JP6558296B2 - Magnetic heat pump device - Google Patents

Description

  The technology disclosed herein relates to a magnetic heat pump device that uses the magnetocaloric effect of a magnetic working material.

  As a conventional technique, for example, there is a magnetic refrigeration apparatus disclosed in Non-Patent Document 1 below. In the apparatus disclosed in Non-Patent Document 1 below, the work chamber is configured to generate a high temperature end and a low temperature end at both ends of the work chamber while modulating the external magnetic field applied to the magnetocaloric element provided in the work chamber. A heat transport medium is caused to flow through. As a result, cold heat is output from the low temperature end of the working chamber.

S.JACOBS et al., `` THE PERFORMANCE OF A LARGE-SCALE ROTARY MAGNETIC REFRIGERATOR '', Fifth IIF-IIR International Conference on Magnetic Refrigeration at Room Temperature, ThermagV, Grenoble, France, 17-20 September 2012 p.421-428

  However, the non-patent document 1 does not disclose in detail the configuration when the magnetic heat pump device is applied to a heat utilization system such as an air conditioner. When the heat output from the magnetic heat pump device is used, for example, a high temperature side heat exchanger and a low temperature side heat exchanger are connected to both ends of the working chamber. In the high temperature side heat exchanger, the heat can be used by discharging the heat from the heat transport medium guided from the high temperature end of the working chamber. On the other hand, in the low temperature side heat exchanger, the cold heat can be used by discharging the cold heat from the heat transport medium guided from the low temperature end of the working chamber.

  The inventor connected a heat exchanger to both ends of the work chamber of the magnetic heat pump device and tried to use the heat of the heat transport medium guided from the work chamber to the heat exchanger. I faced the problem of being small. The inventor has conducted extensive studies on this problem and found that the cause of the decrease in the coefficient of performance is the pressure loss of the heat transport medium in the heat exchanger.

  In the work chamber of the magnetic heat pump apparatus, it is necessary to flow a heat transport medium having a flow rate determined by the target heat output from the work chamber, the material characteristics of the magnetocaloric element, and the like. When a heat transport medium having a work chamber flow rate is passed through a heat exchanger connected to the work chamber, the pressure loss of the heat transport medium in the heat exchanger may become extremely large. When a relatively small heat exchanger is used, the pressure loss of the heat transport medium in the heat exchanger tends to increase. When the heat exchanger is a low temperature side heat exchanger connected to the low temperature end of the working chamber, the pressure loss of the heat transport medium in the heat exchanger tends to be particularly large due to the viscosity increase of the heat transport medium.

  When the work chamber flow rate, which is the flow rate of the heat transport medium flowing to the work chamber, is larger than the target heat exchanger flow rate of the heat transport medium, excess heat transport medium flows through the heat exchanger, and the heat transport in the heat exchanger The pressure loss of the medium increases. An increase in pressure loss in a heat exchanger requires an increase in input energy to a device that causes a heat transport medium to flow through a circulation circuit including a work chamber and a heat exchanger, resulting in a decrease in the coefficient of performance of the magnetic heat pump device. The present inventor has found that an increase in the pressure loss of the heat transport medium in this heat exchanger is an impediment to improving the coefficient of performance of the magnetic heat pump apparatus.

  The technology disclosed herein has been made in view of the above points, and an object thereof is to provide a magnetic heat pump device capable of realizing a high coefficient of performance.

In order to achieve the above object, in the disclosed magnetic heat pump device,
A magnetocaloric element (12) which is provided between both ends of the high temperature end (11b) and the low temperature end (11a) of the working chamber (11) and generates heat and heat absorption by the strength of an external magnetic field;
A magnetic field modulation device (14) for modulating an external magnetic field applied to the magnetocaloric element;
A heat transport device (16) for flowing a heat transport medium that exchanges heat with the magnetocaloric element in the working chamber so as to generate a high temperature end and a low temperature end;
A heat exchanger (24) for releasing cold or hot heat of the heat transport medium by heat exchange;
A forward path (51) for guiding the heat transport medium from one end of the both ends of the work chamber to the heat exchanger, and a return path (52) for guiding the heat transport medium from the heat exchanger to the one end. A medium circuit (50) for circulating the heat transport medium at one end to the heat exchanger;
If the work chamber flow rate, which is the flow rate of the heat transport medium flowing into the work chamber by the heat transport device, is larger than the target heat exchanger flow rate of the heat transport medium determined based on the flow characteristics of the heat transport medium in the heat exchanger, the target A flow rate that adjusts the flow rate of the heat transport medium flowing in the heat exchanger by removing the heat transport medium of the difference between the heat exchanger flow rate and the work chamber flow rate from the forward path and supplementing the return path with the heat transport medium of the difference. And an adjusting device (70, 170).

  According to this, when the working chamber flow rate is larger than the target heat exchanger flow rate, the flow control device removes the heat transport medium of the difference between the target heat exchanger flow rate and the working chamber flow rate from the outgoing path and removes it. The same amount of heat transport medium can be replenished in the return path. Therefore, it is possible to prevent an excessive heat and heat transport medium that exceeds the target heat exchanger flow rate from flowing through the heat exchanger. Thereby, the increase in the pressure loss of the heat transport medium in the heat exchanger can be suppressed, and the input energy to the heat transport device can be suppressed. In this way, the coefficient of performance of the magnetic heat pump device can be improved by suppressing the pressure loss of the heat transport medium in the heat exchanger, and a high coefficient of performance can be realized.

  In addition, the code | symbol in the parenthesis described in a claim and this clause shows the correspondence with the specific means as described in embodiment mentioned later as one aspect, Comprising: The range of an indication technique is limited It is not a thing.

It is a block diagram of the thermal equipment containing the magnetic heat pump apparatus which concerns on 1st Embodiment. It is a schematic block diagram of a vehicle air conditioner provided with the magnetic heat pump apparatus of 1st Embodiment. It is a block diagram which shows the control system structure of the magnetic heat pump apparatus of 1st Embodiment. It is a flowchart which shows the control action of the heat pump control apparatus of 1st Embodiment. It is an example of the target opening degree characteristic map of the valve apparatus which the heat pump control apparatus of 1st Embodiment controls. It is a flowchart which shows the control action of the heat pump control apparatus of 2nd Embodiment. It is an example of the target opening characteristic map of the valve apparatus which the heat pump control apparatus of 2nd Embodiment controls. It is a schematic block diagram of a vehicle air conditioner provided with the magnetic heat pump apparatus of 3rd Embodiment. It is a schematic block diagram of a vehicle air conditioner provided with the magnetic heat pump apparatus of other embodiment. It is a schematic block diagram of a vehicle air conditioner provided with the magnetic heat pump apparatus of other embodiment.

  Hereinafter, a plurality of modes for carrying out the disclosed technology will be described with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. In the case where only a part of the configuration is described in each embodiment, the other parts of the configuration are the same as those described previously. In addition to the combination of parts specifically described in each embodiment, the embodiments may be partially combined as long as the combination is not particularly troublesome.

(First embodiment)
As shown in FIG. 1, the vehicle air conditioner 1 includes a magnetocaloric effect type heat pump device 2. The magnetocaloric effect type heat pump apparatus 2 is also called an MHP (Magnetic Heat Pump) apparatus 2 or simply a magnetic heat pump apparatus 2. The MHP device 2 provides a thermomagnetic cycle device.

  In this specification, the term heat pump device is used in a broad sense. That is, the term “heat pump device” includes both a device that uses the cold heat obtained by the heat pump device and a device that uses the heat obtained by the heat pump device. An apparatus using cold heat may be referred to as a refrigeration cycle apparatus. Therefore, in this specification, the term heat pump apparatus is used as a concept including a refrigeration cycle apparatus.

