JP2017002750A - Centrifugal compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a centrifugal compressor which uses an oil to cool a radial bearing and an electric motor while inhibiting oil leakage.SOLUTION: A centrifugal compressor 10 includes: a rotary shaft 11; an electric motor 12 and an impeller 13 attached to the rotary shaft 11; and a housing 20 in which the electric motor 12 and the impeller 13 are housed. In the housing 20, a first bearing chamber A4 for housing a first radial bearing 54 rotatably supporting the rotary shaft 11 and a first oil passage 130 for supplying an oil O to the first bearing chamber A4 are formed. A first mechanical seal 102 is provided between the first radial bearing 54 and an impeller chamber A2, and a first seal member 103 which is more likely to leak the oil O than the first mechanical seal 102 is provided between the first radial bearing 54 and a motor chamber A1.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a centrifugal compressor.

  The centrifugal compressor is, for example, a rotation shaft, an electric motor that is attached to the rotation shaft and rotates the rotation shaft, and is attached to the rotation shaft, and compresses the fluid by rotating with the rotation of the rotation shaft. And a housing in which the electric motor and the impeller are accommodated (see, for example, Patent Document 1). Patent Document 1 describes a radial bearing that supports a rotating shaft. Patent Document 2 describes a turbocharger in which a mechanical seal is provided between a turbine wheel and a floating bush.

JP 2009-257165 A Japanese Patent No. 4367628

  Here, in a configuration in which both the impeller and the electric motor are attached to one rotating shaft without using a speed increaser, the rotation speed of the impeller and the rotation speed of the electric motor coincide with each other. In such a configuration, if the rotation speed of the impeller is increased to increase the flow rate of the fluid discharged from the centrifugal compressor, the heat generated by the radial bearing or the electric motor tends to increase. Then, the radial bearing and the electric motor generate excessive heat, and as a result, the operation of the centrifugal compressor may be hindered.

In contrast, the present inventors have focused on cooling the radial bearing using oil. In this case, there is a concern that the oil leaks to an unintended location.
This invention is made | formed in view of the situation mentioned above, The objective is to provide the centrifugal compressor which can cool a radial bearing and an electric motor using oil, suppressing oil leakage. .

  A centrifugal compressor that achieves the above object includes a rotating shaft, an electric motor that is attached to the rotating shaft and rotates the rotating shaft, and is attached to the rotating shaft and rotates with the rotation of the rotating shaft. An impeller that compresses fluid, a housing that houses the electric motor and the impeller, and a radial bearing that rotatably supports the rotating shaft, and the motor that houses the electric motor in the housing A partition wall having a through hole through which the rotating shaft is inserted while partitioning the motor chamber and the predetermined chamber, and an inner surface of the through hole and the rotating shaft. A bearing chamber formed between the outer peripheral surface and accommodating the radial bearing; and an oil passage for supplying oil to the bearing chamber; and the rotating shaft includes the motor chamber and the A mechanical seal is provided between the predetermined chamber in the through hole and the radial bearing, and the motor chamber and the radial bearing in the through hole are arranged between the predetermined chamber and the radial bearing. In the meantime, a seal member in which oil leaks more easily than the mechanical seal, or an opening for communicating the bearing chamber and the motor chamber is provided.

  According to this configuration, the inflow of oil from the bearing chamber to the predetermined chamber is regulated by the mechanical seal. Thereby, it can suppress that oil flows in into a predetermined chamber. On the other hand, between the radial bearing in the through hole and the motor chamber, there is provided a seal member or an opening that allows oil to leak more than the mechanical seal. As a result, part of the oil supplied from the oil flow path to the bearing chamber flows into the motor chamber. Therefore, the electric motor is cooled by oil. Therefore, it is possible to cool the radial bearing and the electric motor using oil while suppressing oil leakage to the predetermined chamber.

  In the centrifugal compressor, the predetermined component may be the impeller, and the predetermined chamber may be an impeller chamber that houses the impeller. According to such a configuration, it is possible to suppress inconvenience that the oil is mixed into the compressed fluid due to the oil flowing into the impeller chamber.

  In the centrifugal compressor, a thrust bearing that receives a thrust force generated by the rotation of the impeller is accommodated in the bearing chamber, and the thrust bearing is disposed between the mechanical seal and the radial bearing. The oil flow path is provided in a first supply flow path for supplying oil to a region closer to the impeller chamber than the thrust bearing in the bearing chamber, and to a region closer to the motor chamber than the thrust bearing in the bearing chamber. It is good to have the 2nd supply channel which supplies oil. According to such a configuration, oil can be supplied to both the radial bearing and the mechanical seal in the configuration in which the thrust bearing is provided in the bearing chamber. As a result, inconvenience due to the provision of the thrust bearing, in particular, the movement of oil between the region closer to the motor chamber than the thrust bearing and the region closer to the impeller chamber than the thrust bearing is regulated by the thrust bearing. Thus, it is possible to suppress oil exhaustion in either the radial bearing or the mechanical seal.

  The centrifugal compressor includes, as the predetermined component, a rotation angle sensor that is attached to the rotation shaft and detects a rotation angle of the electric motor, and the predetermined chamber is a sensor chamber that houses the rotation angle sensor. Good. According to such a configuration, it is possible to suppress inconvenience that an abnormality occurs in the detection result of the rotation angle sensor due to the oil flowing into the sensor chamber.

  In the centrifugal compressor, the seal member may be a seal ring or a labyrinth seal. According to such a configuration, the seal ring and the labyrinth seal are likely to have a relatively simple configuration as compared with the mechanical seal. Further, since a gap is formed in the seal ring due to its structure, oil leaks from the gap to the motor chamber. Since the labyrinth seal has a non-contact seal structure, a gap through which oil leaks is formed. As a result, the effects described above can be achieved while suppressing the complexity of the configuration.

  According to the present invention, the radial bearing and the electric motor can be cooled using oil while suppressing oil leakage.

Sectional drawing which shows the outline | summary of the centrifugal compressor of 1st Embodiment typically. Sectional drawing which expands and shows the 1st oil flow path periphery. Sectional drawing which expands and shows the 1st bearing chamber periphery. Sectional drawing which expands and shows the 2nd oil flow path periphery. Sectional drawing which expands and shows the 2nd bearing chamber periphery. Sectional drawing which shows the outline | summary of the centrifugal compressor of 2nd Embodiment typically. Sectional drawing which expands and shows the 2nd oil flow path periphery. Sectional drawing which shows the 1st bearing chamber of another example.

(First embodiment)
Hereinafter, a first embodiment of the centrifugal compressor will be described. The centrifugal compressor of this embodiment is mounted on, for example, a fuel cell vehicle (FCV) on which a fuel cell is mounted, and is used in an air supply device that supplies air to the fuel cell.

  As shown in FIG. 1, the centrifugal compressor 10 is attached to a rotating shaft 11, an electric motor 12 that is attached to the rotating shaft 11, and rotates to the rotating shaft 11, and is attached to the rotating shaft 11. And an impeller 13 that compresses fluid (air in the present embodiment) by rotating. In the present embodiment, the centrifugal compressor 10 includes a resolver 14 as a rotation angle sensor that detects the rotation angle of the electric motor 12.

  The centrifugal compressor 10 constitutes the outline of the centrifugal compressor 10 and includes a housing 20 in which a rotating shaft 11, an electric motor 12, an impeller 13, and a resolver 14 are accommodated. The housing 20 as a whole has a substantially cylindrical shape (specifically, a substantially cylindrical shape).

  The housing 20 includes a motor housing 21 in which the electric motor 12 is accommodated, a compressor housing 22 in which a suction port 20a through which fluid is sucked is formed, and a resolver housing 23 in which the resolver 14 is accommodated. The suction port 20 a is provided on one end surface 20 b in the axial direction of the housing 20. The compressor housing 22, the motor housing 21, and the resolver housing 23 are arranged in this order in the axial direction of the housing 20 when viewed from the suction port 20a. The housing 20 includes two plates 25 and 26 provided between the compressor housing 22 and the motor housing 21.

