Patent Publication Number: US-2018038388-A1

Title: Compressor system

Description:
TECHNICAL FIELD 
     The present invention relates to a compressor system. 
     Priority is claimed on Japanese Patent Application Nos. 2015-054570, 2015-055098, 2015-054983, and 2015-055099, filed Mar. 18, 2015, the contents of which are incorporated herein by reference. 
     BACKGROUND ART 
     A compressor system in which a motor and a compressor are integrated has a compressor for compressing gases such as air and other gases, and a motor for driving the compressor. In the compressor system, a rotary shaft extending from a casing of the compressor is connected to a rotary shaft of a motor similarly extending from the casing of the motor, and the rotation of the motor is transmitted to the compressor. The rotary shafts of the motor and the compressor are supported by a plurality of bearings and stably rotate. 
     Such a compressor system is used in, for example, a subsea production system as in Non-Patent Literature 1 or a floating production storage and offloading (FPSO) unit as in Non-Patent Literature 2. When used in the subsea production system, the compressor system is installed on the seabed, and delivers production fluid mixed with crude oil and natural gas to the top of the sea surface from a production well drilled to the depth of several thousand meters from the seabed. Also, when used for floating type marine oil storage facilities, compressor systems are installed in marine facilities such as ships. 
     CITATION LIST 
     
         
         [Non-Patent Literature 1] 
       
    
     Mitsubishi Heavy Industries Technical Review Vol. 34 No. 5 P310-P313
     [Non-Patent Literature 2]   

     Turbomachinery International September/October 2014 P18-P24 
     Incidentally, in the motor of the compressor system, as the rotor rotates at a high speed, heat is generated between the rotor and the stator, and temperatures of the rotor and the stator rise. Since there is a possibility that the efficiency of the motor may be lowered or the lifetime of the motor may be shortened if the temperature of the rotor or the stator rises, it is necessary to cool the rotor and the stator. 
     However, in the case of cooling the rotor and the stator by circulating a cooling medium in the interior of the stator or in the gap between the stator and the rotor from one side to the other side in an axial direction of the rotor, the cooling medium warms during the circulation. Consequently, it is difficult to efficiently cool the rotor and the stator. 
     SUMMARY OF INVENTION 
     One or more embodiments of the present invention provide a compressor system capable of efficiently cooling a motor. 
     A compressor system according to a first aspect of the present invention includes a motor which has a rotor configured to rotate around an axis, and a stator disposed on an outer circumferential side of the rotor with a gap from the rotor; a compressor which rotates together with the rotor to generate a compressed fluid; and a partitioning member which is disposed in the gap formed between the rotor and the stator to partition the gap in the radial direction, and forms a rotor-side flow passage through which a cooling fluid can flow along the axis with the rotor, and a stator-side flow passage through which the cooling fluid can flow along the axis with the stator, wherein the partitioning member has a surface in which a flow passage area decreases in a cross section orthogonal to the axis in at least one of the rotor-side flow passage and the stator-side flow passage in a direction in which the cooling fluid flows. 
     The temperature of the cooling fluid subjected to heat exchange with the rotor and the stator rises toward the downstream side in the flowing direction. Here, according to the compressor system of this aspect, by providing the partitioning member, the flow passage area becomes smaller in the flowing direction of the cooling fluid in at least one of the rotor-side flow passage and the stator-side flow passage. As a result, the flow velocity of the cooling fluid can be increased toward the downstream side, and the heat transfer coefficient can be improved. Therefore, even with the cooling fluid in which the temperature rises on the downstream side, sufficient heat exchange can be performed with the rotor and the stator. That is, it is possible to more uniformly cool the rotor and the stator over the direction of the axis by the cooling fluid. 
     In the compressor system according to the second aspect of the present invention, the cooling fluid flowing through the rotor-side flow passage and the stator-side flow passage in the first aspect may be a leaked flow of the compressed fluid from the compressor. 
     From the compressor, a leaked flow in which a part of the compressed fluid passes through the seal occurs. By positively using the leaked flow as a cooling fluid, it is not necessary to separately introduce the cooling fluid into the rotor-side flow passage and the stator-side flow passage. Therefore, since it is not necessary to newly provide a separate structure for introducing such a cooling fluid, which leads to cost reduction. 
     In the compressor system according to a third aspect of the present invention, the partitioning member in the first or second aspect may have a cylindrical shape with the axis as the center, and may have a shape in which an inner diameter dimension decreases from one side to the other side of the axis, and the cooling fluid may flow into the rotor-side flow passage from one side of the axis. 
     According to one or more embodiments, since the partitioning member has a cylindrical shape in which the inner diameter dimension decreases toward the other side in the direction of the axis, the cross-sectional area of the flow passage of the rotor-side flow passage can be made smaller in the flowing direction of the cooling fluid. Therefore, in the rotor-side flow passage, the flow velocity of the cooling fluid can be increased toward the downstream side, and the heat transfer coefficient can be improved. For this reason, heat exchange can be sufficiently performed even by a cooling medium in which the temperature rises on the downstream side, and the rotor can be cooled more uniformly over the direction of the axis. 
     Further, in the compressor system according to a fourth aspect of the present invention, the partitioning member in any one of the first to third aspects may have a cylindrical shape with the axis as the center, and may have a shape in which an outer diameter dimension decreases from one side to the other side of the axis, and the cooling fluid may flow into the stator-side flow passage from the other side of the axis. 
     According to one or more embodiments, by making the cooling fluid from the other side of the axis flow into the stator-side flow passage formed by the cylindrical partitioning member in which the outer diameter dimension decreases toward the other side in the direction of the axis, even in the stator-side flow passage, it is possible to reduce the cross-sectional area of the flow passage toward the downstream side. Therefore, the flow velocity of the cooling fluid can be increased toward the downstream side, and the heat transfer coefficient can be improved. Therefore, the stator can be more uniformly cooled throughout the direction of the axis. 
     In the compressor system according to a fifth aspect of the present invention, the partitioning member in the first or second aspect may have a cylindrical shape with the axis as the center, and may have a shape in which the thickness dimension in the radial direction of the rotor increases from one side to the other side of the axis, and the cooling fluid may flow into the rotor-side flow passage and the stator-side flow passage from one side of the axis. 
     According to one or more embodiments, since the partitioning member has a cylindrical shape in which the wall thickness dimension in the radial direction increases toward the other side in the direction of the axis, and the cooling fluid flows in from the one side in the direction of the axis, it is possible to reduce the cross-sectional area of the flow passage toward the downstream side in both of the rotor-side flow passage and the stator-side flow passage. Therefore, the flow velocity of the cooling fluid can be increased toward the downstream side in both of the rotor-side flow passage and the stator-side flow passage, and the heat transfer coefficient can be improved. Therefore, the rotor and the stator can be more uniformly cooled throughout the direction of the axis. 
     In the compressor system according to a sixth aspect of the present invention, the partitioning member according to any one of the first to fifth aspects may be provided at least in a region in which the rotor and the stator face in the radial direction of the rotor. 
     According to one or more embodiments, by providing the partitioning member in such a region, effective cooling can be performed by the cooling fluid in the facing region between the rotor and the stator having the largest calorific value. 
     A compressor system according to a seventh aspect of the present invention includes a motor which has a rotor configured to rotate around an axis, and a stator disposed on an outer circumferential side of the rotor with a gap allowing the cooling fluid to flow along the axis from the rotor; a compressor which rotates together with the rotor to generate a compressed fluid; and a turn imparting section which imparts a turning component directed forward in a rotational direction of the rotor to the cooling fluid which flows through the gap formed between the rotor and the stator. 
     According to one or more embodiments of such a compressor system, by imparting the turning component directed forward in the rotational direction with respect to the cooling fluid flowing through the gap between the rotor and the stator by the turn imparting unit, the flowing direction of the cooling fluid can be made to follow the advancing direction of the outer surface of the rotating rotor. Therefore, it is possible to suppress the amount of heat generated by shearing caused by rapid acceleration of the cooling fluid due to the contact between the cooling fluid and the outer surface of the rotor, and the cooling efficiency of the rotor can be improved. 
     In the compressor system according to an eighth aspect of the present invention, the turn imparting unit in the seventh aspect may be a partitioning member which is disposed in the gap between the rotor and the stator to partition the gap in the radial direction so that the cooling fluid can flow along the axis with the rotor, and in which a protrusion or a recess extending forward in the rotational direction of the rotor is formed on a surface facing the rotor toward a downstream side in the flowing direction of the cooling fluid. 
