JP2006125340A - Composite fluid machine and refrigerator using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide composite fluid machine capable of eliminating influence of a pump when operated only by a compressor while enabling operation of the pump by an expander and utilizing exhaust heat effectively when operation of the compressor is unnecessary, and to provide a refrigerator using the machine. <P>SOLUTION: This composite fluid machine has the compressor 110 for compressing fluid and discharging it, the expander 110 for generating driving force by expansion of working fluid circulated by the pump 130, and a rotary electric machine 120 having both functions of a power generator and an electric motor. The compressor 110, the expander 110, the rotary electric machine 120, and the pump 130 are connected in series. An intermittent switching means 140 for switching a connection condition of the rotary electric machine 120 and the pump 130 into a disconnected condition when the compressor 110 is driven by the rotary electric machine 120 is provided. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a composite fluid machine having a function of an expander that outputs mechanical energy by expansion of a working fluid in a Rankine cycle in a compressor that compresses and discharges a fluid, and a refrigeration apparatus using the same. .

  Conventionally, as shown in Patent Document 1, for example, a complex fluid machine (a rolling piston type rotating machine in Patent Document 1) in which a compressor, an expander, a drive motor, and a circulation pump are integrally provided is known. . Each of the above devices is arranged in series and connected on the same axis (the compressor and the expander are connected via a connecting means such as a magnet coupling or directly connected). The compressor is used for compressing the refrigerant in the refrigeration cycle, for example, and the expander is driven by the working fluid in the Rankine cycle.

Regarding the specific operation of the above composite fluid machine, the expander is driven by the drive motor for an initial fixed time (the time until the expander enters a stable state), and the working fluid in the Rankine cycle (the burner is turned on). It is driven by the expansion of a high-temperature, high-pressure gas (heated as a heating source), and generates a driving force on its own shaft. This driving force is transmitted to the compressor via the magnet coupling (or directly), and the compressor is operated. The compressor compresses the refrigerant in the refrigeration cycle. The circulation pump is driven by the driving force generated from the expander, and circulates the working fluid in the Rankine cycle without using a dedicated motor or the like.
JP-A-8-86289

  However, the above complex fluid machine requires a heating source such as a burner in the Rankine cycle, and the expander is driven by the heat energy of the burner (burning dedicated fuel). ing. In light of global warming, which has been a problem in recent years, the present inventors have effectively used waste heat from a heat-generating device such as an internal combustion engine for a vehicle, in mind, how to reduce energy consumption. We are studying a composite fluid machine that can be used.

  Therefore, when the complex fluid machine disclosed in Patent Document 1 is used to operate the expander from waste heat, when there is little waste heat depending on the situation of the heat generating device, the driving force in the expander is Since it cannot be obtained, it is conceivable to drive the compressor with a drive motor. However, at this time, since the circulation pump connected to the same shaft also rotates together, it becomes an operating resistance for the drive motor, and the compressor cannot be operated efficiently.

  Also, even if there is enough waste heat from the heat generating equipment, it is necessary to stop the expander when the compressor operation is not required (when the refrigeration cycle is not required), and the waste heat can be used effectively. Can not do it.

  In view of the above problems, an object of the present invention is to enable operation of a pump by an expander in a compressor having a compressor for a refrigeration cycle and an expander driven by waste heat of a heat generating device such as an internal combustion engine. It is another object of the present invention to provide a composite fluid machine that eliminates the influence of a pump when operated by a compressor alone and enables effective use of waste heat even when the compressor is not required to operate, and a refrigeration apparatus using the same. .

  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 (110) that compresses and discharges the fluid, the expander (110) that generates a driving force by the expansion of the working fluid circulated by the pump (130), and the generator And a rotary electric machine (120) having both functions of an electric motor, and a compressor (110), an expander (110), a rotary electric machine (120), and a pump (130) are connected in series. 110) is provided with intermittent switching means (140) that can switch the connection state between the rotating electrical machine (120) and the pump (130) to the disconnected state when driven by the rotating electrical machine (120). Yes.

  Thus, the pump (130) can be driven by the driving force when the expander (110) is operated, and a dedicated drive source for operating the pump (130) can be dispensed with. The compressor (110) can be operated by the rotating electrical machine (120) regardless of the presence or absence of the expansion energy of the fluid. At this time, since the pump (130) is disconnected from the rotating electrical machine (120) by the intermittent switching means (140), the pump (130) can be prevented from becoming an operating resistance of the rotating electrical machine (120). Furthermore, when the expansion of the working fluid is sufficiently obtained, but the operation of the compressor (110) is unnecessary, the rotating electricity (120) is operated as a generator by the driving force of the expander (110) to generate power. And expansion energy can be regenerated as electrical energy.

  Here, when the compressor (110) is driven by the rotating electrical machine (120) using the complex fluid machine (100) according to claim 1, the expander (110) connected to the same shaft is also a friend. Since it rotates together, the expander (110) acts as an operating resistance for the rotating electrical machine (120), and the compressor (110) cannot be operated efficiently.

  Therefore, in the invention according to claim 2, the compressor (110) is provided with the high pressure chamber (116, 117d) by the switching means (116, 117d) for switching the flow path between the working chamber (V) and the high pressure chamber (114). 114), when the working fluid flows in, the expander / compressor (110) functions as the expander (110).

  As a result, when the expander / compressor (110) is operated as the compressor (110) by the rotating electrical machine (120), the expander (110) can be made nonexistent, as described above. The expander (110) does not become an operating resistance of the rotating electrical machine (120).

