JP2008297961A - Refrigeration device provided with waste heat using apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigeration device provided with a waste heat using device capable of securing reliability and exerting sufficient performances for both cycles in devices provided with a refrigeration cycle and a Rankine cycle. <P>SOLUTION: The refrigeration device provided with a waste heat using apparatus is mounted on a vehicle and includes the cooling cycle 200 and the Rankine cycle 300. A condenser 220 for the refrigeration cycle and a condenser 340 for the Rankine cycle are arranged at predetermined sections of a vehicle in parallel with a direction of flow of cooling external air. The condenser 220 for the refrigeration cycle is arranged at an external air upstream side of the condenser 340 for the Rankine cycle. When the refrigeration cycle 200 and the Rankine cycle 300 are simultaneously operated, rotation speed of an expander 330 is controlled to keep expander differential pressure ΔP greater than a predetermined value ΔPa. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a refrigeration apparatus including a waste heat utilization device that operates an expander using waste heat of a vehicle, for example, an internal combustion engine as a heating source.

  As a refrigeration apparatus provided with a conventional waste heat utilization apparatus, for example, one disclosed in Patent Document 1 is known. That is, this refrigeration apparatus has a Rankine cycle and a refrigeration cycle that use cooling waste heat of an internal combustion engine as a heat generating device. A compressor that compresses and discharges refrigerant is provided in the refrigeration cycle, and an expander that is operated by expansion of the refrigerant heated by the cooling waste heat is provided independently in the Rankine cycle. The condenser (heat radiator) is shared with the condenser for the refrigeration cycle.

In such a refrigeration apparatus, the refrigeration cycle, the Rankine cycle can be operated independently, or the refrigeration cycle and the Rankine cycle can be operated simultaneously, depending on the necessity of cooling and whether or not the cooling waste heat can be recovered.
JP 2006-46763 A

  However, in the refrigeration apparatus, when the refrigeration cycle and the Rankine cycle are simultaneously operated, the condenser simultaneously condenses (heatsinks) the refrigerant in both cycles, and the refrigerant pressure in the condenser increases. Therefore, the power of the compressor of the refrigeration cycle increases (deteriorates), and the reliability of the compressor may be lowered, and the coefficient of performance of the refrigeration cycle decreases.

  In addition, during a stand-alone operation of only the Rankine cycle, a pressure difference is generated between the condenser and the evaporator due to an increase in the refrigerant pressure in the condenser, although the refrigeration cycle is stopped. Is accumulated on the refrigeration cycle side (evaporator side), the amount of refrigerant on the Rankine cycle side is reduced, and the original Rankine cycle capability cannot be fully exhibited. Furthermore, the lubricating oil contained in the refrigerant also accumulates on the refrigeration cycle side, resulting in insufficient lubrication for the expander and the refrigerant pump, which may reduce the reliability of the expander and the refrigerant pump.

  In view of the above problems, an object of the present invention is to provide a refrigeration apparatus including a waste heat utilization apparatus capable of ensuring reliability and exhibiting sufficient performance for both cycles in a refrigeration cycle including a Rankine cycle. There is to do.

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

  In the first aspect of the present invention, the compressor (210), the refrigeration condenser (220), the expansion valve (240), and the evaporator (250) are connected in an annular shape while being mounted on a vehicle. Refrigerating cycle (200) in which refrigerant circulates, pump (310), heater (320) using waste heat of heat engine (10) of vehicle as heating source, expander (330), and Rankine condenser (340) ) Are connected in a ring shape and a Rankine cycle (300) through which Rankine refrigerant circulates, a refrigeration apparatus comprising a waste heat utilization device, the refrigeration condenser (220) and Rankine condenser (340) It is arranged in series with respect to the flow direction of the external air for cooling at a predetermined site, and the refrigeration condenser (220) is arranged upstream of the external air with respect to the Rankine condenser (340). Characteristic It is.

  Thereby, regardless of whether or not the Rankine cycle (300) is operated, an external fluid equal to the outside air temperature can always flow into the refrigeration condenser (220). Therefore, in the operation of the refrigeration cycle (200), There is no reduction in reliability due to deterioration in power of the compressor (210), or reduction in refrigeration capacity due to reduction in coefficient of performance.

  In addition, during the independent operation of the Rankine cycle (300), each cycle (200, 300) forms an independent refrigerant circuit, so that the refrigerant flows from the Rankine cycle (300) side to the refrigeration cycle (200) side. In addition, the oil does not accumulate, and the ability of the original Rankine cycle (300) can be fully exerted, and the reliability of the expander (330) and the pump (310) can be reliably ensured.

  In general, it is possible to obtain a refrigeration apparatus (100A) including a waste heat utilization apparatus capable of ensuring reliability and exhibiting sufficient performance for both cycles (200, 300).

  Here, as in the invention of the first aspect, in the case where the refrigeration condenser (220) is arranged on the upstream side of the external air with respect to the Rankine condenser (340), the refrigeration cycle (200 ) And the Rankine cycle (300), the external air flows into the Rankine condenser (340) after heat exchange in the refrigeration condenser (220). The outside air temperature is higher than the outside air. Therefore, in the Rankine condenser (340), the refrigerant pressure increases, the expander differential pressure (ΔP) in the expander (330) decreases, and the regenerative power by the expander (330) is surely increased. A situation that cannot be obtained may occur or an unstable Rankine cycle (300) may be activated.

  Therefore, in invention of Claim 2, it has the control means (50) which controls the action | operation of a refrigerating cycle (200) and a Rankine cycle (300), and a control means (50) is a refrigerating cycle (200) and Rankine. When the cycle (300) is operated simultaneously, the rotational speed of the expander (330) is set so that the expander differential pressure (ΔP) in the Rankine refrigerant expander (330) is equal to or greater than a predetermined value (ΔPa). It is characterized by control.

  As a result, even when the refrigeration cycle (200) and the Rankine cycle (300) are operated simultaneously, a sufficient expander differential pressure (ΔP) is ensured to operate the unstable Rankine cycle (300). While preventing, sufficient regenerative power by the expander (330) can be obtained.

  The invention according to claim 3 is characterized in that the control means (50) reduces the rotational speed of the expander (330) when the expander differential pressure (ΔP) is smaller than a predetermined value (ΔPa). .

  Thereby, the expander differential pressure (ΔP) can be surely set to a predetermined value (ΔPa) or more.

  In the invention according to claim 4, the control means (50) controls the rotational speed of the expander (330) so that the expander differential pressure (ΔP) becomes a value that provides a predetermined appropriate expansion ratio. It is characterized by that.

  Thereby, since an appropriate expansion operation can be performed on the expander (330), effective power regeneration can be performed.

  According to the fifth aspect of the present invention, the high pressure is disposed in the high pressure side region from the downstream side of the pump (310) to the upstream side of the expander (330) and detects the high pressure side pressure (PHr) of the Rankine refrigerant. Side pressure detection means (301) and a low pressure that is disposed in the low pressure side region from the downstream side of the expander (330) to the upstream side of the pump (310) and detects the low pressure side pressure (PLr) of the Rankine refrigerant. Side pressure detection means (302), and the control means (50) is based on the difference (PHr-PLr) between the high pressure side pressure (PHr) and the low pressure side pressure (PLr) indicating the expander differential pressure (ΔP). It is characterized by controlling the rotation speed of the expander (330).

  Thereby, the expander differential pressure (ΔP) can be calculated easily and reliably.

