plurality of heat exchange fins 433 provided on the outer wall of the evaporation pipe 410. The heat exchange fins 433 are heated by exchanging heat with a heat exchange fluid heated by external heat (equipment such as an engine or fuel cell, solar heat, geothermal heat, etc.).

(Embodiment 3)
FIG. 4 shows a third embodiment. The present embodiment has basically the same configuration and the same operational effects as the above-described embodiments. The heat pump 4 is an integrated evaporator and pump. The heat pump 4 has a plurality of evaporating pipes 410 arranged in parallel so as to form a passage-like evaporating chamber 41 that accommodates a fluid capable of phase change from a liquid phase to a gas phase. The heat input element 43 forms a heat exchange chamber 430 that covers the plurality of evaporation pipes 410 from the outside, and includes a heat exchanger 431 having an inlet 431i and an outlet 431p. Heat exchange fluid such as hot water heated by external heat (waste heat of equipment such as engines and fuel cells, solar heat, geothermal heat) flows into the heat exchange chamber 430 from the inlet 431i, flows out of the outlet 431p, and evaporates. The refrigerant in the chamber 41 is heated.

(Embodiment 4)
FIG. 5 shows a fourth embodiment. The present embodiment has basically the same configuration and the same operational effects as the above-described embodiments. The heat pump 4 is an integrated evaporator and heat pump. The evaporator of the heat pump 4 forms a housing 412 having an evaporation chamber 41 that houses a refrigerant (fluid) that can change phase from a liquid phase to a gas phase. The heat input element 43 is formed of a pipe-like meandering heat exchange pipe 435 immersed in a liquid refrigerant stored near the bottom of the evaporation chamber 41. The heat exchange fluid heated by external heat (waste heat of equipment such as engines and fuel cells, solar heat, geothermal heat, etc.) flows into the heat exchange pipe 435 and heats the liquid refrigerant near the bottom of the evaporation chamber 41. .

(Embodiment 5)
FIG. 6 shows a fifth embodiment. The present embodiment has basically the same configuration and the same operational effects as the above-described embodiments. As shown in FIG. 6A, the heat pump 4 is an integrated evaporator and heat pump. The evaporator of the heat pump 4 has a passage-shaped evaporation chamber 41 formed by a pipe 41w that stores a refrigerant (fluid) capable of changing phase from a liquid phase to a gas phase. The heat input element 43 includes a heat exchange pipe 436 that runs in parallel with the pipe 41w. The heat exchange fluid heated by external heat (waste heat of equipment such as engines and fuel cells, solar heat, geothermal heat, etc.) flows into the heat exchange pipe 436 and heats the liquid refrigerant in the passage-shaped evaporation chamber 41. Evaporate. In the form shown in FIG. 6B, the heat input element 43 has a heat exchange passage 435 that forms a heat exchanger chamber 438 that encloses and accommodates a pipe 41 w that forms the evaporation chamber 41.

(Embodiment 6)
FIG. 7 shows a sixth embodiment. The present embodiment has basically the same configuration and the same operational effects as the above-described embodiments. FIG. 7 shows a circuit diagram of a cycle in which the Rankine cycle device 1 is combined with the vapor compression heat pump device 6. As shown in FIG. 7, the expansion compressor 2 of the Rankine cycle device 1 includes an expander 21 having an expansion chamber having a first suction port 25 and a first discharge port 26 for the Rankine cycle, and a first for the vapor compression cycle. And a compressor 23 having a compression chamber having two suction ports 27. The Rankine cycle device 1 is further connected to a common condenser 3 that condenses the gaseous refrigerant returned from the first discharge port 26 common to the expander 21 and the compressor 23, and the outlet 3 p side of the condenser 3. The heat pump 4 is provided. The condenser 3 is shared by the Rankine cycle and the vapor compression cycle, but may be provided independently.