  In invention of Claim 3, the pump (130) is arrange | positioned at the one end side to which a compressor (110), an expander (110), an electric motor (120), and a pump (130) are connected in series, The intermittent switching means (140) is provided between the pump (130) and the adjacent device (120) adjacent to the pump (130).

  Thus, the intermittent switching means (140) can be easily provided without providing a complicated shaft structure regardless of the arrangement of the devices (110, 110, 120) except the pump (130). Can do.

  In the invention according to claim 4, when the expander (110) is to rotate in the reverse direction with respect to the compressor (110), the intermittent switching means (140) is provided with the pump shaft of the pump (130). The one-way clutch (140) disengaged in the rotational operation direction of the compressor (110) and meshed in the rotational operation direction of the expander (110) between the shaft (124) and the shaft (124) of the adjacent device (120). ).

  Further, as in the fifth aspect of the present invention, the intermittent switching means (140) includes an electric signal between the pump shaft (134) of the pump (130) and the shaft (124) of the adjacent device (120). It is good also as an electromagnetic clutch interrupted by.

  In this case, even when the pump (130) is driven by the operation of the expander (110), the pump (130) can be turned on and off by the engagement of the electromagnetic clutch, and the flow rate of the working fluid can be controlled. .

  The invention according to claim 6 further includes a shaft seal device (150) that prevents leakage of fluid or working fluid between the pump (130) and the adjacent device (120), and the shaft seal device (150) is a pump. It is characterized by being provided on the shaft (134).

  Thereby, when the pump (130) is disconnected by the one-way clutch (140) or the electromagnetic clutch, the shaft seal device (150) can be prevented from becoming an operating resistance of the rotating electrical machine (120).

  In the invention according to claim 6, the outer diameter of the pump shaft (134) at the site where the shaft seal device (150) is provided as in the invention according to claim 7 is set smaller than the general site. Is good.

  The loss caused by the shaft seal device (150) during the operation of the pump (130) is due to the tightening force of the shaft seal device (150) on the pump shaft (134) and the outside of the pump shaft (134) that contacts the shaft seal device (150). It is proportional to the rotation speed of the diameter part. Therefore, by reducing the outer diameter of the pump shaft (134) where the shaft seal device (150) is provided, the rotational speed can be reduced and the loss can be reduced.

  The composite fluid machine (100) according to the first to seventh aspects is formed as the condenser (31) in the refrigeration cycle (30) as in the invention according to the eighth aspect. It is suitable for application to a refrigeration apparatus including a Rankine cycle (40) using the waste heat of the heat generating device (10) as a heating source. At this time, the compressor (110) is used for the refrigeration cycle (30), and the pump (130) and the expander (110) are used for the Rankine cycle (40).

  And like invention of Claim 9, a heat-emitting device (10) is suitable for heat engine (10) object.

  Incidentally, the reference numerals in parentheses of each means described above are an example showing the correspondence with the specific means described in the embodiments described later.

(First embodiment)
In the present embodiment, the composite fluid machine (heat medium pump integrated expansion generator / electric compressor) 100 of the present invention is used as a refrigeration apparatus 1 for a vehicle in which the refrigeration cycle 30 including the Rankine cycle 40 is applied.

  First, the configuration of the composite fluid machine 100 will be described with reference to FIG. The complex fluid machine 100 includes an expander / compressor 110 having both functions of a compressor and an expander, and a motor generator having both functions of a generator and an electric motor (adjacent equipment to the rotating electrical machine and the heat medium pump 130 in the present invention). 120) and a heat medium pump (corresponding to the pump in the present invention) 130.

  The expander / compressor 110 has the same structure as a known scroll-type compression mechanism. Specifically, the expander / compressor 110 is fixed to the fixed scroll 112 fixed between the front housing 111 and the motor housing 121, The revolving scroll 113 that turns and opposes, a discharge port 115 that allows the working chamber V and the high pressure chamber 114 to communicate with each other, a valve mechanism 117 that opens and closes the inflow port 116, and the like.

  The fixed scroll 112 includes a plate-like substrate portion 112a and a spiral tooth portion 112b that protrudes from the substrate portion 112a toward the orbiting scroll 113. On the other hand, the orbiting scroll 113 contacts the tooth portion 112b. The swirl-shaped tooth portion 113b and the base plate portion 113a on which the tooth portion 113b is formed are configured, and the orbiting scroll 113 is swung while the both tooth portions 112b and 113b are in contact with each other. The volume of the working chamber V formed by both scrolls 112 and 113 is enlarged or reduced.

  The shaft 118 is a crankshaft that is rotatably supported by a bearing 118 c fixed to the motor housing 121 and has a crank portion 118 a that is eccentric with respect to the rotation center axis at one longitudinal end portion. The crank portion 118a is connected to the orbiting scroll 113 via a bushing 118b and a bearing 113c.

  Further, the rotation prevention mechanism 119 makes the orbiting scroll 113 rotate once around the crank portion 118a while the shaft 118 rotates once. For this reason, when the shaft 118 rotates, the orbiting scroll 113 revolves around the rotation center axis of the shaft 118 without rotating. The working chamber V changes such that, for example, when the shaft 118 rotates in the forward direction, the volume of the orbiting scroll 113 decreases as the displacement from the outer diameter side to the center side of the orbiting scroll 113 decreases. When rotating in the direction, the volume of the orbiting scroll 113 changes so as to increase as it is displaced from the center side to the outer diameter side.