  In the sixth aspect of the present invention, the high pressure is disposed in the high pressure side region extending from the downstream side of the pump (310) to the upstream side of the expander (330), and detects the high pressure side pressure (PHr) of the Rankine refrigerant. Passing air temperature of external air that is disposed between the side pressure detecting means (301), the refrigeration condenser (220), and the Rankine condenser (340) and passes between the condensers (220, 340). The amount of heat radiation (Qor) in Rankine condenser (340) that balances the amount of heat absorption (Qir) to the heater (320) due to waste heat, and the passing air temperature detection means (101) for detecting (Tas), Rankine Of the Rankine refrigerant in the Rankine condenser (340) from the amount of external air (Ga) passing through the condenser (340) and the passing air temperature (Tas) detected by the passing air temperature detecting means (101) (TLr) and calculation means (S115) for calculating the low pressure side pressure (PLr), and the control means (50) includes a high pressure side pressure (PHr) and a low pressure side pressure indicating the expander differential pressure (ΔP). The rotational speed of the expander (330) is controlled based on the difference (PHr−PLr) from (PLr).

  Thereby, with respect to the invention of the fifth aspect, the low pressure side pressure detecting means (302) is replaced with the passing air temperature detecting means (101), and further the calculating means (S115) is used to expand the pressure difference (ΔP ) Can be calculated (estimated).

  According to the seventh aspect of the present invention, the high pressure is disposed in the high pressure side region from the downstream side of the pump (310) to the upstream side of the expander (330) and detects the high pressure side pressure (PHr) of the Rankine refrigerant. Side pressure detection means (301), inflow air temperature detection means (102) for detecting the inflow air temperature (Ta) of the external air before flowing into the freezing condenser (220) and Rankine condenser (340), , The amount of heat release (Qoa) in the refrigeration condenser (220) that balances the required cooling capacity (Qia) in the evaporator (250), the amount of external air (Ga) that passes through the refrigeration condenser (220), While calculating the passing air temperature (Tas) of the external air after passing through the refrigeration condenser (220) from the inflowing air temperature (Ta) detected by the inflowing air temperature detection means (102), the heater (320) by waste heat is used. Sucking into) From the amount of heat release (Qor) in the Rankine condenser (340) that balances the quantity (Qir), the amount of external air (Ga) that passes through the Rankine condenser (340), and the passing air temperature (Tas), And a calculation means (S116) for calculating the temperature (TLr) of the Rankine refrigerant in the condenser (340) and further the low pressure side pressure (PLr), and the control means (50) calculates the expander differential pressure (ΔP). The rotational speed of the expander (330) is controlled based on the difference (PHr−PLr) between the high-pressure side pressure (PHr) and the low-pressure side pressure (PLr).

  Thereby, with respect to the invention described in claim 5, the low-pressure side pressure detection means (302) is replaced with the inflow air temperature detection means (102), and further the calculation means (S116) is used to further expand the pressure difference (ΔP ) Can be calculated (estimated).

  In the invention according to claim 8, the positions at which the inlet portion (220a) and the outlet portion (220b) for the refrigerant for refrigeration with respect to the condenser (220) for refrigeration are disposed as viewed from the flow direction of the external air, It is characterized in that it is in the same region as the position where the Rankine refrigerant inlet part (340a) and outlet part (340b) for the Rankine condenser (340) are disposed.

  Thereby, the inflow part area | region and outflow part area | region of the refrigerant | coolant for freezing in the condenser for freezing (220) are respectively the same positional relationship as the inflow part area | region and outflow part area | region of the refrigerant | coolant for Rankine in the Rankine condenser (340). Can be. The temperature rise of the external air after passing through the refrigeration condenser (220) is higher on the inflow side of the refrigeration refrigerant and lowers toward the outflow side. Further, the temperature of the Rankine refrigerant in the Rankine condenser (340) is naturally lowered from the inflow portion side to the outflow portion side by heat exchange. Therefore, since the positional relationship in which the temperature distribution between the external air flowing into the Rankine condenser (340) and the Rankine refrigerant have the same tendency can be obtained, the temperature difference between the external air and the Rankine refrigerant is totally It can be made uniform, and effective heat radiation in the Rankine condenser (340) becomes possible.

  In the invention according to claim 9, the Rankine condenser (340) passes between the refrigeration condenser (220) and the Rankine condenser (340) from the upstream side of the external air of the refrigeration condenser (220). And an introduction flow path section (103) that allows external air to be introduced into the refrigeration condenser (220) and the opening area toward the refrigeration condenser (220) and the introduction flow path section (103). ) Side opening adjustment part (104) for adjusting the opening area to the side.

  Thereby, according to the required heat dissipation of the condenser for freezing (220) and the condenser for Rankine (340), the inflow amount of the external air to each condenser (220, 340) can be adjusted, Effective heat radiation in the condensers (220, 340).

  In the invention according to claim 10, the front surface area of the refrigeration condenser (220) is formed smaller than the front surface area of the Rankine condenser (340), and the outside air upstream side of the Rankine condenser (340). Is characterized in that a region where the refrigeration condenser (220) does not overlap is provided.

  As a result, external air equal to the outside air temperature that is not subjected to heat exchange in the refrigeration condenser (220) can be directly flowed into the Rankine condenser (340), and the heat dissipation capability in the Rankine condenser (340) can be increased. Can be improved.

  The invention according to claim 11 is characterized in that the dimension of the refrigeration condenser (220) in the external air flow direction is set larger than the dimension of the Rankine condenser (340) in the external air flow direction. .

  Thereby, the heat dissipation capability of the freezing condenser (220) can be gained by increasing the size of the external air in the flow direction, and the front area of the freezing condenser (220) can be easily reduced.

  In the twelfth aspect of the present invention, the inlet portion (220a) and the outlet portion (220b) of the refrigeration refrigerant in the refrigeration condenser (220) are opened toward the upstream side in the flow direction of the external air. It is characterized by.

  This eliminates the need for piping between the refrigeration condenser (220) and the Rankine condenser (340) when routing the refrigeration refrigerant pipe to the refrigeration condenser (220). The dimension between the condensers (220, 340) is not deteriorated. Moreover, the connection of piping to the freezing condenser (220) can be facilitated.

  In the invention according to claim 13, the inlet part (340 a) and the outlet part (340 b) of the Rankine refrigerant in the Rankine condenser (340) are opened in a direction orthogonal to the flow direction of the external air. It is characterized by.

  Accordingly, in the routing of the Rankine refrigerant pipe to the Rankine condenser (340), the pipe is disposed between the refrigeration condenser (220) and the Rankine condenser (340), or the blown air. Since there is no need to arrange piping from the upstream side to the downstream side in the flow direction, the size between the two condensers (220, 340) is deteriorated, or the front surface of the refrigeration condenser (220). It is possible to prevent the area from being reduced. Furthermore, the connection of the piping to the Rankine condenser (340) can be facilitated.

