Patent Publication Number: US-2019173140-A1

Title: Temperature conditioning unit, temperature conditioning system, and vehicle

Description:
TECHNICAL FIELD 
     The present invention relates to a temperature conditioning unit, a temperature conditioning system, and a vehicle mounted with the temperature conditioning unit or the temperature conditioning system. The present invention relates more particularly to reduction of noise from the temperature conditioning unit. 
     BACKGROUND ART 
     Power storage devices that include a secondary battery and power converters that include an inverter and a converter (hereinafter collectively referred to as elements to temperature-condition) each produce heat because of internal resistance and external resistance during passage of electric current. When a temperature of the element to temperature-condition is too high, the element to temperature-condition does not fully exhibit its performance. Even when used at too low an ambient temperature, for example, in a cold region, the element to temperature-condition does not fully exhibit its performance. In other words, the temperature of the element to temperature-condition greatly affects an output characteristic or a power conversion characteristic of the element to temperature-condition and a life of the element to temperature-condition. 
     Those elements to temperature-condition can be mounted, for example, in a hybrid vehicle or an electric vehicle (EV). To ensure an internal cabin space of the vehicle, the element to temperature-condition is mounted in a limited area. As such, a plurality of battery cells that form the secondary battery are closely mounted in a housing that accommodates these battery cells, and their heat is hard to dissipate. Similarly, the power converter is placed in an environment where its heat is hard to dissipate. Moreover, the hybrid vehicle and the EV, for example, are required to be used in a wide temperature range. Even the element to temperature-condition mounted in these vehicles is required to operate in the wide temperature range. 
     In PTL 1, an intake and exhaust device (blower) forcibly feeds gas into a housing that accommodates an element to temperature-condition, thereby adjusting an interior of the housing to a temperature that is suitable for output of the secondary battery or operation of the power converter. Recently, higher output and smaller size are required of the secondary battery that is mounted in the hybrid vehicle. Accordingly, heat dissipation or heating of the secondary battery and the power converter is an increasingly important challenge. 
     To further dissipation of heat from the element to temperature-condition or to further heating of the element to temperature-condition, combined use of a plurality of intake and exhaust devices is conceivable. However, the combined use of the plurality of intake and exhaust devices can cause production of a considerably loud sound (noise) from these intake and exhaust devices. 
     CITATION LIST 
     Patent Literature 
     PTL 1: Unexamined Japanese Patent Publication No. 2010-080134 
     SUMMARY OF THE INVENTION 
     In one aspect, a temperature conditioning unit according to the present invention includes a first intake and exhaust device, a second intake and exhaust device, and a housing that accommodates an element to temperature-condition. The first intake and exhaust device and the second intake and exhaust device each include: a rotary drive device including a shaft and a rotary drive source that rotates the shaft; an impeller including an impeller disk that engages the shaft at its central part and includes a surface extending in a direction intersecting the shaft, and a plurality of rotor vanes erected on the impeller disk; and a fan case including a side wall surrounding the impeller, an intake port, and a vent communicating with an interior of the housing. The plurality of rotor vanes each extend in a direction from the central part to an outer peripheral part of the impeller disk in the shape of a circular arc bulging in a rotation direction of the shaft. A frequency at which the first intake and exhaust device produces a sound having an energy peak is different from a frequency at which the second intake and exhaust device produces a sound having an energy peak. 
     In one aspect, a temperature conditioning system according to the present invention includes a temperature conditioning unit, an intake duct connecting with respective intake ports of a first intake and exhaust device and a second intake and exhaust device, a plurality of supply ducts that supply gas to the intake duct, and a system controller that selects one or more from among the plurality of supply ducts to effect supply of the gas to the intake duct. 
     In another aspect, a temperature conditioning system according to the present invention includes a first temperature conditioning unit, a second temperature conditioning unit, a first intake duct connecting with respective intake ports of a first intake and exhaust device and a second intake and exhaust device of the first temperature conditioning unit, a first exhaust duct that lets gas out from an outlet of the first temperature conditioning unit, a second intake duct connecting with respective intake ports of a first intake and exhaust device and a second intake and exhaust device of the second temperature conditioning unit, a second exhaust duct that lets gas out from an outlet of the second temperature conditioning unit, and a circulation controller that selects at least one of the first exhaust duct and the second exhaust duct to effect supply of the gas to at least one of the first intake duct and the second intake duct. 
     In yet another aspect, a temperature conditioning system according to the present invention includes a first temperature conditioning unit, a second temperature conditioning unit, a first intake duct connecting with respective intake ports of a first intake and exhaust device and a second intake and exhaust device of the first temperature conditioning unit, a second intake duct connecting with respective intake ports of a first intake and exhaust device and a second intake and exhaust device of the second temperature conditioning unit, a connection duct branching off and connecting with the first intake duct and the second intake duct, and a flow rate controller that controls a flow rate of gas in the first intake duct and a flow rate of gas in the second intake duct. 
     In one aspect, a vehicle according to the present invention is mounted with a temperature conditioning unit. 
     In another aspect, a vehicle according to the present invention is mounted with a temperature conditioning system. 
     According to the present invention, a noise is produced in suppressed condition by the temperature conditioning unit including the plurality of intake and exhaust devices. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1A  is a perspective view schematically illustrating a temperature conditioning unit according to a first exemplary embodiment. 
         FIG. 1B  is a sectional view of the temperature conditioning unit, the section being taken on plane  1 B- 1 B of  FIG. 1A . 
         FIG. 2A  is a perspective view of a first intake and exhaust device of the temperature conditioning unit according to the first exemplary embodiment. 
         FIG. 2B  is a longitudinal section of the first intake and exhaust device of the temperature conditioning unit according to the first exemplary embodiment. 
         FIG. 3A  is a perspective view of an impeller that is disposed in the first intake and exhaust device of the temperature conditioning unit according to the first exemplary embodiment. 
         FIG. 3B  is a top plan view of first rotor vanes that are disposed in the first intake and exhaust device of the temperature conditioning unit according to the first exemplary embodiment. 
         FIG. 3C  is a perspective view of an impeller that is disposed in a second intake and exhaust device of the temperature conditioning unit according to the first exemplary embodiment. 
         FIG. 3D  is a top plan view of second rotor vanes that are disposed in the second intake and exhaust device of the temperature conditioning unit according to the first exemplary embodiment. 
         FIG. 4  is a graph showing a relationship between rotational order and energy of blade passing frequency (BPF) noise produced by the first and second intake and exhaust devices of the temperature conditioning unit of the first exemplary embodiment. 
         FIG. 5  illustrates a gas flow effected by each of the first rotor vanes disposed in the first intake and exhaust device of the temperature conditioning unit of the first exemplary embodiment. 
         FIG. 6  illustrates a gas flow effected by each of forward swept vanes disposed in the first intake and exhaust device of the temperature conditioning unit of the first exemplary embodiment. 
         FIG. 7  is a graph showing respective gas volume-pressure relationships of the gas flows that are respectively effected by the first rotor vane disposed in the first intake and exhaust device of the temperature conditioning unit of the first exemplary embodiment and the forward swept vane disposed in the first intake and exhaust device of the temperature conditioning unit of the first exemplary embodiment. 
         FIG. 8  is a graph showing a specific speed-fan efficiency relationship of the first intake and exhaust device using the first rotor vanes in the temperature conditioning unit of the first exemplary embodiment and a specific speed-fan efficiency relationship of the first intake and exhaust device using the forward swept vanes in the temperature conditioning unit of the first exemplary embodiment. 
         FIG. 9  is a graph showing a flow coefficient-pressure coefficient relationship of the first intake and exhaust device using the first rotor vanes in the temperature conditioning unit of the first exemplary embodiment and a flow coefficient-pressure coefficient relationship of the first intake and exhaust device using the forward swept vanes in the temperature conditioning unit of the first exemplary embodiment. 
         FIG. 10  is a block diagram illustrating a first temperature conditioning system according to the first exemplary embodiment. 
         FIG. 11  is a block diagram illustrating a second temperature conditioning system according to the first exemplary embodiment. 
         FIG. 12  is a block diagram illustrating a third temperature conditioning system according to the first exemplary embodiment. 
         FIG. 13A  is a schematic view of a vehicle according to the first exemplary embodiment. 
         FIG. 13B  is a schematic view of another vehicle according to the first exemplary embodiment. 
         FIG. 14A  is a longitudinal section of a first intake and exhaust device according to a second exemplary embodiment. 
         FIG. 14B  is a longitudinal section of a second intake and exhaust device according to the second exemplary embodiment. 
         FIG. 15  is a sectional perspective view of a first intake and exhaust device according to a third exemplary embodiment. 
         FIG. 16  is a perspective view illustrating an impeller and stator vanes according to the third exemplary embodiment. 
         FIG. 17A  is a perspective view schematically illustrating a temperature conditioning unit according to a fourth exemplary embodiment. 
         FIG. 17B  is a sectional view of the temperature conditioning unit, the section being taken on plane  17 B- 17 B of  FIG. 17A . 
         FIG. 18A  is a perspective view schematically illustrating a temperature conditioning unit according to a fifth exemplary embodiment. 
         FIG. 18B  is a sectional view of the temperature conditioning unit, the section being taken on plane  18 B- 18 B of  FIG. 18A . 
         FIG. 19A  is a perspective view of a third intake and exhaust device of the temperature conditioning unit according to the fifth exemplary embodiment. 
         FIG. 19B  is a longitudinal section of the third intake and exhaust device of the temperature conditioning unit according to the fifth exemplary embodiment. 
         FIG. 20A  is a perspective view of an impeller that is disposed in the third intake and exhaust device of the temperature conditioning unit according to the fifth exemplary embodiment. 
         FIG. 20B  is a top plan view of third rotor vanes that are disposed in the third intake and exhaust device of the temperature conditioning unit according to the fifth exemplary embodiment. 
         FIG. 20C  is a perspective view of an impeller that is disposed in a fourth intake and exhaust device of the temperature conditioning unit according to the fifth exemplary embodiment. 
         FIG. 20D  is a top plan view of fourth rotor vanes that are disposed in the fourth intake and exhaust device of the temperature conditioning unit according to the fifth exemplary embodiment. 
         FIG. 21  is a graph showing a relationship between rotational order and energy of BPF noise produced by the third and fourth intake and exhaust devices of the temperature conditioning unit of the fifth exemplary embodiment. 
         FIG. 22  is a sectional view of the third intake and exhaust device in the temperature conditioning unit of the fifth exemplary embodiment, as viewed from an intake port. 
         FIG. 23  is a block diagram illustrating a fourth temperature conditioning system according to the fifth exemplary embodiment. 
         FIG. 24  is a block diagram illustrating a fifth temperature conditioning system according to the fifth exemplary embodiment. 
         FIG. 25  is a block diagram illustrating a sixth temperature conditioning system according to the fifth exemplary embodiment. 
         FIG. 26A  is a schematic view of a vehicle according to the fifth exemplary embodiment. 
         FIG. 26B  is a schematic view of another vehicle according to the fifth exemplary embodiment. 
         FIG. 27A  is a longitudinal section of a third intake and exhaust device according to a sixth exemplary embodiment. 
         FIG. 27B  is a longitudinal section of a fourth intake and exhaust device according to the sixth exemplary embodiment. 
         FIG. 28A  is a perspective view schematically illustrating a temperature conditioning unit according to a seventh exemplary embodiment. 
         FIG. 28B  is a sectional view of the temperature conditioning unit, the section being taken on plane  28 B- 28 B of  FIG. 28A . 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     An aerodynamic sound caused by rotor vanes is cited as a typical noise produced by an intake and exhaust device. The aerodynamic sound is also referred to as BPF noise or discrete frequency noise. Frequency Fb (Hz) at which BPF noise energy peaks is calculated by Formula 1 below. 
         Fb=m×r/ 60× N   Formula 1
 
