JP2021173162A - Fuel cell vehicle pump - Google Patents

Abstract

To provide a fuel cell vehicle pump capable of suppressing the rise of pressure in a rear cavity.SOLUTION: In a fuel cell vehicle pump 10, a collar member 100 has a non-abutment face H1 and an abutment face H2. The non-abutment face H1 is opposed to a base end side taper face 24b of an impeller 24 at the outer periphery part in the axial direction of a high speed side shaft 31 without abutting on a base end face 24a of the impeller 24. The abutment face H2 abuts on the base end face 24a of the impeller 24 at the inner periphery side further than the outer periphery part of a first large diameter part 101. A base end side taper face 24b of the impeller 24 and a taper face 14j and an annular face 14k of a plate 14 are opposed to each other via a first rear cavity K1 in the axial direction. The base end side taper face 24b of the impeller 24 and the non-abutment face H1 are opposed to each other via a second rear cavity K2 in the axial direction. A restriction passage 110 is formed between the collar member 100 and the plate 14, and the restriction passage 110 is opened to the first rear cavity K1.SELECTED DRAWING: Figure 3

Description

The present invention relates to a fuel cell vehicle pump.

A fuel cell vehicle that runs on a fuel cell as a power source is equipped with a centrifugal compressor as a pump, and the centrifugal compressor supplies air to the fuel cell. The centrifugal compressor includes a low-speed side shaft, an impeller and a diffuser that rotate integrally with the high-speed side shaft to compress gas, and a speed-increasing machine that transmits the power of the low-speed side shaft to the high-speed side shaft. In the housing of the centrifugal compressor, an impeller chamber for accommodating the impeller and a speed increaser chamber for accommodating the speed increaser are formed. The impeller room and the speed increaser room are separated by a partition wall.

Further, the centrifugal compressor has a diffuser flow path into which the air sent by the impeller flows in, a discharge chamber in which the air passing through the diffuser flow path flows in, and an impeller back surface and a partition wall along the axial direction of the high-speed shaft. It has a back gap partitioned between them. Further, a shaft insertion hole is formed in the partition wall. The high-speed side shaft passes through the shaft insertion hole from the speed increaser chamber and protrudes into the impeller chamber. The back gap formed on the back of the impeller communicates with the shaft insertion hole.

In such a centrifugal compressor, oil is supplied to the speed increaser as in Patent Document 1, for example, in order to suppress friction and seizure of the sliding portion between the high speed side shaft and the speed increaser. The centrifugal compressor of Patent Document 1 includes an oil pan in which oil supplied to the speed increaser room is stored, an oil supply passage for supplying the oil stored in the oil pan to the speed increaser room, and a speed increaser room. It is equipped with an oil recirculation passage for recirculating the oil of the above to the oil pan.

Then, the oil supplied from the oil pan to the speed increaser room through the oil supply passage is supplied to the speed increaser, stored in the speed increaser room, and returned to the oil pan through the oil return passage. NS. A sealing member is provided between the peripheral surface of the high-speed shaft and the inner peripheral surface of the shaft insertion hole. The seal member suppresses the oil stored in the speed increaser chamber from leaking into the impeller chamber through the shaft insertion hole.

Japanese Unexamined Patent Publication No. 2016-186238

During the operation of the centrifugal compressor, a part of the gas sent by the impeller flows from the diffuser flow path into the back gap. Then, the pressure in the back gap increases. Then, the gas that has flowed into the back gap flows into the shaft insertion hole and leaks into the drive chamber in which the drive source that rotates the impeller is housed. As a result, the efficiency of the centrifugal compressor is reduced.

An object of the present invention is to provide a fuel cell vehicle pump capable of suppressing an increase in pressure in a back gap.

A fuel cell vehicle pump for solving the above problems includes an impeller fixed to one end of a shaft, an impeller chamber for accommodating the impeller, and a drive chamber for accommodating a drive source for rotating the shaft. A fuel cell vehicle pump having a housing provided with a partition wall for partitioning the impeller chamber and the drive chamber and having a shaft insertion hole through which the shaft is inserted, wherein the shaft insertion hole and the shaft are provided. A rotating body fixed to the shaft and rotating integrally with the shaft is interposed between the rotating bodies, and the rotating body faces the back surface of the impeller at the outer peripheral portion and hits the back surface of the impeller. It has a non-contact surface that does not contact and a contact surface that abuts on the back surface of the impeller on the inner peripheral side of the outer peripheral portion, and the back surface of the impeller and the wall surface of the partition wall are first. The back surface of the impeller and the non-contact surface face each other through a second back surface gap, and a drawing passage is provided between the rotating body and the partition wall. Is formed, and the squeezing passage is open to the first back gap.

According to this, as the rotation speed of the impeller increases, the amount of gas flowing from the impeller chamber into the second back gap through the first back gap increases. The gas that has flowed into the second back gap easily stays in the second back gap by colliding with the non-contact surface of the rotating body, and is more likely to stay in the second back gap than when there is no non-contact surface. It becomes difficult for gas to flow into the shaft insertion hole. Further, the throttle passage can suppress the amount of gas flowing from the second back gap into the shaft insertion hole, suppress the amount of gas flowing into the drive chamber, and suppress a decrease in the efficiency of the fuel cell vehicle pump.