  In addition, the code | symbol in the bracket | parenthesis of each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

(First embodiment)
A first embodiment of the present invention is shown in FIGS. 1 to 6, and a specific configuration will be described first. FIG. 1 is a schematic diagram showing an entire system of a refrigeration apparatus (hereinafter referred to as a refrigeration apparatus) 100A including a waste heat utilization apparatus, and FIG. 2 is a refrigeration condenser (hereinafter referred to as an AC condenser) 220 for vehicles, a Rankine condenser ( Hereinafter, a side view showing the mounted state of the RA condenser) 340 and the radiator 21, FIG. 3 is a perspective view showing the refrigerant inlet portions 220a and 340a and the outlet portions 220b and 340b of the AC condenser 220 and the RA condenser 340, respectively. FIG. 4 is a perspective view showing the pipe connection directions of the AC condenser 220, the RA condenser 340, the refrigerant of the radiator 21, and the cooling water inlet portions 220a, 340a, 21a, the outlet portions 220b, 340b, 21b. 5 is a control characteristic diagram showing an operation mode with respect to the refrigerant pressure of the electric fan 260, and FIG. 6 is a case where the refrigeration cycle 200 and the Rankine cycle 300 are simultaneously operated. It is a flowchart 1 showing a control method.

  As shown in FIG. 1, the refrigeration apparatus 100A according to the first embodiment is applied to a vehicle using an engine 10 as a drive source. The refrigeration apparatus 100 </ b> A is provided with a refrigeration cycle 200 and a Rankine cycle 300, and the operation of each cycle 200, 300 is controlled by an energization control circuit 50.

  The engine 10 is a water-cooled internal combustion engine (corresponding to the heat engine in the present invention), and heats conditioned air by using a radiator circuit 20 that cools the engine 10 by circulation of engine cooling water and cooling water (hot water) as a heat source. A heater circuit 30 is provided.

  The radiator circuit 20 is provided with a radiator 21, and the radiator 21 cools the cooling water circulated by the hot water pump 22 by heat exchange with the outside air. The hot water pump 22 may be either an electric pump or a mechanical pump. A heater 320 of a Rankine cycle 300, which will be described later, is disposed in a flow path on the outlet side of the engine 10 (a flow path between the engine 10 and the radiator 21), and cooling water flows through the heater 320. It is like that. In the radiator circuit 20, there is provided a radiator bypass passage 23 through which the coolant flows around the radiator 21. The amount of cooling water that flows through the radiator 21 by the thermostat 24 and the amount of cooling water that flows through the radiator bypass passage 23. Is to be adjusted.

  A heater core 31 is provided in the heater circuit 30, and cooling water (hot water) is circulated by the hot water pump 22. The heater core 31 is disposed in the air conditioning case 410 of the air conditioning unit 400, and heats the conditioned air blown by the blower 420 by heat exchange with hot water. The heater core 31 is provided with an air mix door 430, and the amount of conditioned air flowing through the heater core 31 is varied by opening and closing the air mix door 430.

  The refrigeration cycle 200 includes a compressor 210, an AC condenser 220, a liquid receiver 230, an expansion valve 240, and an evaporator 250, which are connected in a ring shape to form a closed circuit. The compressor 210 is a fluid device that compresses the refrigerant in the refrigeration cycle 200 (corresponding to the refrigeration refrigerant in the present invention, hereinafter referred to as AC refrigerant) to high temperature and high pressure, and is driven by the driving force of the engine 10 here. It has become so. That is, a pulley 211 as a driving means is fixed to the drive shaft of the compressor 210, and the driving force of the engine 10 is transmitted to the pulley 211 via the belt 11 to drive the compressor 210. The pulley 211 is provided with an electromagnetic clutch (not shown) that intermittently connects between the compressor 210 and the pulley 211. The connection / disconnection of the electromagnetic clutch is controlled by an energization control circuit 50 described later. The AC refrigerant circulates in the refrigeration cycle 200 by driving the compressor 210.

  The AC condenser 220 is connected to the discharge side of the compressor 210 and is a heat exchanger that condenses and liquefies the AC refrigerant that circulates in the interior by heat exchange with cooling air (corresponding to external air in the present invention). The liquid receiver 230 is a receiver that separates the AC refrigerant condensed by the AC condenser 220 into two layers of gas and liquid, and causes only the separated liquefied AC refrigerant to flow out to the expansion valve 240 side. The expansion valve 240 decompresses and expands the liquefied AC refrigerant from the liquid receiver 230. In this embodiment, the expansion valve 240 decompresses the AC refrigerant in an enthalpy manner, and at the same time, the AC refrigerant sucked into the compressor 210 from the evaporator 250. A temperature-type expansion valve that controls the throttle opening is employed so that the degree of superheat of the gas reaches a predetermined value.

  The evaporator 250 is disposed in the air conditioning case 410 of the air conditioning unit 400 in the same manner as the heater core 31, evaporates the AC refrigerant decompressed and expanded by the expansion valve 240, and air-conditions from the blower 420 by the latent heat of evaporation at that time. It is a heat exchanger that cools air. The refrigerant outlet side of the evaporator 250 is connected to the suction side of the compressor 210. The mixing ratio of the conditioned air cooled by the evaporator 250 and the conditioned air heated by the heater core 31 is varied according to the opening degree of the air mix door 430 and adjusted to a temperature set by the occupant.

  On the other hand, the Rankine cycle 300 collects waste heat energy (heat of cooling water) generated in the engine 10, and uses the waste heat energy as mechanical energy (driving force of the expander 330), and further electric energy (generator). 331) and used. Hereinafter, the Rankine cycle 300 will be described.

  The Rankine cycle 300 includes a pump 310, a heater 320, an expander 330, a condenser 340, and a liquid receiver 350, which are connected in a ring shape to form a closed circuit.

  The pump 310 is an electric type that circulates the refrigerant in the Rankine cycle 300 (corresponding to the Rankine refrigerant in the present invention, hereinafter referred to as RA refrigerant) using an electric motor 311 operated by an energization control circuit 50 described later as a drive source. It is a pump. Here, the RA refrigerant is the same as the AC refrigerant. The heater 320 is a heat exchanger that heats the RA refrigerant by exchanging heat between the RA refrigerant sent from the pump 310 and the high-temperature cooling water flowing through the radiator circuit 20.

  The expander 330 is a fluid device that generates a rotational driving force by the expansion of the superheated steam RA refrigerant heated by the heater 320. A generator 331 is connected to the drive shaft of the expander 320. Then, as will be described later, the generator 331 is operated by the driving force of the expander 330, and the electric power generated by the generator 331 is charged to the battery 40 via an inverter 51 that forms an energization control circuit 50 described later. It has become. The RA refrigerant flowing out from the expander 330 reaches the RA condenser 340.

  The RA condenser 340 is a heat exchanger that is connected to the discharge side of the expander 330 and condenses and liquefies the RA refrigerant by heat exchange with cooling air (corresponding to external air in the present invention). The liquid receiver 350 is a receiver that separates the RA refrigerant condensed by the RA condenser 340 into two layers of gas and liquid, and allows only the liquefied RA refrigerant separated here to flow out to the pump 310 side.

  In a high pressure side region from the discharge side (downstream side) of the pump 310 of the Rankine cycle 300 to the inflow side (upstream side) of the expander 330, a pressure sensor that detects the pressure of the RA refrigerant (high pressure side pressure PHr) (the present invention). (Corresponding to the high pressure side pressure detecting means) in FIG. Here, the pressure sensor 301 is provided between the heater 320 and the expander 330 in the high pressure side region. A pressure sensor (low pressure in the present invention) detects the pressure of the RA refrigerant (low pressure side pressure PLr) in a low pressure side region from the discharge side (downstream side) of the expander 330 to the suction side (upstream side) of the pump 310. 302 corresponding to the side pressure detecting means). Here, the pressure sensor 302 is provided between the expander 330 and the RA condenser 340 in the low pressure side region. The pressure signals detected by both pressure sensors 301 and 302 are output to an energization control circuit 50 described later.