     In Formula 1, m is an integer greater than or equal to 1, r is rotational speed (rpm) of an impeller, and N is a number of rotor vanes. 
     Pressure (static pressure) and volume of gas that is supplied or discharged by the intake and exhaust device affect efficiency of cooling an element to temperature-condition. As such, in cases where a plurality of intake and exhaust devices are disposed for a housing, the intake and exhaust devices generally have impellers of the same type and are driven with their impellers having common rotational speed r. In this way, the intake and exhaust devices respectively supply or discharge gases that are comparable in pressure and volume. Accordingly, the element to temperature-condition is uniformly cooled or heated. In such cases, respective BPF noise frequencies Fb of the intake and exhaust devices that are calculated by Formula 1 are the same. This means that the intake and exhaust devices have coincident BPF noise energy peaks. As a consequence, a noise produced is at a maximum level. It is to be noted that a BPF noise generally has the highest energy peak at the lowest frequency Fb (i.e., when m=1) that is calculated by Formula 1. 
     In exemplary embodiments of the present invention, in cases where intake and exhaust devices to dispose for a housing are greater than or equal to two in number, frequency Fb at which at least one of those intake and exhaust devices produces a sound (BPF noise) having peak energy is made different from frequency Fb at which another intake and exhaust device produces a BPF noise having peak energy. In this way, BPF noise peaks are dispersed when the plurality of intake and exhaust devices are used. 
     As shown in Formula 1, frequency Fb at which a BPF noise has peak energy varies based on number N of rotor vanes and rotational speed r of the rotor vanes. A description is hereinafter provided of the first exemplary embodiment in which two intake and exhaust devices with different numbers N of rotor vanes are used, the second exemplary embodiment in which two intake and exhaust devices with different rotational speeds r are used, and modifications of these exemplary embodiments (the third exemplary embodiment). 
     First Exemplary Embodiment 
     A temperature conditioning unit according to the present exemplary embodiment includes a first intake and exhaust device, a second intake and exhaust device, and a housing that accommodates an element to temperature-condition. The first intake and exhaust device and the second intake and exhaust device have different numbers of rotor vanes. 
     With reference to  FIGS. 1A to 4 , a specific description is hereinafter provided of temperature conditioning unit  100 X according to the first exemplary embodiment.  FIG. 1A  is a perspective view schematically illustrating temperature conditioning unit  100 X according to the first exemplary embodiment.  FIG. 1B  is a sectional view of temperature conditioning unit  100 X, the section being taken on plane  1 B- 1 B of  FIG. 1A .  FIG. 2A  is a perspective view of first intake and exhaust device  10 A of temperature conditioning unit  100 X according to the first exemplary embodiment.  FIG. 2B  is a longitudinal section of first intake and exhaust device  10 A of temperature conditioning unit  100 X in the first exemplary embodiment.  FIG. 3A  is a perspective view of impeller  110 A that is disposed in first intake and exhaust device  10 A of temperature conditioning unit  100 X according to the first exemplary embodiment.  FIG. 3B  is a top plan view of first rotor vanes  112 A that are disposed in first intake and exhaust device  10 A of temperature conditioning unit  100 X according to the first exemplary embodiment.  FIG. 3C  is a perspective view of impeller  210 A that is disposed in second intake and exhaust device  20 A of temperature conditioning unit  100 X according to the first exemplary embodiment.  FIG. 3D  is a top plan view of second rotor vanes  212 A of temperature conditioning unit  100 X according to the first exemplary embodiment. In  FIGS. 3B and 3D , shrouds  113 A,  213 A are omitted. In  FIGS. 3B and 3D , impeller disks  111 A,  211 A are indicated by broken lines.  FIG. 4  is a graph showing a relationship between rotational order and energy of BPF noise produced by first and second intake and exhaust devices  10 A and  20 A of temperature conditioning unit  100 X of the first exemplary embodiment. In the drawings, members having identical functions have the same reference marks. 
     (Temperature Conditioning Unit) 
     As illustrated in  FIGS. 1A and 1B , temperature conditioning unit  100 X includes first intake and exhaust device  10 A, second intake and exhaust device  20 A, and housing  30 . Housing  30  accommodates element  50  to temperature-condition. Housing  30  is provided with at least one inlet  30   a  where external gas is taken in and at least one outlet  30   b  where the gas is discharged out of housing  30 . 
     First intake and exhaust device  10 A and second intake and exhaust device  20 A are mounted such that their respective vents  123  face inlets  30   a , respectively. This means that first intake and exhaust device  10 A and second intake and exhaust device  20 A function as blowers in the present exemplary embodiment. Inlets  30   a  communicate with external space, an exhaust duct (described later), or an intake duct (described later) via respective first and second intake and exhaust devices  10 A and  20 A. Also outlets  30   b  communicate with the external space, the exhaust duct (described later), or the intake duct (described later). Thus, the gas flows into housing  30  through first intake and exhaust device  10 A and second intake and exhaust device  20 A. 
     As illustrated in  FIG. 1B , element  50  to temperature-condition is disposed to divide an interior of housing  30  into intake-side chamber  31  including inlets  30   a  and exhaust-side chamber  32  including outlets  30   b . The gas forcibly fed through inlets  30   a  by first intake and exhaust device  10 A and second intake and exhaust device  20 A diffuses throughout intake-side chamber  31 , passes through gaps in element  50  to temperature-condition or between element  50  to temperature-condition and housing  30  and then flows into exhaust-side chamber  32 . That is when element  50  is temperature-conditioned, namely, cooled or heated. The gas that has flowed into exhaust-side chamber  32  is discharged into the external space through outlets  30   b . Here the flow of gas is indicated as an example by outlined arrows. 
     Intake-side chamber  31  and exhaust-side chamber  32  may be equal or different in capacity. Above all, intake-side chamber  31  preferably has a larger capacity than exhaust-side chamber  32 . Intake-side chamber  31  generally has a higher internal pressure than exhaust-side chamber  32 . With the capacity of intake-side chamber  31  being larger, intake-side chamber  31  has decreased pressure resistance, thus having uniform pressure distribution. Consequently, the gas spreads throughout element  50  to temperature-condition without nonuniformity, whereby element  50  is entirely temperature-conditioned, namely, cooled or heated with efficiency. 
     Temperature conditioning unit  100 X may have one outlet  30   b  or outlets  30   b  that are greater than or equal to two in number. A number of intake and exhaust devices to dispose in temperature conditioning unit  100 X is not particularly limited as long as the number of intake and exhaust devices is greater than or equal to 2. Also disposition of element  50  to temperature-condition is not particularly limited. Element  50  to temperature-condition may be suitably disposed based on, for example, a use or its kind. 
     (Intake and Exhaust Devices) 
     First intake and exhaust device  10 A is given as an example to describe structure of first intake and exhaust device  10 A and structure of second intake and exhaust device  20 A. Except for the difference in the number of rotor vanes, first intake and exhaust device  10 A and second intake and exhaust device  20 A may be structurally similar. Alternatively, in addition to the difference in the number of rotor vanes, there may be another structural difference (for example, a difference in impeller disk size) between first intake and exhaust device  10 A and second intake and exhaust device  20 A. 
     As shown in  FIGS. 2A and 2B , first intake and exhaust device  10 A includes impeller  110 A, fan case  120 , and rotary drive device  130 . Impeller  110 A includes impeller disk  111 A and the plurality of first rotor vanes  112 A. Fan case  120  includes side wall  121 , intake port  122 , and vent  123 . Rotary drive device  130  includes shaft  131  and rotary drive source  132  that rotates shaft  131 . 
     (Impeller) 
     Impeller  110 A includes impeller disk  111 A and the plurality of first rotor vanes  112 A. Impeller  110 A may also include shroud  113 A. 
     (Impeller Disk) 
     Impeller disk  111 A is substantially circular and has a surface extending in a direction intersecting shaft  131  (preferably, perpendicularly to shaft  131 ). The plurality of first rotor vanes  112 A are erected on one of principal surfaces of impeller disk  111 A. Impeller disk  111 A has an opening in a part of its central part  111 AC (refer to  FIG. 3B ). Shaft  131  is inserted into this opening to engage impeller disk  111 A. Rotary drive source  132  is rotationally driven, whereby impeller  110 A rotates. As illustrated in  FIG. 2B , outer peripheral part  111 AP (refer to  FIG. 3B ) of impeller disk  111 A may be partly bent toward vent  123 . In this way, the gas taken into first intake and exhaust device  10 A flows smoothly toward vent  123 . 
     (Shroud) 
     Shroud  113 A is formed of a ring-shaped plate and is disposed to face impeller disk  111 A via first rotor vanes  112 A. When impeller  110 A is viewed in an axial direction of shaft  131 , an outer peripheral edge of impeller disk  111 A is substantially aligned with an outer peripheral edge of shroud  113 A. Here outer peripheral part  111 AP of impeller disk  111 A is partly covered by shroud  113 A. Each of first rotor vanes  112 A is partly joined to shroud  113 A. The gas taken into impeller  110 A flows along first rotor vanes  112 A, flows out from the outer peripheral edge of impeller disk  111 A and then collides against side wall  121 , thereby being guided to vent  123 . Shroud  113 A suppresses outflow of the gas that has flowed out from the outer peripheral edge of impeller disk  111 A from intake port  122 . Shroud  113 A suppresses entry of the gas that has flowed out of an inter-vane passage formed by two adjacent first rotor vanes  112 A into an adjacent inter-vane passage. To suppress a turbulent flow of gas, shroud  113 A is preferably funnel-shaped or tapered having a gently curved surface that narrows toward intake port  122 . 
     (Rotor Vanes) 
     The plurality of first rotor vanes  112 A are erected on the one of the principal surfaces of impeller disk  111 A. As illustrated in  FIG. 3B , first rotor vanes  112 A each extend in a direction from central part  111 AC to outer peripheral part  111 AP of impeller disk  111 A in the shape of a circular arc bulging in rotation direction D of shaft  131 . 
     Similarly, the plurality of second rotor vanes  212 A disposed in second intake and exhaust device  20 A each extend, as illustrated in  FIGS. 3C and 3D , in a direction from central part  211 AC to outer peripheral part  211 AP of impeller disk  211 A in the shape of a circular arc bulging in rotation direction D. Impeller  210 A of second intake and exhaust device  20 A is structurally similar to impeller  110 A. Impeller  210 A may also include shroud  213 A. 
     Here number N1 of first rotor vanes  112 A and number N2 of second rotor vanes  212 A satisfy Relational Expression 1 and Relational Expression 2. 
         N 1≠ N 2× n 1 (where n1 is an integer greater than or equal to 1)  Relational Expression 1
 
         N 1≠ N 2/ n 2 (where n2 is an integer greater than or equal to 2)  Relational Expression 2
 