     According to one or more embodiments, by providing such a partitioning member, the cooling fluid flowing between the partitioning member and the rotor is guided by the protrusion or the recess. As a result, a turning component directed forward in the rotational direction toward the downstream side is imparted to the cooling fluid. Therefore, the flowing direction of the cooling fluid can be made to follow the advancing direction of the outer surface of the rotor, the amount of heat generated by shearing can be suppressed, and the cooling efficiency of the rotor can be improved. 
     In the compressor system according to the ninth aspect of the present invention, the recess may be formed in the partitioning member according to the eighth aspect, and a width dimension of the recess in the direction of the axis may be smaller on a downstream side than on an upstream side in the flowing direction of the cooling fluid. 
     According to one or more embodiments, by reducing the width dimension of the recess on the downstream side in this way, it is possible to increase the velocity component in the rotational direction (circumferential direction) on the downstream side. Therefore, the cooling fluid can be accelerated in the rotational direction on the downstream side, and the heat transfer on the downstream side can be improved. For this reason, it is possible to sufficiently cool the rotor even by the cooling air which has been heated up by performing heat exchange with the rotor on the upstream side, and the cooling efficiency of the rotor can be further improved. 
     In the compressor system according to a tenth aspect of the present invention, the turn imparting unit in the seventh aspect may be a guide member which is disposed on an upstream side in the flowing direction from an inflow port of the cooling fluid in the gap between the rotor and the stator, and is provided to be relatively non-rotatable with respect to the stator, and the guide member may have a guide surface which faces the upstream side in the flowing direction of the cooling fluid and inclines forward in the rotational direction of the rotor with respect to the axis, toward the downstream side. 
     According to one or more embodiments, by providing the guide member having such a guide surface, the cooling fluid can be guided by the guide surface. As a result, a turning component directed forward in the rotational direction toward the downstream side is imparted to the cooling fluid. Therefore, the flowing direction of the cooling fluid can be made to follow the advancing direction of the outer surface of the rotor, the amount of heat generated by shearing can be suppressed, and the cooling efficiency of the rotor can be improved. 
     In the compressor system according to an eleventh aspect of the present invention, a plurality of the guide members in the tenth aspect may be provided in a rotational direction of the rotor with a gap, and a gap dimension in the rotational direction between trailing edges of the guide members is smaller than the gap dimension in the rotational direction between leading edges of the guide members adjacent in the rotational direction. 
     According to one or more embodiments, the gap dimension between the trailing edges, which are the downstream end portions, is smaller than the gap dimension between the leading edges which are the upstream end portions of the guide member. Therefore, when the cooling fluid guided by the guide surface flows out from the space between the trailing edges of the guide members toward the gap formed between the rotor and the stator, the flow velocity increases as compared with the case of flowing into the space between the leading edges of the guide members. That is, the flow passage area of the cooling fluid can be reduced on the trailing edge side. Therefore, the cooling fluid can be accelerated forward in the rotational direction (circumferential direction), and the flowing direction of the cooling fluid can be made to follow the advancing direction of the outer surface of the rotor. Therefore, it is possible to suppress the amount of heat generated by shearing, and to improve the cooling efficiency of the rotor. 
     A compressor system according to a twelfth aspect of the present invention includes a motor which has a rotor configured to rotate around an axis, and a stator disposed on an outer circumferential side with a gap, which allows cooling fluid to flow along the axis side, from the rotor, a compressor which rotates together with the rotor to generate a compressed fluid; a plurality of partitioning members which are provided to be relatively non-rotatable with respect to the stator and to extend from the stator toward the rotor, and partition the gap formed between the stator and the rotor into a plurality of spaces in a circumferential direction; and a fluid introduction section which allows the cooling fluid to flow in at least two spaces among the plurality of spaces from different sides in the direction of the axis. 
     According to one or more embodiments of such a compressor system, the cooling air flows into each of a plurality of spaces formed by partitioning the gap between the rotor and the stator in the circumferential direction by the partitioning member, from different sides. Therefore, in these spaces, the cooling fluid flows in the mutually opposite directions of the axis. Since the cooling fluid flows, while heat exchange with the rotor is performed, the temperature of the cooling fluid on the downstream side in the flowing direction of the cooling fluid becomes higher than the temperature on the upstream side. However, since the flowing directions of the cooling fluid are the opposite directions between the plurality of spaces aligned in the circumferential direction and the rotor relatively rotates with respect to the plurality of spaces, for example, at the position (the position on the upstream side and the downstream side in a certain space) of the end portion in the direction of the axis of the partitioning member, the high-temperature cooling air and the low-temperature cooling air are alternately brought into contact with the rotor. Therefore, even if the cooling air reaches a high temperature at the position on the downstream side in a certain space, the high-temperature cooling air does not always come into contact with the same position of the rotor, and the rotor can be efficiently cooled over the direction of the axis. 
     Further, in the compressor system according to a thirteenth aspect of the present invention, the partitioning member in the twelfth aspect may have a plate shape, and may have a guide surface which faces the upstream side in the flowing direction of the cooling fluid and is inclined forward in the rotational direction of the rotor with respect to the axis, toward the downstream side 
     According to one or more embodiments, by guiding the cooling fluid with such a guide surface, the turning component directed forward in the rotational direction toward the downstream side is imparted to the cooling fluid. Therefore the flowing direction of the cooling fluid can be made to follow the advancing direction of the outer surface of the rotating rotor, and it is possible to suppress the amount of heat generated by shearing caused by rapid cooling of the cooling fluid due to the contact between the cooling fluid and the outer surface of the rotor. Therefore, the cooling efficiency of the rotor can be improved. 
     Further, in the compressor system according to a fourteenth aspect of the present invention, the partitioning member in the thirteenth aspect may be a member having a spiral plate shape which extends forward in the rotational direction of the rotor, toward the downstream side in the flowing direction of the cooling fluid, and the guide surface may be a surface which faces the upstream side in the flowing direction of the cooling fluid in the member having the spiral plate shape. 
     According to one or more embodiments, by using a member having a spiral plate shape as the partitioning member in this manner, a turning component directed forward in the rotational direction toward the downstream side can be effectively imparted to the cooling fluid. Since the cooling fluid comes into contact with the outer surface of the rotor, it is possible to suppress the amount of heat generated by shearing caused by rapid acceleration of the cooling fluid due to the contact between the cooling fluid and the outer surface of the rotor, and the cooling efficiency of the rotor can be improved. 
     In the compressor system according to a fifteenth aspect of the present invention, the partitioning member according to any one of the twelfth to fourteenth aspects may be provided at least in a region in which the rotor and the stator face in the radial direction of the rotor. 
     According to one or more embodiments, by providing the partitioning member in such a region, effective cooling can be performed by the cooling fluid in the facing region between the rotor and the stator having the largest calorific value. 
     A compressor system according to a sixteenth aspect of the present invention includes a motor which has a rotor configured to rotate around an axis, and a stator disposed on an outer circumferential side of the rotor with a gap from the rotor; a compressor which rotates together with the rotor to generate a compressed fluid; and a fluid supply member which is disposed in the gap formed between the rotor and the stator, is provided to be relatively non-rotatable with respect to the stator, extends in a direction of the axis of rotation of the rotor, and opens toward the rotor to form an ejection port capable of ejecting the cooling fluid. 
     According to one or more embodiments of such a compressor system, by separately providing a fluid supply member having an injection port for a cooling fluid formed therein, a low-temperature cooling fluid before heat exchange with the rotor can be supplied to the ejection port at all times. For this reason, it is possible to eject the low-temperature cooling fluid to the rotor from the ejection port at all times, thereby improving the cooling efficiency of the rotor. 
     In the compressor system according to a seventeenth aspect of the present invention, the ejection port in the fluid supply member in the sixteenth aspect may be formed so that the cooling fluid can be ejected toward the front side in the rotational direction of the rotor. 
     Since the rotor rotates, by ejecting the cooling fluid from the ejection port forward in the rotational direction of the rotor, the flowing direction of the cooling fluid can be made to follow the advancing direction of the outer surface of the rotating rotor. Therefore, it is possible to suppress the amount of heat generated by shearing caused by rapid acceleration of the cooling fluid due to the contact between the cooling fluid and the outer surface of the rotor. Therefore, the cooling efficiency of the rotor can be improved. 
     In the compressor system according to an eighteenth aspect of the present invention, in the fluid supply member according to the sixteenth or seventeenth aspect, a plurality of ejection ports may be formed at intervals in the direction of the axis, and a communication hole which extends in the direction of the axis and communicates with the plurality of ejection ports so that the cooling medium from the outside can flow in from one side of the axis may be formed. 