  According to the present embodiment, the inlet 3 i side of the condenser 3 functions as a low-pressure source that has a lower pressure than the liquid suction port 107 of the evaporation chamber 41 when the evaporation chamber 41 discharges gas. Positionally, the condenser 3 is disposed above the evaporation chamber 41 in the height direction, and the head difference of the liquid refrigerant due to this height is utilized to (4) to (1) described later. In the suction process shown, the condenser 3 causes the evaporation 41 to be sucked through the liquid suction valve 47.

  As described above, the heat pump 4 evaporates and gasifies the liquid refrigerant by heat input from external heat (waste heat of equipment such as engines and fuel cells, solar heat, and geothermal heat). The condenser 3 has an inlet 3i and an outlet 3p. As shown in FIG. 7, the vapor compression heat pump device 6 includes an expansion valve 60 that is connected to the outlet of the condenser 3 via a passage 100 k and expands the liquid refrigerant condensed in the condenser 3. The refrigerant which is connected to the outlet 60p and expanded by the expansion valve 60 (expansion element) is evaporated and the evaporated gaseous refrigerant is sucked into the second suction port 27 of the compressor 23 of the expansion compressor 2 through the passage 100m. The heat pump evaporator 7 is provided. The heat pump evaporator 7 has an inlet 7i and an outlet 7p. In the vapor compression heat pump device 6, the liquid refrigerant is expanded by the expansion valve 60 and then gasified in the heat pump evaporator 7. The gasified refrigerant is sucked into the second suction port 27 of the compressor 23.

(Embodiment 7)
FIG. 8 shows a seventh embodiment. This embodiment has basically the same configuration as the above-described embodiment, and has the same functions and effects. Also in this embodiment, the heat pump 4 is not an electric type but a heat drive type. FIG. 8 is a circuit diagram of a cycle in which the Rankine cycle device 1 is combined with the vapor compression heat pump device 6. As shown in FIG. 8, the Rankine cycle device 1 has an expansion compressor 2. The expansion compressor 2 has an expander 21 and a compressor 23. The expander 21 has an expansion chamber that can communicate with the first suction port 25 and the first discharge port 26 for Rankine cycle. The compressor 23 has a compression chamber that can communicate with the second suction port 27 and the second discharge port 28 for the vapor compression cycle. The Rankine cycle apparatus 1 is connected to the expander 21 of the expansion compressor 2 in addition to the expansion compressor 2 described above, and gas returned from the first discharge port 26 of the expander 21 and the second discharge port 28 of the compressor 23. A common condenser 3 for condensing the refrigerant in the form of a liquid, a liquid reservoir tank 35 connected to the outlet 3p side of the condenser 3, and a heat pump 4 for sucking the refrigerant in the liquid reservoir tank 35.

  As described above, the heat pump 4 evaporates and gasifies the liquid refrigerant by the input heat of the external heat Q (waste heat of equipment such as an engine, solar heat, geothermal heat, etc.). The condenser 3 has an inlet 3i and an outlet 3p. As shown in FIG. 8, the liquid reservoir tank 35 is provided downstream of the outlet 3 p of the condenser 3. The liquid storage tank 35 has a gas-liquid separation function of the refrigerant. The liquid reservoir tank 35 has an inlet 35i and a plurality of outlets 35p. As shown in FIG. 8, the liquid reservoir tank 35 supplies the liquid refrigerant stored in the liquid reservoir tank 35 from the liquid inlet 107 to the evaporation chamber 41 of the heat pump 4 through the suction passage 470, and also the liquid refrigerant. Is supplied to the expansion valve 60 through the passage 100k.

  As shown in FIG. 8, the vapor compression heat pump device 6 includes an expansion valve 60 that is connected to the condenser 3 via a liquid reservoir tank 35 and a passage 100 k and expands the liquid refrigerant condensed in the condenser 3. The refrigerant which is connected to the outlet 60p of the valve 60 and is expanded by the expansion valve 60 (expansion element) is evaporated and the evaporated gaseous refrigerant is sucked into the second suction port 27 of the expansion compressor 2 through the passage 100m. A heat pump evaporator 7. The heat pump evaporator 7 has an inlet 7i and an outlet 7p.