     In other words, number N1 of first rotor vanes  112 A is different from number N2 of second rotor vanes  212 A, and number N1 is neither an integral multiple of number N2 nor a value obtained by division of number N2 by the integer. Accordingly, BPF noise frequency Fb1 of first intake and exhaust device  10 A does not coincide with BPF noise frequency Fb2 of second intake and exhaust device  20 A, irrespective of integer m. In this way, BPF noises are dispersed in terms of energy, and a noise is produced in suppressed condition by temperature conditioning unit  100 X. 
       FIG. 4  is a graph showing a relationship between rotational order and energy of BPF noise produced by first and second intake and exhaust devices  10 A and  20 A of temperature conditioning unit  100 X of the first exemplary embodiment. The rotational order is obtained by division of measured frequency F by a rotational frequency (r/60) of the intake and exhaust device. Generally, BPF noise energy is greater when the rotational order is a multiple of number N of rotor vanes. A broken line in  FIG. 4  indicates the BPF noise energy of the exemplary embodiment&#39;s temperature conditioning unit  100 X including first intake and exhaust device  10 A and second intake and exhaust device  20 A. A solid line in  FIG. 4  indicates BPF noise energy of a temperature conditioning unit of a comparative example that includes two first intake and exhaust devices  10 A. In the case of the exemplary embodiment, it is shown that BPF noise energy peaks are dispersed and that BPF noise is suppressed. When respective overall values (each of which represents total energy of sounds produced by the temperature conditioning unit at all frequencies) of those temperature conditioning units were compared, the overall value was about 2% lower in the exemplary embodiment compared with the overall value of the comparative example. While  FIG. 4  shows the relationship between the rotational order and the BPF noise energy when first intake and exhaust device  10 A includes eleven first rotor vanes  112 A with second intake and exhaust device  20 A including nine second rotor vanes  212 A, a similar tendency is seen even when first intake and exhaust device  10 A and second intake and exhaust device  20 A each have the number of rotor vanes varied. 
     Number N1 of first rotor vanes  112 A and number N2 of second rotor vanes  212 A are not particularly limited. Number N1 of first rotor vanes  112 A and number N2 of second rotor vanes  212 A may be set appropriately in consideration of, for example, sizes of impellers  110 A and  210 A and respective gas volumes and respective pressures of first and second intake and exhaust devices  10 A and  20 A. Number N1 of first rotor vanes  112 A is, for example, between 5 and 30 inclusive. Number N2 of second rotor vanes  212 A is, for example, between 8 and 15 inclusive. As long as Relational Expression 1 and Relational Expression 2 are satisfied, the difference between number N1 and number N2 is not particularly limited and may be greater than or equal to 1. When the respective gas volumes and the respective pressures of first and second intake and exhaust devices  10 A and  20 A are taken into consideration, the difference between number N1 and number N2 is preferably between 1 and 5 inclusive. 
     In cases where an electric motor is used as rotary drive device  130 , a stator is disposed in the electric motor. The stator generally has an even number of poles. For this reason, in cases where at least one of number N1 of first rotor vanes  112 A and number N2 of second rotor vanes  212 A is even, first rotor vanes  112 A and second rotor vanes  212 A become exciting forces, whereby rotary drive device  130 , first intake and exhaust device  10 A, and second intake and exhaust device  20 A all experience vibrational excitation, and an increased noise can be caused. As such, it is preferable that number N1 of first rotor vanes  112 A and number N2 of second rotor vanes  212 A be both odd in such cases. The number of poles is a number of magnetic poles generated in rotary drive device  130 . Even in cases where a number of slots of the stator corresponds to at least one of number N1 of first rotor vanes and number N2 of second rotor vanes  212 A or even in cases where the number of slots and the at least one of number N1 and number N2 are integral multiples of each other, an increased noise can be caused. As such, each of number N1 of first rotor vanes and number N2 of second rotor vanes  212 A is preferably set so as to neither correspond to the number of slots nor be the integral multiple of the number of slots or vice versa. 
     As illustrated in  FIG. 3B , each of first rotor vanes  112 A extends in the shape of the circular arc bulging in rotation direction D of shaft  131 , starting from a point of choice as starting point  112 As in central part  111 AC and ending at a point of choice (end point  112 Ae) in outer peripheral part  111 AP. First rotor vane  112 A includes a projecting portion that projects in rotation direction 
     D. Accordingly, gas taken into first intake and exhaust device  10 A can flow out along the projecting portion in the direction from central part  111 AC to outer peripheral part  111 AP with the gas flow not being greatly disturbed. It is to be noted here that when impeller disk  111 A has radius r, central part  111 AC of impeller disk  111 A is a circle that is concentric with impeller disk  111 A and has a radius of 1/2×r. Outer peripheral part  111 AP of impeller disk  111 A is a doughnut-shaped area surrounding central part  111 AC. 
     When rotor vanes are longer radially of an impeller disk, an impeller generally produces easily increased fluid energy. Since first rotor vane  112 A including the above-described projecting portion does not easily disturb the gas flow, first rotor vane  112 A can be made longer radially of impeller disk  111 A. Because fluid energy is easily increased, end point  112 Ae is preferably positioned near the outer peripheral edge of impeller disk  111 A. From a similar point of view, starting point  112 As is preferably near center C (e.g., in a circle that is concentric with impeller disk  111 A and has a radius of 1/3×r). 
     The shape of first rotor vane  112 A is not particularly limited as long as first rotor vane  112 A includes the projecting portion. For example, when impeller  110 A is viewed in the axial direction of shaft  131 , straight line Ls connecting starting point  112 As of first rotor vane  112 A and center C of impeller disk  111 A may be positioned ahead of straight line Le connecting end point  112 Ae of first rotor vane  112 A and center C of impeller disk  111 A in rotation direction D. 
     (Fan Case) 
     Fan case  120  includes side wall  121  surrounding impeller  110 A, intake port  122 , and vent  123  communicating with the interior of housing  30 . In  FIG. 2B , fan case  120  disposed is illustrated as having intake port  122  and vent  123  that face each other in the axial direction of shaft  131 . However, fan case  120  is not limited to this shape. For example, fan case  120  may be scroll-shaped with a distance from shaft  131  to side wall  121  increasing in rotation direction D. In this case, gas drawn in at intake port  122  flows in an axial direction of shaft  131 . When blown from vent  123 , the gas flows in a direction intersecting the axial direction of shaft  131 . Above all, fan case  120  that is illustrated in  FIGS. 2A and 2B  is preferable in terms of ease of reduction in size. With fan case  120  (specifically side wall  121 ) partly inserted in housing  30  in this case, temperature conditioning unit  100 X can be made smaller in size. A description is hereinafter provided of fan case  120  illustrated in  FIGS. 2A and 2B . 
     Side wall  121  is, for example, substantially cylindrical with shaft  131  being its center. A distance from shaft  131  to side wall  121  is substantially fixed. Side wall  121  includes shoulder  121 S near an opening edge of intake port  122 . Because of shoulder  121 S, the opening edge of intake port  122  has a smaller diameter than an opening edge of vent  123 . Intake port  122  is, for example, substantially circular with shaft  131  being its center. Vent  123  is, for example, doughnut-shaped encircling impeller disk  111 A with shaft  131  being its center. 
     Intake port  122  and vent  123  are disposed to face each other in the axial direction of shaft  131 . Gas around intake port  122  (generally, ambient air) is taken in through intake port  122  by rotation of first rotor vanes  112 A. At the same time, the gas taken in through intake port  122  is given energy, gains speed, flows along first rotor vanes  112 A, and flows out from the outer peripheral edge of impeller disk  111 A. Subsequently, the gas changes its direction by colliding against side wall  121  of fan case  120  and then flows into housing  30  through vent  123 . It is to be noted here that shoulder  121 S is preferably formed to have a gently curved surface for suppressing a turbulent flow of gas. 
     Respective materials for the impeller disk, the rotor vane, the shroud, the side wall, and a stator vane that is described later are not particularly limited and are suitably selected based on a use. Given examples of those materials include various metallic materials, various resin materials, and combinations of these materials. 
     (Rotary Drive Device) 
     Rotary drive device  130  includes shaft  131  and rotary drive source  132  that rotates shaft  131 . As shaft  131  is rotationally driven by rotary drive source  132 , impeller  110 A rotates, and gas is taken into fan case  120  through intake port  122 . 
     Rotary drive device  130  is, for example, the electric motor. The electric motor is an electric appliance that outputs rotational motion through use of force of interaction between a magnetic field and an electric current (namely, Lorentz force). In the electric motor, rotary drive source  132  includes a rotor (not illustrated) and the stator (not illustrated) that produces force to rotate the rotor. Respective shapes of and respective materials for the rotor and the stator are not particularly limited, and a publicly known electric motor may be used. An output of the electric motor is not particularly limited and may be set appropriately based on, for example, a desired gas volume and a desired pressure. For example, in cases where temperature conditioning unit  100 X is mounted in a hybrid vehicle, the output of the electric motor is about several tens of watts. 
     The stator has stator windings. When the electric current is passed through the stator winding, a magnetic field is produced around the stator winding. The magnetic field causes the rotor to rotate. A material for the stator winding is not particularly limited as long as the material is electrically conductive. Above all, the stator winding preferably includes at least one selected from the group consisting of copper, copper alloy, aluminum, and aluminum alloy in terms of low resistance. 
     (Blower Controller) 
       FIG. 10  is a block diagram illustrating first temperature conditioning system  500  according to the first exemplary embodiment. Temperature conditioning unit  100 X may be provided with blower controller  40  (refer to  FIG. 10 ) that controls first intake and exhaust device  10 A and second intake and exhaust device  20 A. Blower controller  40  controls, for example, the rotational speed of each of the impellers and an amount of gas that is supplied to each of the intake ports. 
     (Element to Temperature-Condition) 
     Element  50  to temperature-condition is not particularly limited. Given examples of element  50  to temperature-condition include various devices that are mounted in a vehicle such as an electric vehicle or the hybrid vehicle. Those various devices include, for example, a power storage device including a secondary battery, power converters such as an inverter and a converter, an engine control unit, and a motor. The power storage device is formed of, for example, a battery pack that is a combination of a plurality of secondary batteries. A gap is formed between adjacent secondary batteries here, and gas passes through this gap. Similarly, even with the power converter having a gap formed between its components, gas passes through that gap. 
     A number of elements  50  to temperature-condition that are accommodated by housing  30  may be greater than or equal to 1 or may be greater than or equal to 2. In cases where elements  50  to temperature-condition that are accommodated by housing  30  are greater than or equal to two in number, the interior of housing  30  may be divided based on the number of elements  50  to temperature-condition. A course of gas blown from first intake and exhaust device  10 A and a course of gas blown from second intake and exhaust device  20 A may be independent of each other or may be connected. At least one of the gas course of first intake and exhaust device  10 A and the gas course of second intake and exhaust device  20 A may branch off based on the number of elements  50  to temperature-condition. 
     With reference to  FIGS. 5 to 9 , first rotor vanes  112 A are compared below with rotor vanes (hereinafter “forward swept vanes  912 ”) that each have a projecting portion projecting in a direction opposite to rotation direction D in contrast to first rotor vanes  112 A.  FIG. 5  illustrates gas flow C effected by first rotor vane  112 A disposed in first intake and exhaust device  10 A of temperature conditioning unit  100 X of the first exemplary embodiment.  FIG. 6  illustrates gas flow C 912  effected by forward swept vane  912  disposed in first intake and exhaust device  10 A of temperature conditioning unit  100 X of the first exemplary embodiment. In  FIG. 5 , end point  112 Ae of first rotor vane  112 A is positioned near the outer peripheral edge of impeller disk  111 A. In  FIG. 6 , end point  912   e  of forward swept vane  912  is positioned near an outer peripheral edge of impeller disk  911  on which forward swept vane  912  is erected. 
     When first rotor vane  112 A is rotated, as illustrated in  FIG. 5 , gas flow C is effected by first rotor vane  112 A, making angle θ 1  with line Li that is tangent to impeller disk  111 A at end point  112 Ae. When forward swept vane  912  is rotated, as illustrated in  FIG. 6 , gas flow C 912  is effected by forward swept vane  912 , making angle θ 2  with line Lif that is tangent to impeller disk  911  at end point  912   e . Here angle θ 1  is greater than angle θ 2 . This means that gas flow C effected by first rotor vane  112 A has larger flow component Cb in a direction indicated by line Lb that is tangent to first rotor vane  112 A at end point  112 Ae compared with flow component Cf in a direction indicated by line Lf that is tangent to forward swept vane  912  at end point  912   e . For this reason, fluid energy produced by impeller  110 A is greater when first rotor vanes  112 A are used compared to when forward swept vanes  912  are used. 
       FIG. 7  is a graph showing respective gas volume Q-pressure P relationships of the gas flows that are respectively effected by first rotor vane  112 A disposed in first intake and exhaust device  10 A of temperature conditioning unit  100 X of the first exemplary embodiment and forward swept vane  912  disposed in first intake and exhaust device  10 A of temperature conditioning unit  100 X of the first exemplary embodiment. As described above, first rotor vane  112 A can be made longer radially of impeller disk  111 A. With first rotor vane  112 A being longer radially of impeller disk  111 A, a gas flow velocity difference is increased between starting point  112 As and end point  112 Ae when impeller  110 A is rotated. Thus, as illustrated by  FIG. 7 , intake and exhaust device  10 A including first rotor vanes  112 A can perform high-pressure blowing, irrespective of the shape of the fan case. On the other hand, forward swept vane  912  cannot be made longer radially of impeller disk  911  compared with first rotor vane  112 A because forward swept vane  912  easily disturbs the gas flow. Accordingly, pressure of an intake and exhaust device including forward swept vanes  912  is generally increased by a scroll-shaped fan case (see above). This means that first intake and exhaust device  10 A including first rotor vanes  112 A can be reduced in size. Moreover, because the pressure is high, first intake and exhaust device  10 A including first rotor vanes  112 A is suitable for cooling or heating (temperature-conditioning) of element  50  even with increased pressure resistance due to the reduction in size. 
       FIG. 8  is a graph showing a specific speed n s -fan efficiency η (%) relationship of first intake and exhaust device  10 A using first rotor vanes  112 A in temperature conditioning unit  100 X of the first exemplary embodiment and a specific speed n s -fan efficiency η (%) relationship of first intake and exhaust device  10 A using forward swept vanes  912  in temperature conditioning unit  100 X of the first exemplary embodiment. When forward swept vanes  912  are used, with increasing specific speed n s , energy loss increases, and fan efficiency η decreases. When first rotor vanes  112 A are used, while energy loss increases with increasing specific speed n s , higher fan efficiency is exhibited than when forward swept vanes  912  are used. 
     Specific speed n s  is obtained by Formula 2. 
         n   s   =r×√Q /( gH ) 3/4   Formula 2
 
      where r is rotational speed (per minute), Q is a flow rate (m 3 /min), g is gravitational acceleration (m/s 2 ), and H is head (m). 
     Fan efficiency η is obtained by Formula 3. 
       η= E/P   Formula 3
 
     where E is effective energy per second (J/s) that gas receives from the impeller, and P is drive shaft power (W). 
       FIG. 9  is a graph showing a flow coefficient ( 1 )-pressure coefficient w relationship of first intake and exhaust device  10 A using first rotor vanes  112 A in temperature conditioning unit  100 X of the first exemplary embodiment and a flow coefficient ϕ-pressure coefficient Ψ relationship of first intake and exhaust device  10 A using forward swept vanes  912  in temperature conditioning unit  100 X of the first exemplary embodiment. When forward swept vanes  912  are used in the intake and exhaust device, pressure coefficient Ψ is higher than when first rotor vanes  112 A are used, irrespective of flow coefficient ϕ. However, with increasing flow coefficient ϕ, pressure coefficient Ψ of the intake and exhaust device greatly fluctuates between a positive side and a negative side, showing an unsteady tendency. On the other hand, when first rotor vanes  112 A are used in the intake and exhaust device, even with increasing flow coefficient ϕ, pressure coefficient Ψ decreases only gently. In other words, intake and exhaust device  10 A including first rotor vanes  112 A exhibits steady pressure coefficient Ψ that is not greatly affected by flow coefficient ϕ, so that high-speed rotation cab be carried out for an increased gas volume. 
     Pressure coefficient Ψ is obtained by Formula 4. 
       Ψ=2× g×H/u   2   Formula 4
 
     where H is head (m), and u is peripheral speed (m/s) of a periphery (fan outside diameter) of a circle formed by connection of end points  112 Ae of the plurality of first rotor vanes. It is to be noted that in the preset exemplary embodiment, respective outside diameters of impeller disk  111 A and shroud  113 A correspond to the above fan outside diameter. 
     As described above, temperature conditioning unit  100 X according to the present exemplary embodiment includes first intake and exhaust device  10 A, second intake and exhaust device  20 A, and housing  30  that accommodates element  50  to temperature-condition. First intake and exhaust device  10 A and second intake and exhaust device  20 A each include: rotary drive device  130  including shaft  131  and rotary drive source  132  that rotates shaft  131 ; impeller  110 A including impeller disk  111 A that engages shaft  131  at central part  111 AC and includes the surface extending in the direction intersecting shaft  131 , and a plurality of rotor vanes corresponding to first rotor vanes  112 A erected on impeller disk  111 A; and fan case  120  including side wall  121  surrounding impeller  110 A, intake port  122 , and vent  123  communicating with the interior of housing  30 . The plurality of rotor vanes each extend in the direction from central part  111 AC to outer peripheral part  111 AP of the impeller disk in the shape of the circular arc bulging in the rotation direction of shaft  131 . Frequency Fb1 at which first intake and exhaust device  10 A produces a sound having an energy peak is different from frequency Fb2 at which second intake and exhaust device  20 A produces a sound having an energy peak. 
     In this way, a noise is produced in suppressed condition by the temperature conditioning unit including the plurality of intake and exhaust devices. 
     It is to be noted here that intake port  122  and vent  123  are disposed to face each other in the axial direction of the shaft. 
     Number N1 of first rotor vanes  112 A of first intake and exhaust device  10 A and number N2 of second rotor vanes  212 A of second intake and exhaust device  20 A preferably satisfy the relationships: 
         N 1≠ N 2× n 1 (where n1 is the integer greater than or equal to 1); and
 
         N 1≠ N 2/ n 2 (where n2 is the integer greater than or equal to 2).
 