  Incidentally, in this embodiment, the centrifugal compressor 10 is mounted on the vehicle in a state where the axial direction of the housing 20 and the horizontal direction coincide with each other. Further, the rotating shaft 11 is accommodated in the housing 20 in a state where the axial direction of the rotating shaft 11 and the axial direction of the housing 20 coincide with each other. 1 corresponds to the vertical direction.

  The motor housing 21 has a cylindrical shape (in detail, a cylindrical shape) that is open on both sides in the axial direction as a whole. Specifically, the motor housing 21 includes a cylindrical side wall portion 21 a and openings 21 b and 21 c disposed on both sides of the motor housing 21 in the axial direction.

  The housing 20 includes a water jacket 24 that covers the motor housing 21. The water jacket 24 has a bottomed cylindrical shape as a whole, and has a jacket bottom 24 a that closes the first opening 21 b disposed on the resolver housing 23 side of the motor housing 21, and a side wall 21 a of the motor housing 21. And a jacket side wall portion 24b covering from the outside in the direction. The water jacket 24 is unitized with the motor housing 21 and the resolver housing 23 in a state where the jacket bottom 24 a is sandwiched between the motor housing 21 and the resolver housing 23. In this case, the first bottom surface 24aa on the motor housing 21 side of the jacket bottom 24a is in contact with the first end surface 21d on the first opening 21b side of both end surfaces 21d and 21e in the axial direction of the motor housing 21. The second bottom surface 24ab of the jacket bottom 24a opposite to the first bottom surface 24aa is in contact with the surface 23a of the resolver housing 23 on the motor housing 21 side. In addition, the surface 23b opposite to the surface 23a of the resolver housing 23 constitutes the other end surface 20c opposite to the one end surface 20b where the suction port 20a is located among the both end surfaces 20b and 20c in the axial direction of the housing 20. .

  As shown in FIG. 1, a refrigerant recess 31 that is recessed radially inward from the outer peripheral surface of the side wall 21 a is formed in the side wall 21 a of the motor housing 21. The refrigerant recess 31 is formed over the entire circumference of the side wall 21a. A gap 32 through which the coolant flows is formed by the coolant recess 31 and the side wall 21 a of the motor housing 21. When the refrigerant (for example, water) flows through the gap 32, the motor housing 21 can be cooled.

  In addition, fins 33 are provided in the coolant recess 31. The fin 33 stands up radially outward from the bottom surface of the refrigerant recess 31. The fins 33 extend in the circumferential direction of the motor housing 21, and are formed over the entire circumference of the side wall portion 21 a of the motor housing 21 in this embodiment. A plurality of fins 33 are provided side by side in the axial direction of the motor housing 21. The contact area between the motor housing 21 and the refrigerant is improved by the fins 33.

  Both plates 25, 26 disposed between the compressor housing 22 and the motor housing 21 have a disk shape having an outer diameter that is slightly larger than that of the motor housing 21. Both plates 25 and 26 are arranged such that the plate thickness direction thereof coincides with the axial direction of the housing 20.

  As shown in FIGS. 1 and 2, the motor side plate 25 disposed on the motor housing 21 side of both the plates 25 and 26 includes a first motor side plate plate surface 25 a orthogonal to the rotation shaft 11, and a first side. It has the 2nd motor side plate board surface 25b arrange | positioned on the opposite side to the motor side plate board surface 25a. The first motor side plate plate surface 25 a is in contact with the second end surface 21 e on the second opening 21 c side of both end surfaces 21 d and 21 e in the axial direction of the motor housing 21. The second opening 21 c of the motor housing 21 is closed by the motor side plate 25. The motor housing 21 that houses the electric motor 12 is partitioned by the motor housing 21, the water jacket 24, and the motor side plate 25.

  Of the two plates 25, 26, the compressor side plate 26 disposed on the compressor housing 22 side includes a first compressor side plate plate surface 26a in contact with the second motor side plate plate surface 25b, and a first compressor side plate. It has the 2nd comp side plate board surface 26b arrange | positioned on the opposite side to the board surface 26a.

  As shown in FIG. 2, the first comp side plate plate surface 26a is formed with a recess 41 recessed from the first comp side plate plate surface 26a, and the second motor side plate is correspondingly formed. On the plate surface 25b, a convex portion 42 protruding from the second motor side plate plate surface 25b is formed. Both plates 25 and 26 are assembled in a state in which the convex portion 42 is fitted into the concave portion 41.

  As shown in FIGS. 1 to 3, the motor-side plate 25 penetrates in the plate thickness direction together with the first boss 51 erected from the first motor-side plate plate surface 25 a toward the jacket bottom 24 a and the first boss 51. The motor side plate through hole 52 is formed. Since the motor side plate through hole 52 is formed, the first boss 51 has a cylindrical shape as a whole.

  Further, the comp side plate 26 is formed with a comp side plate through hole 53 penetrating in the thickness direction. The motor side plate through hole 52 and the comp side plate through hole 53 communicate with each other in the axial direction of the rotary shaft 11. Both plate through-holes 52 and 53 are formed larger than the rotating shaft 11. The rotating shaft 11 is inserted through both plate through holes 52 and 53. A part of the rotating shaft 11 is disposed in the compressor housing 22 through both plate through holes 52 and 53. Between the outer peripheral surface 11a of the rotating shaft 11 and the inner surface 52a of the motor side plate through-hole 52, the 1st radial bearing 54 which supports the rotating shaft 11 rotatably is provided.

  As shown in FIG. 1, the jacket bottom 24 a is formed with a second boss 55 erected from the first bottom surface 24 aa of the jacket bottom 24 a toward the motor side plate 25. The second boss 55 is provided at a position facing the first boss 51 in the axial direction of the rotary shaft 11. A jacket through hole 56 that penetrates the second boss 55 in the thickness direction is formed in the jacket bottom 24a. The jacket through hole 56 is formed larger than the rotation shaft 11. Since the jacket through-hole 56 is formed, the second boss 55 has a cylindrical shape as a whole.

  The rotating shaft 11 is inserted through the jacket through hole 56. And between the outer peripheral surface 11a of the rotating shaft 11, and the inner surface 56a of the jacket through-hole 56, the 2nd radial bearing 57 which supports the rotating shaft 11 rotatably is provided. The rotary shaft 11 is supported by the housing 20 in a rotatable state by both radial bearings 54 and 57.

Incidentally, both radial bearings 54 and 57 of this embodiment are contact types, for example, a rolling bearing such as a ball bearing or a sliding bearing.
As shown in FIG.1 and FIG.2, the compressor housing 22 is a substantially cylindrical shape which has the compressor through-hole 61 penetrated to the axial direction. One end surface 22a in the axial direction of the compressor housing 22 constitutes one end surface 20b in the axial direction of the housing 20, and an opening on the one end surface 22a side in the compressor through hole 61 functions as the suction port 20a.

  As shown in FIG. 2, the compressor housing 22 and the compressor side plate 26 are composed of the other end surface 22 b opposite to the one end surface 22 a in the axial direction of the compressor housing 22, and the second compressor side plate plate surface of the compressor side plate 26. It is assembled in a state where it is in contact with 26b. In this case, an impeller chamber A <b> 2 that accommodates the impeller 13 is formed by the inner surface of the comp through hole 61 and the second comp side plate surface 26 b of the comp side plate 26. That is, the comp through hole 61 functions as the suction port 20a and functions as a partition for the impeller chamber A2. The suction port 20a and the impeller chamber A2 communicate with each other.

  Here, the compressor through-hole 61 has a constant diameter from the suction port 20a to the midway position in the axial direction, and has a substantially truncated cone shape that gradually increases in diameter from the midway position toward the second comp side plate plate surface 26b. It has become. For this reason, the impeller chamber A2 has a substantially truncated cone shape.