  As shown in FIG. 8, the heat input element 43 provided in the heat pump 4 evaporates by supplying heat such as waste heat, solar heat, and geothermal heat from devices such as engines and fuel cells to the refrigerant in the evaporation chamber 41. The refrigerant in the chamber 41 is heated to cause the heat pump 4 to exert a pumping action. Here, as shown in FIG. 8, the other end 460 f of the gas discharge passage 460 is a low pressure between the outlet 60 p of the expansion valve 60 and the second suction port 27 of the compressor 23 in the vapor compression heat pump device 6. It communicates with the part 100w (low pressure source). Specifically, the gas discharge port 49 and the other end portion 460f of the gas discharge passage 460 are in communication with the low pressure portion 100w (for example, 0.08 MPa) on the second suction port 27 side of the compressor 23. The second suction check valve 92i and the outlet 7p of the heat pump evaporator 7 are located.

  In the vapor compression heat pump device 6 shown in FIG. 8A, the passage from the outlet 60p of the expansion valve 60 to the second suction port 27 of the expansion compressor 2 has a refrigerant pressure of about 0.08 MPa, for example. The low pressure passage (low pressure source) is lower than the evaporation chamber 41. If it is such a low pressure circuit, the other end portion 460f of the gas discharge passage 460 can be communicated to discharge the gas in the evaporation chamber 41 to the low pressure circuit. According to the present embodiment, the low pressure portion 100w on the second suction port 27 side of the compressor 23 is used as a low pressure source, and the other end 460f is communicated with the low pressure portion 100w.

  As described above, the heat pump 4 uses the liquid refrigerant in the evaporation chamber 41 as a gaseous refrigerant based on the heat input from the heat input element 43, and the first suction port 25 of the expander 21 of the expansion compressor 2. A pump discharge function to be supplied to the gas chamber, a gaseous refrigerant supply function to supply the gaseous refrigerant in the evaporation chamber 41 to the low-pressure portion 100w having a lower pressure than the gas layer 42 of the pressure vessel 40 in the vapor compression heat pump device 6, A liquid refrigerant suction function for sucking the liquid refrigerant on the condenser 3 side from the liquid suction port 107 into the evaporation chamber 41 can be performed.

  As shown in FIG. 8, the gas release passage 460 has an electrically openable gas release valve 46. The suction passage 470 has a liquid suction valve 47 that is a check valve. The liquid suction valve 47 is opened based on the pressure reduction of the evaporation chamber 41 and causes the evaporation chamber 41 to suck the liquid refrigerant in the liquid storage tank 35 on the condenser 3 side. The suction valve 47 allows the refrigerant to pass in the direction from the condenser 3 and the liquid reservoir tank 35 toward the evaporation chamber 41, but does not allow the refrigerant to pass in the opposite direction. The gas discharge passage 450 has a gas discharge valve 48. As the gas discharge valve 48 is opened, the gaseous refrigerant in the evaporation chamber 41 is supplied to the first suction port 25 of the expander 21 via the first suction opening / closing valve 91i. The gas discharge valve 48 allows the refrigerant to pass in the direction from the evaporation chamber 41 toward the first suction port 25 of the expander 21, but does not allow the refrigerant to pass in the opposite direction. In addition, according to this embodiment, the gas discharge valve 48 of the heat pump 4 of the Rankine cycle apparatus 1 can operate independently with respect to the vapor compression heat pump apparatus 6.