     Temperature conditioning unit  100 X may also be provided with blower controller  40  that controls first intake and exhaust device  10 A and second intake and exhaust device  20 A. 
     Element  50  to temperature-condition may be the secondary battery. 
     Another alternative may be that element  50  to temperature-condition is the power converter. 
     At least one of rotary drive device  130  of first intake and exhaust device  10 A and rotary drive device  130  of second intake and exhaust device  20 A may be the electric motor. 
     The stator winding of the electric motor preferably includes at least one selected from the group consisting of copper, copper alloy, aluminum, and aluminum alloy. 
     The distance from shaft  131  to side wall  121  of fan case  120  may increase in rotation direction D of shaft  131 . 
     Gas drawn in at intake port  122  preferably flows in the direction along shaft  131 , and when blown from vent  123 , the gas preferably flows in the direction intersecting shaft  131 . 
     (Temperature Conditioning Systems) 
     A description is provided next of temperature conditioning systems. 
     The temperature conditioning systems are each formed to include a plurality of ducts connected to temperature conditioning unit(s)  100 X. With reference to  FIGS. 10 to 12 , the temperature conditioning systems according to the first exemplary embodiment are hereinafter described specifically.  FIG. 10  is the block diagram illustrating first temperature conditioning system  500  according to the first exemplary embodiment.  FIG. 11  is a block diagram illustrating second temperature conditioning system  600  according to the first exemplary embodiment.  FIG. 12  is a block diagram illustrating third temperature conditioning system  700  according to the first exemplary embodiment. In the drawings, members having identical functions have the same reference marks. In the following description, an example in which each of the temperature conditioning systems is mounted in the hybrid vehicle is given; however, the present invention is not limited to this. 
     (First Temperature Conditioning System) 
     As illustrated in  FIG. 10 , first temperature conditioning system  500  includes, for example, intake duct  511 , a plurality of supply ducts, and system controller  530 . Intake duct  511  connects with the respective intake ports of first intake and exhaust device  10 A and second intake and exhaust device  20 A of temperature conditioning unit  100 X. The plurality of supply ducts each supply gas to intake duct  511  and includes, in  FIG. 10 , first supply duct  512 A, second supply duct  512 B, and third supply duct  512 C. System controller  530  controls gas supply sources for temperature conditioning unit  100 X. 
     Intake duct  511  connects with supply ducts  512 A to  512 C via supply source switching unit  510 . First supply duct  512 A has one end connecting with an exterior of the vehicle and another end connecting with supply source switching unit  510 . Second supply duct  512 B has one end connecting with an interior of the vehicle and another end connecting with supply source switching unit  510 . Third supply duct  512 C has one end connecting with discharge destination switching unit  520  that is described later and another end connecting with supply source switching unit  510 . It is to be noted that the one end of third supply duct  512 C may connect directly with the outlets (not illustrated) of temperature conditioning unit  100 X. 
     Supply source switching unit  510  is controlled by system controller  530 . Supply source switching unit  510  opens or closes parts of connection with supply ducts  512 A to  512 C to effect switching(s) among the gas supply sources for temperature conditioning unit  100 X. The gas supplied from any one of supply ducts  512 A to  512 C passes through intake duct  511  and is taken into the impellers through the respective intake ports of first and second intake and exhaust devices  10 A and  20 A. The amount of gas supply for each of first and second intake and exhaust devices  10 A and  20 A is controlled by blower controller  40 . System controller  530  controls supply source switching unit  510  that supplies the gas to temperature conditioning unit  100 X. System controller  530  may control a flow rate of gas that is supplied to intake duct  511 . Moreover, system controller  530  may control blower controller  40 . 
     In cases where a temperature outside the vehicle is a temperature (hereinafter “cooling temperature”) suitable for cooling of element  50  to temperature-condition, supply source switching unit  510  opens the part of connection with first supply duct  512 A to supply gas from outside the vehicle to temperature conditioning unit  100 X. In cases where a temperature of the vehicle&#39;s interior is the cooling temperature or a temperature (hereinafter “heating temperature”) that is suited to heat element  50  to temperature-condition, supply source switching unit  510  opens the part of connection with second supply duct  512 B to supply gas from the interior of the vehicle to temperature conditioning unit  100 X. In cases where exhaust gas from temperature conditioning unit  100 X has a cooling temperature or a heating temperature, supply source switching unit  510  may open the part of connection with third supply duct  512 C to supply the exhaust gas to temperature conditioning unit  100 X. 
     First temperature conditioning system  500  also includes discharge duct  521  connecting with the outlets of temperature conditioning unit  100 X, exhaust duct  522 A that lets the gas out of the vehicle, and exhaust duct  522 B that discharges the gas into the interior of the vehicle. Discharge duct  521  connects with exhaust duct  522 A and exhaust duct  522 B via discharge destination switching unit  520 . Exhaust duct  522 A has one end connecting with the exterior of the vehicle and another end connecting with discharge destination switching unit  520 . Exhaust duct  522 B has one end connecting with the interior of the vehicle and another end connecting with discharge destination switching unit  520 . As described above, discharge destination switching unit  520  also connects with the other end of third supply duct  512 C. 
     Also discharge destination switching unit  520  is controlled by system controller  530 . Discharge destination switching unit  520  opens or closes parts of connection with exhaust duct  522 A, exhaust duct  522 B, and third supply duct  512 C to effect switching(s) among discharge destinations for the gas from temperature conditioning unit  100 X. System controller  530  changes the discharge destination(s) of the gas from temperature conditioning unit  100 X and may control a flow rate of gas that is discharged into discharge duct  521 . 
     Discharged gas generally has a higher temperature than gas that is drawn in. As such, when the interior (particularly an internal cabin space) of the vehicle has a lower temperature, discharge destination switching unit  520  preferably opens the part of connection with exhaust duct  522 B. In this way, the warmer gas is discharged into the vehicle&#39;s interior, and the vehicle&#39;s interior can be warmed up accordingly. In cases where the temperature of the vehicle&#39;s interior is high enough, discharge destination switching unit  520  opens the part of connection with exhaust duct  522 A to let the gas out of the vehicle. 
     As described above, first temperature conditioning system  500  according to the present exemplary embodiment includes temperature conditioning unit  100 X, intake duct  511  connecting with respective intake ports  122  of first and second intake and exhaust devices  10 A and  20 A, the plurality of supply ducts respectively corresponding to first supply duct  512 A, second supply duct  512 B, and third supply duct  512 C that supply gas to intake duct  511 , and system controller  530  that selects one or more from among the plurality of supply ducts to effect supply of the gas to intake duct  511 . 
     Thus, in first temperature conditioning system  500 , the gas supply source(s) for element  50  to temperature-condition and the discharge destination(s) of gas discharged from element  50  to temperature-condition can be changed based on the temperature outside the vehicle, the temperature of the vehicle&#39;s interior, and the temperature of the gas discharged from temperature conditioning unit  100 X. In other words, according to first temperature conditioning system  500 , the gas from outside the vehicle or from the vehicle&#39;s interior is taken in, or the gas is discharged into the vehicle&#39;s interior. In this way, element  50  can be temperature-conditioned while energy is effectively utilized. Moreover, with gas taken in from outside the vehicle or from a closed space in the vehicle or with gas discharged out of the vehicle or into the closed space in the vehicle, gas quantity is equalized between intake and discharge, thus enabling suppression of pressure changes in the vehicle&#39;s interior. 
     (Second Temperature Conditioning System) 
     There are also cases where a plurality of temperature conditioning units  100 X are disposed in the hybrid vehicle. In such cases, from the viewpoint of effective energy utilization, respective gas courses of temperature conditioning units  100 X may be connected to each other to achieve a gas circulation system. This facilitates equalization of gas quantity between intake and discharge, thus leading to suppression of pressure changes in the interior of the vehicle. 
     As illustrated in  FIG. 11 , second temperature conditioning system  600  that allows gas circulation between the plurality of temperature conditioning units includes, for example, first temperature conditioning unit  100 XA, second temperature conditioning unit  100 XB, intake duct  611 , exhaust duct  612 , intake duct  621 , exhaust duct  622 , and circulation controller  630 . Intake duct  611  connects with the respective intake ports of first intake and exhaust device  10 A and second intake and exhaust device  20 A of first temperature conditioning unit  100 XA. Exhaust duct  612  lets gas out from the outlets of first temperature conditioning unit  100 XA. Intake duct  621  connects with the respective intake ports of first intake and exhaust device  10 A and second intake and exhaust device  20 A of second temperature conditioning unit  100 XB. Exhaust duct  622  lets gas out from the outlets of second temperature conditioning unit  100 XB. From exhaust duct  612  and exhaust duct  622 , circulation controller  630  determines exhaust duct(s) for connection to at least one of intake duct  611  and intake duct  621 . 
     Intake duct  611 , intake duct  621 , exhaust duct  612 , and exhaust duct  622  are interconnected via circulation switching unit  640 . In other words, intake duct  611  has one end connecting with the intake ports of first temperature conditioning unit  100 XA and another end connecting with circulation switching unit  640 . Exhaust duct  612  has one end connecting with the outlets of first temperature conditioning unit  100 XA and another end connecting with circulation switching unit  640 . Intake duct  621  has one end connecting with the intake ports of second temperature conditioning unit  100 XB and another end connecting with circulation switching unit  640 . Exhaust duct  622  has one end connecting with the outlets of second temperature conditioning unit  100 XB and another end connecting with circulation switching unit  640 . Circulation switching unit  640  may also connect with one end of duct  650 . Another end of duct  650  connects with, for example, the exterior or the interior of the vehicle. Duct  650  takes in gas from outside the vehicle or from the vehicle&#39;s interior or discharges the gas out of the vehicle or into the vehicle&#39;s interior when necessary. 
     Circulation switching unit  640  is controlled by circulation controller  630 . From exhaust duct  612  and exhaust duct  622 , circulation controller  630  determines exhaust duct(s) for connection to at least one of intake duct  611  or intake duct  621 . Based on this determination, circulation switching unit  640  opens or closes parts of connection with intake duct  611 , intake duct  621 , exhaust duct  612 , and exhaust duct  622  to effect switching(s) among gas supply sources or gas discharge destinations for first temperature conditioning unit  100 XA and second temperature conditioning unit  100 XB. Circulation controller  630  may also control a flow rate of gas in each of the ducts. The amount of gas supply for each of the intake and exhaust devices of each of the temperature conditioning units is controlled by corresponding blower controller  40 . Circulation controller  630  may also control blower controllers  40 . 
     As described above, second temperature conditioning system  600  according to the present exemplary embodiment includes first temperature conditioning unit  100 XA, second temperature conditioning unit  100 XB, a first intake duct that corresponds to intake duct  611  connecting with respective intake ports  122  of first intake and exhaust device  10 A and second intake and exhaust device  20 A of first temperature conditioning unit  100 XA, a first exhaust duct corresponding to exhaust duct  612  that lets gas out from outlets  30   b  of first temperature conditioning unit  100 XA, a second intake duct that corresponds to intake duct  621  connecting with respective intake ports  122  of first intake and exhaust device  10 A and second intake and exhaust device  20 A of second temperature conditioning unit  100 XB, a second exhaust duct corresponding to exhaust duct  622  that lets gas out from outlets  30   b  of second temperature conditioning unit  100 XB, and circulation controller  630  that selects at least one of the first exhaust duct and the second exhaust duct to effect supply of the gas to at least one of the first intake duct and the second intake duct. 
     With second temperature conditioning system  600 , elements  50  can be temperature-conditioned while energy is effectively utilized through gas circulation between the plurality of temperature conditioning units. Such a system is useful in cases where gas discharged from first temperature conditioning unit  100 XA or second temperature conditioning unit  100 XB has a suitable temperature for cooling or heating of element  50  to temperature-condition. While second temperature conditioning system  600  has two temperature conditioning units  100 XA and  100 XB in the illustrated example, it is to be noted that this is not limiting. Second temperature conditioning system  600  may, for example, include one temperature conditioning unit  100 XA or  100 XB and another temperature conditioning unit (such as the one that includes one intake and exhaust device). The temperature conditioning units of second temperature conditioning system  600  may be greater than or equal to three in number with gas circulated at least between two of those temperature conditioning units. While temperature conditioning units  100 XA and  100 XB each have two intake and exhaust devices  10 A and  20 B in the illustrated example, this is not limiting. Each of temperature conditioning units  100 XA and  100 XB may, for example, include intake and exhaust devices that are greater than or equal to three in number. Temperature conditioning units  100 XA and  100 XB may have the same intake and exhaust devices disposed or different intake and exhaust devices disposed. The same goes for a third temperature conditioning system that is described later. 
     (Third Temperature Conditioning System) 
     In cases where a plurality of temperature conditioning units  100 X are disposed, temperature conditioning units  100 X may be connected in parallel for collective quantitative control of gases that are respectively drawn into temperature conditioning units  100 X. This enables effective energy utilization. 
     As illustrated in  FIG. 12 , third temperature conditioning system  700  having the plurality of temperature conditioning units  100 X connected in parallel includes, for example, first temperature conditioning unit  100 XA, second temperature conditioning unit  100 XB, intake duct  711 , intake duct  721 , intake connection duct  710 , and flow rate controller  730 . Intake duct  711  connects with the respective intake ports of first intake and exhaust device  10 A and second intake and exhaust device  20 A of first temperature conditioning unit  100 XA. Intake duct  721  connects with the respective intake ports of first intake and exhaust device  10 A and second intake and exhaust device  20 A of second temperature conditioning unit  100 XB. Intake connection duct  710  branches off to connect with intake duct  711  and intake duct  721 . Flow rate controller  730  controls a flow rate of gas in intake duct  711  and a flow rate of gas in intake duct  721 . 
     Intake connection duct  710  connects with intake duct  711  and intake duct  721  via supply amount adjuster  740 . Intake connection duct  710  connects with, for example, the exterior or the interior of the vehicle. Supply amount adjuster  740  is controlled by flow rate controller  730 . Supply amount adjuster  740  opens or closes parts of connection with intake duct  711  and intake duct  721  to adjust an amount of gas supply for first temperature conditioning unit  100 XA and an amount of gas supply for second temperature conditioning unit  100 XB. The amount of gas supply for each of first and second intake and exhaust devices  10 A and  20 A of each of the temperature conditioning units is controlled by corresponding blower controller  40 . Flow rate controller  730  may also control blower controllers  40 . 
     Third temperature conditioning system  700  may also include exhaust duct  712 , exhaust duct  722 , and exhaust connection duct  720 . Exhaust duct  712  connects with the outlets of first temperature conditioning unit  100 XA. Exhaust duct  722  connects with the outlets of second temperature conditioning unit  100 XB. Exhaust connection duct  720  connects with exhaust duct  712  and exhaust duct  722 . 
     Exhaust connection duct  720  connects with exhaust duct  712  and exhaust duct  722  via discharge amount adjuster  750 . Exhaust connection duct  720  connects with, for example, the exterior or the interior of the vehicle. Discharge amount adjuster  750  is controlled by flow rate controller  730 . Discharge amount adjuster  750  opens or closes parts of connection with exhaust duct  712  and exhaust duct  722  to adjust an amount of gas discharge from first temperature conditioning unit  100 XA and an amount of gas discharge from second temperature conditioning unit  100 XB. 
     As described above, third temperature conditioning system  700  according to the present exemplary embodiment includes first temperature conditioning unit  100 XA, second temperature conditioning unit  100 XB, a first intake duct that corresponds to intake duct  711  connecting with respective intake ports  122  of first intake and exhaust device  10 A and second intake and exhaust device  20 A of first temperature conditioning unit  100 XA, a second intake duct that corresponds to intake duct  721  connecting with respective intake ports  122  of first intake and exhaust device  10 A and second intake and exhaust device  20 A of second temperature conditioning unit  100 XB, a connection duct corresponding to intake connection duct  710  that branches off and connects with the first intake duct and the second intake duct, and flow rate controller  730  that controls the flow rate of gas in the first intake duct and the flow rate of gas in the second intake duct. 
     With third temperature conditioning system  700 , elements  50  can be temperature-conditioned while energy is effectively utilized through collective quantitative control of gases that are respectively drawn into the plurality of temperature conditioning units (first and second temperature conditioning units  100 XA and  100 XB in  FIG. 12 ). 
     (Vehicles) 
     Temperature conditioning unit  100 X, temperature conditioning system  500 , temperature conditioning system  600 , or temperature conditioning system  700  is mounted, for example, in vehicles including the hybrid vehicle. 
       FIG. 13A  is a schematic view of vehicle  800 A according to the first exemplary embodiment. Vehicle  800 A includes power source  810 , drive wheels  820 , driving controller  830 , and temperature conditioning unit  100 X. Power source  810  supplies power to drive wheels  820 . Driving controller  830  controls power source  810 . 
       FIG. 13B  is a schematic view of another vehicle  800 B according to the first exemplary embodiment. Vehicle  800 B includes power source  810 , drive wheels  820 , driving controller  830 , and temperature conditioning system  500 ,  600 , or  700 . Vehicles  800 A and  800 B can allow the secondary batteries and others to function at suitable temperatures with noises suppressed, thus each offering excellent comfort and high performance. 
     As described above, vehicle  800 A according to the present exemplary embodiment may be mounted with temperature conditioning unit  100 X. 
     Vehicle  800 B may be mounted with temperature conditioning system  500 . 
     Another alternative may be that vehicle  800 B is mounted with temperature conditioning system  600 . 
     Yet another alternative may be that vehicle  800 B is mounted with temperature conditioning system  700 . 
     Second Exemplary Embodiment 
     The present exemplary embodiment differs from the first exemplary embodiment in that a plurality of intake and exhaust devices to use have the same number N of rotor vanes disposed and that an impeller of at least one of the intake and exhaust devices (a first intake and exhaust device) and an impeller of another intake and exhaust device (a second intake and exhaust device) rotate at different rotational speeds r. A temperature conditioning unit, temperature conditioning systems, and vehicles are otherwise similar to those in the first exemplary embodiment. With the impellers varying in rotational speed r, BPF noise frequency Fb1 of the first intake and exhaust device does not coincide with BPF noise frequency Fb2 of the second intake and exhaust device. In this way, BPF noise peaks are dispersed, and a noise is produced in suppressed condition by the temperature conditioning unit. 
     Variations in rotational speed r result in variations in gas volume obtained. When cooling efficiency and ease of control are taken into account, it is preferable that a plurality of intake and exhaust devices disposed in one temperature conditioning system be comparable in gas volume. To achieve comparable gas volumes with variations in rotational speed r, maximum diameter L 1  of an impeller disk of the first intake and exhaust device and maximum diameter L 2  of an impeller disk of the second intake and exhaust device are varied in the present exemplary embodiment when these impeller disks are each viewed in an axial direction of a shaft. The impeller having the smaller impeller disk is rotated at a higher speed than the other impeller is rotated, thereby being adjusted to a comparable gas volume. 
     With reference to  FIGS. 14A and 14B , a description is provided of the intake and exhaust devices according to the present exemplary embodiment.  FIG. 14A  is a sectional view of first intake and exhaust device  10 B according to the second exemplary embodiment.  FIG. 14B  is a sectional view of second intake and exhaust device  20 B according to the second exemplary embodiment. First intake and exhaust device  10 B and second intake and exhaust device  20 B may be structurally similar, except that impeller disk  111 B has the different maximum diameter when viewed in the axial direction of the shaft. This means that first rotor vanes  112 B of first intake and exhaust device  10 B are the same in number as second rotor vanes  212 B of second intake and exhaust device  20 B. Moreover, fan case  120  of first intake and exhaust device  10 B has the same outside diameter as fan case  120  of second intake and exhaust device  20 B. First intake and exhaust device  10 B and second intake and exhaust device  20 B are not structurally limited to this, but may differ in the number of rotor vanes disposed or may have fan cases  120  of different outside diameters. In  FIGS. 14A and 14B , first intake and exhaust device  10 B and second intake and exhaust device  20 B are structurally similar to first intake and exhaust device  10 A but are not limited to this. It is to be noted that  FIGS. 14A and 14B  show that maximum diameter L 1 &gt;maximum diameter L 2 . 
     L 1 /L 2 , which is a ratio of maximum diameter L 1  to maximum diameter L 2 , is not particularly limited and may be determined appropriately in consideration of, for example, desired gas volumes and desired rotational speeds of the intake and exhaust devices. In the case of L 1 &gt;L 2 , L 1 /L 2  is, for example, greater than 1 and less than or equal to 1.7 and is preferably greater than 1 and less than or equal to 1.4. In the above cases, an operating point of a rotary drive source of first intake and exhaust device  10 B and an operating point of a rotary drive source of second intake and exhaust device  20 B do not have to be varied largely. For this reason, rotary drive sources  132  of the same type can be used in first intake and exhaust device  10 B and second intake and exhaust device  20 B, respectively. The operating point of the rotary drive source is a point of intersection of a speed characteristic curve that shows a rotational speed with respect to an electric current and a torque characteristic curve that shows torque with respect to the electric current. 
     As described above, in temperature conditioning unit  100 X according to the present exemplary embodiment, maximum diameter L 1  of impeller disk  111 A of first intake and exhaust device  10 A is different from maximum diameter L 2  of impeller disk  211  of second intake and exhaust device  20 A when these impeller disks  111 A and  211  are each viewed in the axial direction of shaft  131 . In this way, BPF noise peaks are dispersed, and a noise is produced in suppressed condition by the temperature conditioning unit. 
     Third Exemplary Embodiment 
     A temperature conditioning unit, temperature conditioning systems, and vehicles according to the present exemplary embodiment are similar to those in the first or second exemplary embodiment, except that a first intake and exhaust device also includes a plurality of stator vanes disposed between the side wall and the rotor vanes. 
     With reference to  FIGS. 15 and 16 , a description is provided of the present exemplary embodiment.  FIG. 15  is a sectional perspective view of first intake and exhaust device  10 A according to the third exemplary embodiment.  FIG. 16  is a perspective view illustrating impeller  110 A and stator vanes  141  according to the third exemplary embodiment. While  FIGS. 15 and 16  illustrate the example in which first intake and exhaust device  10 A includes stator vanes  141 , this is not limiting. First intake and exhaust device  10 B or second intake and exhaust device  20 A or  20 B may replace first intake and exhaust device  10 A to include stator vanes  141 . First intake and exhaust device  10 A or  10 B and second intake and exhaust device  20 A or  20 B may both include stator vanes  141 . Because of stator vanes  141  disposed, air flowing out from impeller  110 A is slowed down and increases in pressure when blown from the intake and exhaust device. 
     The plurality of stator vanes  141  are disposed between side wall  121  and first rotor vanes  112 A while being erected, for example, at equally spaced intervals on a principal surface of diffuser ring  142  closer to intake port  122  (refer to  FIG. 16 ). The plurality of stator vanes  141  may be joined to an inner side of side wall  121 . Diffuser ring  142  is a ring-shaped plate and has a larger inside diameter than maximum diameter L 1  of impeller disk  111 A. 
     It is to be noted here that in cases where stator vanes  141  are disposed, a BPF noise can be caused by, for example, differential pressure or turbulence that occurs between stator vanes  141 . When stator vanes  141  are included in first intake and exhaust device  10 A, BPF noises are dispersed further in terms of energy. To this end, it is preferable that number N1 of first rotor vanes  112 A of first intake and exhaust device  10 A and number Nd1 of stator vanes  141  of first intake and exhaust device  10 A satisfy Relational Expression 3 and Relational Expression 4. 
         N 1≠ Nd 1× n 3 (where n3 is an integer greater than or equal to 1)  Relational Expression 3
 