  The impeller 13 has a cylindrical shape with a diameter gradually reduced from the base end surface 13a toward the front end surface 13b. The impeller 13 has an insertion hole 13c that extends in the rotation axis direction of the impeller 13 and through which the rotation shaft 11 can be inserted. The impeller 13 is attached to the rotary shaft 11 so as to rotate integrally with the rotary shaft 11 in a state where a portion of the rotary shaft 11 protruding into the comp through hole 61 is inserted into the insertion hole 13c. Thereby, the impeller 13 is rotated by the rotation of the rotating shaft 11, and the fluid sucked from the suction port 20a is compressed.

  The centrifugal compressor 10 also includes a diffuser channel 62 into which the fluid compressed by the impeller 13 flows and a discharge chamber 63 into which the fluid that has passed through the diffuser channel 62 flows. The diffuser flow path 62 is continuous with the opening end of the compressor through hole 61 on the second compressor side plate plate surface 26b side of the compressor through hole 61 and faces the second compressor side plate plate surface 26b, and the second compressor side. The flow path is defined by the plate plate surface 26b. The diffuser flow path 62 is disposed on the radially outer side of the rotating shaft 11 with respect to the impeller chamber A2, and is formed in an annular shape (specifically, an annular shape) so as to surround the impeller 13 (and the impeller chamber A2). The discharge chamber 63 has an annular shape that is disposed on the radially outer side of the rotating shaft 11 with respect to the diffuser flow path 62. The impeller chamber A2 and the discharge chamber 63 communicate with each other through a diffuser channel 62. The fluid compressed by the impeller 13 is further compressed by passing through the diffuser flow path 62, flows into the discharge chamber 63, and is discharged from the discharge chamber 63.

  As shown in FIG. 1, the electric motor 12 housed in the motor chamber A <b> 1 is a rotor 71 fixed to the rotating shaft 11, and is disposed radially outside the rotating shaft 11 with respect to the rotor 71. And a stator 72 fixed to the inner peripheral surface of the side wall 21a of the motor housing 21. The rotation axis of the rotor 71 and the center axis of the stator 72 are arranged on the same axis as the rotation axis of the rotation shaft 11. The rotor 71 and the stator 72 are opposed to each other in the radial direction of the rotating shaft 11.

  The stator 72 includes a cylindrical stator core 73 and a coil 74 wound around the stator core 73. When the current flows through the coil 74, the rotor 71 and the rotating shaft 11 rotate integrally.

  Although illustration is omitted, the side wall portion 21a of the motor housing 21 is provided with a wiring hole through which a wiring for electrically connecting the coil 74 and an inverter that supplies current to the coil 74 is inserted. The inverter may be integrated with the centrifugal compressor 10 or may be a separate body.

  As shown in FIG. 1, the resolver housing 23 has a substantially cylindrical shape having a resolver through hole 81 that penetrates in the axial direction of the rotating shaft 11. The resolver through hole 81 is formed larger than the rotation shaft 11. A part of the rotating shaft 11 passes through the jacket through hole 56 and enters the resolver through hole 81.

  Incidentally, in the present embodiment, the centrifugal compressor 10 includes a cover member 82 that closes one opening in the resolver through hole 81. As shown in FIGS. 4 and 5, the inner surface 81 a of the resolver through hole 81 is formed with an annular wall portion 83 that protrudes radially inward of the rotary shaft 11 from the inner surface 81 a. The projecting dimension of the annular wall portion 83 is set so that the tip of the annular wall portion 83 does not contact the rotating shaft 11. The annular wall portion 83 is provided at an intermediate position in the axial direction of the rotary shaft 11 in the resolver through hole 81.

  A region defined by the inner surface 81 a of the resolver through hole 81 and the outer peripheral surface 11 a of the rotating shaft 11 is divided into two by an annular wall portion 83. That is, it can be said that the resolver through-hole 81 is composed of two parts through-holes 91 and 92 that communicate with each other with the annular wall 83 as a boundary. Specifically, the resolver through-hole 81 is disposed on the side opposite to the motor chamber A1 side of the first part through-hole 91 disposed on the motor chamber A1 side from the annular wall portion 83 and the annular wall portion 83. The second part through hole 92 is formed.

  The resolver 14 is disposed in the resolver through hole 81. Specifically, the resolver 14 includes an outer peripheral surface 11a of the rotating shaft 11, an inner surface 81a of the resolver through hole 81 (more specifically, an inner surface 92a of the second part through hole 92), an annular wall portion 83, and a cover member. 82 is arranged in the sensor chamber A3 partitioned by the reference numeral 82.

  The resolver 14 includes a resolver rotor 14a fixed to the rotating shaft 11 and a resolver stator 14b fixed to the inner surface 92a of the second part through hole 92. In other words, the electrical angle of the rotor 71 (in other words, the rotor 71). And a relative angle between the stator 72 and the stator 72). The specific configuration of the resolver 14 is arbitrary.

  As already described, in the centrifugal compressor 10 of the present embodiment, the impeller 13 and the electric motor 12 are directly connected without using a speed increaser. Specifically, an impeller 13 and an electric motor 12 are attached to one rotating shaft 11. For this reason, the rotation speed of the impeller 13 and the rotation speed of the rotating shaft 11 correspond.

  Here, the flow rate of the compressed fluid discharged from the centrifugal compressor 10 depends on the rotational speed of the impeller 13. Further, the required value of the flow rate of the compressed fluid is changed according to the traveling state of the fuel cell vehicle. In this case, depending on the required flow rate of the compressed fluid, it may be necessary to rotate the impeller 13 at a very high rotational speed. When the impeller 13 rotates at a high speed, excessive heat may be generated in the radial bearings 54 and 57. Further, in order to rotate the impeller 13 at a high speed, it is necessary to rotate the rotor 71 at a high speed, so that the electric motor 12 easily generates heat. In this case, the operation of the centrifugal compressor 10 may be hindered.

  On the other hand, the centrifugal compressor 10 of the present embodiment includes the water jacket 24 that cools the motor housing 21, but cooling by the water jacket 24 may be insufficient.

  On the other hand, the centrifugal compressor 10 of the present embodiment has a configuration for supplying the oil O to the radial bearings 54 and 57 and cooling the electric motor 12 using the oil O. The configuration will be described together with the detailed configuration around the radial bearings 54 and 57.

First, the configuration around the first radial bearing 54 will be described.
As shown in FIGS. 2 and 3, the impeller chamber A <b> 2 and the motor chamber A <b> 1 are partitioned by both plates 25 and 26. As described above, the rotating shaft 11 passes through (inserts) the plate through holes 52 and 53 formed in the plates 25 and 26 and communicates with each other, and is provided in both the impeller chamber A2 and the motor chamber A1. It is arranged across. Both plates 25 and 26 correspond to “partition wall portions”.

  For convenience of explanation, both plate through holes 52 and 53 are simply referred to as first through holes 101 in the following explanation. The first through-hole 101 is composed of both plate through-holes 52 and 53 communicating with each other. The first through hole 101 corresponds to “a through hole through which the rotation shaft is inserted”.

  The motor side plate through hole 52 includes a first diameter-expanded portion 52b and a first diameter-reduced portion 52c that are different in size. The first enlarged diameter portion 52b is arranged closer to the impeller chamber A2 than the first reduced diameter portion 52c, and the first reduced diameter portion 52c is arranged closer to the motor chamber A1 than the first enlarged diameter portion 52b. Yes. The first radial bearing 54 is disposed between the inner surface of the first reduced diameter portion 52 c and the outer peripheral surface 11 a of the rotating shaft 11. A first step surface 52d is formed on the inner surface 52a of the motor side plate through hole 52 due to the difference in size between the first enlarged diameter portion 52b and the first reduced diameter portion 52c. The first step surface 52 d is a plane orthogonal to the axial direction of the rotation shaft 11.