     According to one or more embodiments, by supplying the cooling fluid to the plurality of ejection ports aligned in the direction of the axis through the communication hole in this manner, the cooling fluid can be ejected to the outer surface of the rotor evenly throughout the direction of the axis. Therefore, the cooling efficiency of the rotor can be further improved. 
     Further, in the fluid supply member in the compressor system according to a nineteenth aspect of the present invention, the ejection port located on the downstream side in the flowing direction of the cooling fluid flowing through the communication hole in the eighteenth aspect may have an opening diameter larger than that of the ejection port located on the upstream side. 
     When the cooling fluid flows through the communication hole, the pressure loss increases toward the downstream side. Here, since the opening diameter of the ejection port on the downstream side is large, the cooling fluid having a sufficient flow rate can be ejected toward the rotor even on the downstream side. Therefore, the cooling efficiency of the rotor can be further improved. 
     Further, in the fluid supply member in the compressor system according to a twentieth aspect of the present invention, the plurality of the ejection ports of the fluid supply member in the eighteenth or nineteenth aspect may be formed at intervals in the direction of the axis and the circumferential direction of the rotor, and in the fluid supply member, more of the ejection ports located on the downstream side in the flowing direction of the cooling fluid flowing through the communication hole may be formed in the circumferential direction than the ejection ports located on the upstream side. 
     According to one or more embodiments, by increasing the number of ejection ports on the downstream side in this way, it is possible to eject the cooling fluid having a sufficient flow rate toward the rotor on the downstream side in which the pressure loss increases. Therefore, the cooling efficiency of the rotor can be further improved. 
     According to one or more embodiments of the compressor system, the motor can be efficiently cooled. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1  is a schematic view illustrating a compressor system in a first embodiment of the present invention. 
         FIG. 2  is a schematic view illustrating a compressor system in a modified example of the first embodiment of the present invention. 
         FIG. 3  is a schematic view illustrating a compressor system in a second embodiment of the present invention. 
         FIG. 4  is a schematic view illustrating a compressor system in a third embodiment of the present invention. 
         FIG. 5  is an enlarged cross-sectional view including an axis illustrating a partitioning member in a compressor system in a third embodiment of the present invention. 
         FIG. 6  is a schematic view illustrating a main part of a compressor system in a modified example of the third embodiment of the present invention. 
         FIG. 7  is a schematic view illustrating a compressor system in a fourth embodiment of the present invention. 
         FIG. 8  is a schematic view illustrating a compressor system in a fourth embodiment of the present invention, and is a cross-sectional view taken along line A 4 -A 4  of  FIG. 7 . 
         FIG. 9  is an enlarged exploded view of a guide member in a compressor system in a fourth embodiment of the present invention. 
         FIG. 10  is a schematic view illustrating a compressor system in a fifth embodiment of the present invention. 
         FIG. 11  is a cross-sectional view illustrating a main part of a compressor system of the fifth embodiment of the present invention and illustrating a cross-section taken along a line A 5 -A 5  of  FIG. 10 . 
         FIG. 12  is a perspective view illustrating a fluid introduction section of the compressor system in the fifth embodiment of the present invention. 
         FIG. 13  is a cross-sectional view illustrating a main part of a compressor system according to a sixth embodiment of the present invention, taken along a cross-section corresponding to a cross-section taken along line A 5 -A 5  of  FIG. 10 . 
         FIG. 14  is a cross-sectional view illustrating a main part of a modified example of a fifth embodiment and a sixth embodiment of the present invention, taken along a cross-section corresponding to the A 5 -A 5  cross-section of  FIG. 10 . 
         FIG. 15  is a schematic view illustrating a compressor system of a seventh embodiment of the present invention. 
         FIG. 16  is a schematic view illustrating a compressor system in the seventh embodiment of the present invention and is a cross-sectional view taken along the line A 7 -A 7  of  FIG. 15 . 
         FIG. 17  is a schematic view illustrating a main part of a compressor system in a first modified example of the seventh embodiment of the present invention. 
         FIG. 18  is a schematic view illustrating a main part of a compressor system in a second modified example of the seventh embodiment of the present invention. 
         FIG. 19  is a schematic view illustrating a main part of a compressor system in a third modified example of the seventh embodiment of the present invention. 
         FIG. 20  is a schematic view illustrating a compressor system according to a third modified example of the seventh embodiment of the present invention, and is a cross-sectional view taken along the line B 7 -B 7  of  FIG. 19 . 
         FIG. 21  is a schematic view illustrating a compressor system in an eighth embodiment of the present invention, and is a cross-sectional view taken along a cross-section corresponding to a cross-section taken along the line A 7 -A 7  of  FIG. 15 . 
         FIG. 22  is a schematic view illustrating a main part of a compressor system in a ninth embodiment of the present invention. 
         FIG. 23  is a schematic view illustrating a main part of a compressor system in a modified example of the ninth embodiment of the present invention. 
     
    
    
     DETAILED DESCRIPTION OF EMBODIMENTS 
     First Embodiment 
     Hereinafter, a first embodiment of the present invention will be described with reference to  FIG. 1 . 
     A compressor system  1  is used in a subsea production system which is one of the development methods of a marine oil and gas field and is provided on the seabed, or is used in floating production storage and offloading (FPSO) and is provided on the sea surface. The compressor system  1  pumps a production fluid (hereinafter simply referred to as a fluid F) such as oil and gas collected from a production well of an oil and gas field present in the seabed from hundreds to thousands of meters. 
     The compressor system  1  includes a compressor  2  having a shaft  21  extending in the direction of the axis O (a left-right direction of  FIG. 1 ), a motor  3  having a rotor  31  directly connected to the shaft  21 , a bearing unit  4  which supports the shaft  21 , a casing  5  which houses the motor  3  and the compressor  2 , and a partitioning member  6  disposed on the outer circumferential side of the rotor  31 . 
     The compressor  2  is housed in the casing  5  and compresses the fluid F by the rotation of the shaft  21  around the axis O together with the rotor  31  to generate the compressed fluid CF. The compressor  2  of the present embodiment has a shaft  21  extending in the direction of the axis O, an impeller  22  fixed to the shaft  21 , and a housing  23  which houses the impeller  22 . 
     The shaft  21  is a rotary shaft extending in the direction of the axis O and is supported by the casing  5  to be rotatable around the axis O. The shaft  21  penetrates the housing  23 , and both ends thereof extend from the housing  23 . The shaft  21  extends inside the casing  5  described later in the direction of the axis O. 
     The impeller  22  rotates together with the shaft  21  to compress the fluid F passing through the interior of the impeller  22  and generate a compressed fluid CF. 
     The housing  23  is an exterior component of the compressor  2  and houses the impeller  22  therein. The housing  23  is housed in the casing  5 . 
     The motor  3  is housed in the casing  5  with a space in the direction of the axis O with respect to the compressor  2 . The motor  3  has a rotor  31  fixed to be integrated with the shaft  21 , and a stator  32  disposed on the outer circumferential side of the rotor  31 . 
     The rotor  31  is rotatable around the axis O integrally with the shaft  21 . The rotor  31  is directly fixed to the outer circumferential side of the shaft  21  to integrally rotate with respect to the shaft  21  of the compressor  2  without using a gear or the like. The rotor  31  has a rotor core (not illustrated) through which an induced current flows as the stator  32  generates a rotating magnetic field. 
     The stator  32  is provided with an annular gap  33  in the radial direction centered on the axis O with respect to the rotor  31  to cover the rotor  31  from the outer circumferential side. The stator  32  has a plurality of stator cores (not illustrated) disposed in the circumferential direction of the rotor  31 , and a stator winding (not illustrated) wound around the stator core. The stator  32  rotates the rotor  31  by generating a rotating magnetic field when a current flows from the outside. The stator  32  is fixed to the casing  5  in the casing  5 . 
     The bearing unit  4  is housed in the casing  5  to rotatably support the shaft  21 . The bearing unit  4  of the present embodiment includes a plurality of journal bearings  41  and thrust bearings  42 . 
     The journal bearing  41  supports the load acting on the shaft  21  in the radial direction. The journal bearing  41  is disposed at both ends of the shaft  21  in the direction of the axis O to sandwich the motor  3  and the compressor  2  from the direction of the axis O. The journal bearing  41  is also disposed between the region in which the compressor  2  is provided and the region in which the motor  3  is provided, and on the side closer to the motor  3  than the seal member  51  to be described later. 
     The thrust bearing  42  supports the load acting on the shaft  21  in the direction of the axis O via a thrust collar  21   a  formed on the shaft  21 . The thrust bearing  42  is disposed between the region in which the compressor  2  is provided and the region in which the motor  3  is provided, and on the side closer to the compressor  2  than the seal member  51  to be described later. 
