Abstract:
A magnetic heat pump system which arranges permanent magnets at the two sides of a magnetocalorific effect material to thereby strengthen the magnetic field to improve the cooling and heating ability, which magnetic heat pump system uses first and second magnets which move inside and outside of the containers in the state facing each other to change a magnitude of a magnetic field which is applied to a plurality of containers in which a magnetocalorific effect material is stored so as to change a temperature of a heat transport medium which is made to flow through the containers by a reciprocating pump, the intensity of the magnetic field which is applied to the magnetocalorific effect material in the containers being increased to enlarge the change of temperature of the heat transport medium which is discharged from the magnetic heat pump and improve the cooling and heating efficiency.

Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention relates to a magnetic heat pump system and to an air-conditioning system which uses that system. 
     2. Description of the Related Art 
     Known in the art is a magnetic heat pump system (also called a “magnetic refrigerating system”) which uses a magnetocalorific material as a work element. A magnetic heat pump system, compared with a refrigeration technique which utilizes conventional gas compression and expansion, that is, a gas heat pump system, does not use Freon or Freon alternatives, so is environmentally friendly. Further, in a magnetic heat pump system, the compression process or the expansion process using a compressor which was necessary for the gas heat pump system is unnecessary, so the energy efficiency is high. The only components which are required for a magnetic heat pump system are a pump which runs a fluid through a magnetocalorific effect material for heat exchange and a magnetic field applying device which imparts a change in magnetic field to the magnetocalorific effect material. 
     A magnetocalorific effect material which is used for a magnetic heat pump system has the characteristic of changing in temperature when a magnetic field is applied. Explained in further detail, a magnetocalorific effect material exhibits the phenomenon of becoming warmer when a magnetic field is applied and of becoming cooler when the magnetic field is removed (magnetocalorific effect). A rotary magnet type magnetic refrigerator which uses such a magnetocalorific material is disclosed in Japanese Patent No. 4284183. Further, it is known to apply a magnetic heat pump system to a vehicular air-conditioning system, for example, a heat pump system of an air-conditioning system of an automobile or railroad car. 
     SUMMARY OF THE INVENTION 
     However, in the rotary magnet type magnetic refrigerator which is disclosed in Japanese Patent No 4284183, a magnetic circuit which is made by two magnets attached on a shaft with their opposite pole facing each other is made to rotate so as to apply and remove a magnetic field to and from a magnetocalorific effect material, but the flow of a heat transport medium to the magnetocalorific effect material container is bent vertically. For this reason, in the rotary magnet type magnetic refrigerator which is disclosed in Japanese Patent No. 4284183, at the time of high speed rotation of the magnetic circuit, there were the problems that the pressure loss became greater, the efficiency fell, and the cooling ability and heating ability fell. 
     The present invention, in consideration of the present problems, provides a magnetic heat pump system which can improve a magnetic circuit which applies a magnetic field to a magnetocalorific effect material so as to improve heat generating and cooling performances of the magnetocalorific effect material and provides an air-conditioning system which uses such a magnetic heat pump system. 
     To solve the above problem, there is provided a magnetic heat pump system which comprises material containers ( 25 ) inside of which a magnetocalorific effect material ( 26 ) which has a magnetocalorific effect is arranged and inside of which a heat transport medium circulates, magnetic field changing means ( 22 ) for changing a magnitude of a magnetic field which is applied to the magnetocalorific effect material ( 26 ), heat transport medium moving means ( 13 ) for making the heat transport medium move back and forth between the two ends of the material containers ( 25 ), heat absorbing means ( 2 ) for making the heat transport medium which is discharged from one end sides of the material containers ( 25 ) absorb heat of the outside, and heat radiating means ( 5 ) for radiating to the outside the heat which the heat transport medium which is discharged from the other end sides of the material containers ( 25 ) has, the magnetic heat pump system characterized in that the magnetic field changing means ( 22 ) are provided with first magnets ( 23 ) and a yoke which are arranged at one sides of the material containers ( 25 ), second magnets ( 43 ) and a yoke which are arranged at the other sides of the material Containers ( 25 ) so as to face the first magnets ( 23 ) with different poles, a drive means ( 20 ) which is coupled with the first magnets ( 23 ) and yoke, and a holding mechanism ( 41 ) which holds the second magnets ( 43 ) and a yoke so as to rotate following the first magnets ( 23 ) and yoke. 