Further, regarding the fuel cell vehicle pump, the rotating body is a collar member that regulates the movement of the impeller in the axial direction of the shaft, and the collar member is the blade along the axial direction of the shaft. It has a tubular shape having a first large diameter portion and a first small diameter portion whose outer diameter gradually decreases from the vehicle side toward the drive chamber side, and the first large diameter portion is the contact surface and the contact surface. The shaft insertion hole includes the non-contact surface, and has a second large-diameter portion facing the first large-diameter portion and a second small-diameter portion facing the first small-diameter portion. The throttle passage includes a gap in which the first large-diameter portion and the second large-diameter portion face each other, and a gap in which the first small-diameter portion and the second small-diameter portion face each other, and the shaft. The diameter may be gradually reduced from the impeller side to the drive chamber side along the axial direction of the above.

According to this, as the diameter of the throttle passage is gradually reduced, a plurality of resistors that obstruct the flow of gas are formed in the throttle passage, and it becomes difficult for gas to flow through the throttle passage. Therefore, the throttle passage can suppress the amount of gas flowing from the second back gap into the shaft insertion hole.

Further, regarding the fuel cell vehicle pump, a mechanical seal adjacent to the second small diameter portion is arranged in the shaft insertion hole, and the mechanical seal includes a rotating ring that rotates integrally with the shaft and the shaft. A first fixed ring fixed to the insertion hole and a tubular cartridge covering the fixing ring and fixed to the shaft insertion hole, the cartridge being separated from the peripheral surface of the shaft and facing the first. A second inner peripheral wall that is closer to the peripheral surface of the shaft than the first inner peripheral wall, and the collar member faces the first inner peripheral wall from the peripheral surface of the shaft. Further having a tubular seal inner cylinder portion extending by the water, the drawing passage includes a gap in which the second inner peripheral wall and the peripheral surface of the shaft face each other, the first inner peripheral wall and the seal inner cylinder portion. The throttle is provided with a gap in which the first small diameter portion and the second small diameter portion face each other, and a gap in which the first large diameter portion and the second large diameter portion face each other. The passage may be gradually reduced in diameter from the impeller side to the drive chamber side along the axial direction of the shaft.

According to this, a throttle passage can be formed inside the mechanical seal, the length of the throttle passage in the axial direction is lengthened, and the amount of gas flowing from the second back gap into the shaft insertion hole is further suppressed. Can be done.

Further, regarding the fuel cell vehicle pump, the shaft has a low-speed side shaft and a high-speed side shaft, and the housing has the low-speed side shaft between the drive chamber and the impeller chamber in the axial direction of the shaft. The speed-up machine room as the drive chamber for accommodating the speed-up gear as the drive source that accelerates the power and transmits the power to the high-speed side shaft, the oil supply passage communicating with the speed-up machine room, and the speed-up. An oil pan for storing the oil supplied to the speed machine and a depressurization passage for releasing the pressure of the oil pan may be provided.

According to this, the amount of gas flowing from the second back gap into the shaft insertion hole can be suppressed, and the amount of gas flowing into the speed increaser chamber can be suppressed. Therefore, the amount of gas flowing from the speed increaser room to the oil supply passage is suppressed, and when the pressure is released from the pressure relief passage to the outside of the fuel cell vehicle pump, the gas discharged to the outside of the fuel cell vehicle pump. As a result, the amount of oil discharged with the gas is suppressed.

According to the present invention, it is possible to suppress an increase in the pressure in the back gap.

The figure which shows the pump of an embodiment. FIG. 2-2 is a cross-sectional view taken along the line 2-2 in FIG. A side sectional view showing the periphery of the color member in an enlarged manner.

Hereinafter, an embodiment in which the fuel cell vehicle pump is embodied will be described with reference to FIGS. 1 to 3. The fuel cell vehicle pump of the present embodiment is an air pump mounted on a fuel cell vehicle traveling by using a fuel cell as a power source and supplying air to the fuel cell. In the following description, the fuel cell vehicle pump is simply referred to as a "pump".

As shown in FIG. 1, the housing 11 of the pump 10 is connected to the motor housing 12, the speed-up gear housing 13 connected to the motor housing 12, the plate 14 connected to the speed-up gear housing 13, and the plate 14. The compressor housing 15 is provided. The motor housing 12, the speed increaser housing 13, the plate 14, and the compressor housing 15 are made of, for example, a metal material made of aluminum. The housing 11 has a substantially cylindrical shape. The motor housing 12, the speed increaser housing 13, the plate 14, and the compressor housing 15 are arranged in this order in the axial direction of the housing 11.

The motor housing 12 has a disk-shaped bottom wall 12a and a peripheral wall 12b that cylindrically protrudes from the outer peripheral edge of the bottom wall 12a toward the speed increaser housing 13. The speed increaser housing 13 has a disk-shaped bottom wall 13a and a peripheral wall 13b that cylindrically protrudes from the outer peripheral edge of the bottom wall 13a toward the plate 14.

The opening in the peripheral wall 12b of the motor housing 12 is closed by the bottom wall 13a of the speed increaser housing 13. A through hole 13h is formed in the central portion of the bottom wall 13a. The opening in the peripheral wall 13b of the speed increaser housing 13 is closed by the plate 14. A shaft insertion hole 14h is formed in the central portion of the plate 14.

On the compressor housing 15 side of the plate 14, a tapered surface 14j continuous with the opening edge of the shaft insertion hole 14h, an annular surface 14k continuous with the outer peripheral edge of the tapered surface 14j, and an end surface 14m continuous with the outer peripheral edge of the annular surface 14k. And are formed. The tapered surface 14j, the annular surface 14k, and the end surface 14m form the wall surface of the plate 14. The tapered surface 14j is formed in a mortar shape in which the diameter gradually increases from the opening edge of the shaft insertion hole 14h toward the inner peripheral edge of the annular surface 14k. The annular surface 14k is a radial flat surface orthogonal to the axis of the housing 11. The end surface 14m is a surface that is flat in the radial direction orthogonal to the axis of the housing 11. The annular surface 14k is recessed closer to the motor housing 12 than the end surface 14m.