     The casing  5  houses the compressor  2  and the motor  3  therein. The casing  5  has a cylindrical shape along the axis O. The inner surface of the casing  5  protrudes toward the shaft  21  between the compressor  2  and the motor  3  in the direction of the axis O. A seal member  51 , which seals a part between the region in which the compressor  2  is provided and the region in which the motor  3  is provided, is provided in the protruding portion. 
     The partitioning member  6  is disposed in the annular gap  33  between the rotor  31  and the stator  32 , and is provided in a state in which it does not come into contact with the rotor  31  and the stator  32 . Specifically, the partitioning member  6  has a cylindrical shape with the axis O as the center, and has a shape in which the outer diameter dimension and the inner diameter dimension gradually decrease from one side (the side close to the compressor  2 ) of the axis O toward the other side (the side away from the compressor  2 ). 
     In the present embodiment, the inner diameter dimension of the partitioning member  6  linearly decreases toward the other side of the axis O. That is, the inner surface (surface)  6   a  of the partitioning member  6  facing inward in the radial direction, is linearly inclined from one side of the axis O to the other side on a cross-section including the axis O. Further, the length dimension of the partitioning member  6  in the direction of the axis O is substantially the same as the length dimension in the direction of the axis O of the region in which the rotor  31  faces the stator  32  in the radial direction. The partitioning member  6  is provided in the facing region. 
     The thickness dimension of the partitioning member  6  is constant, and similarly, the outer diameter dimension of the partitioning member  6  decreases linearly toward the other side of the axis O. That is, the outer surface (surface)  6   b  of the partitioning member  6  facing outward in the radial direction is linearly inclined from one side of the axis O to the other side on the cross-section including the axis O. 
     Various materials such as metals, ceramics, and organic materials such as resins can be used as the partitioning member  6 . 
     The partitioning member  6  is fixed to the casing  5  to be relatively non-rotatable with respect to the stator  32 . For example, support members  10  which protrude inward in the radial direction to face each other in the direction of the axis O are provided in the casing  5  at both end surfaces facing in the direction of the axis O of the stator  32 , and the partitioning member  6  is fixed to the radially inner side of the support members  10 . 
     The support members  10  may have annular shapes with the axis O as the center or columnar shapes protruding radially inward at a part in the circumferential direction, and the shapes are not limited. 
     Further, the partitioning member  6  partitions the gap  33  in the radial direction and forms two spaces between the partitioning member  6  and the rotor  31 . The two spaces are a rotor-side flow passage C 1  between the partitioning member  6  and the rotor  31 , and a stator-side flow passage C 2  between the partitioning member  6  and the stator  32 . 
     Here, in the compressor system  1  of the present embodiment, a part of the compressed fluid CF from the compressor  2  flows into the rotor-side flow passage C 1  using the leaked flow LF leaking from the seal member  51  as a cooling fluid. 
     The leaked flow LF is caused to flow into the rotor-side flow passage C 1  by, for example, a fluid introduction section (not illustrated). The fluid introduction section is, for example, a guide plate, a conduit, or the like provided in the casing  5  to guide the leaked flow LF flowing out of the seal member  51  to the motor  3  side. 
     In the aforementioned compressor system  1  of the present embodiment, the partitioning member  6  has an inner surface  6   a  in which a flow passage area in the cross-section orthogonal to the axis O in the rotor-side flow passage C 1  gradually decreases in the direction in which the leaked flow LF flows along the rotor-side flow passage C 1  along the axis O, that is, from one side toward the other side in the direction of the axis O. 
     Therefore, the temperature of the leaked flow LF subjected to heat exchange with the rotor  31  rises toward the downstream side in the flowing direction of the leaked flow LF. Here, in the compressor system  1  of the present embodiment, by providing the partitioning member  6 , the cross-sectional area of the flow passage in the cross-section orthogonal to the axis O in the rotor-side flow passage C 1  decreases in the flowing direction of the leaked flow LF. As a result, the flow velocity of the leaked flow LF can be increased toward the downstream side, and the heat transfer coefficient can be improved. 
     Therefore, even with the leaked flow LF having a higher temperature on the downstream side, it is possible to perform sufficient heat exchange with the rotor  31 . That is, it is possible to more uniformly cool the rotor  31  over the direction of the axis O with the leaked flow LF. As a result, the motor  3  can be efficiently cooled. 
     Furthermore, when the leaked flow LF from the compressor  2  is actively used as a cooling fluid, it is not necessary to separately introduce the cooling fluid into the rotor-side flow passage C 1 . Therefore, there is no need to newly provide a structure which introduces such a cooling fluid, which leads to a reduction in cost. 
     Further, since the partitioning member  6  has a cylindrical shape in which the inner diameter dimension decreases toward the other side in the direction of the axis O, it is possible to easily form the rotor-side flow passage C 1  so that the cross-sectional area of the flow passage decreases in the flowing direction of the leaked flow LF. Therefore, the flow velocity of the leaked flow LF can be increased toward the downstream side, and the heat transfer coefficient can be improved. 
     Furthermore, by providing the partitioning member  6  in the facing region between the rotor  31  and the stator  32 , effective cooling can be performed by the leaked flow LF in the facing region in which the heat generation amount is the largest. 
     Here, in the present embodiment, as illustrated in  FIG. 2 , the leaked flow LF may flow into the stator-side flow passage C 2  from the other side of the axis O. As the fluid introduction section, for example, an introduction flow passage or the like which is formed inside the casing  5  and is capable of guiding the leaked flow LF toward the other side in the direction of the axis O is used. 
     In the example illustrated in  FIG. 2 , a through-hole (not illustrated) penetrating in the direction of the axis O to open to the stator-side flow passage C 2  is formed on the support member  10  so that the leaked flow LF can flow into the stator-side flow passage C 2  and can flow out from the stator-side flow passage C 2 . Further, a columnar member provided in a part in the circumferential direction is used as the support member  10 . 
     In this way, in the example illustrated in  FIG. 2 , the cylindrical partitioning member  6  having a smaller outer diameter dimension toward the other side in the direction of the axis O is provided, and the leaked flow LF is made to flow into the stator-side flow passage C 2  from the other side of the axis O. Therefore, in addition to the rotor-side flow passage C 1 , the flow velocity of the leaked flow LF can also be increased toward the downstream side in the stator-side flow passage C 2 , and the heat transfer coefficient can be improved. Therefore, the stator  32  can be more uniformly cooled throughout the direction of the axis O. 
     Here, in the present embodiment, both of the inner diameter dimension and the outer diameter dimension of the partitioning member  6  are formed to become smaller toward the other side in the direction of the axis O. However, for example, at least one of the inner diameter dimension and the outer diameter dimension may be formed to become smaller toward the other side in the direction of the axis O. 
     Second Embodiment 
     Next, a compressor system  61  of a second embodiment will be described with reference to  FIG. 3 . 
     In the second embodiment, the same constituent elements as those of the first embodiment are denoted by the same reference numerals, and a detailed description thereof will not be provided. In the compressor system  61  of the second embodiment, the shape of the partitioning member  66  is different from that of the first embodiment. Further, the leaked flow LF serving as a cooling fluid is caused to flow into both of the rotor-side flow passage C 1  and the stator-side flow passage C 2  from one side in the direction of the axis O. 
     The partitioning member  66  has a cylindrical shape with the axis O as a center and has a shape in which the wall thickness in the radial direction increases from one side of the axis O toward the other side. An inner surface  66   a  facing the radially inner side and an outer surface  66   b  facing the radially outer side in the partitioning member  66  are linearly inclined from one side of the axis O to the other side on a cross-section including the axis O. 
     In order to allow the leaked flow LF to flow into the stator-side flow passage C 2  and to flow out of the stator-side flow passage C 2 , as in the case illustrated in  FIG. 2 , a through-hole (not illustrated) penetrating in the direction of the axis O is formed in the support member  10  to open to the stator-side flow passage C 2 . Further, a columnar member provided in a part in the circumferential direction is used as the support member  10 . 
     According to the compressor system  61  of the present embodiment described above, since the partitioning member  66  has a cylindrical shape in which the wall thickness dimension in the radial direction increases toward the other side in the direction of the axis O, it is possible to easily form the rotor-side flow passage C 1  and the stator-side flow passage C 2  so that the cross-sectional area of the flow passage decreases toward the flowing direction of the leaked flow LF. 
     Therefore, the flow velocity of the leaked flow LF can be increased toward the downstream side, and the heat transfer coefficient can be improved. Therefore, heat exchange can be sufficiently performed even by the leaked flow LF having a high temperature on the downstream side, and the rotor  31  and the stator  32  can be more uniformly cooled over the direction of the axis O. 