         N 1≠ Nd 1/ n 4 (where n4 is an integer greater than or equal to 2)  Relational Expression 4
 
     As long as Relational Expression 3 and Relational Expression 4 are satisfied, number Nd1 of stator vanes  141  is not particularly limited and may be set appropriately in consideration of, for example, a size of the intake and exhaust device or a desired gas volume. Number Nd1 of stator vanes  141  is, for example, between 5 and 30 inclusive and preferably between 8 and 15 inclusive. Above all, from the viewpoint of a flow regulating effect, number Nd1 is preferably greater than number N1. If number Nd1 of stator vanes  141  is less than or equal to the number of first rotor vanes  112 A, a space between adjacent stator vanes  141  becomes wider than a space between first rotor vanes  112 A that are positioned inwardly of stator vanes  141 , thereby easily lowering the flow regulating effect. On the other hand, if there are too many stator vanes  141 , increased friction loss is caused to gas by side wall  121 . A difference between number N1 and number Nd1 is not particularly limited and may be greater than or equal to 1. The difference between number N1 and number Nd1 is, for example, between 1 and 5 inclusive. Frequency Fd at which BPF noise energy ascribable to stator vanes  141  peaks is calculated by Formula 1 with number Nd of stator vanes  141  substituted for number N of rotor vanes. 
     Similarly, even in cases where second intake and exhaust device  20 A includes stator vanes  141 , number N2 of rotor vanes  212 A of second intake and exhaust device  20 A and number Nd2 of stator vanes of second intake and exhaust device  20 A preferably satisfy Relational Expression 5 and Relational Expression 6. 
         N 2‥ Nd 2× n 4 (where n4 is an integer greater than or equal to 1)  Relational Expression 5
 
         N 2‥ Nd 2/ n 6 (where n6 is an integer greater than or equal to 1)  Relational Expression 6
 
     Disposition of stator vanes  141  is not particularly limited. Stator vanes  141  may be suitably disposed based on, for example, the maximum diameter of impeller disk  111 A or disposition of first rotor vanes  112 A. Above all, each of stator vanes  141  is preferably disposed to have its principal surface extend along gas flow C (refer to  FIG. 5 ) that is effected by first rotor vane  112 A in terms of efficient deceleration of air flowing out from impeller  110 A. In other words, each of stator vanes  141  is preferably disposed at such an angle as to open in rotation direction D. In this case, a size of stator vane  141  is not particularly limited and may be set appropriately to allow a desired volume of gas to be blown from between stator vanes  141  at a desired pressure. 
     As described above, at least one of first intake and exhaust device  10 A and second intake and exhaust device  20 A according to the preset exemplary embodiment may include the plurality of stator vanes  141  disposed between side wall  121  of fan case  120  and the rotor vanes corresponding to first rotor vanes  112 A. 
     First intake and exhaust device  10 A includes the plurality of stator vanes  141 , and number N1 of rotor vanes corresponding to first rotor vanes  112 A of first intake and exhaust device  10 A and number Nd1 of stator vanes  141  of first intake and exhaust device  10 A preferably satisfy the relationships: 
         N 1≠ Nd 1× n 3 (where n3 is the integer greater than or equal to 1); and
 
         N 1≠ Nd 1/ n 4 (where n4 is the integer greater than or equal to 2).
 
     Moreover, second intake and exhaust device  20 A includes the plurality of stator vanes  141 , and number N2 of rotor vanes corresponding to first rotor vanes  112 A of second intake and exhaust device  20 A and number Nd2 of stator vanes  141  of second intake and exhaust device  20 A preferably satisfy the relationships: 
         N 2≠ Nd 2× n 5 (where n5 is the integer greater than or equal to 1); and
 
         N 2≠ Nd 2/ n 6 (where n6 is the integer greater than or equal to 2).
 