  As shown in FIG. 2, the AC condenser 220 in the refrigeration cycle 200, the RA condenser 340 in the Rankine cycle 300, and the radiator 21 in the radiator circuit 20 are disposed at the rear of the vehicle grill, that is, the front side in the engine room. ing. While the vehicle travels, cooling air (external air) flows from the grille into the engine room. The AC condenser 220, RA condenser 340, and radiator 21 are directed from the upstream side to the downstream side with respect to the flow direction of the cooling air. The AC condenser 220, the RA condenser 340, and the radiator 21 are arranged in series in this order. Hereinafter, the upstream side in the flow direction of the cooling air is referred to as the front side and the downstream side is referred to as the rear side in accordance with the position in the front-rear direction of the vehicle.

  As shown in FIG. 3, the AC refrigerant inlet 220a and outlet 220b for the AC condenser 220 are both provided at one end in the horizontal direction (the right side when mounted on the vehicle), and the inlet 220a is on the upper side ( The outlet 220b is disposed on the lower side (lower right side when mounted on the vehicle). The RA refrigerant inlet 340a and outlet 340b with respect to the RA condenser 340 are arranged in the same area as the inlet 220a and outlet 220b of the AC condenser 220. That is, the position of the inlet part 220a of the AC condenser 220 and the position of the inlet part 340a of the RA condenser 340 are on the upper right side when mounted on the vehicle, respectively, and the position of the outlet part 220b of the AC condenser 220 is The position of the outlet 340b of the RA condenser 340 is on the lower right side when the vehicle is mounted.

  Further, as shown in FIG. 4, the inlet 220a and outlet 220b of the AC condenser 220 are opened toward the front side (grill side), and the refrigerant pipe is connected from the front side toward the rear side. It has become. Further, the inlet portion 340a and the outlet portion 340b of the RA condenser 340 are opened in a direction orthogonal to the cooling air flow direction (right side of the vehicle width direction), and the refrigerant pipe is directed from the right side to the left side in the width direction. To be connected. Further, the cooling water inlet 21a and outlet 21b of the radiator 21 are opened toward the rear side (engine 10 side), and the cooling water pipe is connected from the rear side toward the front side. Yes.

  Of the AC condenser 220, the RA condenser 340, and the radiator 21 arranged in series in the engine room, an electric fan in which an axial flow type blower fan is rotationally driven by an electric motor as a drive source on the rear side of the radiator 21 260 is provided (FIG. 1). The electric fan 260 is a so-called suction-type air blowing means that forcibly supplies cooling air from the front side to the rear side to the AC condenser 220, the RA condenser 340, and the radiator 21 by rotationally driving the air blowing fan. When the inflow amount of cooling air from the vehicle grill cannot be expected (during idling or low-speed climbing, etc.), the cooling air is not sufficiently extracted from the AC condenser 220, RA condenser 340, and radiator 21. Operates to promote the supply.

  Specifically, as shown in FIG. 5, the electric fan 260 is controlled in operation by an energization control circuit 50 described later, and the AC refrigerant pressure on the high pressure side of the refrigeration cycle 200 is α or less (or the cooling water temperature is a predetermined temperature or less). ) In the Lo mode, and further in the Hi mode when the high-pressure side AC refrigerant pressure is equal to or higher than α + β (or the coolant temperature is equal to or higher than the predetermined temperature + γ).

  The energization control circuit 50 is a control means for controlling the operation of various devices in the refrigeration cycle 200 and Rankine cycle 300, and includes an inverter 51 and a control device 52.

  The inverter 51 controls the operation of the generator 331 connected to the expander 330, and charges the battery 40 with the generated electric power when the generator 331 is operated by the driving force of the expander 330.

  In addition, the control device 52 controls the operation of the inverter 51, acquires detection signals from the pressure sensors 301 and 302, and operates the refrigeration cycle 200 and the Rankine cycle 300 to operate the electromagnetic clutch, the electric fan 260, The motor 311 and the like of the pump 310 are also controlled.

  Next, the operation based on the above configuration and the operation and effect thereof will be described.

1. Refrigeration cycle single operation When waste heat cannot be obtained during warming up immediately after the engine 10 is started and there is an air conditioner request, the energization control circuit 50 stops the motor 311 of the pump 310 (the expander 320 stops). The electromagnetic clutch is connected, the compressor 210 is driven by the driving force of the engine 10, and the refrigeration cycle 200 is operated alone. In this case, the same operation as a normal vehicle air conditioner is performed.

2. Rankine cycle single operation When there is no air conditioner request and there is sufficient waste heat of the engine 10, the energization control circuit 50 disconnects the electromagnetic clutch (the compressor 210 is stopped), operates the electric motor 311 (pump 310), and rankine The cycle 300 is operated alone to generate power.

  In this case, the RA liquid refrigerant in the liquid receiver 350 is boosted by the pump 310 and sent to the heater 320, where the RA liquid refrigerant is heated by the high-temperature engine cooling water and becomes RA superheated vapor refrigerant. To the expander 330. In the expander 330, the RA superheated steam refrigerant is expanded and reduced in an isentropic manner, and a part of the heat energy and pressure energy is converted into a rotational driving force. The generator 331 is operated by the rotational driving force extracted by the expander 330, and the generator 331 generates power. The electric power obtained by the generator 331 is charged into the battery 40 via the inverter 51 and used for the operation of various auxiliary machines. The RA refrigerant decompressed by the expander 330 is condensed by the RA condenser 340, separated into gas and liquid by the liquid receiver 350, and again sucked into the pump 310.

3. Simultaneous operation of refrigeration cycle and Rankine cycle When there is an air conditioner request and there is sufficient waste heat, the energization control circuit 50 operates the refrigeration cycle 200 and Rankine cycle 300 simultaneously to perform both air conditioning and power generation.

  In this case, an electromagnetic clutch is connected and the electric motor 311 (pump 310) is operated. AC refrigerant and RA refrigerant circulate in the refrigeration cycle 200 and Rankine cycle 300, respectively. About the operation | movement of each cycle 200,300, it is the same as the case of the said independent operation.

  Here, in the above-described simultaneous operation of the refrigeration cycle and the Rankine cycle, since the RA condenser 340 is disposed on the rear side of the AC condenser 220, cooling air having an outside temperature flows into the AC condenser 220. The RA condenser 340 is supplied with cooling air whose temperature has been increased by the heat exchange in the AC condenser 220. Therefore, in the RA condenser 340, the heat radiation capability is lowered as compared with a case where purely cooled air (external air that has not undergone heat exchange) is introduced, and accordingly, the low pressure of the Rankine cycle 300 is reduced. The side pressure PLr will increase. When the low-pressure side pressure PLr increases, the expander differential pressure ΔP of the RA refrigerant in the expander 330 decreases, the regenerative driving force decreases, and the power generation amount decreases. Furthermore, the operation of the Rankine cycle 300 becomes unstable. Therefore, here, in order to suppress the unstable operation of the Rankine cycle 300 while suppressing the power generation amount decrease, the energization control circuit 50 executes the differential pressure decrease suppression control based on the control flowchart 1 shown in FIG. To do.

  That is, first, when the refrigeration cycle and Rankine simultaneous operation are executed in step S100, the energization control circuit 50 reads the high pressure side pressure PHr and the low pressure side pressure PLr detected by the pressure sensors 301 and 302 in step S110. In step s120, the expander differential pressure ΔP is calculated by subtracting the low pressure side pressure PLr from the high pressure side pressure PHr.