  The discharge port 115 is provided at the center of the substrate portion 112a, and when the expander / compressor 110 operates as a compressor (hereinafter, in the compression mode), the working chamber V and the front housing 111 have a minimum volume. This is a port for discharging a compressed refrigerant (corresponding to the fluid in the present invention) by communicating with the high-pressure chamber 114 provided in. Similarly, the inflow port 116 is provided in the substrate portion 112a (adjacent to the discharge port 115), and when the expander / compressor 110 operates as an expander (hereinafter, in the expansion mode), the high-pressure chamber. 114 is a port that leads the working chamber V to a high-temperature, high-pressure refrigerant introduced into the high-pressure chamber 114, that is, a superheated vapor refrigerant (corresponding to the working fluid in the present invention). .

  The high-pressure chamber 114 has a function of a discharge chamber that smoothes the pulsation of the refrigerant discharged from the discharge port 115, and is connected to the heater 43 and the condenser 31 side described later. A high-pressure port 111a is provided.

  Note that a low pressure port 121a connected to the evaporator 34 and the second bypass flow path 42 described later is provided in the motor housing 121 and communicates with the fixed scroll 112 side through the motor housing 121. .

  The valve mechanism 117 includes a discharge valve 117a, a valve body 117d, an electromagnetic valve 117f, and the like. The discharge valve 117a is a reed valve-like check valve that is disposed on the high-pressure chamber 114 side of the discharge port 115 and prevents the refrigerant discharged from the discharge port 115 from flowing back from the high-pressure chamber 114 to the working chamber V. The stopper 117b is a valve stop plate that regulates the maximum opening of the discharge valve 117a, and the discharge valve 117a and the stopper 117b are fixed to the substrate portion 112a by bolts 117c.

  The valve body 117d is a switching valve that opens and closes the inflow port 116 to switch between the compression mode and the expansion mode of the expander / compressor 110, and a rear end side thereof along the back pressure chamber 117e provided in the front housing 111, It is slidably arranged. A spring (elastic means) 117f is inserted in the back pressure chamber 117e, and the spring 117f applies an elastic force in a direction in which the distal end side of the valve body 117d closes the inflow port 116. Further, the front housing 111 is provided with a throttle 117g as a resistance means having a predetermined passage resistance and allowing the back pressure chamber 117e and the high pressure chamber 114 to communicate with each other.

  The electromagnetic valve 117h is a control valve that controls the pressure in the back pressure chamber 117e by controlling the communication state between the low pressure port 121a side and the back pressure chamber 117e, and is controlled by a control device (not shown).

  When the electromagnetic valve 117h is opened, the pressure in the back pressure chamber 117e is lowered from the high pressure chamber 114, and the valve body 117d is displaced to the right in FIG. 1 while pushing and contracting the spring 117f, so that the inflow port 116 is opened. Since the pressure loss at the throttle 117g is very large, the amount of refrigerant flowing from the high pressure chamber 114 into the back pressure chamber 117e is so small that it can be ignored.

  Conversely, when the electromagnetic valve 117h is closed, the pressure in the back pressure chamber 117e and the pressure in the high pressure chamber 114 are equalized by the throttle 117g, and the valve body 117d is displaced to the left in FIG. 1 by the elastic force of the spring 117f. Inflow port 116 is closed. That is, a pilot-type electric on-off valve that opens and closes the inflow port 116 is configured by the valve body 117d, the back pressure chamber 117e, the spring 117f, the throttle 117g, the electromagnetic valve 117h, and the like. The inflow port 116 and the valve body 117d correspond to switching means for switching the flow path between the working chamber V and the high pressure chamber 114 in the present invention.

  The motor generator 120 includes a stator 122 and a rotor 123 that rotates in the stator 122, and is housed in a motor housing 121 (low pressure side atmosphere of the expander / compressor 110) fixed to the fixed scroll 112. . The stator 122 is a stator coil wound with a winding, and is fixed to the inner peripheral surface of the motor housing 121. The rotor 123 is a magnet rotor in which a permanent magnet is embedded, and is fixed to the motor shaft 124. One end side of the motor shaft 124 is connected to the shaft 118 of the expander / compressor 110, and the other end side is provided with a hole 124a. It is connected to 130 pump shafts 134.

  When electric power is supplied to the stator 122 from the battery 13 to be described later via the inverter 12, the motor generator 120 rotates the rotor 123 (rotates in the forward direction), and causes the expander / compressor 110 to operate ( Acts as a driving motor (electric motor). Alternatively, the rotor 123 is rotated (reversely rotated) to operate as a motor (electric motor) that drives a heat medium pump 130 described later. Further, when a torque for rotating the rotor 123 is input by the driving force generated during the expansion mode of the expander / compressor 110 (during reverse rotation), the generator operates as a generator (generator) that generates electric power. The obtained power is charged into the battery 13 via the inverter 12.

  The heat medium pump 130 is disposed adjacent to the motor generator 120 on the side opposite to the expander and is housed in a pump housing 131 that is fixed to the motor housing 121. Similar to the expander / compressor 110, the heat medium pump 130 includes a fixed scroll 132 including a base plate portion 132a and a tooth portion 132b, and a revolving scroll 133 including a base plate portion 133a and a tooth portion 133b. The fixed scroll 132 is fixed to the pump housing 131, and the orbiting scroll 133 is disposed in a space formed by the pump housing 131 and the fixed scroll 132. The orbiting scroll 133 is capable of revolving while being prevented from rotating by the rotation preventing mechanism 135.

  The pump housing 131 is provided with an inflow port 131a that is connected from the gas-liquid separator 32 side described later and communicates with the inside of the pump housing 131 and the orbiting scroll 133 side. Further, the fixed scroll 132 is provided with a discharge port 132c connected from the working chamber P formed by the scrolls 132 and 133 to the heater 43 described later.