     Fourth Exemplary Embodiment 
     Temperature conditioning unit  100 Y according to the present exemplary embodiment is similar to the temperature conditioning unit of the first, second or third exemplary embodiment and is also similar to those in the temperature conditioning systems and the vehicles of the first, second or third exemplary embodiment, except that respective intake ports  122  of the first and second intake and exhaust devices are mounted to face outlets  30   b , respectively. It is to be noted that in each of temperature conditioning systems, the intake duct and the exhaust duct, for example, are appropriately replaced before connection to temperature conditioning unit  100 Y. In this way, internal gas of housing  30  is discharged through the intake and exhaust devices. This means that the intake and exhaust devices function as dischargers in the present exemplary embodiment. 
     With reference to  FIGS. 17A and 17B , a specific description is hereinafter provided of temperature conditioning unit  100 Y according to the present exemplary embodiment.  FIG. 17A  is a perspective view schematically illustrating temperature conditioning unit  100 Y according to the fourth exemplary embodiment.  FIG. 17B  is a sectional view of temperature conditioning unit  100 Y, the section being taken on plane  17 B- 17 B of  FIG. 17A . It is to be noted that an internal structure of each of the intake and exhaust devices is omitted in  FIG. 17A . First intake and exhaust device  10 C is structurally similar to first intake and exhaust device  10 A or first intake and exhaust device  10 B, and second intake and exhaust device  20 C is structurally similar to second intake and exhaust device  20 A or second intake and exhaust device  20 B. It is to be noted that temperature conditioning unit  100 Y is not limited to the above structure. 
     Element  50  to temperature-condition is disposed, for example, to divide the interior of housing  30  into intake-side chamber  31  including inlets  30   a  and exhaust-side chamber  32  including outlets  30   b  as in the case described above. As the gas is forcibly discharged out of exhaust-side chamber  32  through outlets  30   b  by first and second intake and exhaust devices  10 C and  20 C, internal pressure of exhaust-side chamber  32  lowers. Accordingly, external gas is aggressively taken in through inlets  30   a , diffuses throughout intake-side chamber  31 , passes through gaps in element  50  to temperature-condition or between element  50  to temperature-condition and housing  30 , and then flows into exhaust-side chamber  32 . That is when element  50  is temperature-conditioned, namely, cooled or heated. Here the flow of gas is indicated as an example by outlined arrows. 
     Intake-side chamber  31  and exhaust-side chamber  32  may be equal or different in capacity. Above all, it is preferable as in the case described above that intake-side chamber  31  have a larger capacity than exhaust-side chamber  32 . This is for the purpose of efficiently temperature-conditioning, namely, cooling or heating entire element  50 . 
     Fifth Exemplary Embodiment 
     A temperature conditioning unit according to the present exemplary embodiment includes a third intake and exhaust device, a fourth intake and exhaust device, and a housing that accommodates an element to temperature-condition. The third intake and exhaust device and the fourth intake and exhaust device have different numbers of rotor vanes. 
     With reference to  FIGS. 18A to 22 , a specific description is hereinafter provided of temperature conditioning unit  150 X according to the fifth exemplary embodiment.  FIG. 18A  is a perspective view schematically illustrating temperature conditioning unit  150 X according to the fifth exemplary embodiment.  FIG. 18B  is a sectional view of the temperature conditioning unit, the section being taken on plane  18 B- 18 B of  FIG. 18A .  FIG. 19A  is a perspective view of third intake and exhaust device  60 A of temperature conditioning unit  150 X according to the fifth exemplary embodiment.  FIG. 19B  is a longitudinal section of third intake and exhaust device  60 A of temperature conditioning unit  150 X according to the fifth exemplary embodiment.  FIG. 20A  is a perspective view of impeller  160 A that is disposed in third intake and exhaust device  60 A of temperature conditioning unit  150 X according to the fifth exemplary embodiment.  FIG. 20B  is a top plan view of third rotor vanes  162 A that are disposed in third intake and exhaust device  60 A of temperature conditioning unit  150 X according to the fifth exemplary embodiment.  FIG. 20C  is a perspective view of impeller  260 A that is disposed in fourth intake and exhaust device  70 A of temperature conditioning unit  150 X according to the fifth exemplary embodiment.  FIG. 20D  is a top plan view of fourth rotor vanes  262 A that are disposed in fourth intake and exhaust device  70 A of temperature conditioning unit  150 X according to the fifth exemplary embodiment. In  FIGS. 20B and 20D , shrouds  163 A,  263 A are omitted, and impeller disks  161 A,  261 A are indicated by broken lines.  FIG. 21  is a graph showing a relationship between rotational order and energy of BPF noise produced by third and fourth intake and exhaust devices  60 A and  70 A of temperature conditioning unit  150 X of the fifth exemplary embodiment.  FIG. 22  is a sectional view of third intake and exhaust device  60 A in temperature conditioning unit  150 X of the fifth exemplary embodiment, as viewed from intake port  172 . In the drawings, members having identical functions have the same reference marks. 
     (Temperature Conditioning Unit) 
     As illustrated in  FIGS. 18A and 18B , temperature conditioning unit  150 X includes third intake and exhaust device  60 A, fourth intake and exhaust device  70 A, and housing  80 . Housing  80  accommodates element  99  to temperature-condition. Housing  80  is provided with at least one inlet  80   a  where external gas is taken in and at least one outlet  80   b  where the gas is discharged out of housing  80 . 
     Third intake and exhaust device  60 A and fourth intake and exhaust device  70 A are mounted such that their respective vents  173  face inlets  80   a , respectively. This means that third intake and exhaust device  60 A and fourth intake and exhaust device  70 A function as blowers in the present exemplary embodiment. Inlets  80   a  communicate with external space, an exhaust duct (described later), or an intake duct (described later) via respective third and fourth intake and exhaust devices  60 A and  70 A. Also outlets  80   b  communicate with the external space, the exhaust duct (described later), or the intake duct (described later). Thus, the gas flows into housing  80  through third intake and exhaust device  60 A and fourth intake and exhaust device  70 A. 
     Element  99  to temperature-condition is disposed to divide an interior of housing  80  into intake-side chamber  81  including inlets  80   a  and exhaust-side chamber  82  including outlets  80   b . The gas forcibly fed through inlets  80   a  by third intake and exhaust device  60 A and fourth intake and exhaust device  70 A diffuses throughout intake-side chamber  81 , passes through gaps in element  99  to temperature-condition or between element  99  to temperature-condition and housing  80 , and then flows into exhaust-side chamber  82 . That is when element  99  is temperature-conditioned, namely, cooled or heated. The gas that has flowed into exhaust-side chamber  82  is discharged into the external space through outlets  80   b . Here the flow of gas is indicated as an example by outlined arrows. 
     As illustrated in  FIG. 18B , intake-side chamber  81  and exhaust-side chamber  82  may be equal or different in capacity. Above all, intake-side chamber  81  preferably has a larger capacity than exhaust-side chamber  82 . Intake-side chamber  81  generally has a higher internal pressure than exhaust-side chamber  82 . With the capacity of intake-side chamber  81  being larger, intake-side chamber  81  has decreased pressure resistance, thus having uniform pressure distribution. Consequently, the gas spreads throughout element  99  to temperature-condition without nonuniformity, whereby element  99  is entirely temperature-conditioned, namely, cooled or heated with efficiency. 
     Temperature conditioning unit  150 X may have one outlet  80   b  or outlets  80   b  that are greater than or equal to 2 in number. A number of intake and exhaust devices to dispose in temperature conditioning unit  150 X is not particularly limited as long as the number of intake and exhaust devices is greater than or equal to 2. Also disposition of element  99  to temperature-condition is not particularly limited. Element  99  to temperature-condition may be suitably disposed based on, for example, a use or its kind. 
     (Intake and Exhaust Devices) 
     Third intake and exhaust device  60 A is given as an example to describe structure of third intake and exhaust device  60 A and structure of fourth intake and exhaust device  70 A. Except for the difference in the number of rotor vanes, third intake and exhaust device  60 A and fourth intake and exhaust device  70 A may be structurally similar. Alternatively, in addition to the difference in the number of rotor vanes, there may be another structural difference (for example, a difference in impeller disk size) between third intake and exhaust device  60 A and fourth intake and exhaust device  70 A. A number of outlets (not illustrated) where the gas is discharged out of temperature conditioning unit  150 X is not particularly limited and may be 1 or may be greater than or equal to 2. 
     (Intake and Exhaust Devices) 
     As shown in  FIGS. 19A and 19B , third intake and exhaust device  60 A includes impeller  160 A, fan case  170 , and rotary drive device  180 . Impeller  160 A includes impeller disk  161 A and the plurality of third rotor vanes  162 A. Fan case  170  includes side wall  171 , intake port  172 , and vent  173 . Rotary drive device  180  includes shaft  181  and rotary drive source  182  that rotates shaft  181 . 
     (Impeller) 
     Impeller  160 A includes impeller disk  161 A and the plurality of third rotor vanes  162 A. Impeller  160 A may also include shroud  163 A. 
     (Impeller Disk) 
     Impeller disk  161 A is substantially circular and has a surface extending in a direction intersecting shaft  181 . The plurality of third rotor vanes  162 A are erected on one of principal surfaces of impeller disk  161 A. Impeller disk  161 A has an opening in a part of its central part  161 AC (refer to  FIG. 20B ). Shaft  181  is inserted into this opening to engage impeller disk  161 A. Rotary drive source  182  is rotationally driven, whereby impeller  160 A rotates. 
     (Shroud) 
     Shroud  163 A is formed of a ring-shaped plate and is disposed to face impeller disk  161 A via third rotor vanes  162 A. When impeller  160 A is viewed in an axial direction of shaft  181 , an outer peripheral edge of impeller disk  161 A is substantially aligned with an outer peripheral edge of shroud  163 A. Here outer peripheral part  161 AP (refer to  FIG. 20B ) of impeller disk  161 A is partly covered by shroud  163 A. Each of third rotor vanes  162 A is partly joined to shroud  163 A. The gas taken into impeller  160 A flows along third rotor vanes  162 A, flows out from the outer peripheral edge of impeller disk  161 A, and then collides against side wall  171 , thereby being guided to vent  173 . Here shroud  163 A suppresses outflow of the gas that has flowed out from the outer peripheral edge of impeller disk  161 A from intake port  172 . Shroud  163 A also suppresses entry of the gas that has flowed out of an inter-vane passage formed by two adjacent third rotor vanes  162 A into an adjacent inter-vane passage. To suppress a turbulent flow of gas, shroud  163 A is preferably funnel-shaped or tapered having a gently curved surface that narrows toward intake port  172 . 
     (Rotor Vanes) 
     The plurality of third rotor vanes  162 A are erected on impeller disk  161 A. As illustrated in  FIG. 20B , third rotor vanes  162 A each extend in a direction from central part  161 AC to outer peripheral part  161 AP of impeller disk  161 A in the shape of a circular arc bulging in a direction opposite to rotation direction D of shaft  181 . 
     Similarly, the plurality of fourth rotor vanes  262 A disposed in fourth intake and exhaust device  70 A each extend, as illustrated in  FIGS. 20C and 20D , in a direction from central part  261 AC to outer peripheral part  261 AP of impeller disk  261 A in the shape of a circular arc bulging in a direction opposite to rotation direction D of shaft  181 . Impeller  260 A of fourth intake and exhaust device  70 A is structurally similar to impeller  160 A. Impeller  260 A may also include shroud  263 A. 
     Here number N3 of third rotor vanes  162 A and number N4 of fourth rotor vanes  262 A satisfy Relational Expression 7 and Relational Expression 8. 
         N 3≠ N 4× n 3 (where n3 is an integer greater than or equal to 1)  Relational Expression 7
 
         N 3≠ N 4/ n 4 (where n4 is an integer greater than or equal to 2)  Relational Expression 8
 