  The vehicle air conditioner 1 has a heat exchanger 60 provided on the high temperature side of the MHP device 2. The heat exchanger 60 provides heat exchange between the high temperature of the MHP device 2 and a medium such as air. The heat exchanger 60 is mainly used for heat dissipation. In the illustrated example, the heat exchanger 60 provides heat exchange between the heat transport medium of the MHP device 2 and air. The heat exchanger 60 is one of high temperature system devices in the vehicle air conditioner 1. The heat exchanger 60 is installed, for example, in a vehicle interior and warms the air by exchanging heat with air for air conditioning. The heat exchanger 60 heats, for example, air for air conditioning, which is a fluid to be heated, using the thermal output from the high temperature end of the thermal output from the work chamber 11. The heat exchanger 60 is a high temperature side heat exchanger that heats the fluid to be heated by heat exchange with the heat transport medium.

  The vehicle air conditioner 1 has a heat exchanger 24 provided on the low temperature side of the MHP device 2. The heat exchanger 24 provides heat exchange between the cold end of the MHP device 2 and a medium such as air. The heat exchanger 24 is mainly used for heat absorption. In the illustrated example, the heat exchanger 24 provides heat exchange between the heat transport medium of the MHP device 2 and the heat source medium. The heat exchanger 24 is one of low temperature system devices in the vehicle air conditioner 1. The heat exchanger 24 is installed outside the vehicle, for example, and exchanges heat with the outside air. The heat exchanger 24 uses, for example, the cold output from the low temperature end of the heat output from the work chamber 11 to cool, for example, the outside air that is the fluid to be cooled. The heat exchanger 24 is a low temperature side heat exchanger that cools the fluid to be cooled by heat exchange with the heat transport medium.

  The MHP device 2 has a rotating shaft 2 a for driving the MHP device 2. The rotating shaft 2a is operatively connected to the power source 5. Therefore, the MHP device 2 is rotationally driven by the power source 5. The power source 5 provides rotational power to the MHP device 2. The power source 5 is the only power source of the MHP device 2. The power source 5 is provided by a rotating device such as an electric motor or an internal combustion engine. An example of a power source is an electric motor driven by a battery mounted on a vehicle. Hereinafter, the power source may be referred to as a motor.

  The MHP device 2 includes a housing 6. The housing 6 supports the rotating shaft 2a in a rotatable manner. The MHP device 2 includes a rotor 7. The rotor 7 is rotatably supported in the housing 6. The rotor 7 rotates by receiving a rotational force directly or indirectly from the rotation shaft 2a. The rotor 7 is a rotating body that is rotated by the power source 5. The rotor 7 is a cylindrical member.

  The rotor 7 forms a working chamber 11 through which the heat transport medium can flow. One working chamber 11 extends along the axial direction of the rotor 7. One working chamber 11 is open on both end faces in the axial direction of the rotor 7. The rotor 7 can include a plurality of work chambers 11. The plurality of work chambers 11 are arranged along the rotation direction of the rotor 7. Hereinafter, the rotor may be referred to as a container or an element bed.

  The rotor 7 includes a magnetocaloric element 12. The magnetocaloric element 12 is also called an MCE (Magneto-Caloric Effect) element 12. The MHP device 2 uses the magnetocaloric effect of the MCE element 12. The MHP device 2 generates a low temperature end and a high temperature end by the MCE element 12. The MCE element 12 is provided between the low temperature end and the high temperature end. In the illustrated example, the right side in the figure is the low temperature end, and the left end in the figure is the high temperature end.

  The MCE element 12 is disposed in the work chamber 11 so as to exchange heat with the heat transport medium. The MCE element 12 is fixed and held on the rotor 7. The MCE element 12 is arranged along the flow direction of the heat transport medium. The MCE element 12 is elongated along the axial direction of the rotor 7. The rotor 7 can include a plurality of MCE elements 12. The plurality of MCE elements 12 are arranged away from each other along the rotation direction of the rotor 7.

  The MCE element 12 generates heat when an external magnetic field is applied, and absorbs heat when the external magnetic field is removed. When an external magnetic field is applied to the MCE element 12 and the electron spins are aligned in the direction of the magnetic field, the magnetic entropy decreases and releases heat. Further, the MCE element 12 increases the magnetic entropy and absorbs heat when the electron spin becomes disordered by removing the external magnetic field. The MCE element 12 is made of a magnetic material that exhibits a high magnetocaloric effect in a normal temperature range. For example, a gadolinium-based material or a lanthanum-iron-silicon compound can be used. Also, a mixture of manganese, iron, phosphorus and germanium can be used. As the MCE element 12, an element that absorbs heat by applying an external magnetic field and generates heat by removing the external magnetic field may be used.

  The MHP device 2 includes a stator 8 that is disposed to face the rotor 7. The stator 8 is provided by a part of the housing 6. The stator 8 is disposed on the radially inner side and / or radially outer side of the rotor 7 and has a portion facing the rotor 7 with respect to the radial direction. These regions facing each other in the radial direction are used for providing a magnetic field modulation device. The stator 8 is disposed at one axial end and / or the other axial end of the rotor 7 and has a portion facing the rotor 7 in the axial direction. These axially opposed portions are used to provide a heat transport device, specifically, a flow path switching mechanism.

  The MHP device 2 includes a magnetic field modulation device 14 and a heat transport device 16 for causing the MCE element 12 to function as an element of an AMR (Active Magnetic Refrigeration) cycle. The magnetic field modulation device 14 is provided by the rotor 7 and the stator 8. The magnetic field modulation device 14 periodically increases or decreases the magnetic field by the relative rotational movement of the rotor 7 with respect to the stator 8. The magnetic field modulator 14 is driven by the rotational power given to the rotary shaft 2a. The heat transport device 16 includes a pump 17 and a flow path switching mechanism 18. The flow path switching mechanism 18 is provided by the rotor 7 and the stator 8. The flow path switching mechanism 18 functions by the relative rotational movement of the rotor 7 with respect to the stator 8. The flow path switching mechanism 18 switches the flow direction of the heat transport medium with respect to the work chamber 11 and the MCE element 12 by switching the connection state of the work chamber 11 to the heat transport medium flow path.

  The magnetic field modulator 14 applies an external magnetic field to the MCE element 12 and increases or decreases the strength of the external magnetic field. The magnetic field modulator 14 periodically switches between an excitation state in which the MCE element 12 is placed in a strong magnetic field and a demagnetization state in which the MCE element 12 is placed in a weak magnetic field or a zero magnetic field. The magnetic field modulator 14 modulates the external magnetic field so as to periodically repeat the excitation period in which the MCE element 12 is placed in a strong external magnetic field and the demagnetization period in which the MCE element 12 is placed in an external magnetic field weaker than the excitation period. To do. The magnetic field modulation device 14 repeats application and removal of the magnetic field to the MCE element 12 in synchronization with a reciprocating flow of a heat transport medium described later. The magnetic field modulation device 14 includes a magnetic source 13 for generating an external magnetic field, for example, a permanent magnet or an electromagnet.

  Specifically, the magnetic field modulation device 14 positions one work chamber 11 and the MCE element 12 alternately at the first position and the second position. The magnetic field modulator 14 positions the MCE element 12 at the first position in a strong magnetic field. The magnetic field modulator 14 positions the MCE element 12 at the second position in a weak magnetic field or a zero magnetic field.