  The pump shaft 134 is rotatably supported by a bearing 134c fixed to the pump housing 131. The pump shaft 134 has a crank portion 134a that is eccentric with respect to the rotation center shaft at one longitudinal end, and has a bushing 134b and a bearing 133c. Via the orbiting scroll 133. The other longitudinal end of the pump shaft 134 is formed as a small-diameter portion 134d having a small outer diameter with respect to the general portion (portion supported by the bearing 134c), and the small-diameter portion 134d is a motor. The shaft 124 is inserted into the hole 124a.

  A one-way clutch (corresponding to the intermittent switching means in the present invention) 140 is provided between the motor shaft 124 and the pump shaft 134 (small diameter portion 134d). The one-way clutch 140 rotates the pump shaft 134 by meshing with the pump shaft 134 (small-diameter portion 134d) when the motor shaft 124 rotates in the reverse direction (rotation in the expansion mode). When rotating in the forward direction (rotation in the compression mode), the engagement with the pump shaft 134 (small diameter portion 134d) is disengaged, and the motor shaft 124 and the pump shaft 134 are disconnected (the pump shaft 134 is not rotated). Yes.

  Further, a shaft seal device is provided between the pump housing 131 and the small diameter portion 134d of the pump shaft 134 to seal between the motor generator 120 and the heat medium pump 130 (low pressure side connected to the orbiting scroll 133 from the inflow port 131a). Shaft seal 150 is provided.

  The complex fluid machine 100 configured as described above is incorporated in the refrigeration cycle 30 including the Rankine cycle 40 to form the refrigeration apparatus 1. Specifically, an expander / compressor 110 (compressor in compression mode) is incorporated in the refrigeration cycle 30, and the expander / compressor 110 (expander in expansion mode) and the heat medium pump 130 It is designed to be incorporated in the Rankine cycle 40. Hereinafter, the refrigeration apparatus 1 will be described with reference to FIG.

  The refrigeration cycle 20 moves the heat on the low temperature side to the high temperature side and uses the heat and heat for air conditioning. The expander / compressor 110, the condenser 31, the gas-liquid separator 32, the decompressor 33, the evaporator 34 and the like are connected in a ring shape.

  The condenser 31 is a heat exchanger that is provided on the refrigerant discharge side of the expander / compressor 110 in the compression mode and cools the refrigerant compressed to high temperature and high pressure to condense and liquefy it. The fan 31a sends cooling air (air outside the passenger compartment) to the condenser 31.

  The gas-liquid separator 32 is a receiver that separates the refrigerant condensed in the condenser 31 into a gas-phase refrigerant and a liquid-phase refrigerant and causes the liquid-phase refrigerant to flow out. The decompressor 33 decompresses and expands the liquid-phase refrigerant separated by the gas-liquid separator 32. In the present embodiment, the decompressor 33 decompresses the refrigerant in an enthalpy manner, and the expander / compressor 110 in the compression mode. A temperature-type expansion valve that controls the throttle opening is employed so that the degree of superheat of the sucked refrigerant becomes a predetermined value.

  The evaporator 34 is a heat exchanger that exerts an endothermic effect by evaporating the refrigerant decompressed by the decompressor 33, and cools the outside air (outside air) or the inside air (inside air) supplied by the fan 34a. To do. On the refrigerant outflow side of the evaporator 34, a check valve 34b that allows the refrigerant to flow only from the evaporator 34 side to the expander / compressor 110 side is provided.

  The Rankine cycle 40 generates energy (driving force in the expansion mode of the expander / compressor 110) from waste heat generated in the engine 10 (which corresponds to the heat generating device and the heat engine in the present invention) that generates vehicle driving power. It is to be collected. In the Rankine cycle 40, the condenser 31 is shared with the refrigeration cycle 30, and the gas-liquid separator 32 and the expander / compressor 110 and the condenser 31 are bypassed so as to bypass the condenser 31 ( The first bypass flow path 41 connected to the point A), and between the expander / compressor 110 and the check valve 34b (point B) to between the condenser 31 and the point A (point C). 2 bypass flow paths 42 are provided and formed as follows.

  That is, the first bypass flow path 41 is provided with the heat medium pump 130 of the composite fluid machine 100 and a check that allows the refrigerant to flow only from the gas-liquid separator 32 side to the heat medium pump 130 side. A valve 41a is provided. A heater 43 is provided between the point A and the expander / compressor 110.

  The heater 43 is a heat exchanger that heats the refrigerant by exchanging heat between the refrigerant sent from the heat medium pump 130 and the engine coolant (hot water) of the hot water circuit 20 in the engine 10. The case where the engine cooling water flowing out from the engine 10 is circulated to the heater 43 and the case where it is not circulated are switched. The flow path switching of the three-way valve 21 is performed by a control device (not shown).

  Incidentally, the engine 10 is provided with an alternator 11 that is driven by the driving force of the engine 10 to generate electric power, and the electric power generated by the alternator 11 is charged to the battery 13 via the inverter 12. Yes.

  The water pump 22 is a pump that circulates engine coolant in the hot water circuit 20 (for example, a mechanical pump driven by the engine 10), and the radiator 23 exchanges heat between the engine coolant and the outside air. It is a heat exchanger that cools engine coolant.