  Next, the operation of this embodiment will be described with reference to FIG. Under the influence of heat input from the heat input element 43, the gasification of the refrigerant in the evaporation chamber 41 of the heat pump 4 proceeds, and the pressure of the gas layer 42 is maintained at a high pressure. Here, when the gas release valve 46 of the heat-driven heat pump 4 is opened, the high-pressure (for example, 0.8 MPa) gaseous refrigerant in the gas layer 42 of the evaporation chamber 41 is supplied to the gas discharge port 49 and the gas discharge passage. 460 is discharged to a low-pressure low-pressure portion 100w (for example, about 0.08 MPa) on the second suction port 27 side of the compressor 23. As a result, the inside of the evaporation chamber 41 becomes a low pressure (for example, 0.25 MPa or less). For this reason, the liquid suction valve 47 is opened, and the liquid refrigerant stored in the liquid storage tank 35 on the condenser 3 side passes through the liquid suction passage 470, the liquid suction valve 47 and the liquid suction port 107 and enters the evaporation chamber 41. Inhaled automatically. Since the liquid refrigerant is sucked into the evaporation chamber 41 of the heat pump 4 as described above, the liquid level 4k of the liquid refrigerant sucked into the evaporation chamber 41 rises. When the liquid level 4k of the liquid refrigerant rises, the gas release valve 46 is closed. In this case, since the heat input from the heat input element 43 continues continuously, the gasification of the liquid refrigerant in the evaporation chamber 41 proceeds, and the gas pressure in the evaporation chamber 41 is increased. Since the gas pressure in the evaporation chamber 41 rises in this way, the liquid suction valve 47 that is a pressure-responsive relief valve is closed. As described above, since the heat input from the heat input element 43 continues, the liquid refrigerant in the evaporation chamber 41 evaporates due to the heat input, and the pressure gradually increases to increase the pressure. As described above, when the pressure in the evaporation chamber 41 rises to a high pressure value (for example, 0.8 MPa) or higher, that is, higher than the relief pressure of the pressure-responsive gas discharge stop valve 48, the gas discharge valve 48 is automatically opened. As a result, the gaseous refrigerant in the evaporation chamber 41 is automatically introduced into the first suction port 25 of the expansion compressor 2 via the gas discharge valve 48. Thereafter, the same operation is repeated. Accordingly, when external heat is input to the heat input element 43, the heat-driven heat pump 4 automatically transfers the gaseous refrigerant in the evaporation chamber 41 to the first suction port 25 of the expander 21 of the expansion compressor 2. And a pump suction function for automatically sucking the liquid refrigerant in the liquid storage tank 35 into the evaporation chamber 41. Thus, the heat pump 4 is a heat drive type that is driven by heat input to the heat input element 43 and is not an electric motor drive type, so that power can be saved. As described above, according to this embodiment, it is advantageous to suppress power supply from the outside. A cooling heat source for driving the heat pump 4 is unnecessary, energy for generating the heat pump 4 is not required, and overall efficiency can be increased. 8B and 8C show the internal structure of the liquid reservoir tank 35. FIG. A pipe 301 from the outlet 3p of the condenser 3 may be provided directly on the ceiling wall of the liquid storage tank 35. Further, the pipe 301 from the outlet 3p of the condenser 3 may be immersed in the vicinity of the bottom wall of the liquid storage tank 35.

(Embodiment 8)
FIG. 9 shows an eighth embodiment. The present embodiment has basically the same configuration as the above-described seventh embodiment, and has the same functions and effects. In the gas discharge passage 460 in which the gas release valve 46 is provided, a buffer tank 300 and a buffer valve 302 are provided in series downstream of the gas release valve 46. Thereby, the pressure fluctuation of the low-pressure low-pressure part 100m on the second suction port 27 side of the compressor 23 when the gas release valve 46 is opened can be minimized.