The compressor housing 15 is connected to the surface of the plate 14 opposite to the speed increaser housing 13. The compressor housing 15 is formed with a suction port 15a into which air as a gas is sucked. The suction port 15a opens at the center of the end face of the compressor housing 15 opposite to the plate 14, and extends in the axial direction of the housing 11 from the center of the end face of the compressor housing 15 opposite to the plate 14. ..

The pump 10 includes a low-speed side shaft 16 and an electric motor 17 that rotates the low-speed side shaft 16. A motor chamber 12c for accommodating the electric motor 17 is formed in the housing 11. The motor chamber 12c is partitioned by an inner surface of the bottom wall 12a of the motor housing 12, an inner peripheral surface of the peripheral wall 12b, and an outer surface of the bottom wall 13a of the speed increaser housing 13. The low-speed side shaft 16 is housed in the motor housing 12 in a state where the axial direction of the low-speed side shaft 16 coincides with the axial direction of the motor housing 12. The low speed side shaft 16 is made of a metal material made of, for example, iron or an alloy.

A cylindrical boss portion 12f projects from the inner surface of the bottom wall 12a of the motor housing 12. The first end portion of the low speed side shaft 16 is inserted into the boss portion 12f. A first bearing 18 is provided between the first end portion of the low speed side shaft 16 and the boss portion 12f. The first end of the low-speed shaft 16 is rotatably supported by the bottom wall 12a of the motor housing 12 via the first bearing 18.

The second end portion of the low speed side shaft 16 is inserted into the through hole 13h of the speed increaser housing 13. A second bearing 19 is provided between the second end of the low-speed shaft 16 and the through hole 13h. The second end of the low-speed shaft 16 is rotatably supported by the bottom wall 13a of the speed increaser housing 13 via the second bearing 19. Therefore, the low speed side shaft 16 is rotatably supported by the housing 11. The second end of the low-speed side shaft 16 projects from the motor chamber 12c through the through hole 13h into the speed increaser housing 13.

A sealing member 20 is provided between the second end of the low speed shaft 16 and the through hole 13h. The seal member 20 is arranged between the second end of the low-speed shaft 16 and the through hole 13h closer to the motor chamber 12c than the second bearing 19. The seal member 20 seals between the peripheral surface of the low-speed side shaft 16 and the inner peripheral surface of the through hole 13h.

The electric motor 17 includes a cylindrical stator 21 and a rotor 22 arranged inside the stator 21. The rotor 22 is fixed to the low-speed side shaft 16 and rotates integrally with the low-speed side shaft 16. The stator 21 surrounds the rotor 22. The rotor 22 has a cylindrical rotor core 22a anchored to the low-speed side shaft 16 and a plurality of permanent magnets (not shown) provided on the rotor core 22a. The stator 21 has a cylindrical stator core 21a fixed to the inner peripheral surface of the peripheral wall 12b of the motor housing 12, and a coil 21b wound around the stator core 21a. Then, when a current flows through the coil 21b, the rotor 22 and the low-speed side shaft 16 rotate integrally.

The pump 10 includes a high-speed side shaft 31 and a speed increaser 30 that transmits the power of the low-speed side shaft 16 to the high-speed side shaft 31. The high-speed side shaft 31 is inserted into the shaft insertion hole 14h of the plate 14. A speed-up gear chamber 13c for accommodating the speed-up gear 30 is formed in the housing 11. The speed increaser chamber 13c is partitioned by an inner surface of the bottom wall 13a of the speed increaser housing 13, an inner peripheral surface of the peripheral wall 13b, and a plate 14. Oil is stored in the speed increaser chamber 13c. The seal member 20 suppresses the oil stored in the speed increaser chamber 13c from leaking into the motor chamber 12c through between the peripheral surface of the low speed side shaft 16 and the inner peripheral surface of the through hole 13h. ing.

The high speed side shaft 31 is made of a metal material made of, for example, iron or an alloy. The high-speed side shaft 31 is housed in the speed-up gear chamber 13c in a state where the axial direction of the high-speed side shaft 31 coincides with the axial direction of the speed-up gear housing 13. The end of the high-speed shaft 31 opposite to the motor housing 12 passes through the shaft insertion hole 14h of the plate 14 and projects into the compressor housing 15. The axis of the high-speed side shaft 31 coincides with the axis of the low-speed side shaft 16.

The pump 10 includes an impeller 24 fixed to the first end of the high-speed side shaft 31. An impeller chamber 15b for accommodating the impeller 24 is formed in the housing 11. The plate 14 is a partition wall that separates the impeller chamber 15b and the speed increaser chamber 13c that constitutes the drive chamber. The shaft insertion hole 14h through which the high-speed side shaft 31 is inserted is formed in the plate 14 which is a partition wall.

The pump 10 includes a mechanical seal 71 arranged in the shaft insertion hole 14h. The mechanical seal 71 suppresses the oil stored in the speed increaser chamber 13c from leaking to the impeller chamber 15b through the shaft insertion hole 14h, the tapered surface 14j, and the annular surface 14k.

The impeller chamber 15b and the suction port 15a communicate with each other. The impeller chamber 15b has a substantially truncated cone shape in which the diameter gradually increases as the distance from the suction port 15a increases. The protruding end of the high-speed shaft 31 projecting into the compressor housing 15 projects into the impeller chamber 15b.