  The second bypass passage 42 is provided with a check valve 42 a that allows the refrigerant to flow only from the expander / compressor 110 side to the refrigerant inlet side of the condenser 31. An on-off valve 44 is provided between the points A and C. The on-off valve 44 is an electromagnetic valve that opens and closes the refrigerant flow path, and is controlled by a control device (not shown).

  A Rankine cycle 40 is formed by the gas-liquid separator 32, the first bypass passage 41, the heat medium pump 130, the heater 43, the expander / compressor 110, the second bypass passage 42, the condenser 31, and the like. .

  Next, the operation of the composite fluid machine 100 in this embodiment and the operation and effect thereof will be described.

1. Compression mode In this mode, when cooling by the refrigeration cycle 30 is necessary, the motor generator 120 is operated as a motor, and a rotational force (forward rotation) is applied to the motor shaft 124 to thereby turn the scroll 113 of the expander / compressor 110. Is an operation mode in which the refrigerant is sucked and compressed.

  Specifically, a control device (not shown) opens the on-off valve 44 and prevents the engine coolant from circulating to the heater 43 side by switching the three-way valve 21. In addition, with the electromagnetic valve 117h closed and the inflow port 116 closed with the valve body 117d, electric power is supplied from the battery 13 and the inverter 12 to the stator 122 of the motor generator 120 to rotate the motor shaft 124.

  At this time, like the well-known scroll compressor, the expander / compressor 110 sucks the refrigerant from the low pressure port 121a and compresses it in the working chamber V, and then compresses the refrigerant from the discharge port 115 to the high pressure chamber 114. And the refrigerant compressed from the high pressure port 111c is discharged to the condenser 31 side.

  The refrigerant discharged from the high-pressure port 111c is heated by the heater 43 → the on-off valve 44 → the condenser 31 → the gas-liquid separator 32 → the decompressor 33 → the evaporator 34 → the check valve 34b → the expander / compressor 110. Circulation is performed in the order of the low-pressure port 121a (circulation through the refrigeration cycle 30), and cooling by heat absorption of the evaporator 34 is performed. Since the engine cooling water does not circulate in the heater 43, the refrigerant is not heated in the heater 43, and the heater 43 functions as a simple refrigerant flow path.

  Further, since the pump shaft 134 (small diameter portion 134d) of the heat medium pump 130 is disengaged from the motor shaft 124 by the one-way clutch 140, the heat medium pump 130 is stopped.

2. Expansion Mode In this mode, when cooling by the refrigeration cycle 30 is unnecessary, when the waste heat of the engine 10 is sufficiently obtained (the engine coolant temperature is sufficiently high), the high-pressure superheated steam refrigerant heated by the heater 43 is removed. This is an operation mode in which the orbiting scroll 113 is rotated to rotate the motor shaft 124 by introducing it into the expander / compressor 110 to expand, thereby obtaining a driving force (mechanical energy). In addition, the rotor 123 of the motor generator 120 is rotated by the obtained driving force to generate electric power, and the generated electric power is charged in the battery 13.

  Specifically, a control device (not shown) closes the on-off valve 34 and causes the engine cooling water to circulate to the heater 43 side by switching the three-way valve 21. Further, the motor generator 120 is operated as a motor (reverse rotation), the electromagnetic valve 117h is opened, and the inflow port 116 is opened by the valve body 117d.

  At this time, the pump shaft 134 (small diameter portion 134d) of the heat medium pump 130 is engaged with the motor shaft 124 by the one-way clutch 140, and the heat medium pump 130 is driven. Then, the high-pressure superheated vapor refrigerant heated by the heater 43 is introduced into the working chamber V via the high-pressure port 111a, the high-pressure chamber 114, and the inflow port 116 to expand. Due to the expansion of the superheated steam refrigerant, the turning scroll 113 turns in the opposite direction to that in the compression mode, and the driving force applied to the shaft 118 is transmitted to the motor shaft 124 and the rotor 123 of the motor generator 120. When the driving force transmitted to the motor shaft 124 exceeds the driving force for driving the heat medium pump 130, the motor generator 120 operates as a generator, and the obtained electric power is supplied to the battery via the inverter 12. 13 is charged.

  And the refrigerant | coolant which the pressure fell after finishing expansion flows out out of the low voltage | pressure port 121a. The refrigerant flowing out from the low-pressure port 121a is second bypass channel 42 → check valve 42a → condenser 31 → gas-liquid separator 32 → first bypass channel 41 → check valve 41a → heating medium pump 130 → heating. It circulates in order of the unit 43 → the expander / compressor 110 (high pressure port 111c) (circulates the Rankine cycle 40). The heat medium pump 130 is pressurized to a pressure corresponding to the temperature of the superheated steam refrigerant generated by being heated by the heater 43 and sends the liquid phase refrigerant from the gas-liquid separator 32 to the heater 43.

  As described above, in the composite fluid machine 100 of the present invention, the compression mode of the expander / compressor 110 by the motor generator 120 is possible regardless of the presence or absence of the expansion energy of the refrigerant. At this time, since the heat medium pump 130 is disconnected from the motor generator 120 by the one-way clutch 140, the heat medium pump 130 can be prevented from becoming an operating resistance of the motor generator 120.

  Since the expander / compressor 110 is used as both the compressor (110) and the expander (110), the expander (110) is in the compression mode of the expander / compressor 110 by the motor generator 120. ) Does not exist, the expander (110) does not become an operating resistance of the motor generator 120.