     Further, there is provided an air-conditioning system ( 10 ) which uses a magnetic heat pump system ( 30 ), wherein a heat absorbing means ( 2 ) is arranged as a cooler unit at an upstream side of a cooling passage ( 3 ) of an air-conditioning system ( 10 ) and wherein a heat radiating means ( 5 ) is arranged as a heater unit in a heating passage ( 4 ) which is positioned at a downstream side of an air mix damper ( 7 ) which controls an amount of intake of air-conditioned air which passes through the heat absorbing means ( 2 ). 
     Note that, the above reference notations are illustrations which show the correspondence with specific examples described in the embodiments explained next. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The present invention may be more fully understood from the description of preferred embodiments of the invention as set forth below, together with the accompanying drawings. 
         FIG. 1  is an overall view of the configuration which illustrates one embodiment of a magnetic heat pump system according to the present invention mounted on a vehicular air-conditioning system. 
         FIG. 2A  is a cross-sectional view which illustrates a first embodiment of the magnetic heat pump system which is illustrated in  FIG. 1 . 
         FIG. 2B  is a local cross-sectional view along the line A-A of the magnetic heat pump system which is illustrated in  FIG. 2A . 
         FIG. 2C  is a perspective view which illustrates one example of the configuration of a rotor which is provided with magnets which are illustrated in  FIG. 2A . 
         FIG. 2D  is an assembled perspective view which illustrates one example of a material container which holds a magnetocalorific effect material which is illustrated in  FIG. 2A . 
         FIG. 3A  is a cross-sectional view which illustrates a second embodiment of the magnetic heat pump system which is illustrated in  FIG. 1 . 
         FIG. 3B  is a schematic perspective view which illustrates the configuration of a reciprocating pump in the case of driving a piston of a reciprocating pump which is illustrated in  FIG. 3A  by a crankshaft. 
         FIG. 4A  is a cross-sectional view which illustrates a third embodiment of the magnetic heat pump system which is illustrated in  FIG. 1 . 
         FIG. 4B  is a plan view of a rotor unit of  FIG. 4A . 
         FIG. 4C  is a cross-sectional view along a line C-C of  FIG. 4A . 
         FIG. 5A  is a partial cross-sectional view which illustrates a fourth embodiment of the magnetic heat pump system which is illustrated in  FIG. 1 . 
         FIG. 5B  is a plan view which illustrates the configuration of a drive gear of  FIG. 5A . 
         FIG. 5C  is a partial side view which illustrates the configuration of a pulley mechanism which can be installed instead of the gear mechanism of  FIG. 5A . 
         FIG. 6  is a partial cross-sectional view which illustrates a fifth embodiment of the magnetic heat pump system which is illustrated in  FIG. 1 . 
         FIG. 7  is a view which illustrates the configuration of a modified embodiment of a second embodiment which is illustrated in  FIG. 3 . 
         FIG. 8  is a view which illustrates the configuration of a modified embodiment of a fourth embodiment which is illustrated in  FIG. 5A . 
         FIG. 9  is a view which illustrates the configuration of a modified embodiment of a fifth embodiment which is illustrated in  FIG. 6 . 
     
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     Below, referring to the drawings, embodiments of the present invention will be explained. In the embodiments, parts of the same configuration are assigned the same reference notations and explanations are omitted. 
       FIG. 1  illustrates the configuration of a vehicular air-conditioning system  10  using a magnetic heat pump system  30  according to the present invention. The air-conditioning system  10  is installed inside of the vehicle and has a cooler unit  2  in an air flow path  1  of the same as a heat absorbing means. Further, at a downstream side of the cooler unit  2 , there are a cooling passage  3  and a heating passage  4  which is provided with a heater unit  5  and a heater core  6  as a heat radiating means. Further, at the inlet parts of the cooling passage  3  and the heating passage  4 , an air mix damper  7  is provided. Along with movement of the air mix damper  7 , the air which passes through the cooler unit  2  is controlled to flow through the cooling passage  3  or to flow through the heating passage  4 . 
     On the other hand, inside the engine compartment of a vehicle, there are a components which are operated by a shaft  21  which is rotated by a motor  20  (a drive means) such as a cooling water manufacturing part  11 , warm water manufacturing part  12 , and a reciprocating pump  13  which is a heat transport medium moving means. The internal structure of the cooling water manufacturing part  11 , warm water manufacturing part  12 , and reciprocating pump  13  will be explained later. The cooling water manufacturing part  11  cools the heat transport medium by magnetic action. The heat transport medium which was cooled by the cooling water manufacturing part  11  is discharged to a cooling water circulating path  15  by the reciprocating pump  13 , is supplied to the cooler unit  2 , then returns to the cooling water manufacturing part  11 . Conversely, the warm water manufacturing part  12  heats the heat transport medium by magnetic action. The heat transport medium which is heated by the warm water manufacturing part  12  is discharged by the reciprocating pump  13  to a warm water circulating path  16 , is supplied to the heater unit  5 , and returns to the warm water manufacturing part  12 . 