     In other words, number N3 of third rotor vanes  162 A is different from number N4 of fourth rotor vanes  262 A, and number N3 is neither an integral multiple of number N4 nor a value obtained by division of number N4 by the integer. Accordingly, BPF noise frequency Fb3 of third intake and exhaust device  60 A does not coincide with BPF noise frequency Fb4 of fourth intake and exhaust device  70 A, irrespective of integer m. In this way, BPF noises are dispersed in terms of energy, and a noise is produced in suppressed condition by temperature conditioning unit  150 X. 
       FIG. 21  is the graph showing the relationship between the rotational order and the BPF noise energy of third and fourth intake and exhaust devices  60 A and  70 A of temperature conditioning unit  150 X of the fifth exemplary embodiment. The rotational order is obtained by division of measured frequency F by a rotational frequency (r/60) of the intake and exhaust device. Generally, BPF noise energy is greater when the rotational order is a multiple of number N of rotor vanes. A broken line in  FIG. 21  indicates the BPF noise energy of the exemplary embodiment&#39;s temperature conditioning unit  150 X including third intake and exhaust device  60 A and fourth intake and exhaust device  70 A. A solid line in  FIG. 21  indicates BPF noise energy of a temperature conditioning unit of a comparative example that includes two third intake and exhaust devices  60 A. In the case of the exemplary embodiment, it is shown that BPF noise energy peaks are dispersed and that BPF noise is suppressed. When respective overall values (each of which represents total energy of sounds produced by the temperature conditioning unit at all frequencies) of those temperature conditioning units were compared, the overall value was about 2% lower in the exemplary embodiment compared with the overall value of the comparative example. While  FIG. 21  shows the relationship between the rotational order and the BPF noise energy when third intake and exhaust device  60 A includes forty-three third rotor vanes  162 A with fourth intake and exhaust device  70 A including thirty-seven fourth rotor vanes  262 A, a similar tendency is seen even when third intake and exhaust device  60 A and fourth intake and exhaust device  70 A each have the number of rotor vanes varied. 
     Number N3 of third rotor vanes  162 A and number N4 of fourth rotor vanes  262 A are not particularly limited. Number N3 of third rotor vanes  162 A and number N4 of fourth rotor vanes  262 A may be set appropriately in consideration of, for example, sizes of impellers  160 A and  260 A and respective gas volumes and respective pressures of third and fourth intake and exhaust devices  60 A and  70 A. Number N3 of third rotor vanes is, for example, between 25 and 50 inclusive, while number N4 of fourth rotor vanes  262 A is, for example, between 30 and 45 inclusive. As long as Relational Expression 7 and Relational Expression 8 are satisfied, the difference between number N3 and number N4 is not particularly limited and may be greater than or equal to 1. When the respective gas volumes and the respective pressures of third and fourth intake and exhaust devices  60 A and  70 A are taken into consideration, the difference between number N3 and number N4 is preferably between 1 and 5 inclusive. 
     In cases where an electric motor is used as rotary drive device  180 , a stator is disposed in the electric motor. The stator generally has an even number of poles. For this reason, in cases where at least one of number N3 of third rotor vanes and number N4 of fourth rotor vanes  262 A is even, third rotor vanes  162 A and fourth rotor vanes  262 A become exciting forces, whereby rotary drive device  180 , third intake and exhaust device  60 A, and fourth intake and exhaust device  70 A all experience vibrational excitation, and an increased noise can be caused. As such, it is preferable that number N3 of third rotor vanes  162 A and number N4 of fourth rotor vanes  262 A be both odd in such cases. The number of poles is a number of magnetic poles generated in rotary drive device  180 . Even in cases where a number of slots of the stator corresponds to at least one of number N3 of third rotor vanes and number N4 of fourth rotor vanes  262 A or even in cases where the number of slots and the at least one of number N3 and number N4 are integral multiples of each other, an increased noise can be caused. As such, each of number N3 of third rotor vanes and number N4 of fourth rotor vanes  262 A is preferably set so as to neither correspond to the number of slots nor be the integral multiple of the number of slots or vice versa. 
     As illustrated in  FIG. 20 , each of third rotor vanes  162 A extends in a direction from central part  161 AC to outer peripheral part  161 AP, starting from a point of choice as starting point  162 As in outer peripheral part  161 AP and ending at a point of choice as end point  162 Ae in the outer peripheral part  161 AP. Here third rotor vane  162 A forms the circular arc bulging in the direction opposite to rotation direction D of shaft  181 . When impeller disk  161 A has radius r, central part  161 AC of impeller disk  161 A is a circle that is concentric with impeller disk  161 A and has a radius of 1/2×r, while outer peripheral part  161 AP of impeller disk  161 A is a doughnut-shaped area surrounding central part  161 AC. 
     From the viewpoint of suppression of a turbulent flow of gas, end point  162 Ae is preferably positioned near the outer peripheral edge of impeller disk  161 A. From a similar point of view, third rotor vane  162 A preferably has a shorter length along the radius of impeller disk  161 A. For example, starting point  162 As is preferably in an area surrounded by a circle that is concentric with impeller disk  161 A and has a radius of 2/3×r and the outer peripheral edge of impeller disk  161 A. 
     The shape of third rotor vane  162 A is not particularly limited as long as third rotor vane  162 A includes a projecting portion. For example, when impeller disk  161 A is viewed in the axial direction of shaft  181 , straight line Le connecting end point  162 Ae of third rotor vane  162 A and center C of impeller disk  161 A may be positioned ahead of straight line Ls connecting starting point  162 As of third rotor vane  162 A and center C of impeller disk  161 A in rotation direction D. 
     (Fan Case) 
     Fan case  170  includes side wall  171  surrounding impeller  160 A, intake port  172 , and vent  173  communicating with the interior of housing  80 . A shape of fan case  170  is not particularly limited. Above all, fan case  170  is preferably scroll-shaped with a distance from shaft  181  to side wall  171  increasing in rotation direction D as illustrated in  FIG. 22  in terms of increase in gas pressure. In this case, gas drawn in at intake port  172  flows in the axial direction of shaft  181 , and gas W blown from vent  173  flows in a direction intersecting the axial direction of shaft  181 . 
     Respective materials for the impeller disk, the rotor vane, the shroud, and the side wall are not particularly limited and may be suitably selected based on a use. Given examples of those materials include various metallic materials, various resin materials, and combinations of these materials. 
     (Rotary Drive Device) 
     Rotary drive device  180  includes shaft  181  and rotary drive source  182  that rotates shaft  181 . As shaft  181  is rotationally driven by rotary drive source  182 , impeller  160 A rotates, and gas is taken into fan case  170  through intake port  172 . 
     Rotary drive device  180  is, for example, the electric motor. The electric motor is an electric appliance that outputs rotational motion through use of force of interaction between a magnetic field and an electric current (namely, Lorentz force). In the electric motor, rotary drive source  182  includes a rotor (not illustrated) and the stator (not illustrated) that produces force to rotate the rotor. Respective shapes of and respective materials for the rotor and the stator are not particularly limited, and a publicly known electric motor may be used. An output of the electric motor is not particularly limited and may be set appropriately based on, for example, a desired gas volume and a desired pressure. For example, in cases where temperature conditioning unit  150 X is mounted in a hybrid vehicle, the output of the electric motor is about several tens of watts. 
     The stator has stator windings. When the electric current is passed through the stator winding, a magnetic field is produced around the stator winding. The magnetic field causes the rotor to rotate. A material for the stator winding is not specifically limited as long as the material is electrically conductive. Above all, the stator winding preferably includes at least one selected from the group consisting of copper, copper alloy, aluminum, and aluminum alloy in terms of low resistance. 
     (Blower Controller) 
       FIG. 23  is a block diagram illustrating fourth temperature conditioning system  1500  according to the fifth exemplary embodiment. Temperature conditioning unit  150 X may be provided with blower controller  90  (refer to  FIG. 23 ) that controls third intake and exhaust device  60 A and fourth intake and exhaust device  70 A. Blower controller  90  controls, for example, rotational speed of each of impellers  160 A and  260 A and an amount of gas that is supplied to each of the respective intake ports of the intake and exhaust devices. 
     (Element to Temperature-Condition) 
     Element  99  to temperature-condition is structurally the same as element  50  to temperature-condition in the first exemplary embodiment. 
     (Temperature Conditioning Systems) 
     A description is provided next of temperature conditioning systems. 
     The temperature conditioning systems are each formed to include a plurality of ducts connected to temperature conditioning unit(s)  150 X. With reference to  FIGS. 23 to 25 , the temperature conditioning systems according to the fifth exemplary embodiment are hereinafter described specifically.  FIG. 23  is the block diagram illustrating fourth temperature conditioning system  1500  according to the fifth exemplary embodiment.  FIG. 24  is a block diagram illustrating fifth temperature conditioning system  1600  according to the fifth exemplary embodiment.  FIG. 25  is a block diagram illustrating sixth temperature conditioning system  1700  according to the fifth exemplary embodiment. In the drawings, members having identical functions have the same reference marks. In the following description, an example in which each of the temperature conditioning systems is mounted in the hybrid vehicle is given; however, the present invention is not limited to this. 
     (Fourth Temperature Conditioning System) 
     As illustrated in  FIG. 23 , fourth temperature conditioning system  1500  includes, for example, intake duct  1511 , a plurality of supply ducts, and system controller  1530 . Intake duct  1511  connects with the respective intake ports of third intake and exhaust device  60 A and fourth intake and exhaust device  70 A of temperature conditioning unit  150 X. The plurality of supply ducts each supply gas to intake duct  1511  and includes, in  FIG. 23 , fourth supply duct  1512 A, fifth supply duct  1512 B, and sixth supply duct  1512 C. System controller  1530  controls gas supply sources for temperature conditioning unit  150 X. 
     Intake duct  1511  connects with supply ducts  1512 A to  1512 C via supply source switching unit  1510 . Fourth supply duct  1512 A has one end connecting with an exterior of the vehicle and another end connecting with supply source switching unit  1510 . Fifth supply duct  1512 B has one end connecting with an interior of the vehicle and another end connecting with supply source switching unit  1510 . Sixth supply duct  1512 C has one end connecting with discharge destination switching unit  1520  that is described later and another end connecting with supply source switching unit  1510 . It is to be noted that the one end of sixth supply duct  1512 C may connect directly with the outlets (not illustrated) of temperature conditioning unit  150 X. 
     Supply source switching unit  1510  is controlled by system controller  1530 . Supply source switching unit  1510  opens or closes parts of connection with supply ducts  1512 A to  1512 C to effect switching(s) among the gas supply sources for temperature conditioning unit  150 X. The gas supplied from any one of supply ducts  1512 A to  1512 C passes through intake duct  1511  and is taken into the impellers through the respective intake ports of third and fourth intake and exhaust devices  60 A and  70 A. The amount of gas supply for each of third and fourth intake and exhaust devices  60 A and  70 A is controlled by blower controller  90 . System controller  1530  controls the gas supply sources for temperature conditioning unit  150 X. System controller  1530  may control a flow rate of gas that is supplied to intake duct  1511 . Moreover, system controller  1530  may control blower controller  90 . 
     In cases where a temperature outside the vehicle is a temperature (hereinafter “cooling temperature”) suitable for cooling of element  99  to temperature-condition, supply source switching unit  1510  opens the part of connection with fourth supply duct  1512 A to supply gas from outside the vehicle to temperature conditioning unit  150 X. In cases where a temperature of the vehicle&#39;s interior is a temperature (hereinafter “heating temperature”) that is suited to raise the cooling temperature or to heat element  99  to temperature-condition, supply source switching unit  1510  opens the part of connection with fifth supply duct  1512 B to supply gas from the interior of the vehicle to temperature conditioning unit  150 X. In cases where exhaust gas from temperature conditioning unit  150 X has a cooling temperature or a heating temperature, supply source switching unit  1510  may open the part of connection with sixth supply duct  1512 C to supply the exhaust gas to temperature conditioning unit  150 X. 
     Fourth temperature conditioning system  1500  also includes discharge duct  1521  connecting with the outlets of temperature conditioning unit  150 X, exhaust duct  1522 A that lets the gas out of the vehicle, and exhaust duct  1522 B that discharges the gas into the interior of the vehicle. Discharge duct  1521  connects with exhaust duct  1522 A and exhaust duct  1522 B via discharge destination switching unit  1520 . Exhaust duct  1522 A has one end connecting with the exterior of the vehicle and another end connecting with discharge destination switching unit  1520 . Exhaust duct  1522 B has one end connecting with the interior of the vehicle and another end connecting with discharge destination switching unit  1520 . As described above, discharge destination switching unit  1520  also connects with the other end of sixth supply duct  1512 C. 
     Also discharge destination switching unit  1520  is controlled by system controller  1530 . Discharge destination switching unit  1520  opens or closes parts of connection with exhaust duct  1522 A, exhaust duct  1522 B, and sixth supply duct  1512 C to effect switching(s) among discharge destinations for the gas from temperature conditioning unit  150 X. System controller  1530  changes the discharge destination(s) of the gas from temperature conditioning unit  150 X and may control a flow rate of gas that is discharged into discharge duct  1521 . 
     Discharged gas generally has a higher temperature than gas that is drawn in. As such, when the interior (particularly an internal cabin space) of the vehicle has a lower temperature, discharge destination switching unit  1520  preferably opens the part of connection with exhaust duct  1522 B. In this way, the warmer gas is discharged into the vehicle&#39;s interior, and the vehicle&#39;s interior can be warmed up accordingly. In cases where the temperature of the vehicle&#39;s interior is high enough, discharge destination switching unit  1520  opens the part of connection with exhaust duct  1522 A to let the gas out of the vehicle. 
     Thus, in fourth temperature conditioning system  1500 , the gas supply source(s) for element  99  to temperature-condition and the discharge destination(s) of gas discharged from element  99  to temperature-condition can be changed based on the temperature outside the vehicle, the temperature of the vehicle&#39;s interior, and the temperature of the gas discharged from temperature conditioning unit  150 X. In other words, according to fourth temperature conditioning system  1500 , the gas from outside the vehicle or from the vehicle&#39;s interior is taken in, or the gas is discharged into the vehicle&#39;s interior. In this way, element  99  can be temperature-conditioned while energy is effectively utilized. Moreover, with gas taken in from outside the vehicle or from a closed space in the vehicle or with gas discharged out of the vehicle or into the closed space in the vehicle, gas quantity is equalized between intake and discharge, thus enabling suppression of pressure changes in the vehicle&#39;s interior. 
     (Fifth Temperature Conditioning System) 
     There are also cases where a plurality of temperature conditioning units  150 X are disposed in the hybrid vehicle. In such cases, from the viewpoint of effective energy utilization, respective gas courses of temperature conditioning units  150 X may be connected to each other to achieve a gas circulation system. This facilitates equalization of gas quantity between intake and discharge, thus leading to suppression of pressure changes in the interior of the vehicle. 
     As illustrated in  FIG. 24 , fifth temperature conditioning system  1600  that allows gas circulation between the plurality of temperature conditioning units  150 X includes, for example, third temperature conditioning unit  150 XA, fourth temperature conditioning unit  150 XB, intake duct  1611 , exhaust duct  1612 , intake duct  1621 , exhaust duct  1622 , and circulation controller  1630 . Intake duct  1611  connects with the respective intake ports of third intake and exhaust device  60 A and fourth intake and exhaust device  70 A of third temperature conditioning unit  150 XA. Exhaust duct  1612  lets gas out from the outlets of third temperature conditioning unit  150 XA. Intake duct  1621  connects with the respective intake ports of third intake and exhaust device  60 A and fourth intake and exhaust device  70 A of fourth temperature conditioning unit  150 XB. Exhaust duct  1622  lets gas out from the outlets of fourth temperature conditioning unit  150 XB. From exhaust duct  1612  and exhaust duct  1622 , circulation controller  1630  determines exhaust duct(s) for connection to at least one of intake duct  1611  and intake duct  1621 . 
     Intake duct  1611 , intake duct  1621 , exhaust duct  1612 , and exhaust duct  1622  are interconnected via circulation switching unit  1640 . In other words, intake duct  1611  has one end connecting with the intake ports of first temperature conditioning unit  150 XA and another end connecting with circulation switching unit  1640 . Exhaust duct  1612  has one end connecting with the outlets of third temperature conditioning unit  150 XA and another end connecting with circulation switching unit  1640 . Intake duct  1621  has one end connecting with the intake ports of fourth temperature conditioning unit  150 XB and another end connecting with circulation switching unit  1640 . Exhaust duct  1622  has one end connecting with the outlets of fourth temperature conditioning unit  150 XB and another end connecting with circulation switching unit  1640 . Circulation switching unit  1640  may also connect with one end of duct  1650 . Another end of duct  1650  connects with, for example, the exterior or the interior of the vehicle. Duct  1650  takes in gas from outside the vehicle or from the vehicle&#39;s interior or discharges the gas out of the vehicle or into the vehicle&#39;s interior when necessary. 