  Next, in step S130, it is determined whether or not the expander differential pressure ΔP calculated in step S120 is smaller than a predetermined differential pressure (corresponding to a predetermined value in the present invention) ΔPa. Here, the predetermined differential pressure ΔPa is determined as a differential pressure on the lower limit side that allows the expander 330 to operate stably while allowing the expander 330 to perform an overexpansion operation.

  For example, if the expander 330 of the present embodiment is to be appropriately expanded and operated with the high pressure side pressure PHr = 2.3 Mpa and the expansion ratio = 2.0, the low pressure side pressure PLr needs to be set to 1.15 Mpa. Thus, the appropriate expander differential pressure ΔPo for performing the appropriate expansion operation is 1.15 Mpa. When the expander differential pressure ΔP is smaller than the appropriate expander differential pressure ΔPo, the expander 330 is overexpanded. As the expander differential pressure ΔP decreases, the operation of the Rankine cycle 300 becomes unstable. When the expander differential pressure ΔP is larger than the appropriate expander differential pressure ΔPo, the expander 330 is underexpanded. Therefore, the predetermined differential pressure ΔPa is set as a minimum expander differential pressure ΔP that is not accompanied by unstable operation of the Rankine cycle 300. Under the above conditions, for example, the predetermined differential pressure ΔPa = 0.8 Mpa. (70% level of appropriate expansion differential pressure ΔPo).

  If it is determined in step S130 that the expander differential pressure ΔP is smaller than the predetermined differential pressure ΔPa, it is determined in step S140 whether or not the current expander rotational speed of the expander 330 is the minimum operable rotational speed. The expander rotation speed is equal to the rotation speed of the generator 331 and is detected by the inverter 51.

  If it is determined in step S140 that the expander rotation speed is not the minimum rotation speed, the rotation speed of the expander 330 can be decreased, and the energization control circuit 50 decreases the rotation speed of the expander 330 by a predetermined amount. When the rotational speed of the expander 330 is decreased, a current is supplied from the inverter 51 to the generator 331 that is generating power, thereby providing a braking action.

  When the expander rotational speed is decreased in step S150, the resistance action against the RA refrigerant in the expander 330 is increased, the low-pressure side pressure PLr is decreased, and the expander differential pressure ΔP is increased. Therefore, the expander differential pressure ΔP is controlled to be equal to or higher than the predetermined differential pressure ΔPa by repeating steps S110 to S150.

  If it is determined in step S140 that the expander rotation speed is already the minimum rotation speed, the expander differential pressure ΔP cannot be controlled to be equal to or higher than the predetermined differential pressure ΔPa as described above. In step S160, Rankine cycle 300 is stopped as a safety measure. If NO in step S130, that is, if the expander differential pressure ΔP is greater than the predetermined differential pressure ΔPa, the rotational speed control of the expander 330 is not necessary, and the process returns to step S100.

  As described above, in the present embodiment, the dedicated AC condenser 220 and RA condenser 340 are set for the refrigeration cycle 200 and Rankine cycle 300, respectively, and the AC condenser 220 is connected to the front side of the RA condenser 340 (cooling air flow). Therefore, the AC condenser 220 can always be supplied with an external fluid equal to the outside air temperature regardless of whether or not the Rankine cycle 300 is operated. However, the reliability of the compressor 210 is not lowered, and the refrigerating capacity is not lowered due to the decrease of the coefficient of performance.

  In addition, when the Rankine cycle 300 is operated independently, the respective cycles 200 and 300 form independent refrigerant circuits, so that refrigerant and lubricating oil accumulate from the Rankine cycle 300 side to the refrigeration cycle 200 side. In addition, the capability of the original Rankine cycle 300 can be fully exhibited, and the reliability of the expander 330 and the pump 310 can be reliably ensured.

  In general, the refrigerating apparatus 100 </ b> A capable of ensuring reliability and exhibiting sufficient performance for both cycles 200 and 300 can be obtained.

  In addition, during simultaneous operation of the refrigeration cycle and Rankine cycle, the expander rotational speed is reduced so that the expander pressure difference ΔP is equal to or greater than the predetermined differential pressure ΔPa, so that a sufficient expander differential pressure ΔP is ensured. Thus, the unstable Rankine cycle 300 can be prevented from operating, and a sufficient amount of power generated by the expander 330 can be obtained.

  In addition, since the pressure values detected by the two pressure sensors 301 and 302 are used in calculating the expander differential pressure ΔP, an easy and reliable response can be achieved.

  Further, the positions of the inlet part 220a and the outlet part 220b of the AC condenser 220 are set in the same region as the positions of the inlet part 340a and the outlet part 340b of the RA condenser 340, respectively, when viewed from the flow direction of the cooling air. Therefore, the AC refrigerant inflow region and the outflow region in the AC condenser 220 can have the same positional relationship as the RA refrigerant inflow region and the outflow region in the RA condenser 340, respectively. The temperature rise of the cooling air after passing through the AC condenser 220 is higher on the AC refrigerant inflow side and lowers toward the outflow side. Further, the temperature of the RA refrigerant in the RA condenser 340 is naturally lowered from the inflow portion side to the outflow portion side by heat exchange. Therefore, since the positional relationship in which the temperature distribution of the cooling air flowing into the RA condenser 340 and the RA refrigerant have the same tendency can be obtained, the temperature difference between the cooling air and the RA refrigerant can be made uniform as a whole. This enables effective heat dissipation in the RA condenser 340.

  Further, since the inlet portion 220a and the outlet portion 220b of the AC condenser 220 are opened toward the front side, the AC condenser 220 and the RA condenser are arranged in the piping of the AC refrigerant to the AC condenser 220. There is no need to provide piping between the condensers 340 and the dimensions between the condensers 220 and 340 are not deteriorated. In addition, the piping connection to the AC condenser 220 can be facilitated.

  Further, since the inlet portion 340a and the outlet portion 340b of the RA condenser 340 are opened in a direction orthogonal to the flow direction of the cooling air, the AC condenser is arranged in the routing of the RA refrigerant pipe to the RA condenser 340. Since piping is not disposed between 220 and the RA condenser 340, or piping is not disposed from the front side toward the rear side, the size between the condensers 220 and 340 is deteriorated. Alternatively, it is possible to prevent the front surface area of the AC condenser 220 from being reduced. Further, the piping connection to the RA condenser 340 can be facilitated.

  In the differential pressure drop suppression control according to the flowchart 1 shown in FIG. 6, after the expander rotational speed is controlled so that the expander differential pressure ΔP is equal to or higher than the predetermined differential pressure ΔPa, the expander differential pressure ΔP is further increased. It is preferable to control the expander rotation speed so as to achieve an appropriate expander differential pressure ΔPo, and an optimal power generation amount can always be obtained.

(Second Embodiment)
A second embodiment of the present invention is shown in FIGS. The second embodiment is obtained by changing the calculation method of the expander differential pressure ΔP with respect to the first embodiment.

  The basic configuration of the refrigeration apparatus 100B of the second embodiment is the same as that of the refrigeration apparatus 100A of the first embodiment. However, as shown in FIG. 7, the pressure sensor 302 is eliminated, and the AC condenser 220 and RA A temperature sensor (passing air temperature detecting means in the present invention) 101 for detecting the temperature of the cooling air passing between the condenser 340 (passing air temperature Tas) is provided. A temperature signal (passing air temperature Tas) detected by the temperature sensor 101 is output to the energization control circuit 50.