As shown in FIG. 1 or 3, the impeller 24 has an annular base end surface 24a closer to the speed increaser 30 in the axial direction of the high-speed side shaft 31. Further, the impeller 24 includes a base end side tapered surface 24b whose diameter gradually increases from the outer peripheral edge of the base end surface 24a, and a flat surface 24c extending flatly in the radial direction from the outer peripheral edge of the base end side tapered surface 24b. Has. The back surface of the impeller 24 is formed by the base end surface 24a, the base end side tapered surface 24b, and the flat surface 24c. The impeller 24 gradually reduces in diameter from the outer peripheral edge 24d toward the tip surface 24e of the impeller 24, and has a plurality of blades (not shown).

The impeller 24 has an insertion hole 24f extending in the axial direction of the impeller 24. The impeller 24 is fixed to the high-speed side shaft 31 integrally with the high-speed side shaft 31 in a state where the protruding end portion of the high-speed side shaft 31 projecting into the compressor housing 15 is inserted into the insertion hole 24f. Therefore, the impeller 24 rotates integrally with the high-speed side shaft 31.

The base end surface 24a of the impeller 24 faces the collar member 100 in the axial direction of the high-speed side shaft 31. The color member 100 as a rotating body will be described in detail later.
The base end side tapered surface 24b of the impeller 24 and the tapered surface 14j of the plate 14 face each other via the first back gap K1, and the flat surface 24c of the impeller 24 and the annular surface 14k of the plate 14 They face each other through the first back gap K1. That is, the back surface of the impeller 24 and the wall surface of the plate 14 face each other in the axial direction via the first back surface gap K1. Further, the outer peripheral portion of the collar member 100 and a part of the base end side tapered surface 24b face each other in the axial direction via the second back surface gap K2.

The first back gap K1 and the second back gap K2 communicate with the shaft insertion hole 14h.
The impeller 24 rotates due to the rotation of the high-speed shaft 31, air is sucked into the impeller chamber 15b from the suction port 15a, and the air in the impeller chamber 15b flows into the diffuser flow path due to the rotation of the impeller 24. Sent to 25.

Further, as shown in FIG. 1, the diffuser flow path 25 is partitioned between an end surface 14 m radially outside the annular surface 14k of the plate 14 and a surface of the compressor housing 15 facing the end surface 14 m. The diffuser flow path 25 is located radially outside the high-speed side shaft 31 with respect to the impeller chamber 15b and communicates with the impeller chamber 15b. The diffuser flow path 25 is formed in an annular shape surrounding the impeller 24 and the impeller chamber 15b.

Further, the diffuser flow path 25 is located radially outside the high-speed side shaft 31 with respect to the first back gap K1 and communicates with the first back gap K1. Therefore, the diffuser flow path 25 communicates with the shaft insertion hole 14h via the first back gap K1 and the second back gap K2.

The discharge chamber 26 is located radially outside the high-speed side shaft 31 of the diffuser flow path 25 and communicates with the diffuser flow path 25. The discharge chamber 26 is annular. The impeller chamber 15b and the discharge chamber 26 communicate with each other via the diffuser flow path 25. The air sent by the impeller 24 is further compressed by passing through the diffuser flow path 25, flows into the discharge chamber 26, and is discharged from the discharge chamber 26. Further, since the diffuser flow path 25, the first back gap K1 and the second back gap K2 are continuous, the air compressed by the impeller 24 is the first back gap K1 and the first back gap K1 and the first back gap K1 from the diffuser flow path 25. It flows into the back gap K2 of 2.

As shown in FIG. 1, the speed increaser 30 accelerates the rotation of the low-speed side shaft 16 accompanying the rotation of the electric motor 17 and transmits it to the high-speed side shaft 31. Therefore, the low-speed side shaft 16 and the high-speed side shaft 31 form a shaft rotated by the electric motor 17. The impeller 24 is fixed to one end of the high-speed side shaft 31 as one end of the shaft.

Further, the electric motor 17 and the speed increaser 30 form a drive source for rotating the shaft. Therefore, a drive chamber for accommodating the drive source is configured from the accelerator chamber 13c accommodating the accelerator 30 constituting the drive source and the motor chamber 12c accommodating the electric motor 17 also constituting the drive source. There is. In this aspect, the plate 14 constitutes a partition wall that separates the speed increaser chamber 13c as a drive chamber and the impeller chamber 15b. Therefore, the speed increaser chamber 13c is arranged between the motor chamber 12c and the plate 14 in the axial direction of the low speed side shaft 16. A high-speed side shaft 31 constituting the shaft is inserted into the shaft insertion hole 14h of the plate 14.

The speed increasing machine 30 accelerates the rotation of the low speed side shaft 16 and transmits the rotation to the high speed side shaft 31. The speed increaser 30 is a so-called traction drive type (friction roller type). The speed increaser 30 includes a ring member 32 connected to the second end of the low speed side shaft 16. The ring member 32 is made of metal. The ring member 32 rotates with the rotation of the low speed side shaft 16. The ring member 32 has a bottomed cylindrical shape having a disk-shaped base 33 connected to the second end portion of the low-speed side shaft 16 and a cylindrical portion 34 extending cylindrically from the outer edge portion of the base 33. Is. The base 33 extends in the radial direction of the low speed side shaft 16 with respect to the low speed side shaft 16. The axis of the tubular portion 34 coincides with the axis of the low speed shaft 16.

As shown in FIG. 1 or 2, a part of the high-speed side shaft 31 is arranged inside the tubular portion 34. Further, the speed increaser 30 includes three rollers 35 provided between the cylinder portion 34 and the high-speed side shaft 31. The three rollers 35 are made of, for example, metal, and are made of the same metal as the high-speed side shaft 31, such as iron or an alloy of iron. The three rollers 35 are arranged at predetermined intervals (for example, 120 degrees each) in the circumferential direction of the high-speed side shaft 31. The three rollers 35 have the same shape. The three rollers 35 come into contact with both the inner peripheral surface of the tubular portion 34 and the peripheral surface of the high-speed side shaft 31.