     Although the first and second embodiments of the present invention have been described in detail with reference to the drawings, the respective configurations and combinations thereof in the respective embodiments are merely examples, and additions, omissions, substitutions, and other changes to the configuration can be made within the scope that does not depart from the gist of the present invention. Further, the present invention is not limited by the embodiments, and is limited only by the claims. 
     For example, the fluid introduction section is not necessarily provided. That is, the leaked flow LF from the seal member  51  may be made to naturally flow to one side in the direction of the axis O. 
     Also, the support member  10  is not limited to the aforementioned case. That is, the partitioning member  6  ( 66 ) may be held in the gap  33  between the rotor  31  and the stator  32 . 
     Further, the leaked flow LF may flow only through the stator-side flow passage C 2 . 
     Further, in place of the leaked flow LF, a cooling medium introduced from the outside or bleed air from the compressor  2  may be used for the rotor-side flow passage C 1  and the stator-side flow passage C 2 . 
     Further, the partitioning member  6  ( 66 ) is not limited to being provided only in the facing region between the rotor  31  and the stator  32 , and the dimension in the direction of the axis O may be further decreased or may be increased. 
     Further, the inner surface  6   a  ( 66   a ) and the outer surface  6   b  ( 66   b ) of the partitioning member  6  ( 66 ) may be curvedly inclined in a cross-section including the axis O from one side of the axis O toward the other side, and a step or the like may be formed at an intermediate position in the direction of the axis O. 
     Third Embodiment 
     Hereinafter, a third embodiment of the present invention will be described with reference to  FIG. 4 . 
     A compressor system  101  includes a compressor  2  having a shaft  21  extending in the direction of the axis O (left-right direction in the drawing), a motor  3  having a rotor  31  directly connected to the shaft  21 , a bearing unit  4  which supports the shaft  21 , a casing  5  that houses the motor  3  and the compressor  2 , and a partitioning member (turn imparting section)  6 A disposed on the outer circumferential side of the rotor  31 . 
     The partitioning member  6 A is disposed in an annular gap  33  between the rotor  31  and the stator  32 , and is provided in a state in which it does not come into contact with the rotor  31  and the stator  32 . Specifically, the partitioning member  6 A has a cylindrical shape with the axis O as the center. 
     Various materials such as metals, ceramics, and organic materials such as resins can be used for the partitioning member  6 A. 
     The partitioning member  6 A is fixed to the casing  5  to be relatively non-rotatable with respect to the stator  32 . For example, support members  10  that protrude inward in the radial direction to face both end surfaces of the stator  32  directed to the direction of the axis O in the direction of the axis O are provided in the casing  5 . The partitioning member  6 A is fixed to the support members  10 . 
     The support members  10  may have annular shapes with the axis O as the center or column shapes protruding radially inward in a part in the circumferential direction, and the shapes are not limited. 
     Further, a cooling fluid RF can flow through the gap  33   a  between the partitioning member  6 A and the rotor  31 . As the cooling fluid RF, it is possible to use, for example, a leaked flow in which a part of the compressed fluid CF from the compressor  2  has leaked from the seal member  51 , a cooling medium introduced from the outside of the casing  5 , bleed air from the compressor  2  or the like. The cooling fluid RF flows into the gap  33   a  from the compressor  2  side, which is one side in the direction of the axis O, due to a flow passage, a guide plate or the like (not illustrated) provided in the casing  5 . 
     Further, as illustrated in  FIG. 5 , in the partitioning member  6 A, a recess  6 Ab which is recessed radially outward on the inner surface (surface)  6 Aa facing the rotor  31  side, and has a spiral groove shape extending to the front RD 1  of the rotor  31  in the rotational direction RD, toward the downstream side of the cooling fluid RF in the flowing direction. 
     According to the aforementioned compressor system  101  of the present embodiment, since the turning component directed toward the front RD 1  in the rotational direction RD is imparted to the cooling fluid RF flowing between the rotor  31  and the stator  32  by the partitioning member  6 A, the flowing direction of the cooling fluid RF can be made to follow the advancing direction of the outer surface of the rotating rotor  31 . As a result, it is possible to suppress the amount of heat generated by shearing caused by rapid acceleration of the cooling fluid RF due to the contact between the cooling fluid RF and the outer surface of the rotor  31 . Therefore, the cooling efficiency of the rotor  31  can be improved, and the motor can be efficiently cooled. 
     Here, in this embodiment, as illustrated in  FIG. 6 , the dimension of the width W in the direction of the axis O in the recess  6 Ab may be smaller on the downstream side than on the upstream side. In this way, by narrowing the dimension of the width W of the recess  6 Ab on the downstream side, it is possible to increase the velocity component in the rotational direction RD (circumferential direction) on the downstream side. Therefore, the cooling fluid RF can be accelerated on the downstream side, and the heat transfer on the downstream side can be improved. Therefore, it is also possible to sufficiently cool the rotor  31  on the downstream side with the cooling air RF in which the temperature has increased due to heat exchange with the rotor  31  on the upstream side. 
     In the present embodiment, the formation interval of the recess  6 Ab in the direction of the axis O may be narrowed on the downstream side as compared with the upstream side. That is, on the downstream side, the recess  6 Ab may extend to follow the rotational direction RD. In this way, since the formation interval of the recess  6 Ab in the direction of the axis O is narrowed on the downstream side, the cooling fluid RF can be greatly accelerated in the rotational direction RD (circumferential direction) on the downstream side, and the heat transfer on the downstream side can be further improved. 
     Further, although the recess  6 Ab is formed in the partitioning member  6 A, instead of the recess  6 Ab, a spiral protrusion protruding radially inward from the inner surface  6 Aa may be formed. 
     Further, the partitioning member  6 A is not limited to a cylindrical shape, and may be a member divided into a plurality of pieces in the circumferential direction. That is, the partitioning member  6 A may be a member having an inner surface  6 Aa that is curved along the outer surface of the rotor  31 . 
     In addition, the recess  6 Ab may not be continuous in the direction of the axis O and may be discontinuously formed. 
     Fourth Embodiment 
     Next, a compressor system  161  of the fourth embodiment will be described with reference to  FIGS. 7 to 9 . 
     In the fourth embodiment, the same constituent elements as those of the third embodiment are denoted by the same reference numerals, and a detailed description thereof will not be provided. The compressor system  161  of the fourth embodiment is different from the compressor system  161  of the third embodiment in that a guide member (turn imparting portion)  66 A is provided instead of the partitioning member  6 A of the third embodiment. 
     As illustrated in  FIG. 7 , the guide member  66 A is disposed to be closer to the upstream side in the flowing direction of the cooling fluid RF than the inflow port IN of the cooling fluid RF in the gap  33  between the rotor  31  and the stator  32  (on one side in the direction of the axis O). Here, the inflow port IN represents a region on the upstream side of the opening (inlet) on the upstream side of the gap  33 . 
     As illustrated in  FIGS. 8 and 9 , since a plurality of guide members  66 A are fixed to the support member  10  to protrude inward in the radial direction from the support member  10  at an interval therebetween in the rotational direction RD, the plurality of guide members  66 A are provided to be relatively non-rotatable with respect to the stator  32 . 
     As illustrated in  FIG. 9 , each guide member  66 A is formed to be curved toward the front RD 1  in the rotational direction RD toward the downstream side in the flowing direction of the cooling fluid RF which is the other side in the direction of the axis O. Thus, the guide member  66 A has a guide surface  66 Aa that faces the upstream side and is curved and inclined toward the front RD 1  in the rotational direction RD with respect to the axis O toward the downstream side, and a rear surface  66 Ab which faces the downstream side and is curved and inclined toward the front RD 1  in the rotational direction RD with respect to the axis O toward the downstream side. Among the guide members  66 A adjacent to each other in the rotational direction RD, the guide surface  66 Aa of one guide member  66 A and the rear surface  66 Ab of the other guide member  66 A face each other in the rotational direction RD (circumferential direction). 
     Further, in the present embodiment, the guide member  66 A is formed into a blade shape in a cross-section orthogonal to the radial direction with the guide surface  66 Aa and the rear surface  66 Ab. 
     Here, an upstream end portion of the guide member  66 A is set as a leading edge  66 Ac, and a downstream end portion is set as a trailing edge  66 Ad. In the present embodiment, the dimension of the gap S 2  in the rotational direction RD (circumferential direction) between the trailing edges  66 Ad of the guide member  66 A is smaller than the gap S 1  in the rotational direction RD (circumferential direction) between the leading edges  66 Ac of the guide member  66 A adjacent to each other in the rotational direction RD. 