     On the other hand, in the air-conditioning system  10 , the heater core  6  which is provided at the heating passage  4  is supplied through the coolant circulating path  9  with cooling water (coolant) which was warmed by cooling the engine  8 , whereby the air which passes through the heater unit  5  and the heating passage  4  is warmed. The heater core  6  is not directly related to the present invention, so further explanation of the heater core  6  will be omitted. 
     Here, the configuration of the cooling water circulating path  16  and the warm water circulating path  16  will be explained in detail. At the cooling water manufacturing part  11 , there are a plurality of cylinders. At each cylinder, a runner  15 A is connected. A plurality of runners  15 A are collected to form a feed pipe  15 B. A heat transport medium is supplied from the feed pipe  15 B to the cooler unit  2 . The heat transport medium which is discharged from the cooler unit  2  is returned by the return pipe  15 C to the cooling water manufacturing part  11 , is distributed to the runners  15 D which are connected to the cylinders, and is returned to the cylinders. Between the feed pipe  15 B and the return pipe  15 C, a bypass pipe  17 A which bypasses the cooler unit  2  is provided. The bypass pipe  17 A is directly connected to the return pipe  15 C, but is connected to the feed pipe  15 B through a first flow path switching valve  17 . 
     At the time of heating, by switching the first flow path switching valve  17 , the heat transport medium which flows through the feed pipe  15 B can be returned to the cooling water manufacturing part  11 , without going through the cooler unit  2 , by going through the bypass pipe  17 A. Furthermore, at the upstream side of the runner  15 D of the return pipe  15 C, there is a third flow path switching valve  19 . At the third flow path switching valve  19 , a detour pipe  19 A which returns to the return pipe  15 C through the outside unit  14  is connected. At the time of heating, the third flow path switching valve  19  is switched so that the heat transport medium which flows through the return pipe  15 C flows from the third flow path switching valve  19  to the detour pipe  19 A, absorbs heat from the outside air at the outside unit  14 , and flows again from the detour pipe  19 A to the return pipe  15 C. The heat transport medium which again flows to the return pipe  15 C returns to the cooling water manufacturing part  11 . 
     Similarly, at the warm water manufacturing part  12 , there are a plurality of cylinders which heat the heat transport medium to obtain warm water. At the cylinders, runners  16 A are connected. A plurality of runners  16 A are collected to form a feed pipe  16 B which supplies the heat transport medium to the heater unit  5 . The heat transport medium which is discharged from the heater unit  5  is returned by the return pipe  16 C to the warm water manufacturing part  12 , distributed to the runners  16 D which are connected to the cylinders, and is returned to the cylinders. At the return pipe  16 C at the upstream side of the runner  16 D, there is a second flow path switching valve  18 . At the second flow path switching valve  18 , a detour pipe  18 A which returns the heat transport medium through the outside unit  14  to the return pipe  16 C is connected. By switching the second flow path switching valve  18 , the heat transport medium which flowed though the return pipe  16 C can flow to the detour pipe  18 A before returning to the warm water manufacturing part  12 , absorb heat from the outside air at the outside unit  14 , and return to the warm water manufacturing part  12 . 
       FIG. 2A  is a cross-sectional view which illustrates a first embodiment of a magnetic heat pump  40  in the magnetic heat pump system  30  which is illustrated in  FIG. 1 . Further,  FIG. 2B  is a local cross-sectional view along the line A-A of the magnetic heat pump  40  which is illustrated in  FIG. 2A . Furthermore,  FIG. 2C  is a perspective view which illustrates one example of the configuration of a rotor  22  which is provided with magnets  23  which are illustrated in  FIG. 2A , while  FIG. 2D  is an assembled perspective view which illustrates the configuration of one example of a material container  25  which holds the magnetocalorific effect material  26  which is illustrated in  FIG. 2A . 