The speed increaser 30 includes a support member 39 that rotatably supports each roller 35 in cooperation with the plate 14. The support member 39 is arranged inside the tubular portion 34. The support member 39 has a disk-shaped support base 40 and three columnar standing walls 41 erected from the support base 40. The support base 40 is arranged to face the plate 14 in the direction of the rotation axis of each roller 35. Each of the three erection walls 41 extends from the surface 40a on the plate 14 side of the support base 40 toward the plate 14. The three erection walls 41 are arranged so as to fill the three spaces partitioned by the inner peripheral surface of the tubular portion 34 and the peripheral surfaces of the two adjacent rollers. The support member 39 is attached to the plate 14 by screwing the bolt 44 inserted into the bolt insertion hole 45 into the plate 14.

The axial first end of each roller 35 is rotatably supported by the plate 14 via the roller bearing 52, and the axial second end of each roller 35 is rotatably supported by the support member 39 via the roller bearing 54. It is rotatably supported.

The high-speed side shaft 31 is provided with a pair of flange portions 31f arranged so as to face each other so as to be separated from each other in the axial direction of the high-speed side shaft 31. The three rollers 35 are sandwiched by a pair of flange portions 31f. As a result, the misalignment between the high-speed side shaft 31 and the three rollers 35 in the axial direction of the high-speed side shaft 31 is suppressed.

The three rollers 35, the ring member 32, and the high-speed side shaft 31 are unitized in a state where the three rollers 35, the high-speed side shaft 31, and the tubular portion 34 are pressed against each other. The high-speed side shaft 31 is rotatably supported by three rollers 35.

Then, when the electric motor 17 is driven and the low-speed side shaft 16 and the ring member 32 rotate, the rotational force of the ring member 32 is transmitted to the three rollers 35 to rotate the three rollers 35, and the three rollers 35. The rotational force of is transmitted to the high-speed side shaft 31. As a result, the high-speed side shaft 31 rotates. At this time, the ring member 32 rotates at the same speed as the low speed side shaft 16, and the three rollers 35 rotate at a higher speed than the low speed side shaft 16. Then, the high-speed side shaft 31, whose outer diameter is smaller than the outer diameter of the three rollers 35, rotates at a higher speed than the three rollers 35. As a result, the speed increaser 30 causes the high-speed side shaft 31 to rotate at a higher speed than the low-speed side shaft 16.

As shown in FIG. 1, the pump 10 includes an oil supply passage 60 for supplying oil to the speed increaser 30. The oil supply passage 60 also supplies oil to the mechanical seal 71. Further, the pump 10 sucks up and discharges the oil cooler 55 that cools the oil flowing through the oil supply passage 60, the oil pan 56 that stores the oil flowing through the oil supply passage 60, and the oil stored in the oil pan 56. It includes an oil pump 57 and a pressure relief passage 77 for releasing the pressure of the oil pan 56.

The oil cooler 55 has a bottomed cylindrical cover member 55a attached to the outer peripheral surface of the peripheral wall 12b of the motor housing 12. The space 55b is partitioned by the inner surface of the cover member 55a and the outer peripheral surface of the peripheral wall 12b of the motor housing 12. Further, the oil cooler 55 has a cooling pipe 55c arranged in the space 55b. Both ends of the cooling pipe 55c are supported by the motor housing 12. The cooling pipe 55c forms a part of the oil supply passage 60.

Further, the cover member 55a is provided with an introduction pipe 55d and a discharge pipe 55e. A low temperature fluid is introduced into the space 55b from the introduction pipe 55d. The low-temperature fluid introduced into the space 55b is discharged from the discharge pipe 55e, cooled by a cooling device (not shown), and then introduced into the space 55b again via the introduction pipe 55d. The cold fluid is, for example, water.

The oil pan 56 stores the oil to be supplied to the speed increaser 30. The oil pan 56 is installed on the bottom wall 12a of the motor housing 12. The oil pan 56 is located on the outer peripheral side of the bottom wall 12a of the motor housing 12. Further, the oil pump 57 is installed on the bottom wall 12a of the motor housing 12. The oil pump 57 is, for example, a trochoidal pump. The oil pump 57 is connected to the first end of the low speed shaft 16. Then, the oil pump 57 is driven as the low-speed side shaft 16 rotates.

The oil supply passage 60 has a first connection passage 61 that connects the speed increaser chamber 13c and the oil cooler 55. The first connection passage 61 penetrates the speed increaser housing 13 and extends to the inside of the peripheral wall 12b of the motor housing 12. The first end of the first connecting passage 61 is open in the speed increaser chamber 13c. The second end of the first connection passage 61 is connected to the first end of the cooling pipe 55c.

The pump 10 is mounted on the fuel cell vehicle so that the portion of the first connecting passage 61 that opens into the speed increaser chamber 13c is located on the lower side in the direction of gravity. Therefore, the oil in the speed increaser chamber 13c flows into the first connecting passage 61.

The oil supply passage 60 has a second connection passage 62 that connects the oil cooler 55 and the oil pan 56. The second connection passage 62 is formed inside the motor housing 12. The first end of the second connection passage 62 is connected to the second end of the cooling pipe 55c. The second end of the second connecting passage 62 is open in the oil pan 56.

The oil stored in the speed increaser chamber 13c flows into the first connecting passage 61 and passes through the first connecting passage 61, the cooling pipe 55c, and the second connecting passage 62. Here, the oil passing through the cooling pipe 55c is cooled by heat exchange with the low temperature fluid introduced into the space 55b of the oil cooler 55. Then, the oil cooled by the oil cooler 55 is stored in the oil pan 56.