  FIG. 10 shows a ph diagram. p indicates the pressure of the refrigerant, and h indicates the enthalpy of the refrigerant. In the ph diagram (see FIG. 10) showing the state of the refrigerant, the refrigerant at the outlet 3p of the condenser 3 becomes a liquid refrigerant at the position (A) in FIG. Next, when the liquid refrigerant is sucked into the evaporation chamber 41 of the heat pump 4 from the liquid suction port 107 and external heat is applied in the evaporation chamber 41, a part of the refrigerant evaporates and the pressure in the evaporation chamber 41 increases. Then, the pressure is increased to the position shown in FIG. Further, the gas accumulated in the upper portion of the evaporation chamber 41 is also heated, so that the gas is heated from the position (C) in FIG. 10 to the position (D). Thereafter, the gas discharge valve 48 is opened, the gas in the upper portion of the evaporation chamber 41 is discharged into the gas discharge passage 450, and the liquid refrigerant accumulated in the lower portion of the evaporation chamber 41 is also changed from the position of FIG. (D), and sequentially discharged into the gas discharge passage 450. When the discharge is finished, the liquid suction valve 47 is opened, and the liquid refrigerant is again sucked into the evaporation chamber 41 from the liquid suction port 107 through the outlet 3p of the condenser 3. This is repeated below.

  According to the present embodiment, as can be understood from FIG. 9, the gas discharge valve 48 itself shown in FIG. 8 formed by a check valve is abolished, but the first intake on-off valve on the expander 21 side is eliminated. 91i also serves as a gas discharge valve and can function as a gas discharge valve. FIG. 11B shows a first suction on-off valve 91i on the expander 21 side, a first discharge on-off valve 91p, a second suction check valve 92i on the compressor 23 side, and a second discharge check valve. 92p shows a timing chart of opening and closing of the valves such as the gas discharge valve 46, the liquid suction valve 47, and the gas discharge valve 46 of the heat pump 4. As shown in this timing chart, in the expander 21, after the opening of the first discharge on-off valve 91p is completed and the refrigerant of the expander 21 is discharged from the expansion chamber, the first suction on-off valve 91i is opened. Then, gaseous refrigerant is sucked into the expansion chamber of the expander 21. In the compressor 23, after the opening of the second discharge check valve 92p is completed and the refrigerant of the compressor 23 is discharged from the compression chamber, the second suction check valve 92i is opened to remove the gaseous refrigerant. The air is sucked into the compression chamber of the compressor 23. As can be understood from the timing chart shown in FIG. 11B, the heat pump 4 sequentially performs each process of refrigerant discharge, pressure reduction, suction, pressure increase, and discharge. The start timing t1 of the opening operation of the first suction on-off valve 91i on the expander 21 side corresponds to the start timing of opening the gas discharge valve 48 of the heat pump 4 in synchronization. Similarly, the closing timing t2 of the first suction on-off valve 91i corresponds to the timing at which the gas discharge valve 48 of the heat pump 4 is closed. Thus, since the opening time of the gas discharge valve 48 and the opening time of the first suction on-off valve 91i on the expander 21 side are synchronized, according to the present embodiment, a diagram formed of a check valve. The gas discharge valve 48 shown in FIG. 8 is abolished, which is advantageous for cost reduction.

(Embodiment 9)
FIG. 12 shows a ninth embodiment. The present embodiment has basically the same configuration as the above-described embodiment, and has the same functions and effects. As shown in FIG. 12, the present embodiment has basically the same configuration and operational effects as the above-described embodiments. In the present embodiment, pulsation of the discharge pressure of the heat pump 4 is prevented. As shown in FIG. 12, a plurality of heat-driven heat pumps 4A and 4B are installed in parallel. External heat such as waste heat from equipment such as an engine and solar heat is input to the heat input element 43. Each of the heat pumps 4A and 4B repeats the liquid refrigerant suction process from the liquid suction passage 470, the pressure increase process of the evaporation chamber 41, and the discharge process for discharging the gaseous refrigerant. The gaseous refrigerant is intermittently discharged to the first suction port 25 of the expander 21 via 450. For this reason, the refrigerant discharge pressure on the pump outlet side of the heat pumps 4 </ b> A and B may pulsate and affect the expander 21. As a countermeasure, according to the present embodiment, as shown in FIG. 12, two heat-driven heat pumps 4A and 4B are connected in parallel, and the heat pumps 4A and B are alternately alternated while being shifted in phase by 180 °. The pulsation of the discharge pressure is reduced by operating.