     In the first embodiment which is illustrated in  FIG. 2A , for the reciprocating pump  13 , a radial piston pump is used, but as the reciprocating pump  13 , a swash plate compressor may also be used. The structures of the cooling water manufacturing part  11  and the warm water manufacturing part  12  which are attached to the reciprocating pump  13  at opposite sides to the right and left are the same. The cooling water manufacturing part  11  is provided with a cylindrical shell  24  which is arranged concentrically with the shaft  21 . A cross-sectional fan-shaped rotor  22  such as illustrated in  FIGS. 2B and 2C  is provided facing the shaft  21 . Further, at the outer circumferential surface of the rotor  22 , permanent magnets  23  are attached. One of the permanent magnets  23  is arranged with the N pole at the outside, while the other is arranged with the S pole at the outside. 
     Further, between the outside of the path of rotation of the permanent magnets  23  and the inner. circumferential surface of the shell  24 , a plurality of material containers  25  in which a magnetocalorific effect material  26  is filled and a cylindrical yoke part  44  are arranged. The outer circumferential surface of the yoke part  44  is held rotatably at the inner circumferential surface of the shell  24  by a holding mechanism comprised of ball bearings  41 . Further, it is also possible to omit the ball bearings and use a lubricating oil layer or air layer. Furthermore, at the inner circumferential surface of the yoke part  44 , permanent magnets  43  are attached at positions which face the permanent magnets  23  which are attached to the outer circumferential surface of the rotor  22 . One of the permanent magnets  43  faces a permanent magnet  23  which is arranged with the N pole at an inner side and which is arranged with the S pole at an outer side attached to the outer circumferential surface of the rotor  22 . Further, the other of the permanent magnets  43  faces a permanent magnet  23  which is arranged with the S pole at an inner side and with an N pole at an outer side attached to the outer circumferential surface of the rotor  22 . 
     Each material container  25 , as illustrated in  FIG. 2D , is tubular shaped with an outer shape of a fan-shaped cross-section. The inside space is filled with a pellet-shaped magnetocalorific effect material  26 . The two end parts are closed by mesh-like end plates  24 M so as to seal in the magnetocalorific effect material  26 . Liquid can enter the inside of the material container  25  from one end through an end plate  25 M, run through the clearances in the magnetocalorific effect material  26 , and be discharged to the outside from the end part at the opposite side through another end plate  25 M. 
     In the first embodiment, six material containers  25  of the same shape are arranged, at the inner circumferential surface of the yoke part  44 . The permanent magnets  23  which are attached to the outer circumferential surfaces of the rotor  22  rotate over the inner circumferential surface sides of the material containers  25 . Further, along with the rotational movement of the permanent magnets  23 , the rotary magnets  43  which face the permanent magnets  23  move following them by the attraction force acting between the magnets and therefore the yoke part  44  rotates. The rotor  22 , facing permanent magnets  23  and  43  and yoke part  44  function as magnetic field changing means for imparting a magnetic field to the magnetocalorific effect material  26  which is filled in the material containers  25 . The intensity of the magnetic field which is applied to the magnetocalorific effect material  26  which is filled in the material containers  25  is improved 30 to 60% compared with the case where permanent magnets  23  are provided only at the insides of the magnetocalorific effect material  26 . 
     If returning to  FIG. 2A  and continuing the explanation, in the first embodiment, the reciprocating pump  13  is comprised of a radial piston pump. The body of the radial piston pump  13  is formed integrally with the cooling water manufacturing part  11  and warm water manufacturing part  12 . At the radial piston pump  13 , six cylinders  34  are provided in radiating shapes from the shaft  21  matching the number of the material containers  25  at the cooling water manufacturing part  11 . Inside of the cylinders  34 , reciprocating pistons  33  are provided. 
     On the other hand, at the shaft  21  which is rotated by the motor  20 , a control cam  32  is attached eccentric to the shaft  21 . The pistons  33  are engaged with the cam profile of the control cam  32 . Due to the cam profile of the control cam  32 , when the control cam  32  turns once, the pistons  33  in the cylinders  34  can be made to reciprocate. In the first embodiment, there are two poles of permanent magnets  23 , so when the rotor  22  turns once, the control cam  32  is used to make the pistons  33  reciprocate two times. The side faces of the cylinders  34  at the sides far from the shaft  21  are connected to the end faces of the material containers  25  of the cooling water manufacturing part  11  and warm water manufacturing part  12  by connecting passages  38 . 