The oil supply passage 60 has a third connection passage 63 that connects the oil pan 56 and the oil pump 57. The third connection passage 63 is formed inside the motor housing 12. The first end of the third connecting passage 63 projects into the oil pan 56. The second end of the third connection passage 63 is connected to the suction port 57a of the oil pump 57.

The oil supply passage 60 has a fourth connection passage 64 connected to the discharge port 57b of the oil pump 57. The fourth connection passage 64 penetrates the bottom wall 12a and the peripheral wall 12b of the motor housing 12 and extends to the inside of the peripheral wall 13b of the speed increaser housing 13. The first end of the fourth connection passage 64 is connected to the discharge port 57b of the oil pump 57. The second end of the fourth connecting passage 64 is located inside the peripheral wall 13b of the speed increaser housing 13.

The oil supply passage 60 has a first branch passage 65 and a second branch passage 66 that branch from the second end of the fourth connection passage 64. The first branch passage 65 extends from the second end of the fourth connection passage 64 toward the motor housing 12, and penetrates the peripheral wall 13b of the speed increaser housing 13 and the bottom wall 13a of the speed increaser housing 13. .. The first end of the first branch passage 65 communicates with the second end of the fourth connecting passage 64. The second end of the first branch passage 65 is open to the through hole 13h.

The second branch passage 66 extends from the second end of the fourth connecting passage 64 toward the plate 14, penetrates the peripheral wall 13b of the speed increaser housing 13, and extends to the inside of the plate 14. The first end of the second branch passage 66 communicates with the second end of the fourth connecting passage 64. The second end of the second branch passage 66 is located inside the plate 14.

The oil supply passage 60 has a common passage 67 communicating with the other end of the second branch passage 66. The common passage 67 extends in a direction orthogonal to the second branch passage 66 and linearly extends downward from the second end of the second branch passage 66 in the direction of gravity. Further, the oil supply passage 60 has a seal member side supply passage 69 and a speed increaser side supply passage 70 branching from the common passage 67. The first end of the seal member side supply passage 69 communicates with the common passage 67. The second end of the seal member side supply passage 69 is opened in the shaft insertion hole 14h. The speed increaser side supply passage 70 extends linearly from the common passage 67 toward the side opposite to the compressor housing 15 and penetrates the plate 14 and penetrates the erection wall 41 of the rollers 35 in the erection wall 41. It opens at a position facing the outer peripheral surface. Therefore, the speed increaser side supply passage 70 communicates with the speed increaser room 13c.

When the electric motor 17 is driven, the oil pump 57 is driven by the rotation of the low-speed side shaft 16, and the oil stored in the oil pan 56 passes through the third connection passage 63 and the suction port 57a. It is sucked into the inside and discharged to the fourth connection passage 64 through the discharge port 57b. The oil pump 57 is driven so that the amount of oil discharged from the discharge port 57b increases proportionally as the rotation speed of the low-speed side shaft 16 increases. Then, the oil discharged to the fourth connecting passage 64 flows through the fourth connecting passage 64 and is distributed to the first branch passage 65 and the second branch passage 66, respectively.

The oil distributed from the fourth connecting passage 64 to the first branch passage 65 flows through the first branch passage 65, flows into the through hole 13h, and is supplied to the seal member 20 and the second bearing 19. As a result, the lubrication of the sliding portion between the seal member 20 and the low speed side shaft 16 and the sliding portion between the second bearing 19 and the low speed side shaft 16 becomes good.

The oil distributed from the fourth connecting passage 64 to the second branch passage 66 flows into the common passage 67 via the second branch passage 66. A part of the oil flowing through the common passage 67 is distributed to the seal member side supply passage 69, and the other oil flows through the speed increaser side supply passage 70. The oil distributed from the common passage 67 to the seal member side supply passage 69 flows through the seal member side supply passage 69, flows into the shaft insertion hole 14h, and is supplied to the mechanical seal 71. Further, the oil flowing through the speed increaser side supply passage 70 is supplied to the outer peripheral surface of the roller 35. As a result, the lubrication of the sliding portion between the roller 35 and the high-speed side shaft 31 becomes good. The oil supplied to the outer peripheral surfaces of the mechanical seal 71 and the roller 35 is returned to the speed increaser chamber 13c.

The pump 10 includes a pressure relief passage 77 for releasing the pressure of the oil pan 56. The first end of the pressure relief passage 77 communicates with the oil pan 56, and the second end of the pressure relief passage 77 opens to the outer surface of the bottom wall 12a of the motor housing 12 and communicates with the outside. A ventilation membrane 77a is attached to the second end of the pressure relief passage 77. The ventilation membrane 77a suppresses the invasion of foreign matter into the pressure relief passage 77 from the outside. Further, the pressure relief passage 77 is provided with a check valve (not shown). The check valve opens the pressure relief passage 77 when the pressure in the pressure relief passage 77, that is, the pressure in the oil supply passage 60 reaches a predetermined value, and closes the pressure relief passage 77 when the pressure is less than the default value.

The mechanical seal 71 includes a rotating ring 81 that rotates integrally with the high-speed side shaft 31, and a fixed ring 91 that is fixed to the shaft insertion hole 14h. The rotary ring 81 is integrally formed with the high-speed side shaft 31. The rotating ring 81 is an annular shape. The fixed ring 91 is arranged to face the rotating ring 81 in the axial direction of the high-speed side shaft 31 and is fixed to the inner peripheral surface of the shaft insertion hole 14h in a state of surrounding the high-speed side shaft 31. Therefore, the fixed ring 91 is arranged closer to the impeller chamber 15b than the rotating ring 81.