(Embodiment 10)
FIG. 13 shows a tenth embodiment. The present embodiment has basically the same configuration as the above-described Embodiments 7 and 8, and has the same functions and effects. As shown in FIG. 13, in the vapor compression heat pump device 6, an ejector 65 that functions as an expansion element is provided between the outlet 35 p of the liquid reservoir tank 35 and the inlet 7 i of the heat pump evaporator 7. The ejector 65 is an isentropic expansion of the refrigerant, similar to the expansion valve. As shown in FIG. 13, the ejector 65 includes a gas release valve connected to the inlet 65 i connected to the outlet 35 p of the liquid storage tank 35, the outlet 65 p connected to the inlet 7 i of the evaporator 7 for the heat pump, and the gas outlet 49 of the pressure vessel 40. 46, a gas discharge passage 460 and a suction port 65e (low pressure source) connected through a buffer 210 for suppressing pulsation.

  The other end 460 f of the gas discharge passage 460 of the heat pump 4 of the Rankine cycle device 1 communicates with the suction port 65 e of the ejector 65. Along with the operation of the compressor 23, the liquid refrigerant in the liquid storage tank 35 flows into the ejector 65 from the inlet 65i and flows toward the heat pump evaporator 7 from the outlet 65p. At this time, when the gas release valve 46 is opened, the gaseous refrigerant in the evaporation chamber 41 of the heat pump 4 passes through the gas release passage 460 to the suction port 65e of the ejector 65 (low pressure source, low pressure suction portion of the ejector 65). The refrigerant is sucked and joined to the refrigerant flowing from the liquid reservoir tank 35 toward the heat pump evaporator 7.

(Other)
According to the form shown in FIG. 7, the other end portion 400 f of the gas discharge passage 460 is provided between the outlet 7 p of the heat pump evaporator 7 in the vapor compression heat pump device 6 and the second suction port 27 of the compressor 23. It communicates with the low pressure part 100w (low pressure source). Not limited to this, the other end portion 400f of the gas discharge passage 460 may be any low pressure passage between the outlet 60p of the expansion valve 60 and the inlet 7i of the heat pump evaporator 7 in the vapor compression heat pump device 6. It may communicate with the part. The condenser 3 may be shared by the Rankine cycle and the vapor compression cycle, or may be provided independently of each other. The present invention is not limited to the embodiments described above and shown in the drawings, and can be implemented with appropriate modifications within the scope not departing from the gist.

  INDUSTRIAL APPLICABILITY The present invention uses external heat such as waste heat, solar heat, and geothermal heat from devices such as engines and fuel cells as heat input, and is used for cooling, heating, hot water supply, and the like.

  1 is a Rankine cycle device, 2 is an expansion compressor, 21 is an expander, 23 is a compressor, 25 is a first suction port (external gas receiving part), 3 is a condenser (liquid fluid supply source), 3i is condensed 35, a reservoir tank (liquid fluid supply source), 4 an evaporator integrated heat pump, 41 an evaporation chamber, 42 a gas layer, 43 a heat input element, 430 a heat exchange chamber , 431 is a heat exchanger, 435 is a heat exchange pipe, 436 is a heat exchange pipe, 45 is a gas discharge port, 450 is a gas discharge passage, 46 is a gas discharge valve, 460 is a gas discharge passage, 47 is a liquid suction valve, 48 Is a gas discharge valve, 6 is a vapor compression heat pump device, 60 is an expansion valve (expansion element), 65 is an ejector (expansion element), 65e is an inlet (low pressure source), 7 is an evaporator for a heat pump, 91i is the first On-off valve for suction, 91p is a first on-off valve for discharge, 9 i The second intake check valve, 92p and the second discharge check valve, 100 w is the low pressure region (low pressure source) 107 indicates a liquid inlet.