     In the first embodiment which is illustrated in  FIG. 2A , at the end face of the cooling water manufacturing part  11  at the side far from the radial piston pump  13 , an end face plate  29  is attached. At the end face plate  29 , intake valves  28  which guide the heat transport medium to the end faces of the material containers  25  and discharge valves  27  which discharge the heat transport medium which is exhausted from the end faces of the material containers  25  are provided. At each discharge valve  27 , a runner  15 A of the feed pipe  155  of the cooling water circulation path  15  which was explained in  FIG. 1  is connected, while at each intake valve  28 , a runner  15 D of the return pipe  15 C of the cooling water circulation path  15  which was explained in  FIG. 1  is connected. Above, the structure of the cooling water manufacturing part  11  was explained, but when the reciprocating pump  13  is a radial piston pump, the positions of the permanent magnets  23  at the cooling water manufacturing part  11  and the warm water manufacturing part  12  with respect to the shaft  21  are off by 90 degrees. 
     In the warm water manufacturing part  12  which is configured in the same way as the configuration of the cooling water manufacturing part  11  as explained above, at each discharge valve  27  at the end face plate  29  at the opposite side to the reciprocating pump  13 , a runner  16 A of the feed pipe  165  of the warm water circulating path  16  which was explained in  FIG. 1  is connected, while at each intake valve  28 , a runner  16 D of the return pipe  16 C of the warm water circulating path  16  which was explained in  FIG. 1  is connected. Further, in the reciprocating pump  13 , if a piston  33  operates and the heat transport medium is sucked in at a certain material container  25  of the cooling water manufacturing part  11 , if the reciprocating pump  13  is a radial piston pump, the heat transport medium is similarly sucked in at the corresponding material container  25  of the facing warm water manufacturing part  12 . 
     At the cooling water manufacturing part  11  side, when the heat transport medium is discharged from a material container  25 , due to elimination of the magnetic field which had been applied to the magnetocalorific effect material  26  inside the material container  25 , the temperature of the magnetocalorific effect material  26  falls and the discharged heat transport medium is cooled. The heat transport medium which had been cooled at each cooling container  25  is fed into the cooling water circulation path  15 . Conversely, at the warm water manufacturing part  12  side, when the heat transport medium is discharged from a material container  25 , due to the application of a magnetic field to the magnetocalorific effect material  26  inside the material containers  25 , the magnetocalorific effect material  26  generates heat and the discharged heat transport medium is heated and supplied to the warm water circulating path  16 . The permanent magnets  23  are arranged at the outer circumference of the rotor  22 , while the permanent magnets  43  are arranged at the inner circumferential surface of the yoke part  44  so that the above such operation is performed. 
       FIG. 3A  is a cross-sectional view which illustrates a second embodiment of a magnetic heat pump  40  in the magnetic heat pump system  30  which is illustrated in  FIG. 1 . In the magnetic heat pump  40  of the first embodiment, the reciprocating pump  13  was arranged at the part between the cooling water manufacturing part  11  and the warm water manufacturing part  12 , but in the second embodiment, the two reciprocating pumps  13 A and  13 B are provided independently at the two sides of the magnetic heat pump  40 . Therefore, the magnetic heat pump  40  of the second embodiment removes the reciprocating pump  13  and connects the cooling water manufacturing part  11  and the warm water manufacturing part  12  of the first embodiment. However, the rotor  22  is, for example, shaped by extension of the rotor  22  of the warm water manufacturing part  12 . It is not shaped as a rotor of a different phase which is illustrated in  FIG. 2A  connected as it is. 
     The magnetic heat pump  40  of the second embodiment is provided with a shell  24  which is provided with the same diameter as the shell  24  of the first embodiment. Further, at the inner circumferential surface of the shell  24 , a yoke part  44  is attached through ball bearings  41 . The structure of permanent magnets  42  which face permanent magnets  23  at the outer circumferential surface of the rotor  22  being present at the inner circumferential surface of the yoke part  44  is the same as in the first embodiment. The point that one of the permanent magnets  43  faces a permanent magnet  23  which is arranged with the N pole at an inner side and which is arranged with the S pole at an outer side attached to the outer circumferential surface of the rotor  22  of an S pole and the other of the permanent magnets  43  faces a permanent magnet  23  which is arranged with the S pole at an inner side and with an N pole at an outer side attached to the outer circumferential surface of the rotor  22  is also the same. 
     The shape and number of the material containers  25  at the second embodiment are the same as in the first embodiment. The cross-section along the line B-B at the magnetic heat pump  40  of the second embodiment is the same as the cross-section along the line A-A at the magnetic heat pump  40  of the first embodiment which is illustrated in  FIG. 2B . One end part of each material container  25  is connected through a discharge valve  27  or intake valve  28  to a medium passage  46 A which is provided with a heat exchanger  45 A, while the other end part is connected through a discharge valve  27  or an intake valve  28  to a medium passage  46 B which is provided with a heat exchanger  45 B. The medium passages  46 A and  46 B which are connected to the material containers  25  are respectively independent. 