     According to the compressor system  161  of the present embodiment described above, by providing the guide member  66 A having the guide surface  66 Aa, it is possible to guide the cooling fluid RF by the guide surface  66 Aa. As a result, a turning component directed to the front RD 1  in the rotational direction RD toward the downstream side is imparted to the cooling fluid RF. 
     It is possible to make the flowing direction of the cooling fluid RF follow the advancing direction of the outer surface of the rotating rotor  31 . Therefore, it is possible to suppress the amount of heat generated by shearing caused by rapid acceleration of the cooling fluid RF due to the contact of the cooling fluid RF with the outer surface of the rotor  31 . As a result, the cooling efficiency of the rotor  31  can be improved, and the motor  3  can be efficiently cooled. 
     Further, the gap between the trailing edges  66 Ad is smaller than the gap between the leading edges  66 Ac of the guide member  66 A. Therefore, when the cooling fluid RF guided by the guide surface  66 Aa flows out from the space between the trailing edges  66 Ad of the guide member  66 A toward the gap  33  formed between the rotor  31  and the stator  32 , the flow velocity can be enhanced compared to the case in which the flow cooling fluid RF flows into the space between the leading edges  66 Ac of the member  66 A. 
     That is, the flow passage area of the cooling fluid RF can be reduced on the trailing edge  66 Ad side. Therefore, the cooling fluid RF can be accelerated in the rotational direction RD, the cooling fluid RF can be accelerated in the rotational direction RD on the downstream side, and the heat transfer on the downstream side can be improved. Therefore, it is possible to sufficiently cool the rotor  31  even at the downstream side with the cooling air RF increased in temperature by performing heat exchange with the rotor  31  on the upstream side, and the cooling efficiency of the rotor  31  can be further improved. 
     Here, in the present embodiment, a member having a blade shape in the cross-section is provided as the guide member  66 A, but the present invention is not limited thereto. That is, the guide member  66 A may have a simple flat plate shape having a rectangular cross-section. The guide surface  66 Aa is not limited to being formed in a curved shape, but the guide surface  66 Aa may have a planar shape that faces the upstream side and is inclined to the front side in the rotational direction RD with respect to the axis O toward the downstream side. The same also applies to the rear surface  66 Ab. 
     The gap S 1  between the leading edges  66 Ac and the gap S 2  between the trailing edges  66 Ad may have the same dimensions. 
     Further, the guide member  66 A is not limited to being provided at the inflow port IN, but may be disposed, for example, in the gap  33  between the rotor  31  and the stator  32 . In this case, for example, a cylindrical member similar to the partitioning member  6 A of the third embodiment may be provided, and the guide member  66 A may be provided on the inner surface of the cylindrical member facing the rotor  31  side. 
     Although the third and fourth embodiments of the present invention have been described in detail with reference to the drawings, the respective configurations and combinations thereof in the respective embodiments are merely examples, and additions, omissions, substitutions, and other changes to the configuration can be made within the scope that does not depart from the gist of the present invention. Further, the present invention is not limited by the embodiments, and is limited only by the claims. 
     For example, the partitioning member  6 A of the third embodiment and the guide member  66 A of the fourth embodiment may be used in combination. 
     Further, the cooling fluid RF may be circulated between the stator  32  and the partitioning member  6 A. 
     Fifth Embodiment 
     Hereinafter, a fifth embodiment of the present invention will be described with reference to  FIG. 10 . 
     A partitioning member  6 B is disposed in an annular gap  33  between the rotor  31  and the stator  32 , and is provided in a state in which it does not come into contact with the rotor  31  and the stator  32 . Specifically, the partitioning member  6 B is fixed to the casing  5  to be relatively non-rotatable with respect to the stator  32 . For example, the support member  10  is provided on the casing  5  to protrude radially inward at both sides of the stator  32  in the direction of the axis O, and the partitioning member  6 B is fixed to the support member  10 . The support member  10  may have an annular shape with the axis O as the center or may have a columnar shape protruding inward in the radial direction at a part in the circumferential direction, and its shape is not limited. 
     More specifically, as illustrated in  FIG. 11 , the partitioning member  6 B extends to protrude radially inward from the support member  10  to partition the gap  33  into a plurality of spaces R in the circumferential direction, and has a flat plate shape which extends in the gap  33  over the entire region in the direction of the axis O. Further, in the present embodiment, the partitioning members  6 B are provided at two positions separated by 180 degrees in the circumferential direction. As a result, the gap  33  is partitioned into two spaces R 1  and R 2 . 
     Various materials such as metals, ceramics, and organic materials such as resins can be used for the partitioning member  6 B. 
     Here, in the gap  33  between the rotor  31  and the stator  32 , the cooling fluid RF can flow in the direction of the axis O. As the cooling fluid RF, for example, a leaked flow in which a part of the compressed fluid CF from the compressor  2  has leaked from the seal member  51 , a cooling medium introduced from the outside of the casing  5 , or bleed air from the compressor  2  can be used. 
     The fluid introduction section  7  allows the cooling fluid RF to flow in from the different sides in the direction of the axis O for the space R 1  and the space R 2 . That is, the cooling fluid RF flows into the space R 1  from the compressor  2  side, which is one side in the direction of the axis O, and the cooling fluid RF flows into the space R 2  from the other side in the direction of the axis O. 
     More specifically, as illustrated in  FIG. 12 , the fluid introduction section  7  is, for example, a manifold provided integrally with the support member  10 . That is, the fluid introduction section  7  has a semicircular curved flow passage section  8  which covers an opening (inflow port R 1   a ) on one side of the space R 1  in the direction of the axis O, and a protruding flow passage section  9  which protrudes outward in the radial direction from the intermediate position (dead center in the circumferential direction) of the curved flow passage section  8 . 
     The curved flow passage section  8  is formed with a curved flow passage  8   a  which opens over substantially the entire circumferential direction of the surface facing the inflow port R 1   a.    
     A protruding flow passage  9   a  is formed in the protruding flow passage section  9  to communicate with the curved flow passage section  8  and opens radially outward. 
     The cooling fluid RF is introduced into the protruding flow passage  9   a  so that the cooling fluid RF can flow into the space R 1  from the inflow port R 1   a  through the curved flow passage  8   a.    
     Here, in the present embodiment, on the other side of the partitioning member  6 B in the direction of the axis O, a fluid outflow section  7 A having the same shape as the fluid introduction section  7  which has a curved flow passage section  8  which covers an opening (outflow port R 1   b ) on the other side of the space R 1  in the direction of the axis O, and a protruding flow passage section  9  which protrudes outward in the radial direction from the intermediate position (dead center in the circumferential direction) of the curved flow passage section  8  is provided. The cooling fluid RF that has flowed through the space R 1  can flow out of the protruding flow passage section  9  through the fluid outflow section  7 A. 
     Likewise, the fluid introduction section  7  is provided to cover the inflow port R 2   a  which is an opening on the other side of the space R 2  in the direction of the axis O, and a fluid outflow section  7 A is provided to cover an outflow port R 2   b  which is an opening on one side of the space R 2  in the direction of the axis O. 
     According to the compressor system  201  of the present embodiment described above, the cooling fluid RF flows into each of the spaces R 1  and R 2  formed by partitioning the gap  33  between the rotor  31  and the stator  32  in the circumferential direction by the partitioning member  6 B from different sides in the direction of the axis O. Therefore, the cooling fluid RF flows through the spaces R 1  and R 2  in opposite directions from each other. 
     Here, since the cooling fluid RF flows through the gap  33  while exchanging heat with the rotor  31 , the temperature of the cooling fluid RF on the downstream side in each of the spaces R 1  and R 2  is higher than the temperature on the upstream side. However, in the present embodiment, the flowing direction of the cooling fluid RF is in the opposite direction between the plurality of spaces R 1  and R 2  aligned in the circumferential direction, and the rotor  31  relatively rotates with respect to the plurality of spaces R 1  and R 2 . 
     For this reason, on the downstream side of the spaces R 1  and R 2 , the cooling fluid RF having the high temperature and the cooling fluid RF having the low temperature alternately come into contact with the outer surface of the rotor  31 . Therefore, even when the cooling fluid RF reaches a high temperature on the downstream side of the spaces R 1  and R 2 , it is possible to prevent the cooling fluid RF having the high temperature from always coming into contact with the rotor  31  at the same position. Therefore, the rotor  31  can be efficiently cooled throughout the direction of the axis O, and the motor  3  can be efficiently cooled. 
     Sixth Embodiment 
     Next, a compressor system  261  of a sixth embodiment will be described with reference to  FIG. 13 . 