  The comp side plate through-hole 53 includes a second enlarged diameter portion 53b and a second reduced diameter portion 53c having different sizes. The second enlarged diameter portion 53b is disposed closer to the motor chamber A1 than the second reduced diameter portion 53c, and communicates with the first enlarged diameter portion 52b. The second reduced diameter portion 53c is disposed closer to the impeller chamber A2 than the second enlarged diameter portion 53b. Due to the difference in size between the second enlarged diameter portion 53 b and the second reduced diameter portion 53 c, a second step surface 53 d is formed on the inner surface 53 a of the comp-side plate through hole 53. The second step surface 53 d is a plane orthogonal to the axial direction of the rotating shaft 11. In addition, the 1st enlarged diameter part 52b is formed larger than the 2nd enlarged diameter part 53b.

  As shown in FIGS. 2 and 3, a first seal member is provided between the impeller chamber A <b> 2 and the first radial bearing 54 in the first through hole 101 as a seal member that regulates the movement of fluid (specifically, oil O). A mechanical seal 102 is provided. The first mechanical seal 102 is disposed on the side opposite to the motor chamber A <b> 1 side with respect to the first radial bearing 54, specifically, on the impeller chamber A <b> 2 side with respect to the first radial bearing 54. 11 a and the inner surface 53 a of the comp-side plate through-hole 53.

  As shown in FIG. 3, the first mechanical seal 102 slides on the rotary ring 111 fixed to the rotary shaft 11 and is fixed so as not to rotate as the rotary shaft 11 rotates. The fixed ring 112 is provided.

The rotating ring 111 has a flat ring shape and is disposed in the second enlarged diameter portion 53b. The rotating ring 111 rotates as the rotating shaft 11 rotates.
The fixed ring 112 has a ring shape that is slightly larger than the rotating shaft 11. The stationary ring 112 is disposed on the impeller chamber A2 side with respect to the rotating ring 111, and is specifically disposed in the second reduced diameter portion 53c. The end surface 111a of the rotating ring 111 on the fixed ring 112 side and the end surface 112a of the fixed ring 112 on the rotating ring 111 side are in contact with each other.

  The first mechanical seal 102 includes a spring 113 as a pressing portion that presses the fixed ring 112 toward the rotating ring 111, a spring holding portion 114 that holds the spring 113, and the spring 113 and the spring holding portion 114 together with the fixed ring 112. And a cartridge 115 that holds the stationary ring 112 in a covered state.

  The cartridge 115 is provided with an insertion hole 115a formed slightly larger than the rotation shaft 11, and is fixed to the second step surface 53d in a state where the rotation shaft 11 is inserted into the insertion hole 115a. Further, the cartridge 115 has a cartridge bottom portion 115 b, an inner ring 115 c and an outer ring 115 d erected from the cartridge bottom portion 115 b toward the rotating ring 111, and opens toward the rotating ring 111.

  The fixed ring 112 is disposed in an area partitioned by the cartridge 115. The cartridge 115 holds the fixed ring 112 so as not to rotate integrally with the rotary shaft 11 while being movable in the axial direction of the rotary shaft 11. For this reason, the fixed ring 112 is allowed to move in the axial direction of the rotating shaft 11, while the movement of the rotating shaft 11 in the circumferential direction is restricted.

  The spring 113 and the spring holding portion 114 are disposed between the cartridge bottom portion 115 b of the cartridge 115 and the fixed ring 112. The spring holding portion 114 is in contact with the stationary ring 112, and the spring 113 connects the spring holding portion 114 and the cartridge bottom portion 115b. As a result, the urging force of the spring 113 is transmitted to the fixed ring 112 via the spring holding portion 114, and the fixed ring 112 is pressed toward the rotating ring 111.

  A gap formed by a part of the inner peripheral surface of the fixed ring 112 being recessed radially outward of the rotating shaft 11 and a part of the inner ring 115 c of the cartridge 115 being recessed radially inward of the rotating shaft 11. Is provided with an O-ring 116.

  As shown in FIGS. 2 and 3, a first seal member 103 is provided between the motor chamber A <b> 1 and the first radial bearing 54 in the first through-hole 101 so that the oil O leaks more easily than the first mechanical seal 102. It has been. The first seal member 103 is disposed on the motor chamber A1 side with respect to the first radial bearing 54 in the first through hole 101. The first seal member 103 has an annular shape and is provided between the inner surface 52 a of the motor side plate through hole 52 and the outer peripheral surface 11 a of the rotating shaft 11. The first seal member 103 is, for example, a seal ring or a non-contact type labyrinth seal.

  In the present embodiment, the outer peripheral surface 11 a of the rotating shaft 11, the inner surface 101 a of the first through hole 101 constituted by the inner surfaces 52 a and 53 a of both plate through holes 52 and 53, the first mechanical seal 102 and the first seal member 103. A first bearing chamber A4 for accommodating the first radial bearing 54 is defined. The first bearing chamber A4 is disposed between the impeller chamber A2 and the motor chamber A1. The first bearing chamber A4 and the motor chamber A1 are partitioned by a first seal member 103, and the first bearing chamber A4 and the impeller chamber A2 are partitioned by a first mechanical seal 102.

  As shown in FIGS. 2 and 3, in the first bearing chamber A <b> 4, a thrust bearing 121 that receives a thrust force generated by the rotation of the impeller 13 is accommodated separately from the first radial bearing 54. The thrust bearing 121 is fixed to the thrust collar 122 by being fitted into a fitting groove 122 a formed in a cylindrical thrust collar 122 fixed to the rotary shaft 11. As a result, the thrust bearing 121 rotates with the rotation of the rotating shaft 11.

  The thrust collar 122 and the thrust bearing 121 are disposed between the first mechanical seal 102 and the first radial bearing 54, and are housed in the first enlarged diameter portion 52b in detail. A part of the thrust bearing 121 is disposed between the first step surface 52 d and the bottom surface of the recess 41. The first bearing chamber A4 is divided by a thrust bearing 121 and a thrust collar 122 into a motor side bearing region A41 in which the first radial bearing 54 is disposed and an impeller side bearing region A42 in which the first mechanical seal 102 is disposed. It is divided. The motor side bearing region A41 is a region closer to the motor chamber A1 than the thrust bearing 121 in the first bearing chamber A4, and the impeller side bearing region A42 is closer to the impeller chamber A2 than the thrust bearing 121 in the first bearing chamber A4. It is an area.

  As shown in FIG. 2, a first oil passage 130 that supplies oil O to the first bearing chamber A <b> 4 is formed in the housing 20. The first oil passage 130 is formed across both plates 25 and 26. The first oil passage 130 includes a first inflow passage 131 provided in the comp side plate 26, and two comp side branch passages 132 and 133 that are bifurcated from the first inflow passage 131. . Both the comp-side branch channels 132 and 133 are channels having a smaller channel cross-sectional area than the first inflow channel 131.

  The first inflow channel 131 has a first oil inlet 131 a provided in a vertically upper portion of the side wall surface of the comp-side plate 26, and the radial inner side of the rotary shaft 11 from the first oil inlet 131 a. (In detail, vertically downward).

  As shown in FIGS. 2 and 3, the first comp-side branch channel 132 is provided in the comp-side plate 26 and communicates the first inflow channel 131 and the impeller-side bearing region A42. The first comp-side branch flow path 132 opens in the vertical direction of the rotating ring 111, specifically, the inner surface of the second enlarged diameter portion 53b. The first comp-side branch channel 132 corresponds to the “first supply channel”. The oil O flowing down from the first comp-side branch channel 132 is supplied to the sliding surfaces (specifically, both end surfaces 111a and 112a) of the first mechanical seal 102.