     In the second embodiment as well, if the permanent magnets  23  which are attached to the outer circumferential surface of the rotor  22  rotate due to the motor  20 , along with the rotation of the permanent magnets  23 , the rotary magnets  43  which face the permanent magnets  23  rotate following them due to the attraction force of the magnets and therefore the yoke part  44  rotates. The intensity of the magnetic field which is applied to the magnetocalorific effect material  26  which is filled in the material containers  25  is 30 to 60% higher than the case where the permanent magnets  23  are provided only at the inside of the magnetocalorific effect material  26 . 
     Note that, in the magnetic heat pump  40  of the second embodiment which is illustrated in  FIG. 3A , as the two reciprocating pumps  13 A and  13 B, radial piston pumps which are provided with pistons  33 A and  33 B which are driven by control cams  32 A and  32 B are illustrated. On the other hand, as the two reciprocating pumps  13 A and  13 B, instead of the radial piston pumps, as illustrated in  FIG. 3B , it is also possible to use pistons which are driven by the crankshaft  35 . In this case, it is also possible to couple the crankshaft  35  to the shaft  21  to drive the piston  33 . 
       FIG. 4A  is a cross-sectional view of a magnetic heat pump  50  which is illustrated in a third embodiment in the magnetic heat pump system  30  which is illustrated in  FIG. 1 . Further,  FIG. 4B  is a plan view of a rotor  22  which is illustrated in  FIG. 4A , while  FIG. 4C  is a cross-sectional view along the line C-C of  FIG. 4A . Further, in the third embodiment, the two reciprocating pumps  13 A and  13 B are the same in structure as the second embodiment, so illustration will be omitted. The medium flow paths  46 A and  46 B are illustrated by solid lines. 
     In the third embodiment as well, the two reciprocating pumps  13 A and  13 B which operate by the shaft  21  which is driven by the motor  20  are provided independently at the two sides of the magnetic heat pump  50 . In the magnetic heat pump  50  of the third embodiment, at the side of the inside of the shell  51  near the motor  20 , there is a disk-shaped rotor  52  which is attached to the shaft  21 . At the other surface of the rotor  52 , as illustrated in  FIG. 4B , fan-shaped permanent magnets  53  are attached point symmetrically to the shaft  21 . One of the permanent magnets  53  is arranged with the N pole at the rotor  52  side, while the other of the permanent magnets  53  is arranged with the S pole at the rotor  52  side. The rotor  52  forms the yoke part. 
     At the side of the shell  51  far from the motor  20 , there is a ring-shaped yoke part  54  which is provided ratably with respect to the inner circumferential surface of the shell  51  via ball bearings  41 . The yoke part  54  is not connected to the shaft  21 . The share  21  runs through a hole which is provided at the center part. At the surface of the yoke part  54  at the rotor  52  side, permanent magnets  55  of the same size as the permanent magnets  53  which are attached to the rotor  52  are attached. One of the permanent magnets  55  is arranged with the N pole at the rotor  52  side, while the other permanent magnet  55  is arranged with the S pole at the rotor  52  side. Therefore, between the permanent magnets  55  and the permanent magnets  53 , an attraction force acts. The permanent magnets  55  and the permanent magnets  53  are at facing positions. Further, the yoke part  54  to which the permanent magnets  55  are attached is held rotably inside the shell  51  by ball bearings  41 , so if the shaft  21  rotates and the permanent magnets  53  move by rotating, the permanent magnets  55  move by rotating following the same. 
     At the space inside the shell  51  sandwiched between the permanent magnets  53  and the permanent magnets  55 , there is a container mount  57  which is not connected to the shaft  21 . At the container mount  57 , as illustrated in  FIG. 4C , a plurality of material containers  25  in which a magnetocalorific effect material is filled are attached in a radial manner. The cross-sectional shape of material containers  25  in a direction vertical to the flow of the heat transport medium is rectangular or circular. The container mount  57  may be formed integrally with the shell  51 , or a separate container mount  57  may be attached to the inside of the shell  51 . At the outside and inside parts of the material containers  25 , discharge/intake valve mechanisms  56  with built-in discharge valves  27  and intake valves  28  are provided. In the third embodiment, each of the discharge/intake valve mechanisms  56  at the outside is connected to the medium passage  46 A which is provided with a heat exchanger  45 A, while each of the discharge/intake valve mechanisms  56  at the inside is connected to the medium passage  46 B which is provided with a heat exchanger  45 B. 