     In the sixth embodiment, the same constituent elements as those of the first embodiment are denoted by the same reference numerals, and a detailed description thereof will not be provided. The compressor system  261  of the sixth embodiment is different from the first embodiment in the partitioning member  66 B. 
     As illustrated in  FIG. 13 , the partitioning member  66 B is provided to be inclined with respect to the axis O. More specifically, the partitioning member  66 B has a flat plate shape, and the end surface facing the inflow port R 1   a  (R 2   a ) side extends in the radial direction, and also extends toward the one side RD 1  of the rotational direction RD of the rotor  31  in the circumferential direction toward the downstream side in the flowing direction of the cooling fluid RF. That is, the partitioning member  66 B has a guide surface  66 Ba that faces the upstream side in the flowing direction of the cooling fluid RF and inclines toward the front side RD 1  in the rotational direction RD of the rotor  31  with respect to the axis O toward the downstream side. 
     In the compressor system  261  according to the present embodiment described above, by guiding the cooling fluid RF in the spaces R 1  and R 2  with the guide surface  66 Ba of the partitioning member  66 B, a turning component directed toward the front RD 1  in the rotational direction RD toward the downstream side is imparted to the cooling fluid RF. Therefore, the cooling fluid RF can be made to flow in the flowing direction of the cooling fluid RF in the advancing direction of the outer surface of the rotating rotor  31 . Therefore, it is possible to suppress the amount of heat generated by shearing caused by rapid acceleration of the cooling fluid RF due to the contact between the cooling fluid RF and the outer surface of the rotor  31 , and the cooling efficiency of the rotor  31  can be improved. 
     As illustrated in  FIG. 14 , in the compressor system  261  of the present embodiment, the partitioning member  66 B 1  may be, for example, a member having a spiral plate shape which extends toward the front RD 1  in the rotational direction RD of the rotor  31  toward the downstream side in the flowing direction of the cooling fluid RF. Even with such a spiral member, it is possible to effectively impart a turning component, which is directed to the front RD 1  in the rotational direction RD toward the downstream side, to the cooling fluid RF. Further, it is possible to suppress the amount of heat generated by shearing caused when the cooling fluid RF is rapidly accelerated, and the cooling efficiency of the rotor  31  can be improved. 
     Although the fifth embodiment and the sixth embodiment of the present invention have been described in detail with reference to the drawings, the respective configurations and combinations thereof in the respective embodiments are merely examples, and additions, omissions, substitutions, and other changes to the configuration can be made within the scope that does not depart from the gist of the present invention. Further, the present invention is not limited by the embodiments, and is limited only by the claims. 
     For example, the partitioning members  6 B,  66 B, and  66 B 1  may be disposed at least in a region in which the rotor  31  and the stator  32  face in the radial direction. Further, the partitioning members  6 B,  66 B, and  66 B 1  may be directly fixed to the stator  32 . 
     Further, by using a metal material having high thermal conductivity for the partitioning members  6 B,  66 B, and  66 B 1 , heat exchange between the space R 1  and the space R 2  may be promoted and the cooling of the rotor  31  may be made uniform. 
     Further, the number of the partitioning members  6 B,  66 B, and  66 B 1  is not limited to the above-described case, and at least two or more of them may be provided. Further, they may be provided at irregular intervals in the circumferential direction. When three or more partitioning members  6 B,  66 B, and  66 B 1  are provided, the flowing direction of the cooling fluid RF may be different between the spaces R adjacent to each other in the circumferential direction, but the present invention is not limited thereto. That is, the flowing direction of the cooling fluid RF may be different in at least two spaces. 
     Further, for example, by increasing the wall thickness of the partitioning member  6  B ( 66 B and  66 B 1 ) toward the downstream side, it is possible to reduce the cross-sectional area of the flow passage in the cross-section orthogonal to the axis O of the spaces R 1  and R 2  from the upstream side to the downstream side. In this case, since the flow rate of the cooling fluid RF can be increased on the downstream side, heat transfer between the cooling fluid RF and the rotor  31  can be promoted even by the cooling fluid RF having the higher temperature by performing the heat exchange, and it is possible to effectively perform heat exchange with the rotor  31 . 
     Seventh Embodiment 
     Hereinafter, a seventh embodiment of the present invention will be described with reference to  FIG. 15 . 
     A compressor system  301  includes a fluid supply member  6 C disposed on the outer circumferential side of the rotor  31 , instead of the partitioning member  6  ( 6 A,  66 A,  6 B,  66 B, and  66 B 1 ). 
     The fluid supply member  6 C is disposed in an annular gap  33  between the rotor  31  and the stator  32 , and is provided in a state in which it does not come into contact with the rotor  31  and the stator  32 . Specifically, the fluid supply member  6 C has a cylindrical shape with the axis O as the center. 
     Various materials such as metals, ceramics, and organic materials such as resins can be used for the fluid supply member  6 C. 
     The fluid supply member  6 C is fixed to the casing  5  so as not to be rotatable with respect to the stator  32 . For example, in the casing  5 , the support members  10  are provided at both end surfaces directed in the direction of the axis O of the stator  32  to protrude radially inward to face in the direction of the axis O, and the fluid supply member  6 C is fixed to the support member  10 . 
     The support member  10  may have an annular shape with the axis O as the center or may have a column shape protruding radially inward at a part in the circumferential direction, and its shape is not limited. 
     Further, in the fluid supply member  6 C, a plurality of ejection ports  6 Ca which open toward the rotor  31  and can eject the cooling fluid RF are formed at intervals in the direction of the axis O. 
     Further, as illustrated in  FIG. 16 , a plurality of ejection ports  6 Ca are formed at intervals in the circumferential direction. In the present embodiment, the ejection port  6 Ca is capable of ejecting the cooling fluid RF straight in the radial direction toward the inner side in the radial direction. 
     Further, when the fluid supply member  6 C is viewed from the radially inner side, the ejection ports  6 Ca may be disposed in a staggered pattern or may be disposed in a lattice pattern. 
     The fluid supply member  6 C communicates with a plurality of ejection ports  6 Ca aligned in the direction of the axis O so that the cooling fluid RF from the outside can flow along the axis O, and a communication hole  6 Cb extending in the direction of the axis O is further formed. The cooling fluid RF is supplied to the communication hole  6 Cb by, for example, a fluid supply flow passage (not illustrated) provided in the casing  5 , and the cooling fluid RF is further supplied to the ejection port  6 Ca via the communication hole  6 Cb. 
     As the cooling fluid RF, it is possible to use various fluids such as a leaked flow that is a part of the compressed fluid CF leaked from the seal member  51  to the motor  3  side, a cooling medium introduced from the outside, and bleed air from the compressor  2 . In the present embodiment, the cooling fluid RF flows into the communication hole  6 Cb from the compressor  2  side, which is one side in the direction of the axis O. 
     According to the compressor system  301  of the present embodiment described above, by separately providing the fluid supply member  6 C having the ejection port  6 Ca formed thereon, the low-temperature cooling fluid RF can always be supplied to the ejection port  6 Ca through the communication hole  6 Cb before the heat exchange with the rotor  31  from the outside of the casing  5 . Therefore, it is possible to always eject the low-temperature cooling fluid RF to the rotor from the ejection port  6 Ca. As a result, the cooling efficiency of the rotor  31  can be improved, and the motor can be efficiently cooled. 
     Furthermore, by supplying the cooling fluid RF to the plurality of ejection ports  6 Ca aligned in the direction of the axis O through the communication hole  6 Cb, it is possible to evenly eject the cooling fluid RF over the direction of the axis O with respect to the outer surface of the rotor  31 . Therefore, the cooling efficiency of the rotor  31  can be further improved. 
     Here, in the present embodiment, as illustrated in  FIG. 17 , the communication hole  6 Cb is not formed in the fluid supply member  6 C, and the ejection port  6 Ca may be formed so that the ejection port  6 Ca passes through the fluid supply member  6 C in the radial direction. In this case, by supplying the cooling fluid RF to the gap  33   a   1  formed between the stator  32  and the fluid supply member  6 C, the cooling fluid RF can be ejected from the ejection port  6 Ca toward the rotor  31 . 
     Further, in the present embodiment, as illustrated in  FIG. 18 , the ejection port  6 Ca located on the downstream side (the other side in the direction of the axis O) in the flowing direction of the cooling fluid RF flowing through the communication hole  6 Cb has an opening diameter larger than that of the ejection port  6 Ca located on the upstream side thereof. 
     Here, when the cooling fluid RF flows through the communication hole  6 Cb, the pressure loss increases toward the downstream side in the flowing direction. Since the opening diameter of the ejection port  6 Ca on the downstream side is larger, it is possible to eject the cooling fluid RF of a sufficient flow rate toward the rotor  31  even on the downstream side irrespective of such pressure loss. Therefore, the cooling efficiency of the rotor  31  can be further improved. 