  The second comp-side branch channel 133 is formed across both plates 25 and 26, and communicates the first inflow channel 131 and the motor-side bearing region A41. Specifically, the second comp-side branch channel 133 is provided in the comp-side plate 26, provided in the first part channel 133 a communicating with the first inflow channel 131, and in the motor-side plate 25, It has the 1st parts flow path 133a and the 2nd parts flow path 133b which connects the motor side bearing area | region A41. The second part flow path 133b communicates with the motor-side bearing region A41 at a position on the radially outer side of the first radial bearing 54. The second comp-side branch channel 133 corresponds to the “second supply channel”.

  The first part flow path 133 a opens to the side wall surface of the concave portion 41 of the comp side plate 26, and the second part flow path 133 b opens to the side wall surface of the convex portion 42 of the motor side plate 25. The opening of the first part flow path 133a and the opening of the second part flow path 133b are in contact with each other. Further, the end of the second part flow path 133b on the motor side bearing region A41 side has an enlarged diameter, thereby forming a first storage chamber A5 in which the oil O is stored.

  As shown in FIG. 2, the first oil passage 130 includes a first oil chamber A6 in which the oil O that has flowed through the first bearing chamber A4 is stored. The first oil chamber A6 is provided in the housing 20 below the first bearing chamber A4 in the vertical direction. The first oil chamber A6 is defined by a first oil recess 134 that is recessed from the first compressor side plate surface 26a of the compressor side plate 26. The first oil chamber A6 and the first bearing chamber A4 communicate with each other in the vertical direction.

  The first oil flow path 130 includes a first discharge flow path 135 that discharges the oil O stored in the first oil chamber A6. The first discharge channel 135 is provided in the compressor side plate 26 and communicates with the first oil chamber A6. The first discharge channel 135 extends from the first oil chamber A6 toward the radially outer side of the rotating shaft 11 (specifically, vertically downward). The first discharge flow path 135 has a first oil discharge port 135 a provided in a vertically lower portion of the outer peripheral surface of the comp-side plate 26.

  According to this configuration, the oil O that has flowed in from the first oil inflow port 131 a flows through the first inflow channel 131 and branches into the both comp-side branch channels 132 and 133. Then, the oil O flows through the first bearing chamber A4, specifically, both the bearing regions A41 and A42, reaches the first oil chamber A6, and is then discharged from the first discharge passage 135.

Next, the configuration around the second radial bearing 57 will be described.
As shown in FIGS. 4 and 5, the motor chamber A <b> 1 and the sensor chamber A <b> 3 are partitioned by a jacket bottom 24 a and a resolver housing 23. The rotating shaft 11 passes through (inserts through) the jacket through-hole 56 formed in the jacket bottom 24a and the first part through-hole 91 of the resolver through-hole 81 formed in the resolver housing 23. It is arranged across both A1 and sensor chamber A3. In this case, the jacket bottom 24a and the resolver housing 23 correspond to the “partition wall”.

  For convenience of explanation, in the following explanation, the jacket through hole 56 and the first part through hole 91 are collectively referred to as a second through hole 141. The second through-hole 141 is a through-hole constituted by a jacket through-hole 56 and a first part through-hole 91 that communicate with each other. The second through hole 141 corresponds to “a through hole through which the rotation shaft is inserted”.

  The first part through-hole 91 has a part enlarged diameter part 91 b and a part reduced diameter part 91 c that communicate with each other in the axial direction of the rotating shaft 11. The part enlarged diameter portion 91b is disposed closer to the second radial bearing 57 (in other words, the motor chamber A1 side) than the part reduced diameter portion 91c. A part step surface 91d is formed on the inner surface 91a of the first part through hole 91 due to the difference in size between the part enlarged diameter portion 91b and the part reduced diameter portion 91c. The part step surface 91 d is a plane orthogonal to the axial direction of the rotation shaft 11.

  As shown in FIGS. 4 and 5, a second seal member is provided between the sensor chamber A <b> 3 and the second radial bearing 57 in the second through hole 141 as a seal member for restricting the movement of fluid (specifically, oil O). A mechanical seal 142 is provided. The second mechanical seal 142 is disposed on the side opposite to the motor chamber A1 side with respect to the second radial bearing 57, specifically, on the sensor chamber A3 side with respect to the second radial bearing 57, and the outer peripheral surface of the rotating shaft 11 11a and the inner surface 91a of the first part through-hole 91.

  The specific configuration of the second mechanical seal 142 is the same as that of the first mechanical seal 102 except that the configuration is symmetrical and the surface to be attached is the part step surface 91d. Omitted.

  Between the motor chamber A <b> 1 and the second radial bearing 57 in the second through hole 141, a second seal member 143 in which oil O leaks more easily than the second mechanical seal 142 is provided. The second seal member 143 is disposed on the motor chamber A1 side with respect to the second radial bearing 57. The second seal member 143 is annular and is disposed between the inner surface 56 a of the jacket through hole 56 and the outer peripheral surface 11 a of the rotating shaft 11. The second seal member 143 is, for example, a seal ring or a labyrinth seal.

  In the present embodiment, the inner surface 141a of the second through hole 141 constituted by the outer peripheral surface 11a of the rotating shaft 11, the inner surface 56a of the jacket through hole 56 and the inner surface 91a of the first part through hole 91, and the second mechanical seal 142. The second seal member 143 defines a second bearing chamber A7 that houses the second radial bearing 57. The second bearing chamber A7 is disposed between the motor chamber A1 and the sensor chamber A3. The second bearing chamber A7 and the motor chamber A1 are partitioned by a second seal member 143, and the second bearing chamber A7 and the sensor chamber A3 are partitioned by a second mechanical seal 142.

  As shown in FIG. 4, a second oil flow path 150 that supplies oil O to the second bearing chamber A <b> 7 is formed in the housing 20. The second oil channel 150 is formed across the jacket bottom 24 a and the resolver housing 23. The second oil passage 150 includes a second inflow passage 151 provided in the resolver housing 23, and two resolver-side branch passages 152 and 153 branched from the second inflow passage 151. Both resolver-side branch channels 152 and 153 are channels having a smaller channel cross-sectional area than the second inflow channel 151.

  The second inflow channel 151 includes a second oil inlet 151a provided in a vertically upper portion of the side wall surface of the resolver housing 23, and the second oil inlet 151a is radially inward of the rotary shaft 11 from the second oil inlet 151a ( In detail, it extends vertically downward).

  The first resolver side branch flow path 152 is provided in the resolver housing 23 and communicates the second inflow flow path 151 and the first part through hole 91. The first resolver-side branch flow path 152 opens in the vertical direction of the rotary ring 111, specifically, on the inner surface of the part enlarged portion 91b. The oil O flowing down from the first resolver-side branch flow path 152 is supplied to the sliding surfaces (specifically, both end surfaces 111a and 112a) of the second mechanical seal 142.

  The second resolver side branch channel 153 is formed across the jacket bottom 24 a and the resolver housing 23, and communicates the second inflow channel 151 and the jacket through hole 56. Specifically, the second resolver side branch flow path 153 is provided in the resolver housing 23, provided in the first part flow path 153a communicating with the second inflow flow path 151, and in the jacket bottom 24a. A second part flow path 153b that communicates the flow path 153a and the jacket through hole 56 is provided. The second part flow path 153 b communicates with the jacket through hole 56 at a position radially outside the second radial bearing 57. Further, the end of the second part channel 153b on the jacket through-hole 56 side has an enlarged diameter, thereby forming a second storage chamber A8 in which the oil O is stored.

  As shown in FIG. 4, the second oil flow path 150 includes a second oil chamber A9 in which the oil O that has flowed through the second bearing chamber A7 is stored. The second oil chamber A9 is provided below the second bearing chamber A7 in the housing 20 in the vertical direction. The second oil chamber A9 is defined by a second oil recess 154 that is recessed from a surface 23a that is in contact with the jacket bottom 24a of the resolver housing 23. The second oil chamber A9 and the second bearing chamber A7 communicate with each other in the vertical direction.