  The magnetic field modulator 14 positions the MCE element 12 in the first position so that the MCE element 12 is positioned in a strong magnetic field when the heat transport medium flows along the MCE element 12 in the first direction. The first direction is a direction from the low temperature end toward the high temperature end. The magnetic field modulator 14 is configured such that when one end of the work chamber 11 communicates with the suction port of the pump 17 and the other end of the work chamber 11 communicates with the discharge port of the pump 17, the MCE element 12 in the work chamber 11 The MCE element 12 is positioned at the first position so as to be placed in a strong magnetic field.

  The magnetic field modulator 14 is configured so that the MCE element 12 is positioned in the weak magnetic field or the zero magnetic field when the heat transport medium flows along the MCE element 12 in the second direction opposite to the first direction. Position 12 in the second position. The second direction is a direction from the high temperature end toward the low temperature end. The magnetic field modulator 14 is configured so that the MCE element 12 is in a weak magnetic field or a zero magnetic field when one end of the working chamber 11 communicates with the discharge port of the pump 17 and the other end of the working chamber 11 communicates with the suction port of the pump 17. Position the MCE element 12 in the second position.

  The heat transport device 16 includes a heat transport medium for transporting heat that the MCE element 12 radiates or absorbs heat, and a fluid device for flowing the heat transport medium. The heat transport device 16 is a device that flows a heat transport medium that exchanges heat with the MCE element 12 along the MCE element 12. The heat transport device 16 reciprocates the heat transport medium along the MCE element 12. The heat transport device 16 generates a reciprocating flow of the heat transport medium in synchronization with a change in the external magnetic field by the magnetic field modulation device 14. The heat transport device 16 switches the flow direction of the heat transport medium in synchronization with the increase or decrease of the magnetic field by the magnetic field modulation device 14.

  The heat transport medium that exchanges heat with the MCE element 12 is called a primary medium. The primary medium can be provided by a fluid such as antifreeze, water, oil. The heat transport device 16 includes a pump 17 for flowing a heat transport medium. The pump 17 is a one-way pump that causes a heat transport medium to flow in one direction. The pump 17 has a suction port for sucking in the heat transport medium and a discharge port for discharging the heat transport medium. The pump 17 is arranged on the annular flow path of the heat transport medium. The pump 17 creates a unidirectional flow of the heat transport medium in the annular flow path. The pump 17 is driven by the rotating shaft 2a. The pump 17 is, for example, a positive displacement pump.

  The heat transport device 16 includes a flow path switching mechanism 18. The flow path switching mechanism 18 switches the flow path of the heat transport medium with respect to the work chamber 11 so as to reverse the flow direction of the heat transport medium with respect to one work chamber 11 and one MCE element 12. In other words, the flow path switching mechanism 18 reverses the arrangement of the working chamber 11 in the unidirectional flow of the heat transport medium generated by the unidirectional pump 17 with respect to the flow direction. The flow path switching mechanism 18 positions one work chamber 11 alternately on the forward path and the return path in the annular flow path including the pump 17. The flow path switching mechanism 18 switches the connection relationship between one work chamber 11 and one MCE element 12 and the annular flow path including the pump 17 to at least two states. The first state is a state where one end of the working chamber 11 communicates with the suction port of the pump 17 and the other end of the working chamber 11 communicates with the discharge port of the pump 17. The second state is a state where one end of the work chamber 11 communicates with the discharge port of the pump 17 and the other end of the work chamber 11 communicates with the suction port of the pump 17.

  Specifically, the flow path switching mechanism 18 positions one work chamber 11 and the MCE element 12 alternately at the first position and the second position. The flow path switching mechanism 18 communicates the working chamber 11 containing the MCE element 12 with the flow path so that the heat transport medium flows in the first direction along the MCE element 12 at the first position. The flow path switching mechanism 18 flows through the working chamber 11 that houses the MCE element 12 so that the heat transport medium flows in the second direction opposite to the first direction along the MCE element 12 in the second position. Communicate with. The flow path switching mechanism 18 switches the connection state between the flow path of the heat transport medium including the pump 17 and the MCE element 12, that is, the working chamber 11 so that the heat transport medium flows reciprocally to the MCE element 12. .

  The flow path switching mechanism 18 has a work chamber 11 that houses the MCE element 12 so that when one MCE element 12 is in the first position, the heat transport medium flows in the first direction along the MCE element 12. And the flow path are connected. When one MCE element 12 is in the first position, the flow path switching mechanism 18 communicates one end of the working chamber 11 that accommodates the MCE element 12 and the suction port of the pump 17, and the other end of the pump 17. It communicates with the discharge port.

  The flow path switching mechanism 18 is configured so that when one MCE element 12 is in the second position, the MCE element 12 flows along the MCE element 12 in the second direction opposite to the first direction. 12 is connected to the flow path. When one MCE element 12 is in the second position, the flow path switching mechanism 18 communicates one end of the working chamber 11 that accommodates the MCE element 12 with the discharge port of the pump 17, and the other end of the pump 17. Communicate with the inlet.

  The MHP device 2 has a high temperature side inlet 16 a that receives a heat transport medium from the heat exchanger 60. The high temperature side inlet 16 a can communicate with the suction port of the pump 17. The MHP device 2 has a high temperature side outlet 16 b that supplies a heat transport medium toward the heat exchanger 60. The high temperature side outlet 16b can communicate with one end of the work chamber 11 in the first position. The MHP device 2 has a low temperature side inlet 16 c that receives a heat transport medium from the heat exchanger 24. The low temperature side inlet 16c can communicate with the other end of the work chamber 11 in the first position. The MHP device 2 has a low temperature side outlet 16 d that supplies a heat transport medium toward the heat exchanger 24. The low temperature side outlet 16d can communicate with the other end of the work chamber 11 in the second position. One end of the working chamber 11 in the second position can communicate with the discharge port of the pump 17.

  The rotor 7 is also called an element bed for holding the MCE element 12. In this embodiment, the element bed which forms the working chamber 11 which accommodates the MCE element 12 is operatively connected to the rotating shaft 2a. The element bed including the MCE element 12 related to both the flow path switching mechanism 18 and the magnetic field modulator 14 is moved by the rotating shaft 2a. Therefore, efficient driving is possible.

  The pump 17, the flow path switching mechanism 18, and the magnetic field modulation device 14 are accommodated in a common housing 6. According to this configuration, the pump 17 can be installed in the vicinity of the flow path switching mechanism 18. For this reason, the pump 17 and the flow path switching mechanism 18 are connected without requiring a long pipe. As a result, even if there is a branch in the flow path including the pump 17, the difference in the flow of the heat transport medium can be suppressed. In this configuration, the flow path in the housing 6 can be used without using a pipe such as a hose. Therefore, the difference in the flow of the heat transport medium due to the piping is suppressed between the branched flow paths.

  A transmission mechanism 9 is disposed between the rotary shaft 2a and the rotor 7. The transmission mechanism 9 is provided by, for example, a planetary gear mechanism. The transmission mechanism 9 is disposed between the body of the pump 17 and the stator 8. The speed change mechanism 9 adjusts the rotation speed transmitted from the rotary shaft 2a so that the rotation speed of the pump 17 is higher than the rotation speed of the flow path switching mechanism 18 and the magnetic field modulation device 14. According to this configuration, the rotational speed of the pump 17 is higher than the rotational speeds of the flow path switching mechanism 18 and the magnetic field modulation device 14. Thereby, the high rotation type pump 17 can be utilized. When the pump 17 rotates at a high rotational speed, the flow rate of the pump 17 can be increased and / or the small pump 17 can be used.