As shown in FIG. 3, the mechanical seal 71 includes a spring 72 that presses the fixed ring 91 toward the rotary ring 81, a spring holding portion 73 that holds the spring 72, and the fixed ring 91 together with the spring 72 and the spring holding portion 73. It is provided with a tubular cartridge 74 fixed to the shaft insertion hole 14h in a state of covering the above.

The cartridge 74 has an annular bottom wall 74a extending in the radial direction of the high-speed side shaft 31 and a first cylindrical inner peripheral wall 74b that rises from the inner peripheral edge of the bottom wall 74a toward the rotary ring 81. doing. Further, the cartridge 74 has an annular step wall 74c extending in the radial direction of the high-speed side shaft 31 from the first inner peripheral wall 74b, and a cylindrical first wall rising from the inner peripheral edge of the step wall 74c toward the rotary ring 81. It has 2 inner peripheral walls 74d. The second inner peripheral wall 74d is provided at a position closer to the peripheral surface of the high-speed side shaft 31 along the radial direction of the high-speed side shaft 31 than the first inner peripheral wall 74b. The first inner peripheral wall 74b, the stepped wall 74c, and the second inner peripheral wall 74d provided on the inner peripheral side of the cartridge 74 are radially separated from the peripheral surface of the high-speed side shaft 31 and face each other. The first inner peripheral wall 74b is separated from the peripheral surface of the high-speed side shaft 31 with respect to the second inner peripheral wall 74d. The high-speed side shaft 31 passes inside the bottom wall 74a, the first inner peripheral wall 74b, the stepped wall 74c, and the second inner peripheral wall 74d.

Further, the cartridge 74 has a cylindrical outer peripheral wall 74e that rises from the outer peripheral edge of the bottom wall 74a toward the rotating ring 81. The outer peripheral wall 74e extends along the inner peripheral surface of the shaft insertion hole 14h. The cartridge 74 is fixed to the shaft insertion hole 14h by fitting the outer peripheral wall 74e to the inner peripheral surface of the shaft insertion hole 14h.

A seal inner gap 76 is formed between the inner peripheral surface of the second inner peripheral wall 74d of the cartridge 74 and the peripheral surface of the high-speed side shaft 31 facing the inner peripheral surface. The seal inner gap 76 is open toward the rotary ring 81.

The fixed ring 91, the spring 72, and the spring holding portion 73 are partitioned by the bottom wall 74a, the inner peripheral surface of the first inner peripheral wall 74b, the inner peripheral surface of the second inner peripheral wall 74d, and the inner peripheral surface of the outer peripheral wall 74e. It is arranged in the space. Further, the fixed ring 91, the spring 72, and the spring holding portion 73 are covered with the cartridge 74. The cartridge 74 holds the fixed ring 91 so as not to rotate integrally with the high-speed side shaft 31 in a state where the cartridge 74 can move in the axial direction of the high-speed side shaft 31. Therefore, the fixed ring 91 is allowed to move in the axial direction of the high-speed side shaft 31, while the movement of the high-speed side shaft 31 in the circumferential direction is restricted.

The spring 72 and the spring holding portion 73 are arranged between the bottom wall 74a of the cartridge 74 and the fixed ring 91. The spring holding portion 73 is in contact with the fixed ring 91, and the spring 72 connects the spring holding portion 73 and the bottom wall 74a. As a result, the urging force of the spring 72 is transmitted to the fixed ring 91 via the spring holding portion 73, and the fixed ring 91 is pressed toward the rotating ring 81.

The end surface 81a on the fixed ring 91 side of the rotating ring 81 has a flat surface-shaped rotating surface 82 that slides on the fixed ring 91. The end surface 91a on the rotation ring 81 side of the fixed ring 91 has a flat surface-like fixed side sliding surface 92 that slides with the rotation side sliding surface 82. The fixed side sliding surface 92 has a sealing surface 92s with the rotating side sliding surface 82.

Further, a part of the inner peripheral surface of the fixed ring 91 is recessed outward in the radial direction of the high-speed side shaft 31. An annular sealing member is formed between the portion of the inner peripheral surface of the fixed ring 91 that is recessed outward in the radial direction of the high-speed side shaft 31, the inner surface of the stepped wall 74c, and the inner peripheral surface of the second inner peripheral wall 74d. 75 is provided.

The second end of the seal member side supply passage 69 is open to the inner peripheral surface of the shaft insertion hole 14h. Therefore, the second end of the seal member side supply passage 69 faces the sliding portion between the rotating side sliding surface 82 and the fixed side sliding surface 92 in the radial direction of the high speed side shaft 31. Then, oil is injected from the second end of the seal member side supply passage 69 toward the inside of the shaft insertion hole 14h.

When the rotary ring 81 rotates with the rotation of the high-speed shaft 31, a positive pressure is generated between the rotating side sliding surface 82 and the fixed side sliding surface 92, and the rotating side sliding surface 82 and the fixed side sliding surface 82. The distance from the surface 92 is widened, and an oil film is formed between the rotating side sliding surface 82 and the fixed side sliding surface 92, and the sealing surface 92s of the rotating side sliding surface 82 and the fixed side sliding surface 92 is formed. The slidability between the two is improved.

Further, when the rotary ring 81 rotates with the rotation of the high-speed side shaft 31, the oil interposed between the rotary side sliding surface 82 and the fixed side sliding surface 92 moves following the rotation of the rotary ring 81. Then, the inside of the negative pressure generating groove (not shown) becomes negative pressure, and the oil that is about to leak from the speed increasing machine chamber 13c into the impeller chamber 15b through the shaft insertion hole 14h enters the negative pressure generating groove. It becomes easy to be inhaled.