  Further, in the flowchart 2 for executing the differential pressure reduction suppression control, as shown in FIG. 8, steps S110 and S120 are changed to steps S111 and S121, respectively, with respect to the flowchart 1 of FIG. 6 described in the first embodiment. In addition, step S115 is added between step S111 and step S121.

  Next, the differential pressure reduction suppression control based on the flowchart 2 will be described. That is, the energization control circuit 50 reads the high-pressure side pressure PHr detected by the pressure sensor 301 and the passing air temperature Tas detected by the temperature sensor 101 in step S111 when the refrigeration cycle and Rankine simultaneous operation are executed in step S100. .

  In step S115, the low-pressure side pressure PLr is calculated. The calculation procedure will be described below. Step S115 is calculation means for calculating the low pressure side pressure PLr.

First, the heat absorption amount Qir that the heater 220 absorbs heat from the cooling water is estimated. Here, if the temperature efficiency of the heater 220 is Φh, the specific heat of the cooling water is Cw, the weight flow rate of the cooling water is Gw, the temperature of the cooling water is Tw, and the RA refrigerant temperature in the heater 220 is THr,
Qir = Φh · Cw · Gw · (Tw−THr)
Can be expressed as

Next, in the Rankine cycle 300, if the heat dissipation amount in the RA condenser 340 that balances the heat absorption amount Qir in the heater 320 is Qor,
Qor = A ・ Qir
Can be estimated as However, A is a coefficient corresponding to the driving force of the expander 330. For example, A = 0.9.

Next, the temperature efficiency of the RA condenser 340 is Φcr, the specific heat of the cooling air is Ca, the weight flow rate of the cooling air is Ga, the temperature of the RA refrigerant in the RA condenser 340 is TLr, and the cooling air flowing into the RA condenser 340 If the temperature, that is, the passing air temperature is Tas,
Qor = Φcr · Ca · Ga · (TLr-Tas)
Can be expressed as Therefore,
(Equation 1)
A · Φh · Cw · Gw · (Tw−THr) = Φcr · Ca · Ga · (TLr−Tas)
It becomes.

  The temperature efficiency Φh is determined according to the specification of the heater 220 to be set. The cooling water specific heat Cw is determined as a physical property value of the cooling water. The cooling water weight flow rate Gw can be estimated from the rotational speed of the hot water pump 22. The coolant temperature data relating to engine control can be used as the coolant temperature Tw. The RA refrigerant temperature THr can be estimated from the high pressure side pressure value (PHr) read in step S111.

  Further, the temperature efficiency Φcr is determined by the specification of the RA condenser 340 to be set. The cooling air specific heat Ca is determined as a physical property value of air. The cooling air weight flow rate Ga can be estimated from the vehicle speed and the operating state of the electric fan 260. As the passing air temperature Tas, the value read in step S111 is used.

  Therefore, the RA refrigerant temperature TLr can be calculated from Equation 1 and the above conditions, and the low pressure side pressure PLr in the RA condenser 340 can be calculated from the RA refrigerant temperature TLr.

  In step S121, the expander differential pressure ΔP is calculated from the difference between the high pressure side pressure PHr read in step S111 and the low pressure side pressure PLr calculated in step S115.

  Hereinafter, by performing Step S130 to Step S160, it is possible to execute the same differential pressure reduction suppression control as that of the first embodiment, so that the same effect as that of the first embodiment can be obtained.

  In the second embodiment, by providing the low-pressure side pressure calculating means in step S115, the pressure sensor 302 can be replaced with the temperature sensor 101 and the expander differential pressure ΔP can be calculated.

(Third embodiment)
A third embodiment of the present invention is shown in FIGS. In the second embodiment, the calculation method of the expander differential pressure ΔP is changed with respect to the first embodiment as in the second embodiment.

  The basic configuration of the refrigeration apparatus 100C of the third embodiment is the same as that of the refrigeration apparatus 100A of the first embodiment, but the pressure sensor 302 is abolished and flows into the AC condenser 220 as shown in FIG. There is provided a temperature sensor (inflow air temperature detecting means in the present invention) 102 for detecting the temperature of the cooling air (inflow air temperature Ta). A temperature signal (inflow air temperature Ta) detected by the temperature sensor 102 is output to the energization control circuit 50.

  Further, in the flowchart 3 for executing the differential pressure reduction suppression control, as shown in FIG. 10, steps S110 and S120 are changed to steps S112 and S122, respectively, with respect to the flowchart 1 of FIG. 6 described in the first embodiment. In addition, step S116 is added between step S112 and step S122.

  Next, the differential pressure reduction suppression control based on the flowchart 3 will be described. That is, the energization control circuit 50 reads the high-pressure side pressure PHr detected by the pressure sensor 301 and the inflow air temperature Ta detected by the temperature sensor 102 in step S112 when the refrigeration cycle and Rankine simultaneous operation are executed in step S100. .

  In step S116, the low pressure side pressure PLr is calculated. The calculation procedure will be described below. Step S116 is calculation means for calculating the low pressure side pressure PLr.

First, in the refrigeration cycle 200, if the required cooling capacity, that is, the heat dissipation amount in the AC condenser 220 that balances the heat absorption amount Qia in the evaporator 250 is Qoa,
B ・ Qoa = Qia
Can be estimated as However, B is a coefficient corresponding to the driving force of the compressor 210. For example, B = 0.7.

Next, the temperature efficiency of the AC condenser 220 is Φca, the specific heat of the cooling air is Ca, the weight flow rate of the cooling air is Ga, the passing air temperature of the cooling air after passing through the AC condenser 220 is Tas, and the AC condenser Since the inflow air temperature to 220 is Ta,
Qoa = Φca · Ca · Ga · (Tas-Ta)
Can be expressed as Therefore,
(Equation 2)
B · Φca · Ca · Ga · (Tas-Ta) = Qia
It becomes.

  The temperature efficiency Φca is determined by the specification of the AC condenser 220 to be set. The cooling air specific heat Ca is determined as a physical property value of air. The cooling air weight flow rate Ga can be estimated from the vehicle speed and the operating state of the electric fan 260. As the inflow air temperature Ta, the value read in step S112 is used. The endothermic amount Qia is calculated from the environmental conditions and the set temperature of the occupant.

  Therefore, the passing air temperature Tas can be calculated from Equation 2 and the above conditions.

  Hereinafter, the low pressure side pressure PLr can be calculated by performing the same calculation as step S115 of the second embodiment using the passing air temperature Tas calculated above.

  In step S122, the expander differential pressure ΔP is calculated from the difference between the high pressure side pressure PHr read in step S112 and the low pressure side pressure PLr calculated in step S116.

  Hereinafter, by performing Step S130 to Step S160, it is possible to execute the same differential pressure reduction suppression control as that of the first embodiment, so that the same effect as that of the first embodiment can be obtained.

  In the third embodiment, by providing the low-pressure side pressure calculating means in step S116, the expander differential pressure ΔP can be calculated by replacing the pressure sensor 302 with the temperature sensor 102.

(Fourth embodiment)
A fourth embodiment of the present invention is shown in FIG. In the fourth embodiment, the AC condenser 220 and the RA condenser 340 are provided with a duct 103 as an introduction flow path portion and a guide 104 as an opening adjustment portion in the first to third embodiments. Yes.