  The second oil flow path 150 includes a second discharge flow path 155 that discharges the oil O stored in the second oil chamber A9. The second discharge channel 155 is provided in the resolver housing 23 and communicates with the second oil chamber A9. The second discharge channel 155 extends from the second oil chamber A9 toward the radially outer side of the rotating shaft 11 (specifically, vertically downward), and is formed on the lower part of the outer peripheral surface of the resolver housing 23 in the vertical direction. A second oil discharge port 155a is provided.

  According to this configuration, the oil O that has flowed in from the second oil inflow port 151 a flows through the second inflow channel 151 and branches to both the resolver side branch channels 152 and 153. Then, the oil O flows through the second bearing chamber A7 and reaches the second oil chamber A9, and then is discharged from the second discharge channel 155.

  As shown in FIG. 1, the housing 20 is formed with a third oil discharge port 156 for discharging the oil O flowing into the motor chamber A1. The third oil discharge port 156 is provided at a position below the vertical direction in the housing 20, and penetrates both the motor housing 21 and the water jacket 24 in the radial direction of the rotary shaft 11.

  Here, in the fuel cell vehicle of the present embodiment, an oil pipe connecting the oil inlets 131a and 151a and the oil outlets 135a, 155a and 156, an oil pan provided on the oil pipe, and an oil pipe An oil pump for circulating the oil flowing through the oil pipe and an oil cooler for cooling the oil flowing through the oil pipe are mounted. Thereby, the oil O circulates through both the oil flow paths 130 and 150.

Next, the operation of this embodiment will be described.
When the rotating shaft 11 is rotated by the electric motor 12, the impeller 13 is rotated. Thereby, the fluid sucked from the suction port 20a is compressed. In this case, heat is generated in the radial bearings 54 and 57 that support the rotating shaft 11. The heat is absorbed by the oil O circulating in the first bearing chamber A4 and the second bearing chamber A7.

  Here, since the first bearing chamber A4 is partitioned by the first mechanical seal 102 and the first seal member 103, the first bearing chamber A4 is easily filled with the oil O. For this reason, the first radial bearing 54 and the thrust bearing 121 housed in the first bearing chamber A4 are easily cooled by the oil O.

  The inflow of oil O from the first bearing chamber A4 to the impeller chamber A2 is restricted by the first mechanical seal 102 disposed between the first bearing chamber A4 and the impeller chamber A2. On the other hand, since the first seal member 103 disposed between the first bearing chamber A4 and the impeller chamber A2 is more likely to leak oil O than the first mechanical seal 102, the first seal chamber 103 is directed from the first bearing chamber A4 toward the motor chamber A1. A part of oil O flows. The electric motor 12 is cooled by the oil O.

According to the embodiment described above in detail, the following effects are obtained.
(1) The centrifugal compressor 10 rotates the rotating shaft 11, the electric motor 12 and the impeller 13 attached to the rotating shaft 11, the housing 20 in which the electric motor 12 and the impeller 13 are accommodated, and the rotating shaft 11. And a first radial bearing 54 that supports the first radial bearing 54. The electric motor 12 rotates the rotating shaft 11, and the impeller 13 compresses the fluid by rotating with the rotation of the rotating shaft 11.

  In the housing 20, the motor chamber A1 that houses the electric motor 12, the impeller chamber A2 that houses the impeller 13 as a predetermined component, the motor chamber A1 and the impeller chamber A2, and the rotating shaft 11 are inserted. Both plates 25 and 26 as partition walls having both plate through holes 52 and 53 (that is, the first through hole 101) are provided. The rotating shaft 11 is disposed across both the motor chamber A1 and the impeller chamber A2. Further, in the housing 20, a first bearing chamber A4 that is formed between the inner surface 101a of the first through hole 101 and the outer peripheral surface 11a of the rotating shaft 11 and accommodates the first radial bearing 54, A first oil passage 130 for supplying oil O to the first bearing chamber A4 is provided. Accordingly, the first radial bearing 54 can be cooled using the oil O.

  In such a configuration, the first mechanical seal 102 that restricts the inflow of the oil O from the first bearing chamber A4 to the impeller chamber A2 is provided between the impeller chamber A2 and the first radial bearing 54 in the first through hole 101. It has been. Thereby, it is possible to suppress inconvenience that may be caused by cooling the first radial bearing 54 using the oil O, specifically, the oil O leaks into the impeller chamber A2 and the oil O is mixed into the compressed fluid.

  On the other hand, a first seal member 103 is provided between the motor chamber A <b> 1 and the first radial bearing 54 in the first through hole 101 so that the oil O is more likely to leak than the first mechanical seal 102. Thereby, the electric motor 12 can be cooled using the oil O leaking into the motor chamber A1 through the first seal member 103. Therefore, heat generation of the first radial bearing 54 and the electric motor 12 can be suppressed while suppressing leakage of the oil O to the impeller chamber A2. Therefore, it can respond suitably to the high-speed rotation of the impeller 13.

  Specifically, when the impeller 13 is rotated at a high speed, for example, it is conceivable to provide a speed increaser and connect the electric motor 12 and the impeller 13 via the speed increaser. However, in this case, there is a concern about the enlargement of the centrifugal compressor 10.

  On the other hand, in this embodiment, the impeller 13 and the electric motor 12 are attached to one rotating shaft 11. Thereby, size reduction of the centrifugal compressor 10 can be achieved by the part which does not have a gearbox. In this case, since the rotation speed of the impeller 13 and the rotation speed of the electric motor 12 are the same, it is necessary to rotate the rotating shaft 11 and the rotor 71 of the electric motor 12 at high speed in order to rotate the impeller 13 at high speed. As a result, the first radial bearing 54 and the electric motor 12 may easily generate heat.

  On the other hand, in this embodiment, since the 1st radial bearing 54 and the electric motor 12 can be cooled using the oil O, the said inconvenience can be suppressed. Thereby, it can respond suitably to the high speed rotation of the impeller 13.

  In particular, since the first seal member 103 may leak oil O more easily than the first mechanical seal 102, a simple configuration can be adopted as compared with the first mechanical seal 102. Thereby, the above-described effects can be obtained while suppressing the complication of the configuration.

  (2) Since the first seal member 103 is provided between the first bearing chamber A4 and the motor chamber A1, the first bearing chamber A4 is compared with a configuration in which the first seal member 103 is not provided. The flow of oil O into the motor chamber A1 is limited to some extent. Thereby, since the oil O is easy to be filled in the first bearing chamber A4, the first radial bearing 54 can be suitably cooled. Therefore, the cooling performance of the first radial bearing 54 using the oil O can be improved.

  Moreover, since the inflow of the oil O into the motor chamber A1 is limited to some extent, an increase in the stirring resistance of the oil O in the motor chamber A1 can be suppressed. Thereby, the electric motor 12 can be cooled while suppressing a decrease in efficiency of the electric motor 12 (in other words, an increase in loss).

  (3) The first seal member 103 is a seal ring or a labyrinth seal provided between the outer peripheral surface 11 a of the rotating shaft 11 and the inner surface 101 a of the first through hole 101. These seal rings and labyrinth seals have a simple configuration as compared with the first mechanical seal 102. In addition, since a gap is formed in the seal ring due to its structure, oil O leaks from the gap. Moreover, since the labyrinth seal has a non-contact seal structure, a gap through which oil O leaks is formed. Thereby, a certain amount of oil O is supplied to the motor chamber A1. Therefore, the effects (1) and (2) can be obtained with a relatively simple configuration.

  (4) The housing 20 includes a water jacket 24 that covers the motor housing 21 that partitions the motor chamber A1. The motor housing 21 can be cooled by the refrigerant flowing through the gap 32 formed between the water jacket 24 and the motor housing 21.