  In addition, when the refrigerant can be sufficiently expanded, but the operation of the compressor (110) is unnecessary, the heat medium pump 130 can be driven by the driving force in the expansion mode of the expander / compressor 110. In addition, a dedicated drive source for operating the heat medium pump 130 can be eliminated, and the motor generator 120 can be operated as a generator to generate electric power, and expansion energy can be regenerated as electric energy. At this time, power for operating the alternator 11 for power generation can be reduced, and the fuel consumption of the engine 10 can be improved.

  Further, since the heat medium pump 130 is arranged on one end side of the composite fluid machine 100 and the one-way clutch 140 is provided between the adjacent device (motor generator 120) and the heat medium pump 130, the heat medium pump Regardless of the arrangement of the devices 110 and 120 except 130, the one-way clutch 140 can be easily provided without providing a complicated shaft structure.

  Also, since the shaft seal 150 that prevents refrigerant leakage between the motor generator 120 and the heat medium pump 130 is provided on the pump shaft 134, when the heat medium pump 130 is disconnected by the one-way clutch 140, the shaft It is possible to prevent the seal 150 from becoming an operating resistance of the motor generator 120.

  The loss due to the shaft seal 150 when the heat medium pump 130 is operated is proportional to the tightening force of the shaft seal 150 to the pump shaft 134 and the rotational speed of the outer diameter portion of the pump shaft 134 that contacts the shaft seal 150. By providing the shaft seal 150 on the small diameter portion 134d of the pump shaft 134, the rotational speed can be reduced and the loss can be reduced.

(Second Embodiment)
A second embodiment of the present invention is shown in FIG. The second embodiment is different from the first embodiment in that a vehicle in which the refrigeration apparatus 1 is mounted is a vehicle (idle stop vehicle, in which the engine 10 is stopped according to running conditions (during idling, low speed running, etc.). In this embodiment, a dedicated main compressor 35 is provided in the refrigeration cycle 30, and each connection flow path 51, 52 and each on-off valve 51a, 52a, 53a are provided.

  The refrigeration cycle 30 is provided with a main compressor 35 independent of the expander / compressor 110. That is, the refrigeration cycle 30 of the present embodiment is based on a main compressor 35, a condenser 31, a gas-liquid separator 32, a decompressor 33, and an evaporator 34 connected in an annular shape.

  The main compressor 35 has a pulley 35 a provided with an electromagnetic clutch as an intermittent means, and this pulley 35 a is connected to the engine 10 via the drive belt 14. The main compressor 35 is driven by the driving force of the engine 10 when the electromagnetic clutch of the pulley 35a is connected, and is stopped when the electromagnetic clutch is disconnected. Note that the engagement / disengagement of the electromagnetic clutch is controlled by a control device (not shown).

  As in the first embodiment, the Rankine cycle 40 uses the complex fluid machine 100, and the heat medium pump 130, the heater 43, the expander / compressor 110, the condenser 31, and the gas-liquid separator 32 are annular. It is connected to and formed.

  A first connection channel 51 is provided to connect the refrigerant suction side (point D) of the main compressor 35 and the low pressure side (point E) of the expander / compressor 110, and the expander / compressor 110 is provided. The second connection flow path 52 is provided to connect the high pressure side (point F) to the refrigerant discharge side (point G) of the main compressor 35.

  A first on-off valve 51 a is provided in the first connection channel 51, a second on-off valve 52 a is provided in the second connection channel 52, and a third on-off valve 53 a is provided between the point E and the condenser 31. Is provided. Each on-off valve 51a, 52a, 53a is an electromagnetic valve that opens and closes the first connection flow path 51, the second connection flow path 52, the point E and the condenser 31, respectively, and is controlled by a control device (not shown). To be controlled.

  Next, the operation based on the above configuration will be described with reference to FIGS.

1. Main A / C single mode (Fig. 4)
This mode is, for example, when the engine 10 is warmed up and sufficient waste heat from the engine 10 is not obtained, or when the battery 13 is sufficiently charged and charging is not necessary, and cooling is required. This is an operation mode in which the main compressor 35 is operated.

  Specifically, a control device (not shown) prevents the engine coolant from circulating to the heater 43 side by switching the three-way valve 21. Further, all the on-off valves 51a, 52a, 53a are closed, and the electromagnetic clutch of the pulley 35a of the main compressor 35 is brought into a connected state.

  At this time, the main compressor 35 is driven by the engine 10 to compress and discharge the refrigerant, and the discharged refrigerant circulates in the refrigeration cycle 30 (solid arrow in FIG. 4), and cooling due to heat absorption of the evaporator 34 is performed. Done. In this mode, the composite fluid machine 100 is in a stopped state.

2. Rankine single mode (Fig. 5)
In this mode, when the vehicle is driven by the engine 10, sufficient waste heat from the engine 10 is obtained, and when the battery 13 needs to be charged and cooling is not necessary, the expansion machine is also used. This is an operation mode (a mode corresponding to the expansion mode of the first embodiment) in which the expansion mode of the compressor 110 is executed.

  Specifically, a control device (not shown) causes the engine coolant to circulate through the heater 43 side by switching the three-way valve 21. Further, the first on-off valve 51a and the second on-off valve 52a are closed, and the third on-off valve 53a is opened. The electromagnetic clutch of the pulley 35a of the main compressor 35 is in a disconnected state, and further, the motor generator 120 is operated as a motor (reverse rotation), and the electromagnetic valve 117h (FIG. 1) of the expander / compressor 110 is opened.