  The vehicle air conditioner 1 is mounted on a vehicle and adjusts the temperature of the passenger compartment of the vehicle. The two heat exchangers 60 and 24 provide a part of the vehicle air conditioner 1. The heat exchanger 60 is a high temperature side heat exchanger 60 that is hotter than the heat exchanger 24. The heat exchanger 24 is a low temperature side heat exchanger 24 that is cooler than the heat exchanger 60. The vehicle air conditioner 1 includes air system equipment such as an air conditioning duct and a blower for using the high temperature side heat exchanger 60 and / or the low temperature side heat exchanger 24 for indoor air conditioning.

  The vehicle air conditioner 1 is used as a cooling device or a heating device. The vehicle air conditioner 1 can include a cooler that cools air supplied to the room and a heater that heats the air cooled by the cooler. The MHP device 2 is used as a cold source or a hot source in the vehicle air conditioner 1. That is, the high temperature side heat exchanger 60 can be used as the heater. The low temperature side heat exchanger 24 can be used as the cooler.

  When the MHP device 2 is used as a heat supply source, the air that has passed through the high temperature side heat exchanger 60 is supplied to the interior of the vehicle and used for heating. At this time, the air that has passed through the low temperature side heat exchanger 24 is discharged outside the vehicle. The heat exchanger 60 is also called an indoor heat exchanger. The heat exchanger 24 is also called an outdoor heat exchanger.

  When the MHP device 2 is used as a cold supply source, the air that has passed through the low temperature side heat exchanger 24 is supplied to the vehicle interior and is used for cooling. At this time, the air that has passed through the high temperature side heat exchanger 60 is discharged outside the vehicle. The heat exchanger 24 is also called an indoor heat exchanger. The heat exchanger 60 is also called an outdoor heat exchanger.

  The MHP device 2 may be used as a dehumidifying device. In this case, the air that has passed through the low temperature side heat exchanger 24 then passes through the high temperature side heat exchanger 60 and is supplied indoors. The MHP device 2 is used as a heat supply source both in winter and in summer.

  The vehicle air conditioner 1 shown in FIG. 2 is an air conditioner mounted on a vehicle that obtains driving force for vehicle travel from an electric motor as an engine, for example.

  The vehicle air conditioner 1 includes an MHP device 2 disposed in an engine room and an indoor air conditioning unit 20 disposed in a vehicle interior. The vehicle air conditioner 1 has a heat transport medium circuit capable of flowing a heat transport medium outside the MHP device 2. Hereinafter, the heat transport medium may be referred to as a refrigerant. Further, the heat transport medium circuit may be referred to as a refrigerant circuit or a medium circuit. The vehicle air conditioner 1 is configured to be able to switch between a cooling mode for cooling the passenger compartment, a heating mode for heating the passenger compartment, and a dehumidifying mode refrigerant circuit for dehumidifying when the passenger compartment is heated. Cooling, heating and dehumidification can be performed.

  FIG. 2 schematically shows a configuration when the vehicle air conditioner 1 is set to a cooling mode for cooling the passenger compartment. In the following description, the heat exchanger 60 on the high temperature side may be referred to as the outdoor heat exchanger 60. In addition, the low temperature side heat exchanger 24 may be referred to as an indoor heat exchanger 24 or a cooling heat exchanger 24. The indoor heat exchanger 24 corresponds to a heat exchanger that releases the cold heat of the heat transport medium by heat exchange in the present embodiment.

  The MHP device 2 shown in FIG. 1 is a device that drives the magnetic field modulation device 14 and the heat transport device 16 with the common power source 5, but the MHP device 2 is not limited to this. For example, as shown in FIG. 2, the pump 17 may be provided separately from the magnetic heat pump unit including the magnetic field modulator 14 and the flow path switching mechanism 18. As described above, the power source for driving the pump 17 and the power source for driving the magnetic field modulator 14 and the flow path switching mechanism 18 may be provided separately.

  The indoor air conditioning unit 20 illustrated in FIG. 2 is disposed, for example, inside the instrument panel at the foremost part of the vehicle interior. The indoor air conditioning unit 20 includes a blower 23, a cooling heat exchanger 24, a heating heat exchanger, and the like in an air conditioning case 21 that forms an outer shell thereof.

  The air conditioning case 21 forms a ventilation path for the blown air blown into the vehicle interior. The air conditioning case 21 is molded of a resin having a certain degree of elasticity and excellent in strength, for example, a polypropylene resin. On the most upstream side of the blast air flow in the air conditioning case 21, an inside / outside air switching box for switching and introducing the inside air as the cabin air and the outside air as the cabin outside air is arranged. The inside / outside air switching box adjusts the introduction ratio of inside air and outside air according to a command output from the air conditioning control device 100.

  On the downstream side of the air flow of the inside / outside air switching box, a blower 23 is disposed to blow the air sucked through the inside / outside air switching box toward the vehicle interior. The blower 23 is an electric blower that drives a sirocco fan, which is an example of a centrifugal multiblade fan, with an electric motor. The blower 23 is an indoor blower that sends wind blown into the vehicle interior. The rotation speed of the blower 23 is controlled by a control voltage command output from the air conditioning control device 100. The blower 23 is controlled in the amount of blown air by a control voltage command output from the air conditioning controller 100. Hereinafter, the blower 23 may be referred to as an indoor blower.

  A cooling heat exchanger 24 for cooling the air flowing through the ventilation path is disposed on the downstream side of the air flow of the blower 23 in the ventilation path in the air conditioning case 21. Further, a heating heat exchanger for heating the air that has passed through the cooling heat exchanger 24 is disposed on the downstream side of the air flow of the cooling heat exchanger 24.

  In the air conditioning case 21, a bypass passage is formed through which the blown air can flow while bypassing the heat exchanger for heating. An air mix door 27 is disposed on the air flow upstream side of the heating heat exchanger in the air flow path downstream of the cooling heat exchanger 24 in the air conditioning case 21. The air mix door 27 adjusts the air volume ratio between the air volume of the blown air passing through the heat exchanger for heating and the air volume of the blown air passing through the bypass passage. The arrangement position of the air mix door 27 is not limited to the upstream side of the air flow of the heat exchanger for heating. The arrangement position of the air mix door 27 may be on the air flow downstream side of the heat exchanger for heating.

  In the air conditioning case 21, a mixed space is formed in which the air after passing through the heat exchanger for heating and the air after passing through the bypass passage are mixed. A plurality of air outlets that blow out the air whose temperature is adjusted from the mixed space to the vehicle interior that is the air-conditioning target space are formed in the most downstream portion of the air flow of the air conditioning case 21. The plurality of air outlets are, for example, a face air outlet, a foot air outlet, and a defroster air outlet. On the upstream side of the air flow of each outlet, a door for adjusting the opening area of the outlet is arranged to constitute an outlet mode setting device. The blowing mode setting device 28 sets the blowing mode according to a command output from the air conditioning control device 100.

  The vehicle air conditioner 1 includes a high temperature side refrigerant circuit 40 and a low temperature side refrigerant circuit 50. The high temperature side refrigerant circuit 40 guides the refrigerant discharged from the high temperature side outlet 16b of the MHP device 2 to the refrigerant inlet 60a of the outdoor heat exchanger 60 and flows out of the refrigerant outlet 60b of the outdoor heat exchanger 60. Is a refrigerant circulation circuit for returning to the high temperature side inlet 16a. The outdoor heat exchanger 60 is a heat exchanger that is arranged in the engine room and exchanges heat between the refrigerant flowing inside and the outside air. The outdoor heat exchanger 60 is provided with an outdoor fan 63 that adjusts the flow rate of outside air to the heat exchange unit.