  Here, as described above, when the impeller 13 is rotated at a high speed, the electric motor 12 may excessively generate heat even when the motor housing 21 is cooled using a refrigerant. In particular, the cooling of the electric motor 12 using the water jacket 24 is an indirect cooling method via the motor housing 21, and thus the electric motor 12 may not be sufficiently cooled.

  On the other hand, in this embodiment, the electric motor 12 can be directly cooled using the oil O. Thereby, since the electric motor 12 can be cooled more suitably, it can respond more suitably to the high-speed rotation of the impeller 13.

  (5) A thrust bearing 121 that receives a thrust force generated by the rotation of the impeller 13 is accommodated in the first bearing chamber A4. The thrust bearing 121 is disposed between the first mechanical seal 102 and the first radial bearing 54. The first bearing chamber A4 is divided by the thrust bearing 121 into a motor side bearing region A41 on the motor chamber A1 side relative to the thrust bearing 121 and an impeller side bearing region A42 on the impeller chamber A2 side relative to the thrust bearing 121. .

  In this configuration, the first oil flow path 130 includes a first comp side branch flow path 132 that supplies oil O to the impeller side bearing area A42 and a second comp side branch flow that supplies oil O to the motor side bearing area A41. Road 133 is provided. Thereby, in the configuration in which the thrust bearing 121 is provided, the oil O can be supplied to both the first radial bearing 54 and the first mechanical seal 102. Therefore, inconvenience due to the provision of the thrust bearing 121, specifically, the movement of the oil O between the bearing regions A41 and A42 is restricted by the thrust bearing 121, and any of the first radial bearing 54 and the first mechanical seal 102 is detected. On the other hand, depletion of oil O can be suppressed. Therefore, excessive heat generation of the first radial bearing 54 and the first mechanical seal 102 can be suppressed.

  (6) The centrifugal compressor 10 includes a resolver 14 as a rotation angle sensor that is attached to the rotation shaft 11 and detects the rotation angle of the electric motor 12. The housing 20 includes a jacket bottom 24a and a resolver housing 23 as partition walls that separate the motor chamber A1 from the sensor chamber A3 that houses the resolver 14 as a predetermined part. The rotary shaft 11 is inserted through a second through hole 141 including a jacket through hole 56 formed in the jacket bottom 24a and a first part through hole 91 formed in the resolver housing 23, and the motor chamber A1 and the sensor chamber A3. It is arranged straddling both sides. Inside the housing 20, a second bearing chamber A7 is formed between the outer peripheral surface 11a of the rotary shaft 11 and the inner surface 141a of the second through hole 141, and accommodates the second radial bearing 57. The second bearing chamber A7 contains oil. A second oil flow path 150 for supplying O is provided. Accordingly, the second radial bearing 57 can be cooled using the oil O.

  In such a configuration, the second mechanical seal 142 that restricts the inflow of the oil O from the second bearing chamber A7 to the sensor chamber A3 is provided between the sensor chamber A3 and the second radial bearing 57 in the second through hole 141. It has been. Thereby, it is possible to suppress inconvenience that may occur by cooling the second radial bearing 57 using the oil O, specifically, the oil O leaks into the sensor chamber A3 and adversely affects the detection of the rotation angle by the resolver 14.

  On the other hand, a second seal member 143 is provided between the motor chamber A <b> 1 and the second radial bearing 57 in the second through hole 141 so that the oil O leaks more easily than the second mechanical seal 142. Thereby, the electric motor 12 can be cooled using the oil O leaking into the motor chamber A <b> 1 via the second seal member 143. Therefore, heat generation of the electric motor 12 can be suppressed while suppressing leakage of the oil O into the sensor chamber A3. Therefore, it can respond suitably to the high-speed rotation of the impeller 13.

(Second Embodiment)
The present embodiment is different from the first embodiment in that the centrifugal compressor includes two impellers. Hereinafter, differences from the first embodiment will be described in detail. In addition, about the structure same as 1st Embodiment, while attaching | subjecting the same code | symbol, detailed description is abbreviate | omitted.

As shown in FIG. 6, the centrifugal compressor 10 includes a front impeller 201 separately from the impeller 13 of the first embodiment (hereinafter referred to as the rear impeller 13).
Apart from the compressor housing 22 of the first embodiment, the housing 20 includes a front compressor housing 202 in which a front impeller 201 is accommodated. For convenience of explanation, in the following explanation, the compressor housing 22, the suction port 20a, the impeller chamber A2, the diffuser passage 62, and the discharge chamber 63 of the first embodiment are referred to as the rear compressor housing 22, the rear suction port 20a, and the rear impeller chamber. A2, the rear diffuser flow path 62, and the rear discharge chamber 63 are used.

  The front compressor housing 202 is basically symmetrical with the rear compressor housing 22. The front compressor housing 202 has a substantially cylindrical shape having a front compressor through hole 202a. One end face 202b in the axial direction of the front compressor housing 202 constitutes the other end face 20c in the axial direction of the housing 20, and an opening on the other end face 20c side in the front compressor through hole 202a functions as the front suction port 20d.

  The housing 20 of the present embodiment includes a front housing 203 instead of the resolver housing 23. The front housing 203 has a disk shape having a front through hole 204 that penetrates in the axial direction of the rotary shaft 11. As shown in FIG. 7, the front through hole 204 has a first part through hole 206 and a second part, with an annular wall 205 protruding from the inner surface 204 a of the front through hole 204 inward in the radial direction of the rotary shaft 11. It consists of a through hole 207.

  The front housing 203 is disposed between the water jacket 24 and the front compressor housing 202, and is unitized with the water jacket 24 and the front compressor housing 202. The front compressor housing 202 and the front housing 203 define a front impeller chamber A11 that houses the front impeller 201, a front diffuser flow path 208, and a front discharge chamber 209.

  In this embodiment, the rotating shaft 11 penetrates (inserts) the jacket through hole 56 and the front through hole 204, and is disposed across both the motor chamber A1 and the front impeller chamber A11. And the front impeller 201 is attached to the rotating shaft 11 arrange | positioned in front impeller chamber A11.

  The front impeller 201 has a cylindrical shape with a diameter gradually reduced from the base end surface 201a toward the front end surface 201b. The front impeller 201 is attached to the rotary shaft 11 so as to rotate integrally with the rotary shaft 11 in a state where the rotary shaft 11 is inserted through an insertion hole 201 c formed in the front impeller 201. In this case, the rear impeller 13 and the front impeller 201 are opposed to each other at the base end surfaces 13a and 201a.

  Incidentally, in the present embodiment, the front impeller 201 has the same shape as the rear impeller 13. However, the present invention is not limited to this, and the front impeller 201 may be formed slightly larger than the rear impeller 13 or vice versa.

  The second part through-hole 207 opens toward the front impeller 201, and the space in the second part through-hole 207, specifically, the space on the front impeller 201 side from the annular wall portion 205 in the front through-hole 204 is This constitutes a part of the front impeller chamber A11.

  The motor chamber A1 and the front impeller chamber A11 are partitioned by the jacket bottom 24a and the front housing 203. That is, in the present embodiment, the jacket bottom 24a and the front housing 203 correspond to the “partition wall”.

  As shown in FIG. 7, in the present embodiment, the second mechanical seal 142 includes the front impeller chamber A <b> 11 and the second radial bearing 57 in the second through hole 211 configured by the jacket through hole 56 and the first part through hole 206. In detail, it is arranged on the front impeller chamber A11 side with respect to the second radial bearing 57. The second mechanical seal 142 is disposed in the first part through hole 206. The second bearing chamber A12 of the present embodiment includes an inner surface 211a of the second through hole 211 formed by the inner surface 56a of the jacket through hole 56 and the inner surface 206a of the first part through hole 206, the outer peripheral surface 11a of the rotating shaft 11, The two seal members 143 and the second mechanical seal 142 are defined. The second bearing chamber A12 and the front impeller chamber A11 are partitioned by a second mechanical seal 142. A second oil passage 150 is formed in the front housing 203.