     In the third embodiment as well, if the permanent magnets  53  which are attached to one surface of the rotor  52  rotate by the motor  20 , along with rotation of the permanent magnets  53 , the rotary magnets  55  which face the permanent magnets  53  rotate following them due to the attraction force and therefore the yoke part  54  rotates. The point of the intensity of the magnetic field which is applied to the magnetocalorific effect material  26  which is filled in the material containers  25  is improved 30 to 60% compared with the case where permanent magnets  53  are provided only at one side of the magnetocalorific effect material  26  is the same. 
       FIG. 5A  is a cross-sectional view of a magnetic heat pump  40 A which illustrates a fourth embodiment in the magnetic heat pump system  30  which is illustrated in  FIG. 1 . The configuration of the magnetic heat pump  40 A of the fourth embodiment is almost the same as the configuration of the magnetic heat pump  40  of the second embodiment. The only point of difference is the point of provision of a drive mechanism  60  of the yoke part  44  which forcibly makes the yoke part  44  rotate from the outside. Accordingly, illustration of the right half of the magnetic heat pump  40 A not provided with the drive mechanism  60  of the yoke part  44  is omitted. Further, the end face plate  29  need only be attached to the shell  24  so as not to interfere with the ring gear G 4 . 
     In the fourth embodiment, one end of the cylindrical yoke part  44  is extended to the end face plate  29  by the extended part  44 E. The ring gear G 4  is attached to the outer circumferential part of the end part of the extended part  44 E. On the other hand, a large diameter first gear G 1  is attached to the shaft  21  between the reciprocating pump  13 A and the motor  20 . Further, the first gear G 1  and the ring gear G 4  are connected by the second and third gears G 2  and G 3  which are attached to the two ends of the drive shaft  47 . That is, if the first gear G 1  rotates, the second gear G 2  which meshes with the first gear G 1  rotates and the third gear G 3  which is connected to the second gear G 2  by the drive shaft  47  rotates. The third gear G 3  meshes with the ring gear G 4 , so the ring gear G 4  rotates.  FIG. 5B  illustrates the part where the third gear G 3  and the ring gear G 4  mesh. The rotational speed of the first gear G 1  and the rotational speed of the ring gear G 4  can be determined by adjustment of the number of teeth of the first to third gears. 
     If making the cylindrical yoke part  44  rotate by the drive mechanism  60 , it is possible to make the permanent magnets  43  rotate more accurately matching the rotation of the permanent magnets  23  compared with making the permanent magnets  43  rotate by the attraction force of the permanent magnets  23 . 
     Furthermore, as a modification, instead of the first and second gears G 1  and G 2  at the drive mechanism  60 , it is possible to use the belt mechanism  61  which is illustrated in  FIG. 5C  to drive the yoke part  44 . The belt mechanism  61  is provided with pulleys P 1  and P 2  which are attached to the shaft  21  and the drive shaft  47  and a belt  48  which is laid between the pulleys  21  and  22 . The rotation of the shaft  21  can be transmitted to the drive shaft  47  by the belt mechanism  61  in this way. 
       FIG. 6  is a cross-sectional view of a magnetic heat pump  40 B which illustrates a fifth embodiment in the magnetic heat pump system  30  which is illustrated in  FIG. 1 . The configuration of the magnetic heat pump  40 B of the fifth embodiment is almost the same as the configuration of the magnetic heat pump  40  of the second embodiment. The only point of difference is the provision of the drive mechanism  62  of the yoke part  44  which forcibly makes the yoke part  44  rotate from the outside. Accordingly, illustration of the right half of the magnetic heat pump  40 B not provided with the drive mechanism  62  of the yoke part  44  is omitted. 
     In the fifth embodiment, one end of the cylindrical yoke part  44  is extended to the outside of the end face plate  29  by the extended part  44 E. The ring gear G 4  is attached to the outer circumferential part of the extended part  44 E. This configuration is the same as the fourth embodiment. In the fourth embodiment, a large diameter first gear G 1  was attached to the shaft  21  and the rotation of the first gear G 1  was transmitted by the second and third gears G 2 , G 3  which were attached to the two ends of the drive shaft  47  to the ring gear G 4 . On the other hand, the fifth embodiment differs in the point of the drive shaft  47  of the third gear G 3  which meshes with the ring gear G 4  being the shaft of the motor  49  which is set at the outer circumferential surface of the shell  24 . 