  The duct 103 is a wind guide plate member provided on both ends of the RA condenser 340 in the vehicle width direction, and is formed so as to expand from both ends of the RA condenser 340 toward the front side of the AC condenser 220. Has been. As shown by the broken arrow in FIG. 11, the duct 103 does not pass the cooling air from the front side of the AC condenser 220 through the AC condenser 220, and the duct 103 is connected between the AC condenser 220 and the RA condenser 340 on both ends. The cooling air is formed so as to be introduced into the RA condenser 340.

  Further, the guide 104 is provided on both ends of the AC condenser 220 in the vehicle width direction, and is formed as a plate-like member that is rotated in the vehicle width direction by the energization control circuit 50 around each end. Has been. As shown by the solid line in FIG. 11, when the guide 104 is rotated outward in the vehicle width direction, the opening area to the AC condenser 220 is enlarged and the cooling air to the AC condenser 220 is expanded. Increase inflow. On the other hand, when the guide 104 is rotated inward in the vehicle width direction, as shown by a broken line in FIG. 11, the flow path formed by the duct 103, that is, the AC condenser 220 and the RA condenser 340. The opening area of the flow path heading between the two is increased, and the amount of cooling air flowing into the RA condenser 340 is increased.

  In the fourth embodiment formed as described above, the turning position of the guide 104 is controlled by the energization control circuit 50 in accordance with the required heat radiation amount of the AC condenser 220 and the RA condenser 340. That is, in the independent operation of the refrigeration cycle, the guide 104 is controlled to rotate according to the necessary heat radiation amount of the AC condenser 220. By rotating the guide 104 outward in the vehicle width direction, the amount of cooling air flowing into the AC condenser 220 can be increased, and the heat dissipation performance of the AC condenser 220 can be improved. At this time, the guide 104 can prevent the cooling air that has once passed through the AC condenser 220 from flowing around and flowing into the AC condenser 220 again.

  Further, in the Rankine cycle single operation, the guide 104 is controlled to rotate according to the required heat radiation amount of the RA condenser 340. By rotating the guide 104 inward in the vehicle width direction, the amount of cooling air flowing into the RA condenser 340 without increasing the resistance of the AC condenser 220 is increased, and the heat radiation of the RA condenser 340 is increased. The performance can be improved.

  Further, in the simultaneous operation of the refrigeration cycle and the Rankine cycle, the guide 104 is controlled to rotate according to the necessary heat radiation amount of both the condensers 220 and 340. In this case, the heat dissipation performance in the RA condenser 340 can be improved by rotating the guide 104 inward in the vehicle width direction and allowing cooling air having the same outside air temperature to flow into the RA condenser 340.

  In this way, by adjusting the amount of cooling air flowing into the respective condensers 220 and 340 in accordance with the required heat radiation amount of the AC condenser 220 and the RA condenser 340, the respective condensers 220 and 340 Effective heat dissipation becomes possible.

(Fifth embodiment)
A fifth embodiment of the present invention is shown in FIGS. In the fifth embodiment, the front area of the AC condenser 220 is set to be smaller than the front area of the RA condenser 340, and the condensers 220 and 340 do not overlap each other (in FIGS. 12 and 13). A region) is formed.

  Here, by making the vertical dimension of the AC condenser 220 smaller than the vertical dimension of the RA condenser 340, a region where the two condensers 220 and 340 do not overlap is formed below the AC condenser 220. Yes.

  If the vertical dimension of the AC condenser 220 is simply reduced, the heat dissipation capability of the AC condenser 220 will be reduced. Therefore, here, as shown in FIG. By setting the (direction dimension) larger than the thickness dimension of the heat exchanging portion of the RA condenser 340, the heat radiation capability is ensured.

  Thereby, the cooling air equal to the outside air temperature that is not subjected to heat exchange in the AC condenser 220 can be directly flowed into the RA condenser 340, and the heat radiation capability in the RA condenser 340 can be improved.

  Here, by reducing the front area of the AC condenser 220, the heat exchange capacity is increased by increasing the thickness dimension D of the heat exchange part, and the front area of the AC condenser 220 is easily reduced.

(Other embodiments)
The setting positions of the pressure sensors 301 and 302 in the Rankine cycle 300 are not limited to the positions described in the first embodiment. The pressure sensor 301 may be provided in the high pressure side region, and may be provided between the pump 310 and the heater 320. Further, the pressure sensor 302 may be in the low pressure side region, and may be provided between the RA condenser 340 and the pump 310.

  Further, the setting positions and opening directions of the inlet portions 220a and 340a and the outlet portions 220b and 340b of the AC condenser 220 and the RA condenser 340 are not limited to the contents of the above embodiments, It is good also as a position and a direction.

  Further, the compressor 210 in the refrigeration cycle 200 is not limited to the engine driven compressor driven by the engine 10, but may be an electric compressor driven by an electric motor, or a hybrid compressor driven by an engine and an electric motor.

  In Rankine cycle 300, pump 310 is driven by electric motor 311, and generator 331 is connected to expander 330. However, electric motor 311 is abolished and generator 331 is replaced with an electric motor and a generator. As the motor generator having both functions, the pump 310 and the expander 330 may be connected to the motor generator.

  In this case, when operating the Rankine cycle 300, first, the motor generator is operated as an electric motor, and the pump 310 is driven. When sufficient waste heat from the engine 10 is obtained and the driving force in the expander 330 exceeds the power of the pump 310, the motor generator is operated as a generator to generate power.

  Thereby, a dedicated drive source for driving the pump 310 (the electric motor 311 in each of the above embodiments) can be eliminated, the configuration can be simplified, and the energy for driving the pump 310 can be reduced.

It is a schematic diagram which shows the whole system of a freezing apparatus provided with the waste heat utilization apparatus in 1st Embodiment. It is a side view which shows the mounting state of the condenser for freezing in the vehicle in 1st Embodiment, the condenser for Rankine, and the radiator. It is a perspective view which shows the inlet part and outlet part of each refrigerant | coolant of the freezing condenser and Rankine condenser in 1st Embodiment. It is a perspective view which shows the piping connection direction with each refrigerant | coolant of a refrigeration condenser in 1st Embodiment, a condenser for Rankine, and a radiator, the inlet part of a cooling water, and an outlet part. It is a control characteristic figure which shows the operation mode with respect to the refrigerant pressure of the electric fan in a 1st embodiment. It is a flowchart which shows the control method in the case of performing simultaneous operation of the refrigerating cycle and Rankine cycle in 1st Embodiment. It is a schematic diagram which shows the whole system of a freezing apparatus provided with the waste heat utilization apparatus in 2nd Embodiment. It is a flowchart which shows the control method in the case of performing simultaneous operation of the refrigerating cycle and Rankine cycle in 2nd Embodiment. It is a schematic diagram which shows the whole system of a freezing apparatus provided with the waste heat utilization apparatus in 3rd Embodiment. It is a flowchart which shows the control method in the case of performing the simultaneous driving | operation of the refrigerating cycle and Rankine cycle in 3rd Embodiment. It is a top view which shows the duct and guide in 4th Embodiment. It is a perspective view which shows the condenser for freezing in 5th Embodiment, and the condenser for Rankine. It is a perspective view for supplementary explanation showing a freezing condenser and a Rankine condenser in a fifth embodiment.