  As shown in FIGS. 6 and 7, the fuel cell vehicle of this embodiment is equipped with a pipe 212 for introducing the fluid discharged from the front discharge chamber 209 to the rear suction port 20a. Thereby, the fluid sucked from the front suction port 20d is compressed by the front impeller 201 and the like, and the compressed fluid is sucked from the rear suction port 20a. The compressed fluid sucked from the rear suction port 20a is further compressed by the rear impeller 13 and the like and discharged from the rear discharge chamber 63.

According to the embodiment described above in detail, the following operational effects are obtained.
(7) The housing 20 includes a jacket bottom 24a and a front housing 203 that partition the motor chamber A1 from the front impeller chamber A11 that houses the front impeller 201. The rotary shaft 11 is inserted through a second through hole 211 including a jacket through hole 56 formed in the jacket bottom 24a and a first part through hole 206 formed in the front housing 203, and the motor chamber A1 and the front impeller chamber. It is arranged across both A11.

  In such a configuration, the second mechanical seal 142 is provided between the front impeller chamber A11 and the second radial bearing 57 in the second through hole 211, and the motor chamber A1 and the second radial bearing in the second through hole 211 are provided. A second seal member 143 is provided between the second mechanical seal 142 and the second mechanical seal 142 so that the oil O leaks more easily. Thereby, effects (1) etc. can be acquired.

In addition, you may change each said embodiment as follows.
As shown in FIG. 8, instead of the first seal member 103, the first bearing chamber A4 and the motor chamber A1 are communicated between the first radial bearing 54 and the motor chamber A1 in the first through hole 101. An opening 220 may be provided. In this case, since the flow rate of the oil O flowing into the motor chamber A1 can be increased, the electric motor 12 can be further cooled. However, in view of a decrease in the cooling performance of the first radial bearing 54 using the oil O and an increase in loss due to an increase in the stirring resistance of the oil O in the motor chamber A1, the first seal member 103 is provided. Is preferred. Similarly, an opening may be provided instead of the second seal member 143.

  ○ The water jacket 24 may be omitted. In this case, the first opening 21b of the motor housing 21 may be closed using the resolver housing 23 or the front housing 203.

O The installation position of the thrust bearing 121 is not limited to the first bearing chamber A4, and is arbitrary. Further, the thrust bearing 121 may be omitted.
O The specific structure of the oil passages 130 and 150 is arbitrary. For example, either one of the two comp-side branch channels 132 and 133 may be omitted.

  ○ Both plates 25 and 26 are assembled in a state in which the convex portion 42 is fitted in the concave portion 41, but the present invention is not limited to this. The convex portions 42 and the concave portion 41 are omitted, and the flat surfaces are in contact with each other. It may be configured.

The specific configuration of the mechanical seals 102 and 142 is not limited to that of the first embodiment, and is arbitrary.
The rotary ring 111 and the thrust collar 122 may be integrally formed.

  In the first embodiment, the annular wall 83 is omitted, and the first part through hole 91 that defines the second bearing chamber A7 and the second part through hole 92 that defines the sensor chamber A3 are continuous. Good. In short, the resolver through-hole 81 may be formed so as to be accommodated in a state where the second mechanical seal 142 and the resolver 14 are arranged in the axial direction of the rotating shaft 11.

  In the first embodiment, an intermediate plate may be provided between the jacket bottom 24a and the resolver housing 23. The intermediate plate has a through hole through which the rotary shaft 11 passes. In this case, the second mechanical seal 142 may be provided in the through hole, and the resolver housing 23 may contain only the resolver 14. In this case, the jacket bottom 24a and the intermediate plate correspond to the “partition wall”.

  The installation position of the first radial bearing 54 is arbitrary as long as it is in the first through hole 101, and may be disposed, for example, in the comp side plate through hole 53, or in the comp side plate through hole 53 and the motor side. It may be disposed across both plate through holes 52.

  Similarly, the installation position of the second radial bearing 57 is arbitrary as long as it is in the second through holes 141, 211, and may be disposed in the first part through holes 91, 206, for example, or through the jacket It may be disposed across both the hole 56 and the first part through holes 91 and 206.

○ At least one of the first boss 51 and the second boss 55 may be omitted.
○ The first storage chamber A5 and the second storage chamber A8 may be omitted.
The predetermined parts are not limited to the resolver 14 and the impellers 13 and 201, and may be any parts as long as they normally operate in an environment in which the oil O is not mixed, specifically in an air atmosphere. In addition, the specific shape of the predetermined chamber is arbitrary as long as it is a chamber that accommodates the predetermined component and is partitioned in the housing 20.

O The object for mounting the centrifugal compressor 10 is not limited to the vehicle, but is arbitrary.
The centrifugal compressor 10 may be used in an air conditioner that adjusts the temperature in the vehicle using a refrigerant. That is, the fluid compressed by the centrifugal compressor 10 is arbitrary, and may be air or a refrigerant.

Next, a preferable example that can be grasped from each of the above embodiments and other examples will be described below.
(B) The centrifugal compressor according to any one of claims 1 to 5, wherein the housing includes a water jacket that covers a motor housing that partitions the motor chamber.

  DESCRIPTION OF SYMBOLS 10 ... Centrifugal compressor, 11 ... Rotary shaft, 11a ... Outer peripheral surface of rotary shaft, 12 ... Electric motor, 13 ... Impeller (rear impeller), 14 ... Resolver (rotation angle sensor), 20 ... Housing, 54, 57 ... Radial bearing 101, 141, 211 ... through hole, 101a, 141a, 211a ... inner surface of the through hole, 102, 142 ... mechanical seal, 103, 143 ... seal member, 121 ... thrust bearing, 130, 150 ... oil flow path, 201 ... Front impeller, 220 ... opening, A1 ... motor chamber, A2, A11 ... impeller chamber, A3 ... sensor chamber, A4, A7, A12 ... bearing chamber, O ... oil.

Claims (5)

A rotation axis;
An electric motor attached to the rotating shaft and rotating the rotating shaft;
An impeller attached to the rotating shaft and compressing fluid by rotating with the rotation of the rotating shaft;
A housing in which the electric motor and the impeller are housed;
A radial bearing rotatably supporting the rotating shaft;
With
In the housing, a partition wall having a motor chamber that houses the electric motor, a predetermined chamber that houses predetermined components, and a through hole that partitions the motor chamber and the predetermined chamber and through which the rotating shaft is inserted. And a bearing chamber that is formed between the inner surface of the through hole and the outer peripheral surface of the rotating shaft and that accommodates the radial bearing, and an oil passage that supplies oil to the bearing chamber,
The rotating shaft is disposed across both the motor chamber and the predetermined chamber,
A mechanical seal is provided between the predetermined chamber in the through hole and the radial bearing,
Between the motor chamber and the radial bearing in the through hole, there is provided a seal member in which oil is more likely to leak than the mechanical seal, or an opening for communicating the bearing chamber and the motor chamber. Centrifugal compressor characterized by. The predetermined part is the impeller;
The centrifugal compressor according to claim 1, wherein the predetermined chamber is an impeller chamber that houses the impeller. The bearing chamber contains a thrust bearing that receives a thrust force generated by rotation of the impeller.
The thrust bearing is disposed between the mechanical seal and the radial bearing;
The oil flow path is
A first supply passage for supplying oil to a region closer to the impeller chamber than the thrust bearing in the bearing chamber;
A second supply channel for supplying oil to a region on the motor chamber side of the thrust bearing in the bearing chamber;
The centrifugal compressor according to claim 2 provided with. A rotation angle sensor that is attached to the rotation shaft and detects a rotation angle of the electric motor as the predetermined component,
The centrifugal compressor according to claim 1, wherein the predetermined chamber is a sensor chamber that houses the rotation angle sensor.   The centrifugal compressor according to any one of claims 1 to 4, wherein the seal member is a seal ring or a labyrinth seal.