  At this time, the heat medium pump 130 is driven, and a driving force is generated in the expander / compressor 110 by the expansion of the superheated steam refrigerant from the heater 43, and the motor generator 120 is driven by this driving force. When the driving force applied to the expander / compressor 110 exceeds the driving force for driving the heat medium pump 130, the motor generator 120 operates as a generator, and the obtained electric power passes through the inverter 12. The battery 13 is charged. And the refrigerant | coolant which flows out from the expander and compressor 110 circulates through Rankine cycle 40 like the broken-line arrow in FIG. In this mode, the main compressor 35 is stopped.

3. Main A / C, Rankine simultaneous operation mode (Fig. 6)
In this mode, when the vehicle is driven by the engine 10, the waste heat from the engine 10 is sufficiently obtained, and when the battery 13 needs to be charged and the cooling is necessary, the Rankine alone is used. In addition to the mode, the main compressor 35 is also operated in combination.

  Specifically, a control device (not shown) causes the engine coolant to circulate through the heater 43 side by switching the three-way valve 21. Further, the first on-off valve 51a and the second on-off valve 52a are closed, and the third on-off valve 53a is opened. Further, the motor generator 120 is operated as a motor (reverse rotation), the electromagnetic valve 117h (FIG. 1) of the expander / compressor 110 is opened, and the electromagnetic clutch of the pulley 35a of the main compressor 35 is brought into a connected state.

  At this time, the Rankine cycle 40 performs the same operation as the Rankine single mode, and the motor generator 120 generates power by the driving force obtained by the expander / compressor 110 (the refrigerant flow is shown in FIG. 6). Dashed arrows).

  In the refrigeration cycle 30, the same operation as in the main A / C single mode is performed, the main compressor 35 is driven by the engine 10, and cooling is performed by heat absorption of the evaporator 34 (the refrigerant flow is shown in FIG. 6). Solid arrows inside).

4). A / C assist mode (Figure 7)
In this mode, for example, when a large cooling capacity is required, such as during cool-down after being left under the sun in summer, cooling is given first priority, and in addition to the main compressor 35, the expander / compressor 110 This is an operation mode that is operated by executing the compression mode.

  Specifically, a control device (not shown) prevents the engine coolant from circulating to the heater 43 side by switching the three-way valve 21. Further, the first on-off valve 51a and the second on-off valve 52a are opened, and the third on-off valve 53a is closed. The solenoid valve 117h (FIG. 1) of the expander / compressor 110 is closed, and electric power is supplied to the stator 122 of the motor generator 120 to operate as a motor (forward rotation). Further, the electromagnetic clutch of the pulley 35a of the main compressor 35 is brought into a connected state.

  At this time, the main compressor 35 is driven by the engine 10 to compress and discharge the refrigerant, and the discharged refrigerant circulates in the refrigeration cycle 30 (solid arrow in FIG. 7). Further, the expander / compressor 110 is switched to the compression mode by the motor generator 120, and a part of the refrigerant flowing through the refrigeration cycle 30 is supplied from the suction side (point D) of the main compressor 35 to the first connection flow path 51, the first It circulates through the on-off valve 51a, reaches the expander / compressor 110, is compressed and discharged, passes through the second connection flow path 52 and the second on-off valve 52a, and reaches the condenser 31 (the chain line arrow in FIG. 7). ). That is, in the refrigeration cycle 30, the main compressor 35 and the expander / compressor 110 arranged in parallel compress and discharge a high flow rate refrigerant, and the flow rate of the refrigerant flowing through the evaporator 34 and the condenser 31 is increased. The cooling capacity in the vessel 34 is increased. The heat medium pump 130 is disconnected from the motor generator 120 by the one-way clutch 140 and is stopped.

5. Sub A / C single mode (Fig. 8)
In this mode, even when the engine 10 is stopped during traveling, when the cooling is necessary, the operation mode (described above) is performed by executing the compression mode of the expander / compressor 110 instead of the main compressor 35 to perform the cooling. Mode corresponding to the compression mode of the first embodiment).

  Specifically, a control device (not shown) prevents the engine coolant from circulating to the heater 43 side by switching the three-way valve 21. Further, the first on-off valve 51a and the second on-off valve 52a are opened, and the third on-off valve 53a is closed. The solenoid valve 117h (FIG. 1) of the expander / compressor 110 is closed, and electric power is supplied to the stator 122 of the motor generator 120 to operate as a motor (forward rotation).

  At this time, the main compressor 35 is stopped when the engine 10 is stopped, and the expander / compressor 110 is put into a compression mode by the motor generator 120. The refrigerant that has flowed out of the evaporator 34 is the first connection flow path 51 → the first on-off valve 51a → the expander / compressor 110 → the second connection flow path 52 → the second on-off valve 52a → the condenser 31 → the gas-liquid. The separator 32 → the decompressor 33 → the evaporator 34 is circulated (solid arrow in FIG. 8), and the evaporator 34 is cooled by absorbing heat. Here, the cycle in which the refrigerant circulates is a refrigeration cycle. The heat medium pump 130 is disconnected from the motor generator 120 by the one-way clutch 140 and is stopped.

  As described above, in the present embodiment, the main compressor 35 driven by the engine 10 is provided in the refrigeration cycle 30, and each connection flow path 51, 52 and each on-off valve 51 a are provided between the refrigeration cycle 30 and the Rankine cycle 40. , 52a, 53a are provided so that when the engine 10 is operated, both the cooling and power generation functions can be independently performed according to the waste heat state of the engine 10, the cooling request, the power generation request, etc. Both functions can be demonstrated simultaneously.

  In addition, when the demand for cooling capacity is high, in addition to the main compressor 35, the compression mode of the expander / compressor 110 can be executed to operate two compressors arranged in parallel. It can be improved.