Explanation of symbols

10 Engine (heat engine)
50 Energization control circuit (control means)
100A to 100C Refrigeration apparatus including waste heat utilization apparatus 101 Temperature sensor (passing air temperature detection means)
102 Temperature sensor (inflow air temperature detection means)
103 Duct (Introduction channel)
104 Guide (Opening adjustment part)
200 Refrigeration cycle 210 Compressor 220 Refrigeration condenser 240 Expansion valve 250 Evaporator 300 Rankine cycle 301 Pressure sensor (high pressure side pressure detection means)
302 Pressure sensor (low pressure side pressure detection means)
310 Pump 320 Heater 330 Expander 340 Rankine Condenser

Claims (13)

Mounted on the vehicle,
A refrigeration cycle (200) in which a compressor (210), a refrigeration condenser (220), an expansion valve (240), and an evaporator (250) are annularly connected to circulate a refrigeration refrigerant;
The pump (310), the heater (320) using the waste heat of the heat engine (10) of the vehicle as a heating source, the expander (330), and the Rankine condenser (340) are connected in a ring shape to provide a Rankine refrigerant. In a refrigeration apparatus comprising a waste heat utilization device having a Rankine cycle (300) through which
The refrigeration condenser (220) and the Rankine condenser (340) are arranged in series in a predetermined part of the vehicle with respect to the flow direction of the external air for cooling, and the refrigeration condenser (220). ) Is disposed on the upstream side of the external air with respect to the Rankine condenser (340), a refrigeration apparatus including a waste heat utilization apparatus. Control means (50) for controlling the operation of the refrigeration cycle (200) and the Rankine cycle (300),
When the control means (50) operates the refrigeration cycle (200) and the Rankine cycle (300) simultaneously, an expander differential pressure (ΔP) of the Rankine refrigerant in the expander (330) is predetermined. The refrigerating apparatus provided with the waste heat utilization apparatus according to claim 1, wherein the rotation speed of the expander (330) is controlled so as to be equal to or greater than a value (ΔPa).   The said control means (50) reduces the rotation speed of the said expander (330), when the said expander differential pressure ((DELTA) P) is smaller than the said predetermined value ((DELTA) Pa). A refrigeration system equipped with a waste heat utilization device.   The said control means (50) controls the rotation speed of the said expander (330) so that the said expander differential pressure ((DELTA) P) may become a value from which the predetermined appropriate expansion ratio is obtained. A refrigeration apparatus comprising the waste heat utilization apparatus according to Item 2. High pressure side pressure detection means (301) disposed in a high pressure side region extending from the downstream side of the pump (310) to the upstream side of the expander (330) and detecting the high pressure side pressure (PHr) of the Rankine refrigerant. )When,
Low pressure side pressure detection means (302) disposed in a low pressure side region extending from the downstream side of the expander (330) to the upstream side of the pump (310) and detecting the low pressure side pressure (PLr) of the Rankine refrigerant. )
The control means (50) is configured to control the expansion unit (330) based on a difference (PHr-PLr) between the high pressure side pressure (PHr) indicating the expander differential pressure (ΔP) and the low pressure side pressure (PLr). A refrigerating apparatus comprising the waste heat utilization apparatus according to any one of claims 2 to 4, wherein the number of rotations is controlled. High pressure side pressure detection means (301) disposed in a high pressure side region extending from the downstream side of the pump (310) to the upstream side of the expander (330) and detecting the high pressure side pressure (PHr) of the Rankine refrigerant. )When,
It is disposed between the refrigeration condenser (220) and the Rankine condenser (340), and detects the passing air temperature (Tas) of the external air passing between the condensers (220, 340). Passing air temperature detecting means (101),
The amount of heat radiation (Qor) in the Rankine condenser (340) that balances the amount of heat absorbed (Qir) to the heater (320) due to the waste heat, and the external air passing through the Rankine condenser (340). Amount (Ga), the passing air temperature (Tas) detected by the passing air temperature detecting means (101), the Rankine refrigerant temperature (TLr) in the Rankine condenser (340), and the low pressure side Calculating means (S115) for calculating the pressure (PLr),
The control means (50) is configured to control the expansion unit (330) based on a difference (PHr-PLr) between the high pressure side pressure (PHr) indicating the expander differential pressure (ΔP) and the low pressure side pressure (PLr). A refrigerating apparatus comprising the waste heat utilization apparatus according to any one of claims 2 to 4, wherein the number of rotations is controlled. High pressure side pressure detection means (301) disposed in a high pressure side region extending from the downstream side of the pump (310) to the upstream side of the expander (330) and detecting the high pressure side pressure (PHr) of the Rankine refrigerant. )When,
Inflow air temperature detection means (102) for detecting the inflow air temperature (Ta) of the external air before flowing into the refrigeration condenser (220) and the Rankine condenser (340);
The amount of heat radiation (Qoa) in the refrigeration condenser (220) that balances the required cooling capacity (Qia) in the evaporator (250), the amount of the external air that passes through the refrigeration condenser (220) ( Ga), calculating the passing air temperature (Tas) of the external air after passing through the refrigeration condenser (220) from the inflowing air temperature (Ta) detected by the inflowing air temperature detection means (102), and The amount of heat radiation (Qor) in the Rankine condenser (340) that balances the heat absorption amount (Qir) to the heater (320) due to waste heat, and the external air passing through the Rankine condenser (340). Calculation for calculating the temperature (TLr) of the Rankine refrigerant in the Rankine condenser (340) and further the low pressure side pressure (PLr) from the amount (Ga) and the passing air temperature (Tas). And a stage (S116),
The control means (50) is configured to control the expansion unit (330) based on a difference (PHr-PLr) between the high pressure side pressure (PHr) indicating the expander differential pressure (ΔP) and the low pressure side pressure (PLr). A refrigerating apparatus comprising the waste heat utilization apparatus according to any one of claims 2 to 4, wherein the number of rotations is controlled.   The position at which the inlet portion (220a) and the outlet portion (220b) for the refrigerant for refrigeration with respect to the condenser (220) for refrigeration are disposed as viewed from the flow direction of the external air. 340) in the same region as the position where the inlet (340a) and outlet (340b) for Rankine refrigerant are disposed. A refrigeration apparatus comprising the waste heat utilization apparatus described in 1. From the upstream side of the external air of the refrigeration condenser (220), the external air passes between the refrigeration condenser (220) and the Rankine condenser (340) and enters the Rankine condenser (340). An introduction flow path section (103) that enables introduction of
By being controlled and moved by the control means (50), an opening adjusting section (104) for adjusting an opening area toward the refrigeration condenser (220) side and an opening area toward the introduction flow path section (103) side. A refrigeration apparatus comprising the waste heat utilization apparatus according to any one of claims 1 to 8.   A front area of the refrigeration condenser (220) is smaller than a front area of the Rankine condenser (340), and the refrigeration condenser (340) is disposed upstream of the external air. A refrigerating apparatus comprising the waste heat utilization apparatus according to any one of claims 1 to 9, wherein an area where the condenser (220) does not overlap is provided.   The dimension of the external air flow direction of the refrigeration condenser (220) is set larger than the dimension of the external air flow direction of the Rankine condenser (340). A refrigeration system equipped with a waste heat utilization device.   The inlet portion (220a) and the outlet portion (220b) of the refrigerant for freezing in the condenser for freezing (220) are configured to open toward the upstream side in the flow direction of the external air. A refrigeration apparatus comprising the waste heat utilization apparatus according to any one of claims 1 to 11.   The inlet part (340a) and the outlet part (340b) of the Rankine refrigerant in the Rankine condenser (340) are opened in a direction orthogonal to the flow direction of the external air. A refrigeration apparatus comprising the waste heat utilization apparatus according to any one of claims 1 to 12.

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