     In the fifth embodiment, if the motor  49  rotates, the shaft of the motor  49 , that is, the drive shaft  47 , rotates and the third gear G 3  rotates, so the ring gear G 4  meshing with this rotates. In this way, if making the cylindrical yoke part  44  rotate according to the drive mechanism  62 , compared with making the permanent magnets  43  rotate by the attraction force of the permanent magnets  23 , it is possible to make the permanent magnets  43  rotate more accurately in accordance with rotation of the permanent magnets  23 . Further, the magnetic heat pump  40 B of the fifth embodiment can rotate the cylindrical yoke part  44  by drive force from the outside, so has the same effect as the magnetic heat pump  40 A of the fourth embodiment. 
     In the first to fifth embodiments explained above, the shaft  21  of the motor  20  is directly coupled with the magnetic heat pumps  40 ,  40 A,  40 B and  50 , so the rotational speeds of the rotors  22 ,  52  were the same as the rotational speed of the motor  20 . On the other hand, in the second to the fifth embodiments, the reciprocating pumps  13 A,  13 B are provided at the two sides of the magnetic heat pumps  40 ,  40 A,  40 B, and  50 . Therefore, in the second, fourth, and fifth embodiments, if providing a gear box at the shaft  21  between the reciprocating pumps  13 A,  13 B and the magnetic heat pumps  40 ,  40 A,  40 B, and  50 , the rotational speed of the rotor  22  can be made different from the rotational speed of the motor  20 . This will be explained using  FIG. 7  to  FIG. 9 . 
       FIG. 7  is a view which illustrates a configuration of a modified embodiment common to the magnetic heat pump  40  of the second embodiment which is illustrated in  FIG. 3  and the magnetic heat pump  50  of the third embodiment which is illustrated in  FIG. 5 . In this embodiment, a gear box GB 1  is provided at the shaft  21  between the reciprocating pump  13 A and the magnetic heat pump  40 ,  50  while a gear box GB 2  is provided at the shaft  21  between the magnetic heat pump  40 ,  50  and the reciprocating pump  13 B. The gear ratios of the gear boxes GB 1  and GB 2  are 2:1. If the motor  20  turns two times, the rotor at the center of the magnetic heat pump  40 ,  50  turns once. The rotational speed of the reciprocating pump  13 B is the same as the rotational speed of the reciprocating pump  13 A. 
       FIG. 8  is a view which illustrates a configuration of a modified embodiment of a magnetic heat pump  40 A of a fourth embodiment which is illustrated in  FIG. 5 . In this embodiment as well, a gear box GB 1  is provided at the shaft  21  between the reciprocating pump  13 A and the magnetic heat pump  40 , while a gear box GB 2  is provided at the shaft  21  between the magnetic heat pump  40  and the reciprocating pump  13 B. The gear ratios of the gear boxes GB 1  and GB 2  are 2:1. If the motor  20  turns two times, the rotor at the center of the magnetic heat pump  40 A turns once. The rotational speed of the reciprocating pump  13 B is the same as the rotational speed of the reciprocating pump  13 A. 
       FIG. 9  is a view which illustrates a configuration of a modified embodiment of a magnetic heat pump  40 B of a fifth embodiment which is illustrated in  FIG. 6 . In this embodiment as well, a gear box GB 1  is provided at the shaft  21  between the reciprocating pump  13 A and the magnetic heat pump  40 , while a gear box GB 2  is provided at the shaft  21  between the magnetic heat pump  40  and the reciprocating pump  13 B. The gear ratios of the gear boxes GB 1  and GB 2  are 2:1. If the motor  20  turns two times, the rotor in the magnetic heat pump  40 B turns once. The rotational speed of the reciprocating pump  13 B is the same as the rotational speed of the reciprocating pump  13 A. 
     In the above three modified embodiments, the gear ratios of the gear boxes GB 1  and GB 2  are 2:1, but by changing the gear ratios of the gear boxes GB 1  and GB 2 , it is possible to change the rotational speed of the rotor with respect to one turn of the motor  20 . 
     According to the magnetic heat pump system of the present invention, it is possible to increase the changes in the magnetic flux which is applied to the magnetocalorific effect material or the changes in the magnetic flux which is removed from the magnetocalorific effect material. Further, it is possible to increase the heating amount and cooling amount of the magnetic heat pump system and possible to make the magnetic heat pump system high in efficiency. Furthermore, the heating ability and cooling ability at the air-conditioning system are improved. 
     While the invention has been described by reference to specific embodiments chosen for purposes of illustration, it should be apparent that numerous modifications could be made thereto by those skilled in the art without departing from the basic concept and scope of the invention.