  The low temperature side refrigerant circuit 50 guides the refrigerant discharged from the low temperature side outlet 16d of the MHP device 2 to the refrigerant inlet 24a of the indoor heat exchanger 24 and flows out of the refrigerant outlet 24b of the indoor heat exchanger 24. Is a refrigerant circulation circuit for returning the gas to the low temperature side inlet 16c. The indoor heat exchanger 24 is disposed in the air conditioning case 21 of the indoor air conditioning unit 20 on the upstream side of the blast air flow of the heating heat exchanger, and exchanges heat between the refrigerant circulating in the interior and the blast air. It is a heat exchanger for cooling which cools blowing air.

  The low-temperature side refrigerant circuit 50 has a forward path 51 and a return path 52. The forward path 51 connects the low temperature end 11 a, which is one end of the work chamber 11, and the refrigerant inlet 24 a, and guides the heat transport medium from the low temperature end 11 a to the indoor heat exchanger 24. The return path 52 connects the low temperature end 11a of the working chamber 11 and the refrigerant outlet 24b, and guides the heat transport medium from the indoor heat exchanger 24 to the low temperature end 11a. The low temperature side refrigerant circuit 50 corresponds to the medium circuit in the present embodiment.

  As shown in FIG. 2, a temperature sensor 96 for detecting the temperature of the heat transport medium flowing out from the low temperature side outlet 16d is provided at the low temperature side outlet 16d of the MHP device 2. The temperature sensor 96 detects the temperature Tc1 of the heat transport medium before flowing out from the low temperature end 11a of the work chamber 11 and exchanging heat with the cooling heat exchanger 24. The temperature sensor 96 is a low temperature end temperature detection device. The low temperature side inlet 16c of the MHP device 2 is provided with a temperature sensor 97 for detecting the temperature of the heat transport medium flowing into the low temperature side inlet 16c. The temperature sensor 97 detects the temperature Tc <b> 2 of the heat transport medium that returns to the low temperature end 11 a of the work chamber 11 after performing heat exchange with the cooling heat exchanger 24.

  The low-temperature side refrigerant circuit 50 includes a flow rate adjusting device 70 that adjusts the flow rate of the heat transport medium flowing in the cooling heat exchanger 24. The flow rate adjusting device 70 includes a bypass channel 71 and a valve 72. The upstream end of the bypass channel 71 communicates with the forward path 51. The downstream end of the bypass flow path 71 communicates with the return path 52. The bypass flow path 71 is a medium flow path that connects the forward path 51 and the return path 52 and can flow the heat transport medium by bypassing the cooling heat exchanger 24.

  The valve 72 is provided in the bypass channel 71. The valve 72 adjusts the flow rate of the heat transport medium flowing through the bypass channel 71 according to the opening state. The valve 72 corresponds to the valve device in the present embodiment. The valve opening degree of the valve 72 is adjusted by a command output from the heat pump control device 101.

  As shown in FIG. 3, the control system of the vehicle air conditioner 1 includes an air conditioner control device 100 and a heat pump control device 101. The air conditioning control device 100 is a host control device of the heat pump control device 101. The air conditioning control device 100 outputs various commands and information to the heat pump control device 101. The control system of the vehicle air conditioner 1 is not limited to one having two control devices. For example, there may be one control device. Hereinafter, the air conditioning control device may be referred to as ACECU, and the heat pump control device may be referred to as HPECU.

  Each of the air conditioning control device 100 and the heat pump control device 101 includes a microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. An internal air temperature sensor 91, an external air temperature sensor 92, a solar radiation sensor 93, and an operation panel 90 are connected to the input side of the air conditioning control device 100. The inside air temperature sensor 91 outputs air temperature information in the passenger compartment. The outside air temperature sensor 92 outputs air temperature information outside the passenger compartment. The solar radiation sensor 93 outputs the amount of solar radiation information into the passenger compartment. The operation panel 90 is disposed in the vicinity of the instrument panel in the front part of the passenger compartment, and operation signals from various air conditioning operation switches provided on the operation panel 90 are input to the air conditioning control device 100. The operation panel 90 is provided with an operation switch, an auto switch, an air conditioning operation mode setting switch, a vehicle interior temperature setting switch, and the like of the vehicle air conditioner 1.

  The air conditioning control device 100 performs various calculations and processes based on the control program stored in the ROM, and the inside / outside air switching box 22, the blower 23, the air mix door 27, the blow mode setting device 28, etc. connected to the output side. Control the operation of Further, the air conditioning control device 100 outputs a command signal or the like to the heat pump control device 101.

  Temperature sensors 96 and 97 are connected to the input side of the heat pump control apparatus 101. The temperature sensors 96 and 97 output the heat transport medium temperature Tc1 and Tc2 information signals detected by the temperature sensors 96 and 97, respectively. The heat pump control device 101 performs various calculations and processing based on a control program stored in the ROM based on a command signal from the air conditioning control device 100, input signals from the temperature sensors 96 and 97, and the like. Controls the operation of the equipment connected to. Devices connected to the output side are the power source 5A of the magnetic field modulator 14 and the flow path switching mechanism 18, the power source 5B of the pump 17, the outdoor fan 63, and the valve 72.

  In the vehicle air conditioner 1, the heat pump control device 101 sets the air conditioning operation mode based on at least one of the air conditioning operation mode setting switch information from the operation panel 90 or the control processing of the air conditioning control device 100. The air conditioning operation mode set by the heat pump control device 101 includes a cooling operation mode, a heating operation mode, a dehumidifying operation mode, and the like.

  In the cooling operation mode, the amount of heat is transferred from the cooling heat exchanger 24 to the outdoor heat exchanger 60 via the MHP device 2. In the cooling operation mode, of the heat output from the work chamber 11, the cooling air from the low temperature end 11 a of the work chamber 11 is used to cool the blown air that is the fluid to be cooled by the cooling heat exchanger 24. In addition, among the heat outputs from the work chamber 11, the outdoor heat exchanger 60 heats the outdoor air that is the fluid to be heated, using the heat output from the high temperature end 11 b of the work chamber 11.

  In the vehicle air conditioner 1, in each operation mode, the vehicle interior can be air-conditioned using the hot heat obtained at the high temperature end side and the cold heat obtained at the low temperature end side of the work chamber 11 of the MHP device 2.

  For example, when the auto switch of the operation panel 90 is turned on and an auto mode for performing automatic air conditioning is set, the air conditioning control device 100 determines a control target value based on input information from various sensors, setting switches, and the like. To do. For example, the air conditioning control device 100 inputs a set temperature Tset signal from the setting state of the temperature setting switch of the operation panel 90. In addition, the air conditioning control device 100 receives an internal air temperature Tr signal from the internal air temperature sensor 91, an external air temperature Tam signal from the external air temperature sensor 92, and a solar radiation amount information Ts signal from the solar radiation sensor 93. The solar radiation amount information Ts is temperature information corresponding to the temperature increase due to the solar heat load. Based on the input information, the air-conditioning control device 100 obtains a target blowout temperature TAO that is a target value of the air temperature blown into the vehicle interior, a target heat output QO that is a target value of the heat output from the MHP device 2, and the like. decide. The air conditioning control device 100 outputs the target heat output QO as a command value to the heat pump control device 101 which is a lower order control device.

  The air conditioning control device 100 controls the operation of the inside / outside air switching box 22, the blower 23, the air mix door 27, and the blow mode setting device 28 based on, for example, the calculated target blow temperature TAO. When the inside / outside air introduction mode and the blowing mode are manually set on the operation panel 90, the air conditioning control device 100 sets a mode according to the setting state of the manually set switch regardless of the target blowing temperature TAO. .