Claims (5)

(I) an evaporation chamber that contains a fluid capable of phase change from a liquid phase to a gas phase; a heat input element that evaporates a liquid fluid in the evaporation chamber in accordance with heat input from the outside and promotes gasification; A gas discharge port for discharging the gaseous fluid in the evaporation chamber to a low pressure source, a liquid suction port for sucking the liquid fluid from an external liquid fluid supply source into the evaporation chamber, and a high pressure by heat input to the heat input element An evaporation pump unit comprising a gas discharge port for supplying a gaseous fluid in the evaporation chamber to an external gas receiving unit based on the pressure of the evaporated evaporation chamber,
(Ii) The gas discharge port of the evaporation pump unit is provided so as to open and close, and by opening the gas discharge port, the gaseous fluid in the evaporator chamber is discharged to the low pressure source to reduce the pressure of the evaporation chamber. A gas release valve;
(Iii) a liquid suction valve that causes a liquid fluid from an external liquid fluid supply source to be sucked into the evaporation chamber through the liquid suction port into the evaporation chamber whose pressure has been reduced by opening the gas release valve;
(Iv) An evaporator-integrated heat pump comprising: a gas discharge valve for supplying a gaseous fluid in the evaporation chamber to the external gas receiving section by opening.   In Claim 1, the said evaporation pump part has a plurality of evaporation piping which forms the passage-like evaporation chamber which stores the fluid which can change the phase from a liquid phase to a gaseous phase, The above-mentioned heat input element is, An evaporator-integrated heat pump formed by heat exchange fins provided on an outer wall of the evaporation pipe.   In Claim 1, the said evaporation pump part has several evaporation piping which forms the evaporation channel | path which forms the said channel-shaped evaporation chamber which accommodates the fluid which can change a phase from a liquid phase to a gaseous phase, An entry heat element is an evaporator integrated heat pump which has a heat exchange container which forms a heat exchange chamber which covers a plurality of the above-mentioned evaporation piping. An expander having a first suction port and a first discharge port; a condenser that causes condensation of gaseous refrigerant returned from the first discharge port of the expander; and a refrigerant that has undergone condensation in the condenser. In a Rankine cycle apparatus having an evaporator for Rankine cycle to evaporate,
The evaporator is composed of an evaporator-integrated heat pump,
The evaporator-integrated heat pump is
(I) an evaporation chamber that contains a fluid capable of phase change from a liquid phase to a gas phase; a heat input element that evaporates a liquid fluid in the evaporation chamber in accordance with heat input from the outside and promotes gasification; A gas discharge port for discharging the gaseous fluid in the evaporation chamber to a low pressure source, a liquid suction port for sucking the liquid fluid from an external liquid fluid supply source into the evaporation chamber, and a high pressure by heat input to the heat input element An evaporation pump unit comprising a gas discharge port for supplying a gaseous fluid in the evaporation chamber to an external gas receiving unit based on the pressure of the evaporated evaporation chamber,
(Ii) Gas discharge that is provided so as to open and close the gas discharge port of the evaporation pump unit and causes the gaseous fluid in the evaporation chamber to be discharged to a low pressure source by opening the gas discharge port, thereby reducing the pressure of the evaporation chamber. A valve,
(Iii) the liquid suction valve for sucking liquid fluid from an external liquid fluid supply source into the evaporation chamber through the liquid suction port into the evaporation chamber whose pressure has been reduced by opening the gas release valve;
(Iv) A Rankine cycle device comprising: a gas discharge valve that supplies the fluid in the evaporation chamber to the external gas receiving unit when opened. 5. The expander according to claim 4, wherein the expander is connected to a compression chamber which is communicated with a compression chamber compressed by an expansion action of the expansion chamber, in addition to the first suction port and the first discharge port for Rankine cycle. An expansion compressor having two suction ports and a second discharge port;
An expansion element that is connected to the outlet side of the condenser and expands the liquid refrigerant condensed in the condenser; and a gas that is vaporized and evaporated when the refrigerant connected to the expansion element and expanded by the expansion element is evaporated. A Rankine cycle device in which a vapor compression heat pump device including a heat pump evaporator for sucking refrigerant into the second suction port of the expansion compressor is integrally provided.

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