  Furthermore, even when the engine 10 is stopped, continuous cooling can be performed by executing the compression mode of the expander / compressor 110 instead of the main compressor 35.

(Third embodiment)
In contrast to the first and second embodiments, the intermittent switching means of the composite fluid machine 100 may be an electromagnetic clutch that is intermittently connected by an electric signal from a control device (not shown) instead of the one-way clutch 140.

  As a result, even when the heat medium pump 130 is driven in the expansion mode of the expander / compressor 110, the heat medium pump 130 can be turned on and off by the engagement of the electromagnetic clutch, and the refrigerant circulating in the Rankine cycle 40 It is possible to control the flow rate.

(Other embodiments)
In the above embodiment, the compressor (110) and the expander (110) are both used as the expander / compressor 110. However, they are set as independent compressors (110) and expanders (110), respectively. May be.

  Further, although the scroll type expander / compressor 110 is employed, the present invention is not limited to this, and other types such as a rotary type, a piston type, and a vane type can be applied.

  Further, if the heat medium pump 130 is arranged on one end side connected in series, the arrangement of the compressor (110), the expander (110), and the motor generator 120 may be arranged in other ways.

  In the above-described embodiment, the vehicle engine (heat engine, internal combustion engine) 10 is used as the heat generating device. However, the present invention is not limited thereto. For example, an external combustion engine, a fuel cell stack of a fuel cell vehicle, and various motors. As long as the inverter generates heat during operation and discards part of the heat for temperature control (those that generate waste heat), it can be widely applied.

It is sectional drawing which shows the composite fluid machine in this invention. It is a schematic diagram which shows the freezing apparatus in 1st Embodiment of this invention. It is a schematic diagram which shows the freezing apparatus in 2nd Embodiment of this invention. FIG. 4 is a schematic diagram showing a refrigerant flow direction when operating in a main A / C single mode in FIG. 3. It is a schematic diagram which shows the refrigerant | coolant flow direction in the case of operate | moving in Rankine single mode in FIG. It is a schematic diagram which shows the refrigerant | coolant flow direction in the case of operate | moving in main A / C and Rankine simultaneous operation mode in FIG. It is a schematic diagram which shows the refrigerant | coolant flow direction in the case of operate | moving in A / C assist mode in FIG. It is a schematic diagram which shows the refrigerant | coolant flow direction in the case of operate | moving in sub A / C single mode in FIG.

Explanation of symbols

1 Refrigeration equipment 10 Engine (heating equipment, heat engine)
30 Refrigeration cycle 31 Condenser 40 Rankine cycle 100 Heat medium pump integrated expansion generator / electric compressor (composite fluid machine)
110 expander / compressor 114 high pressure chamber 116 inflow port (switching means)
107d Valve body (switching means)
120 Motor generator (rotary electric machine, adjacent equipment)
130 Heat transfer pump (pump)
134 Pump shaft 140 One-way clutch (intermittent switching means)
150 Shaft seal (shaft seal device)
V Working room

Claims (9)

A compressor (110) for compressing and discharging the fluid;
An expander (110) that generates a driving force by expansion of the working fluid circulated by the pump (130);
A rotating electric machine (120) having both functions of a generator and an electric motor,
The compressor (110), the expander (110), the rotating electrical machine (120), and the pump (130) are connected in series,
When the compressor (110) is driven by the rotating electrical machine (120), there is intermittent switching means (140) that can switch the connection state between the rotating electrical machine (120) and the pump (130) to a disconnected state. A composite fluid machine characterized by being provided.   The working fluid flows into the compressor (110) from the high pressure chamber (114) by switching means (116, 117d) for switching the flow path between the working chamber (V) and the high pressure chamber (114). The complex fluid machine according to claim 1, characterized in that it is sometimes an expander and compressor (110) functioning as the expander (110). The pump (130) is disposed on one end side where the compressor (110), the expander (110), the electric motor (120), and the pump (130) are connected in series.
The said intermittent switching means (140) is provided between the said pump (130) and the adjacent apparatus (120) adjacent to the said pump (130), The Claim 1 or Claim 2 characterized by the above-mentioned. Complex fluid machinery. The expander (110) rotates in the opposite direction with respect to the compressor (110),
The intermittent switching means (140) meshes in the rotational operation direction of the compressor (110) between the pump shaft (134) of the pump (130) and the shaft (124) of the adjacent device (120). The composite fluid machine according to claim 3, wherein the one-way clutch (140) meshes in a rotational operation direction of the expander (110).   The intermittent switching means (140) is an electromagnetic clutch that is intermittently connected by an electric signal between the pump shaft (134) of the pump (130) and the shaft (124) of the adjacent device (120). The composite fluid machine according to claim 3, wherein: A shaft seal device (150) for preventing leakage of the fluid or the working fluid between the pump (130) and the adjacent device (120);
The composite fluid machine according to claim 4 or 5, wherein the shaft sealing device (150) is provided on the pump shaft (134).   The composite fluid machine according to claim 6, wherein an outer diameter of the pump shaft (134) at a portion where the shaft seal device (150) is provided is set smaller than a general portion. A refrigeration apparatus comprising a Rankine cycle (40) that is formed using the condenser (31) in the refrigeration cycle (30) and that uses the waste heat of the heat generating device (10) as a heating source,
The compressor (110) of the composite fluid machine (100) according to claims 1-7 is used in the refrigeration cycle (30),
The refrigerating apparatus, wherein the pump (130) and the expander (110) are used in the Rankine cycle (40).   The refrigeration apparatus according to claim 8, wherein the heat generating device (10) is a heat engine (10).

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