  The heat pump control device 101 inputs information such as a command value from the air conditioning control device 100 which is a host control device. Further, the heat pump control apparatus 101 inputs temperature information of the heat transport medium from the temperature sensors 96 and 97. In addition to these input information, the heat pump control apparatus 101 controls the control target device based on heat output characteristic information stored in advance in the storage unit 102 such as a ROM, an opening degree control map of the valve 72, and the like.

  Hereinafter, the control operation of the heat pump control device 101 when the vehicle air conditioner 1 is set to the cooling operation mode will be described. When the heat pump control device 101 inputs a cooling operation start command from the air conditioning control device 100, first, in step 110, the target heat output QO of the MHP device 2 is acquired as shown in FIG.

  If step 110 is executed, then steps 120 and 130 are executed. In step 120, a drive control value of the power source 5A necessary for outputting the target heat output QO from the MHP device 2 is determined, and a control output is performed to the power source 5A. In step 130, a drive control value of the power source 5B necessary for outputting the target heat output QO from the MHP device 2 is determined, and a control output is performed to the power source 5B. In step 130, the power source 5B of the pump 17 is set so as to obtain a suitable working chamber flow rate determined from the target heat output QO, the density and specific heat of the heat transport medium, the adiabatic temperature change of the MCE element 12 due to applied magnetic field modulation, and the like. Is controlled.

  After executing Steps 120 and 130, the process proceeds to Step 140. In step 140, the temperature Tc1 information of the heat transport medium detected by the temperature sensor 96 is acquired. The temperature Tc1 is also the inlet medium temperature of the indoor heat exchanger 24. When step 140 is executed, the process proceeds to step 150. In step 150, the target opening of the valve 72 is calculated based on the temperature Tc1 of the heat transport medium acquired in step 140 and the drive control value of the power source 5B of the pump 17 output in step 130.

  The storage unit 102 of the heat pump control device 101 stores a target opening characteristic map of the valve 72 as illustrated in FIG. As shown in FIG. 5, the target opening degree of the valve 72 is stored as a value corresponding to the rotational speed of the pump 17 for each inlet medium temperature of the indoor heat exchanger 24. The target opening degree of the valve 72 is set so as to increase as the rotational speed of the pump 17 increases.

  The valve target opening degree increases as the heat transport medium flow rate in the working chamber 11 determined based on the pump rotation speed increases. On the other hand, the target heat exchanger flow rate, which is a preferable heat transport medium flow rate in the heat exchanger, determined based on the flow characteristics of the heat transport medium in the indoor heat exchanger 24 is relatively small. Since the indoor heat exchanger 24 is disposed in the air conditioning case 21, it is preferably small. Thereby, in the indoor heat exchanger 24, the flow resistance of the heat transport medium tends to increase, and the target heat exchanger flow rate decreases. In addition, a low temperature heat transport medium guided from the low temperature end 11 a of the work chamber 11 flows through the indoor heat exchanger 24. Low temperature heat transport media are relatively viscous. Also in this case, in the indoor heat exchanger 24, the flow resistance of the heat transport medium tends to increase, and the target heat exchanger flow rate decreases. The target opening degree of the valve 72 is set so that the difference between the work chamber flow rate, which is the flow rate of the heat transport medium in the work chamber 11, and the target heat exchanger flow rate flows in the bypass flow path 71.

  As illustrated in FIG. 5, the target opening degree of the valve 72 can be set to increase stepwise as the rotational speed of the pump 17 increases. The pump speed at which the valve target opening is switched is different when the pump speed is increasing and when the pump speed is decreasing. Thereby, the hunting operation of the valve 72 is prevented. The target opening degree of the valve 72 is not limited to one that increases stepwise as the rotational speed of the pump 17 increases. The target opening degree of the valve 72 may be set to gradually increase as the rotational speed of the pump 17 increases. In FIG. 5, the relationship between the pump speed and the target valve opening is set every time the inlet medium temperature of the indoor heat exchanger 24 changes by 10 ° C., but the present invention is not limited to this.

  In step 150, the target opening degree of the valve 72 is calculated from the rotational speed of the pump 17 corresponding to the output value in step 130 in the map corresponding to the temperature Tc1 of the heat transport medium acquired in step 140.

  When step 150 is executed, the process proceeds to step 160. In step 160, the target opening calculated in step 150 is output as a control value, and the opening of the valve 72 is controlled. When step 160 is executed, the process returns to step 110.

  According to the above configuration and operation, the MHP device 2 includes the indoor heat exchanger 24 corresponding to a heat exchanger, a low-temperature side refrigerant circuit 50 corresponding to a medium circuit, and a flow rate adjusting device 70. The low temperature side refrigerant circuit 50 has a forward path 51 that guides the heat transport medium from one end of the both ends of the work chamber 11 to the heat exchanger, and a return that guides the heat transport medium from the heat exchanger to the one end. The heat transfer medium at one end is circulated to the heat exchanger.

  The flow rate adjusting device 70 is a target heat exchanger for the heat transport medium in which the work chamber flow rate, which is the flow rate of the heat transport medium flowing through the work chamber 11 by the heat transport device 16, is determined based on the flow characteristics of the heat transport medium in the heat exchanger. When it is greater than the flow rate, it operates as follows. The flow rate adjusting device 70 removes the difference heat transport medium between the target heat exchanger flow rate and the work chamber flow rate from the forward path 51, replenishes the difference heat transport medium to the return path 52, and the indoor heat exchanger 24. The flow rate of the heat transport medium flowing through

  According to this, when the work chamber flow rate is larger than the target heat exchanger flow rate, the flow rate adjusting device 70 removes the heat transport medium that is the difference between the target heat exchanger flow rate and the work chamber flow rate from the outgoing path 51. The return path 52 is replenished with the same amount of heat transport medium as the removed amount. Therefore, it is possible to prevent an excessive heat and heat transport medium that exceeds the target heat exchanger flow rate from flowing through the indoor heat exchanger 24. Thereby, the increase in the pressure loss of the heat transport medium in the indoor heat exchanger 24 can be suppressed, and the input energy to the pump 17 of the heat transport device 16 can be suppressed. In this way, by suppressing the pressure loss of the heat transport medium in the indoor heat exchanger 24, the coefficient of performance of the MHP device 2 can be improved, and a high coefficient of performance can be realized.

  One end of the working chamber 11 described above is a low temperature end 11a, and the indoor heat exchanger 24 is a low temperature side heat exchanger that releases the cold heat of the heat transport medium by heat exchange. According to this, the coefficient of performance of the MHP device 2 can be improved by suppressing the pressure loss of the heat transport medium in the low temperature side heat exchanger, and a high coefficient of performance can be realized. Since the viscosity of the heat transport medium increases as the temperature decreases, the pressure loss tends to increase in the low temperature side heat exchanger. Therefore, the coefficient of performance of the MHP device 2 can be reliably improved by suppressing the pressure loss of the heat transport medium in the low temperature side heat exchanger.

  Further, the flow rate adjusting device 70 includes a bypass flow path 71 that connects the forward path 51 and the return path 52, bypasses the indoor heat exchanger 24, and flows the heat transport medium. According to this, by providing the bypass flow path 71, the heat transport medium of the difference between the target heat exchanger flow rate and the work chamber flow rate is removed from the outgoing path 51, and the difference between the target heat exchanger flow rate and the work chamber flow rate. It is possible to easily provide a configuration for replenishing the return path 52 with the heat transport medium. Therefore, a high coefficient of performance can be easily realized.