     Circulation switching unit  1640  is controlled by circulation controller  1630 . From exhaust duct  1612  and exhaust duct  1622 , circulation controller  1630  determines exhaust duct(s) for connection to at least one of intake duct  1611  and intake duct  1621 . Based on this determination, circulation switching unit  1640  opens or closes parts of connection with intake duct  1611 , intake duct  1621 , exhaust duct  1612 , and exhaust duct  1622  to effect switching(s) among gas supply sources or gas discharge destinations for third temperature conditioning unit  150 XA and fourth temperature conditioning unit  150 XB. Circulation controller  1630  may also control a flow rate of gas in each of the ducts. The amount of gas supply for each of the intake and exhaust devices of each of the temperature conditioning units is controlled by corresponding blower controller  90 . Circulation controller  1630  may also control blower controllers  90 . 
     With fifth temperature conditioning system  1600 , elements  99  can be temperature-conditioned while energy is effectively utilized through gas circulation between the plurality of temperature conditioning units. Such a system is useful in cases where gas discharged from third temperature conditioning unit  150 XA or fourth temperature conditioning unit  150 XB has a suitable temperature for cooling or heating of element  99  to temperature-condition. While fifth temperature conditioning system  1600  has two temperature conditioning units  150 XA and  150 XB in the illustrated example, it is to be noted that this is not limiting. Fifth temperature conditioning system  1600  may, for example, include one temperature conditioning unit  150 XA or  150 XB and another temperature conditioning unit (such as the one that includes one intake and exhaust device). The temperature conditioning units of fifth temperature conditioning system  1600  may be greater than or equal to three in number with gas circulated at least between two of those temperature conditioning units. While third and fourth temperature conditioning units  150 XA and  150 XB each have two intake and exhaust devices  60 A and  70 B in the illustrated example, this is not limiting. Each of third and fourth temperature conditioning units  150 XA and  150 XB may, for example, include intake and exhaust devices that are greater than or equal to three in number. Third and fourth temperature conditioning units  150 XA and  150 XB may have the same intake and exhaust devices disposed or different intake and exhaust devices disposed. The same goes for a sixth temperature conditioning system that is described later. 
     (Sixth Temperature Conditioning System) 
     In cases where a plurality of temperature conditioning units  150 X are disposed, temperature conditioning units  150 X may be connected in parallel for collective quantitative control of gases that are respectively drawn into temperature conditioning units  150 X. This enables effective energy utilization. 
     As illustrated in  FIG. 25 , sixth temperature conditioning system  1700  having the plurality of temperature conditioning units  150 X connected in parallel includes, for example, third temperature conditioning unit  150 XA, fourth temperature conditioning unit  150 XB, intake duct  1711 , intake duct  1721 , intake connection duct  1710 , and flow rate controller  1730 . Intake duct  1711  connects with the respective intake ports of third intake and exhaust device  60 A and fourth intake and exhaust device  70 A of third temperature conditioning unit  150 XA. Intake duct  1721  connects with the respective intake ports of third intake and exhaust device  60 A and fourth intake and exhaust device  70 A of second temperature conditioning unit  150 XB. Intake connection duct  1710  branches off to connect with intake duct  1711  and intake duct  1721 . Flow rate controller  1730  controls a flow rate of gas in intake duct  1711  and a flow rate of gas in intake duct  1721 . 
     Intake connection duct  1710  connects with intake duct  1711  and intake duct  1721  via supply amount adjuster  1740 . Intake connection duct  1710  connects with, for example, the exterior or the interior of the vehicle. Supply amount adjuster  1740  is controlled by flow rate controller  1730 . Supply amount adjuster  1740  opens or closes parts of connection with intake duct  1711  and intake duct  1721  to adjust an amount of gas supply for third temperature conditioning unit  150 XA and an amount of gas supply for fourth temperature conditioning unit  150 XB. The amount of gas supply for each of third and fourth intake and exhaust devices  60 A and  70 A of each of the temperature conditioning units is controlled by corresponding blower controller  90 . Flow rate controller  1730  may also control blower controllers  90 . 
     Sixth temperature conditioning system  1700  may also include exhaust duct  1712 , exhaust duct  1722 , and exhaust connection duct  1720 . Exhaust duct  1712  connects with the outlets of third temperature conditioning unit  150 XA. Exhaust duct  1722  connects with the outlets of fourth temperature conditioning unit  150 XB. Exhaust connection duct  1720  connects with exhaust duct  1712  and exhaust duct  1722 . 
     Exhaust connection duct  1720  connects with exhaust duct  1712  and exhaust duct  1722  via discharge amount adjuster  1750 . Exhaust connection duct  1720  connects with, for example, the exterior or the interior of the vehicle. Discharge amount adjuster  1750  is controlled by flow rate controller  1730 . Discharge amount adjuster  1750  opens or closes parts of connection with exhaust duct  1712  and exhaust duct  1722  to adjust an amount of gas discharge from third temperature conditioning unit  150 XA and an amount of gas discharge from fourth temperature conditioning unit  150 XB. 
     With sixth temperature conditioning system  1700 , elements  99  can be temperature-conditioned while energy is effectively utilized through collective quantitative control of gases that are respectively drawn into the plurality of temperature conditioning units (third and fourth temperature conditioning units  150 XA and  150 XB in  FIG. 25 ). 
     (Vehicles) 
     Temperature conditioning unit  150 X, temperature conditioning system  1500 , temperature conditioning system  1600 , or temperature conditioning system  1700  is mounted, for example, in vehicles including the hybrid vehicle. 
       FIG. 26A  is a schematic view of vehicle  1800 A according to the fifth exemplary embodiment. Vehicle  1800 A includes power source  1810 , drive wheels  1820 , driving controller  1830 , and temperature conditioning unit  150 X. Power source  1810  supplies power to drive wheels  1820 . Driving controller  1830  controls power source  1810 . 
       FIG. 26B  is a schematic view of another vehicle  1800 B according to the fifth exemplary embodiment. Vehicle  1800 B includes power source  1810 , drive wheels  1820 , driving controller  1830 , and temperature conditioning system  1500 ,  1600 , or  1700 . Vehicles  1800 A and  1800 B can allow secondary batteries and others to function at suitable temperatures with noises suppressed, thus each offering excellent comfort and high performance. 
     Sixth Exemplary Embodiment 
     The present exemplary embodiment differs from the fifth exemplary embodiment in that a plurality of intake and exhaust devices to use have the same number N of rotor vanes disposed and that an impeller of at least one of the intake and exhaust devices (a third intake and exhaust device) and an impeller of another intake and exhaust device (a fourth intake and exhaust device) rotate at different rotational speeds r. A temperature conditioning unit, temperature conditioning systems, and vehicles are otherwise similar to those in the fifth exemplary embodiment. With the impellers varying in rotational speed r, BPF noise frequency Fb3 of the third intake and exhaust device does not coincide with BPF noise frequency Fb4 of the fourth intake and exhaust device. In this way, the BPF noise peaks are dispersed, and a noise is produced in suppressed condition by the temperature conditioning unit. 
     Variations in rotational speed r result in variations in gas volume obtained. When cooling efficiency and ease of control are taken into account, it is preferable that a plurality of intake and exhaust devices disposed in one temperature conditioning system be comparable in gas volume. To achieve comparable gas volumes with variations in rotational speed r, maximum diameter L 3  of an impeller disk of the third intake and exhaust device and maximum diameter L 4  of an impeller disk of the fourth intake and exhaust device are varied in the present exemplary embodiment when these impeller disks are each viewed in an axial direction of a shaft. The impeller having the smaller impeller disk is rotated at a higher speed than the other impeller is rotated, thereby being adjusted to a comparable gas volume. 
     With reference to  FIGS. 27A and 27B , a description is provided of the intake and exhaust devices according to the present exemplary embodiment.  FIG. 27A  is a longitudinal section of third intake and exhaust device  60 B according to the sixth exemplary embodiment.  FIG. 27B  is a longitudinal section of fourth intake and exhaust device  70 B according to the sixth exemplary embodiment. Third intake and exhaust device  60 B and fourth intake and exhaust device  70 B may be structurally similar, except that impeller disk  161 B has the different maximum diameter when viewed in the axial direction of the shaft. This means that third rotor vanes  162 B of third intake and exhaust device  60 B are the same in number as fourth rotor vanes  262 B of fourth intake and exhaust device  70 B. Moreover, fan case  170  of third intake and exhaust device  60 B has the same outside diameter as fan case  170  of fourth intake and exhaust device  70 B. Third intake and exhaust device  60 B and fourth intake and exhaust device  70 B are not structurally limited to this, but may differ in the number of rotor vanes disposed or may have fan cases  170  of different outside diameters. In  FIGS. 27A and 27B , third intake and exhaust device  60 B and fourth intake and exhaust device  70 B are structurally similar to third intake and exhaust device  60 A but are not limited to this. It is to be noted that  FIGS. 27A and 27B  show that maximum diameter L 3 &gt;maximum diameter L 4 . 
     L 3 /L 4 , which is a ratio of maximum diameter L 3  to maximum diameter L 4 , is not particularly limited and may be determined appropriately in consideration of, for example, desired gas volumes and desired rotational speeds of the intake and exhaust devices. In the case of L 3 &gt;L 4 , L 3 /L 4  is, for example, greater than 1 and less than or equal to 1.7 and is preferably greater than 1 and less than or equal to 1.4. In the above cases, an operating point of a rotary drive source of third intake and exhaust device  60 B and an operating point of a rotary drive source of fourth intake and exhaust device  70 B do not have to be varied largely. For this reason, rotary drive sources  182  of the same type can be used in third intake and exhaust device  60 B and fourth intake and exhaust device  70 B, respectively. The operating point of the rotary drive source is a point of intersection of a speed characteristic curve that shows a rotational speed with respect to an electric current and a torque characteristic curve that shows torque with respect to the electric current. 
     Seventh Exemplary Embodiment 
     Temperature conditioning unit  150 Y according to the present exemplary embodiment is similar to the temperature conditioning unit of the fifth or sixth exemplary embodiment and is also similar to those in the temperature conditioning systems and the vehicles of the fifth or sixth exemplary embodiment, except that respective intake ports  172  of the third and fourth intake and exhaust devices are mounted to face outlets  80   b , respectively. It is to be noted that in each of temperature conditioning systems, the intake duct and the exhaust duct, for example, are appropriately replaced before connection to temperature conditioning unit  150 Y. In this way, internal gas of housing  80  is discharged through the intake and exhaust devices. This means that the intake and exhaust devices function as dischargers in the present exemplary embodiment. 
     With reference to  FIGS. 28A and 28B , a specific description is hereinafter provided of temperature conditioning unit  150 Y according to the present exemplary embodiment.  FIG. 28A  is a perspective view schematically illustrating temperature conditioning unit  150 Y according to the seventh exemplary embodiment.  FIG. 28B  is a sectional view of temperature conditioning unit  150 Y, the section being taken on plane  28 B- 28 B of  FIG. 28A . It is to be noted that an internal structure of each of the intake and exhaust devices is omitted in  FIG. 28A . Third intake and exhaust device  60 C is structurally similar to above-described third intake and exhaust device  60 A or above-described third intake and exhaust device  60 B, and fourth intake and exhaust device  70 C is structurally similar to above-described fourth intake and exhaust device  70 A or above-described fourth intake and exhaust device  70 B. It is to be noted that temperature conditioning unit  150 Y is not limited to the above structure. For example, orientation of each of vents  173  is not particularly limited and may be set appropriately to be right for a use or for the duct that is connected to vent  173 . Alternatively, vent  173  may be connected to the duct via a coupling member (not illustrated) such as an L-shaped elbow pipe. In this case, vent  173  is oriented appropriately to be right for the coupling member. 
     Element  99  to temperature-condition is disposed, for example, to divide the interior of housing  80  into intake-side chamber  81  including inlets  80   a  and exhaust-side chamber  82  including outlets  80   b  as in the case described above. As the gas is forcibly discharged out of exhaust-side chamber  82  through outlets  80   b  by third and fourth intake and exhaust devices  60 A and  60 B, internal pressure of exhaust-side chamber  82  lowers. Accordingly, external gas is aggressively taken in through inlets  80   a , diffuses throughout intake-side chamber  81 , passes through gaps in element  99  to temperature-condition or between element  99  to temperature-condition and housing  80 , and then flows into exhaust-side chamber  82 . That is when element  99  is temperature-conditioned, namely, cooled or heated. Here the flow of gas is indicated as an example by outlined arrows. 
     Intake-side chamber  81  and exhaust-side chamber  82  may be equal or different in capacity. Above all, it is preferable as in the case described above that intake-side chamber  81  have a larger capacity than exhaust-side chamber  82 . This is for the purpose of efficiently temperature-conditioning, namely, cooling or heating entire element  99 . 
     INDUSTRIAL APPLICABILITY 
     A temperature conditioning unit according to the present invention produces a lower level of noise while including a plurality of intake and exhaust devices and thus is useful to vehicles in particular. 
     REFERENCE MARKS IN THE DRAWINGS 
       10 A,  10 B,  10 C first intake and exhaust device 
       20 A,  20 B,  20 C second intake and exhaust device 
       30  housing 
       30   a  inlet 
       30   b  outlet 
       31  intake-side chamber 
       32  exhaust-side chamber 
       40  blower controller 
       50  element to temperature-condition 
       60 A,  60 B,  60 C third intake and exhaust device 
       70 A,  70 B,  70 C fourth intake and exhaust device 
       80  housing 
       80   a  inlet 
       80   b  outlet 
       81  intake-side chamber 
       82  exhaust-side chamber 
       90  blower controller 
       99  element to temperature-condition 
       100 X,  100 Y temperature conditioning unit 
       100 XA first temperature conditioning unit 
       100 XB second temperature conditioning unit 
       110 A impeller 
       111 A,  111 B impeller disk 
       111 AC central part 
       111 AP outer peripheral part 
       112 A,  112 B first rotor vane 
       112 As starting point 
       112 Ae end point 
       113 A shroud 
       120  fan case 
       121  side wall 
       121 S shoulder 
       122  intake port 
       123  vent 
       130  rotary drive device 
       131  shaft 
       132  rotary drive source 
       141  stator vane 
       142  diffuser ring 
       150 X,  150 Y temperature conditioning unit 
       150 XA third temperature conditioning unit 
       150 XB fourth temperature conditioning unit 
       160 A impeller 
       161 A,  161 B impeller disk 
       161 AC central part 
       161 AP outer peripheral part 
       162 A,  162 B third rotor vane 
       162 As starting point 
       162 Ae end point 
       163 A shroud 
       170  fan case 
       171  side wall 
       172  intake port 
       173  vent 
       180  rotary drive device 
       181  shaft 
       182  rotary drive source 
       210 A impeller 
       211 A impeller disk 
       211 AC central part 
       211 AP outer peripheral part 
       212 A,  212 B second rotor vane 
       213 A shroud 
       260 A impeller 
       261 A impeller disk 
       261 AC central part 
       261 AP outer peripheral part 
       262 A,  262 B fourth rotor vane 
       263 A shroud 
       500  first temperature conditioning system 
       510  supply source switching unit 
       511  intake duct 
       512 A first supply duct 
       512 B second supply duct 
       512 C third supply duct 
       520  discharge destination switching unit 
       521  discharge duct 
       522 A exhaust duct 
       522 B exhaust duct 
       530  system controller 
       600  second temperature conditioning system 
       611  intake duct 
       612  exhaust duct 
       621  intake duct 
       622  exhaust duct 
       630  circulation controller 
       640  circulation switching unit 
       650  duct 
       700  third temperature conditioning system 
       710  intake connection duct 
       711  intake duct 
       721  intake duct 
       720  exhaust connection duct 
       712  exhaust duct 
       722  exhaust duct 
       730  flow rate controller 
       740  supply amount adjuster 
       750  discharge amount adjuster 
       800 A,  800 B vehicle 
       810  power source 
       820  drive wheel 
       830  driving controller 
       911  impeller disk 
       912  forward swept vane 
       912   e  end point 
       1500  fourth temperature conditioning system 
       1510  supply source switching unit 
       1511  intake duct 
       1512 A fourth supply duct 
       1512 B fifth supply duct 
       1512 C sixth supply duct 
       1520  discharge destination switching unit 
       1521  discharge duct 
       1522 A exhaust duct 
       1522 B exhaust duct 
       1530  system controller 
       1600  fifth temperature conditioning system 
       1611  intake duct 
       1612  exhaust duct 
       1621  intake duct 
       1622  exhaust duct 
       1630  circulation controller 
       1640  circulation switching unit 
       1650  duct 
       1700  sixth temperature conditioning system 
       1710  intake connection duct 
       1711  intake duct 
       1721  intake duct 
       1720  exhaust connection duct 
       1712  exhaust duct 
       1722  exhaust duct 
       1730  flow rate controller 
       1740  supply amount adjuster 
       1750  discharge amount adjuster 
       1800 A,  1800 B vehicle 
       1810  power source 
       1820  drive wheel 
       1830  driving controller