     Further, in the present embodiment, as illustrated in  FIGS. 19 and 20 , more of the ejection ports  6 Ca ( FIG. 20 ) located on the downstream side in the flowing direction of the cooling fluid RF flowing through the communication hole  6 Cb may be formed in the circumferential direction than the ejection ports  6 Ca (see  FIG. 16 ) located on the upstream side. That is, the formation interval (pitch) in the circumferential direction may be narrower in the ejection port  6 Ca located on the downstream side than the ejection port  6 Ca of the upstream side. 
     By reducing the formation pitch of the ejection ports  6 Ca on the downstream side in this way, it is possible to eject the cooling fluid RF of a sufficient flow rate toward the rotor  31  even on the downstream side on which the pressure loss increases. Therefore, the cooling efficiency of the rotor  31  can be further improved. 
     Eighth Embodiment 
     Next, a compressor system  361  of an eighth embodiment will be described with reference to  FIG. 21 . 
     In the eighth embodiment, the same constituent elements as those in the seventh embodiment are denoted by the same reference numerals, and a detailed description thereof will not be provided. The compressor system  361  of the eighth embodiment is different from the seventh embodiment in the fluid supply member  66 C. 
     The plurality of ejection ports  66 Ca in the fluid supply member  66 C communicate with the communication holes  66 Cb and are formed to be able to eject the cooling fluid RF toward the front RD 1  side in the rotational direction RD of the rotor  31 . In other words, the ejection port  66 Ca is formed so that an extension line of the center axis O 2  of the ejection port  66 Ca passes through the rotor  31 . 
     Since the rotor  31  rotates in the rotational direction RD, by ejecting the cooling fluid RF ejected from the ejection port  66 Ca toward the front RD 1  in the rotational direction RD, it is possible to allow the flowing direction of the cooling fluid RF to follow the advancing direction of the outer surface of the rotating rotor  31 . As a result, it is possible to suppress the amount of heat generated by shearing caused by rapid acceleration of the cooling fluid RF due to the contact between the cooling fluid RF with the outer surface of the rotor  31 . Therefore, the cooling efficiency of the rotor  31  can be further improved. 
     Ninth Embodiment 
     Next, a compressor system  371  of the ninth embodiment will be described with reference to  FIG. 22 . 
     In the ninth embodiment, the same constituent elements as those in the seventh embodiment and the eighth embodiment are denoted by the same reference numerals, and a detailed description thereof will not be provided. In the compressor system  371  of the ninth embodiment, the fluid supply member  76  is different from those of the seventh embodiment and the eighth embodiment. 
     The fluid supply member  76  is provided by being divided into two parts in the direction of the axis O. That is, in the compressor system  371 , a first fluid supply member  76 A is provided on one side in the direction of the axis O, and a second fluid supply member  76 B is provided on the other side in the direction of the axis O. 
     The first fluid supply member  76 A and the second fluid supply member  76 B both have a cylindrical shape with the axis O as the center. The first fluid supply member  76 A and the second fluid supply member  76 B are both provided at a gap in the direction of the axis O and fixed to the casing  5  by the support member  10 . 
     In the first fluid supply member  76 A, the cooling fluid RF is supplied to the communication hole  76   b  from one side in the direction of the axis O. In the second fluid supply member  76 B, the cooling fluid RF is supplied to the communication hole  76   b  from the other side in the direction of the axis O. Further, the cooling fluid RF is ejected from the ejection port  76   a  toward the rotor  31 . 
     In the compressor system  371  of the present embodiment described above, it is possible to always supply the lower temperature cooling fluid RF to the communication hole  76   b  before performing heat exchange with the rotor  31 , and it is possible to always eject the cooling fluid RF from the ejection port  76   a . Accordingly, the cooling efficiency of the rotor  31  can be improved. As a result, the motor can be efficiently cooled. 
     In this embodiment, as illustrated in  FIG. 23 , at the intermediate position (for example, the center position of the fluid supply member  6 C in the direction of the axis O) of the communication hole  6 Cb of one fluid supply member  6 C similar to the seventh embodiment, a stopper  80  for blocking the communication hole  6 Cb may be provided, and the cooling fluid RF may be supplied to the communication hole  6 Cb from both sides in the direction of the axis O. Also in this case, it is possible to always supply the lower temperature cooling fluid RF to the ejection port  6 Ca before heat exchange with the rotor  31 , to eject the cooling fluid RF from the ejection port  6 Ca, and to improve the cooling efficiency of the rotor  31 . As a result, the motor can be efficiently cooled. 
     Although the seventh to ninth embodiments of the present invention have been described in detail with reference to the drawings, the respective configurations and combinations thereof in the respective embodiments are merely examples, and additions, omissions, substitutions, and other changes to the configuration can be made within the scope that does not depart from the gist of the present invention. Further, the present invention is not limited by the embodiments, and is limited only by the claims. 
     For example, the number of communication holes  6 Ca ( 66 Ca and  76   a ) is not particularly limited, and only one may be formed. 
     Further, since the amount of heat generated at the position at which the rotor  31  and the stator  32  face each other in the radial direction increases, the ejection ports  6 Ca ( 66 Ca and  76   a ) may be formed at least in the facing regions in which the rotor  31  and the stator  32  face in the radial direction. 
     The shape of the fluid supply member  6 C ( 66 C and  76 ) is not limited to the above-described case either. For example, the fluid supply member may be a flat plate-like member disposed in the gap  33 . 
     Also, the support member  10  is not limited to the above case. That is, the fluid supply member  6 C ( 66 C,  76 ) may be held in the gap  33  between the rotor  31  and the stator  32 . For example, the fluid supply member  6 C ( 66 C and  76 ) may be directly fixed to the stator  32 . 
     Further, each of the seventh embodiment to the ninth embodiment described above and each modified example can be appropriately combined. 
     Although the disclosure has been described with respect to only a limited number of embodiments, those skilled in the art, having benefit of this disclosure, will appreciate that various other embodiments may be devised without departing from the scope of the present invention. Accordingly, the scope of the invention should be limited only by the attached claims. 
     INDUSTRIAL APPLICABILITY 
     According to the above compressor system, it is possible to efficiently cool the motor. 
     REFERENCE SIGNS LIST 
     
         
         
           
               1  Compressor system 
               2  Compressor 
               3  Motor 
               4  Bearing unit 
               5  Casing 
               6  Partitioning member 
               6   a  Inner surface 
               6   b  Outer surface 
               10  Support member 
               21  Shaft 
               22  Impeller 
               23  Housing 
               31  Rotor 
               32  Stator 
               33  Gap 
               41  Journal bearing 
               42  Thrust bearing 
               51  Seal member 
             F Fluid 
             CF Compressed fluid 
             LF Leaked flow 
             C 1  Rotor-side flow passage 
             C 2  Stator-side flow passage 
             O Axis 
               61  Compressor system 
               66  Partitioning member 
               66   a  Inner surface 
               66   b  Outer surface 
               101 ,  161  Compressor system 
               6 A Partitioning member (turn imparting portion) 
               6 Aa Inner surface (front surface) 
               6 Ab Recess 
               33   a  Gap 
             RF Cooling fluid 
             RD Rotational direction 
             RD 1  Front 
             W Width 
               66 A Guide member (turn imparting portion) 
             IN Inflow port 
               66 Aa Guide surface 
               66 Ab Rear surface 
               66 Ac Leading edge 
               66 Ad Trailing edge 
             S 1 , S 2  Gap 
               201 ,  261  Compressor system 
               6 B,  66 B,  66 B 1  Partitioning member 
               7  Fluid introduction section 
               7 A Fluid outlet section 
               8  Curved flow passage section 
               8   a  Curved flow passage 
               9  Protruding flow passage section 
               9   a  Protruding flow passage 
               66 Ba Guide surface 
             CF Compressed fluid 
             R, R 1 , R 2  Space 
             R 1   a , R 2   a  Inflow port 
             R 1   b , R 2   b  Outflow port 
               301  Compressor system 
               6 C Fluid supply member 
               6 Ca Ejection port 
               6 Cb Communication hole 
               33   a   1  Gap 
               361  Compressor system 
               66 C Fluid supply member 
               66 Ca Ejection port 
               66 Cb Ejection port 
             O 2  Center axis 
               371  Compressor system 
               76  Fluid supply member 
               76   a  Ejection port 
               76   b  Communication hole 
               76 A First fluid supply member 
               76 B Second fluid supply member 
               80  Stopper