  Further, the flow rate adjusting device 70 includes a valve 72 that is provided in the bypass flow channel 71 and is a valve device that adjusts the flow rate of the heat transport medium flowing through the bypass flow channel 71. According to this, it is easy to adjust the flow rate of the heat transport medium flowing through the bypass passage 71 to a suitable flow rate by adjusting the opening degree of the valve 72.

  The flow rate adjusting device 70 includes an HP ECU 101 as a control device that controls the opening degree of the valve 72. The HP ECU 101 controls the valve 72 so that the opening degree of the valve 72 increases as the working chamber flow rate by the pump 17 of the heat transport device 16 increases. According to this, the HP ECU 101 increases the flow rate of the heat transport medium flowing through the bypass flow path 71 by increasing the opening degree of the valve 72 as the working chamber flow rate increases. Therefore, the larger the difference between the target heat exchanger flow rate and the work chamber flow rate, the larger the flow rate of the heat transport medium flowing through the bypass flow path 71. Thereby, even if the working chamber flow rate fluctuates, the pressure loss of the heat transport medium in the indoor heat exchanger 24 can be appropriately suppressed.

  According to the MHP device 2 of the present embodiment, it is possible to ensure the flow rate of the heat transport medium flowing out from the low temperature end 11a of the work chamber 11 and the flow rate of the heat transport medium flowing into the low temperature end 11a. In addition to this, it is possible to suppress the difference between the temperature difference between the heat transport medium flowing out from the low temperature end 11a and the heat transport medium flowing into the low temperature end 11a and the adiabatic temperature change of the MCE element 12 due to external magnetic field modulation. it can.

(Second Embodiment)
Next, 2nd Embodiment is described based on FIG. 6 and FIG.

  The second embodiment is different from the first embodiment in the calculation method of the target opening of the valve 72. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted. Components having the same reference numerals as those in the drawings according to the first embodiment and other configurations not described in the second embodiment are the same as those in the first embodiment and have the same effects.

  As shown in FIG. 6, after executing Step 140, the heat pump control apparatus 101 of the present embodiment proceeds to Step 240 and calculates the heat output Q from the working chamber 11 of the MHP apparatus 2. In step 240, a related value of the heat output Q may be calculated. In step 240, for example, the product of the cycle frequency and the amplitude of the heat transport medium reciprocating in the work chamber 11 can be calculated as a related value of the heat output Q. Here, the cycle frequency is a modulation frequency of the magnetic field by the magnetic field modulator 14. The cycle frequency is also the reciprocating frequency of the heat transport medium flowing in the work chamber 11 by the flow path switching mechanism 18. In step 240, for example, the target heat output QO acquired in step 110 may be used as the heat output Q.

  After executing step 240, the process proceeds to step 250. In step 250, the target opening of the valve 72 is calculated based on the temperature Tc1 of the heat transport medium acquired in step 140 and the heat output Q calculated in step 240 or its related value. The target opening degree characteristic map of the valve 72 as illustrated in FIG. 7 is stored in the storage unit 102 of the heat pump control apparatus 101 of the present embodiment. As shown in FIG. 7, the target opening degree of the valve 72 is stored as a value corresponding to the heat output Q for each inlet medium temperature of the indoor heat exchanger 24. The target opening degree of the valve 72 may be stored as a value corresponding to the related value of the heat output Q for each inlet medium temperature of the indoor heat exchanger 24. The target opening degree of the valve 72 is set so as to increase as the heat output Q increases. Also in this embodiment, the target opening degree of the valve 72 is set so that the difference between the work chamber flow rate, which is the flow rate of the heat transport medium in the work chamber 11, and the target heat exchanger flow rate flows in the bypass flow path 71. Yes.

  As illustrated in FIG. 7, the target opening degree of the valve 72 can be set to increase stepwise as the heat output Q increases. The heat output for switching the target valve opening is different when the heat output is increasing and when the heat output is decreasing. Thereby, the hunting operation of the valve 72 is prevented. The target opening of the valve 72 is not limited to one that increases stepwise as the heat output Q increases. The target opening degree of the valve 72 may be set to gradually increase as the heat output Q increases. In FIG. 7, the relationship between the heat output and the target valve opening is set every time the inlet medium temperature of the indoor heat exchanger 24 changes by 10 ° C., but the present invention is not limited to this.

  In step 250, the target opening degree of the valve 72 is calculated from the heat output Q calculated in step 240 in the map corresponding to the temperature Tc1 of the heat transport medium acquired in step 140. When step 250 is executed, the process proceeds to step 160.

  According to the MHP device 2 of the present embodiment, the flow rate adjusting device 70 includes the HP ECU 101 as a control device that controls the opening degree of the valve 72. The HP ECU 101 controls the valve 72 so as to increase the opening degree of the valve 72 as the heat output from the working chamber 11 increases. According to this, the HP ECU 101 increases the flow rate of the heat transport medium flowing through the bypass passage 71 by increasing the opening degree of the valve 72 as the heat output from the working chamber 11 increases. Therefore, as the heat output from the working chamber 11 increases and the working chamber flow rate increases, the flow rate of the heat transport medium flowing through the bypass channel 71 can be increased. Thereby, even if the working chamber flow rate fluctuates, the pressure loss of the heat transport medium in the indoor heat exchanger 24 can be appropriately suppressed.

(Third embodiment)
Next, a third embodiment will be described with reference to FIG.

  The third embodiment differs from the first embodiment in the configuration of the medium circuit. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted. Components having the same reference numerals as those in the drawing according to the first embodiment, and other configurations not described in the third embodiment are the same as those in the first embodiment, and have the same effects.

  As shown in FIG. 8, the low temperature side refrigerant circuit 50 of the present embodiment has a mixer 53. The mixer 53 is provided at a connection point between the return path 52 and the bypass flow path 71. The mixer 53 is composed of a container body having a relatively large internal volume, for example. The mixer 53 combines the heat transport medium that flows from the indoor heat exchanger 24 through the return path 52 and returns to the low temperature end 11 a and the heat transport medium that flows through the bypass flow path 71, and the junction of the return path 52 and the bypass flow path 71. Mix in.

  The mixer 53 mixes the heat transport medium whose temperature has been increased by heat exchange in the indoor heat exchanger 24 and the heat transport medium which bypasses the indoor heat exchanger 24 and hardly increases in temperature. The mixer 53 mixes two heat transport media having a temperature difference, and returns the heat transport medium having a uniform temperature to the low temperature end 11 a of the work chamber 11.

  The mixer 53 is not limited to that provided at the junction of the return path 52 and the bypass channel 71. The mixer 53 may be provided in the return path 52 on the downstream side of the junction of the return path 52 and the bypass flow path 71. The mixer 53 should just be arrange | positioned between the confluence | merging point of the return path 52 and the bypass flow path 71 in the return path 52, and the low temperature end 11a.

  According to the MHP device 2 of the present embodiment, the heat transport medium provided between the junction of the bypass flow path 71 in the return path 52 and the low temperature end 11a and returning from the indoor heat exchanger 24 to the low temperature end 11a, and the bypass A mixer 53 that mixes the heat transport medium flowing in the flow path 71 is provided. According to this, in the mixer 53, the heat transport medium returning from the indoor heat exchanger 24 having a temperature difference to the work chamber 11 and the heat transport medium flowing through the bypass channel 71 can be mixed. Therefore, the temperature of the heat transport medium returning to the end of the working chamber 11 can be made uniform.

(Other embodiments)
The technology disclosed in this specification is not limited to the embodiment for carrying out the disclosed technology, and can be implemented with various modifications. The disclosed technology is not limited to the combinations shown in the embodiments, and can be implemented in various combinations. Embodiments can have additional parts. The portion of the embodiment may be omitted. The parts of the embodiments can be replaced or combined with the parts of the other embodiments. The structure, operation, and effect of the embodiment are merely examples. The technical scope of the disclosed technology is not limited to the description of the embodiments. Some technical scope of the disclosed technology is indicated by the description of the claims, and should be understood to include all modifications within the meaning and scope equivalent to the description of the claims. .

  In the said embodiment, although the flow volume adjusting device 70 was provided with the valve | bulb 72, it is not limited to this. For example, as shown in FIG. 9, a bypass flow path 71 that connects the forward path 51 and the return path 52 may be used as a flow rate adjusting device. The bypass flow path 71 shown in FIG. 9 is preferably set so that the ratio between the pressure loss of the flow path on the indoor heat exchanger 24 side and the pressure loss of the flow path on the bypass flow path 71 side is suitable. The flow rate ratio between the heat transport medium flow rate flowing through the indoor heat exchanger 24 and the heat transport medium flow rate flowing through the bypass flow path 71 is the reciprocal of the pressure loss ratio of both paths. Therefore, a suitable pressure loss so that the heat transport medium of the target heat exchanger flow rate flows in the indoor heat exchanger 24 and the heat transport medium of the difference between the work chamber flow rate and the target heat exchanger flow flows in the bypass flow channel 71. It is preferable to provide a bypass channel 71 that provides

  Moreover, in the said embodiment, although the flow control apparatus 70 had the bypass flow path 71 which connects the going path | route 51 and the return path | route 52, it is not limited to this. For example, a flow control device 170 as shown in FIG. 10 may be used. The flow control device 170 includes a recovery tank 171 and a supply tank 172. The recovery tank 171 is connected to the forward path 51, and when the work chamber flow rate of the heat transport medium is larger than the target heat exchanger flow rate, the difference heat transport medium is removed from the forward path 51 and recovered in the tank. It is supposed to be. On the other hand, the supply tank 172 is connected to the return path 52, and when the work chamber flow rate of the heat transport medium is larger than the target heat exchanger flow rate, the return path 52 is replenished with the difference heat transport medium from the tank. It is like that. Thereby, the flow volume of the heat transport medium which flows into the indoor heat exchanger 24 can be adjusted.

  Moreover, in the said embodiment, although the flow volume adjustment apparatus was provided in the low temperature side refrigerant circuit 50 by the side of a cold output, it is not limited to this. For example, a flow rate adjusting device may be provided in the high temperature side refrigerant circuit 40 on the warm output side. Moreover, you may provide a flow control apparatus in both the high temperature side refrigerant circuit 40 and the low temperature side refrigerant circuit 50. FIG. Moreover, although the said embodiment demonstrated the structure and operation | movement when the vehicle air conditioner 1 was set to air_conditionaing | cooling operation mode, the structure and operation | movement which have the same technical idea are operation modes other than air_conditioning | cooling operation mode. It can also be applied to.

  Moreover, in the said embodiment, although the pump 17 of the heat transport apparatus 16 was a one-way pump, it is not limited to this. For example, a pump that forms a reciprocating flow of the heat transport medium by alternately sucking and discharging the heat transport medium may be used as the heat transport device. Further, two or more pumps may be provided instead of one.

  Moreover, in the said embodiment, the structure which the element bed which has the working chamber 11 and the MCE element 12 rotates was employ | adopted. Instead, various configurations for providing relative rotation between the element bed and the magnetic field modulation device 14 and relative rotation between the element bed and the flow path switching mechanism 18 are adopted. be able to. For example, the element bed may be kept stationary, and the magnetic field modulation device including the permanent magnet may be rotated and moved relative to the element bed.

  Moreover, in the said embodiment, the magnetic heat pump apparatus disclosed by the vehicle air conditioner was used. However, the present invention is not limited to this. For example, you may use the magnetic heat pump apparatus disclosed by the air conditioner for moving bodies other than vehicles, such as a ship and an aircraft. Further, for example, a magnetic heat pump device disclosed in a stationary air conditioner for home use may be used.

  Moreover, in the said embodiment, although the to-be-heated fluid heated by the heat exchanger 60 and the to-be-cooled fluid cooled by the heat exchanger 24 were air, it is not limited to this. The heated fluid or the cooled fluid may be a gas other than air. Moreover, the fluid to be heated and the fluid to be cooled may be liquid. For example, it is also effective to use a magnetic heat pump device disclosed in a hot water supply apparatus that uses water to be heated.

2 Magneto-caloric effect type heat pump device (magnetic heat pump device, MHP device)
11 Working room 12 Magneto-caloric element (MCE element)
14 Magnetic field modulation device 16 Heat transport device 24 Indoor heat exchanger (heat exchanger, heat exchanger for cooling)
50 Low temperature side refrigerant circuit (medium circuit)
51 Outgoing path 52 Return path 70, 170 Flow control device

Claims (7)

A magnetocaloric element (12) which is provided between both ends of the high temperature end (11b) and the low temperature end (11a) of the working chamber (11) and generates heat and heat absorption by the strength of an external magnetic field;
A magnetic field modulation device (14) for modulating the external magnetic field applied to the magnetocaloric element;
A heat transport device (16) for flowing a heat transport medium that exchanges heat with the magnetocaloric element in the working chamber so as to generate the high temperature end and the low temperature end;
A heat exchanger (24) for releasing cold or hot heat of the heat transport medium by heat exchange;
Outward path (51) for guiding the heat transport medium from one end of the both ends to the heat exchanger, and return path (52) for guiding the heat transport medium from the heat exchanger to the one end A medium circuit (50) for circulating the heat transport medium at the one end to the heat exchanger;
From the target heat exchanger flow rate of the heat transport medium, the work chamber flow rate, which is the flow rate of the heat transport medium flowing through the work chamber by the heat transport device, is determined based on the flow characteristics of the heat transport medium in the heat exchanger. The difference between the target heat exchanger flow rate and the working chamber flow rate is removed from the forward path, and the difference heat transfer medium is replenished to the return path, A magnetic heat pump device comprising: a flow rate adjusting device (70, 170) for adjusting a flow rate of the heat transport medium flowing in the exchanger. The one end is the low temperature end;
The magnetic heat pump device according to claim 1, wherein the heat exchanger is a low-temperature side heat exchanger that releases cold heat of the heat transport medium by heat exchange. The flow control device (70) includes:
The magnetic heat pump device according to claim 1 or 2, further comprising a bypass flow path (71) that connects the forward path and the return path, bypasses the heat exchanger, and flows the heat transport medium. The flow rate adjusting device includes:
The magnetic heat pump device according to claim 3, further comprising a valve device (72) that is provided in the bypass channel and adjusts a flow rate of the heat transport medium flowing through the bypass channel. The flow rate adjusting device includes a control device (101) for controlling the opening degree of the valve device,
The magnetic heat pump device according to claim 4, wherein the control device controls the valve device so that the opening degree of the valve device is increased as the working chamber flow rate by the heat transport device is larger. The flow rate adjusting device includes a control device (101) for controlling the opening degree of the valve device,
The magnetic heat pump device according to claim 4, wherein the control device controls the valve device so that the opening degree of the valve device is increased as the heat output from the working chamber is larger.   The heat transport medium provided between the confluence of the bypass flow path and the one end in the return path and returning from the heat exchanger to the one end, and the heat flowing through the bypass flow path The magnetic heat pump device according to any one of claims 3 to 6, further comprising a mixer (53) for mixing with a transport medium.

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