Then, the oil sucked into the negative pressure generating groove is discharged to the outside in the radial direction of the high-speed side shaft 31 with respect to the outer peripheral surface of the fixed ring 91. As a result, the oil stored in the speed increaser chamber 13c is prevented from leaking into the impeller chamber 15b via the space between the rotating side sliding surface 82 and the sealing surface 92s of the fixed side sliding surface 92. Will be done.

As shown in FIG. 3, the shaft insertion hole 14h has a second large-diameter portion 141h connected to the inner peripheral edge of the tapered surface 14j, and a second small-diameter portion 142h having a diameter smaller than that of the second large-diameter portion 141h. doing. The mechanical seal 71 is adjacent to the second small diameter portion 142h in the axial direction. Further, the shaft insertion hole 14h has a holding portion 143h having a diameter larger than that of the second large diameter portion 141h and the second small diameter portion 142h, and a communication portion 144h having a diameter larger than that of the holding portion 143h. Further, the shaft insertion hole 14h has an annular first step surface 151 extending in the radial direction of the high-speed side shaft 31 so as to connect the second large diameter portion 141h and the second small diameter portion 142h, and the second small diameter portion. It has an annular second stepped surface 152 extending in the radial direction of the high-speed side shaft 31 so as to connect the portion 142h and the holding portion 143h. Further, the shaft insertion hole 14h has an annular third stepped surface 153 extending in the radial direction of the high-speed side shaft 31 so as to connect the holding portion 143h and the communicating portion 144h.

The second large diameter portion 141h communicates with the tapered surface 14j. The communication portion 144h is open toward the speed increaser room 13c. The axis of the second large-diameter portion 141h, the axis of the second small-diameter portion 142h, the axis of the holding portion 143h, and the axis of the communication portion 144h coincide with the rotation axis of the high-speed side shaft 31. There is.

One of the pair of flange portions 31f is arranged in the communication portion 144h.
The high-speed side shaft 31 includes a shaft step 31 g formed by changing the diameter of the high-speed side shaft 31 closer to the impeller 24 than the flange portion 31f in the axial direction of the high-speed side shaft 31. The collar member 100 is integrated with the high-speed side shaft 31 in a state in which movement in the axial direction is restricted by contacting the shaft step 31g.

The collar member 100 is gap-fitted into the high-speed side shaft 31 and fixed to the high-speed side shaft 31. Therefore, the collar member 100 rotates integrally with the high-speed side shaft 31. The collar member 100 is arranged in the shaft insertion hole 14h. Therefore, a collar member 100 as a rotating body that rotates integrally with the high-speed side shaft 31 is interposed between the shaft insertion hole 14h and the high-speed side shaft 31.

The collar member 100 includes a first large diameter portion 101 located inside the second large diameter portion 141h, a first small diameter portion 102 located inside the second small diameter portion 142h, and a first cartridge 74. The seal inner cylinder portion 103 located inside the inner peripheral wall 74b of the above is integrally provided. That is, the shaft insertion hole 14h has a second large diameter portion 141h facing the first large diameter portion 101 and a second small diameter portion 142h facing the first small diameter portion 102. I can say.

The outer diameter of the first large diameter portion 101 is larger than the outer diameter of the proximal end surface 24a. Therefore, the outer peripheral portion of the first large-diameter portion 101 protrudes in the radial direction of the high-speed side shaft 31 from the base end surface 24a of the impeller 24. The collar member 100 has a non-contact surface H1 on the outer peripheral portion of the first large diameter portion 101. The non-contact surface H1 is a portion of the first large-diameter portion 101 that faces a part of the proximal end side tapered surface 24b as the back surface of the impeller 24 and does not abut on the proximal end side tapered surface 24b. .. Further, the collar member 100 has a contact surface H2 on the inner peripheral side of the outer peripheral portion of the first large diameter portion 101. The contact surface H2 is a portion that contacts the base end surface 24a as the back surface of the impeller 24. That is, the collar member 100 includes a non-contact surface H1 and a contact surface H2 on the first large diameter portion 101.

A part of the base end side tapered surface 24b of the impeller 24 and the non-contact surface H1 face each other in the axial direction of the high-speed side shaft 31 via the second back surface gap K2. In the radial direction of the high-speed side shaft 31, the boundary T between the first back gap K1 and the second back gap K2 is the outer circumference of the first large diameter portion 101 as shown by the two-dot chain line in FIG. It is formed along the surface.

The collar member 100 has a first large diameter portion 101 and a first large diameter portion 101 whose outer diameter gradually decreases from the impeller 24 side toward the speed increaser chamber 13c as a drive chamber along the axial direction of the high speed side shaft 31. It can be said that it has a tubular shape having a small diameter portion 102 and a seal inner cylinder portion 103. The seal inner cylinder portion 103 has a cylindrical shape extending from the peripheral surface of the high-speed side shaft 31 toward the first inner peripheral wall 74b along the radial direction.

Further, the collar member 100 includes a first connection surface 104 that connects the outer peripheral surface of the first large diameter portion 101 and the outer peripheral surface of the first small diameter portion 102, the outer peripheral surface of the first small diameter portion 102, and the inside of the seal. It has a second connection surface 105 that connects to the outer peripheral surface of the tubular portion 103.

The color member 100 is restricted from moving in the axial direction of the high-speed side shaft 31 by coming into contact with the shaft step 31g. When the base end surface 24a of the impeller 24 comes into contact with the contact surface H2 of the color member 100 whose movement is restricted, the impeller 24 is restricted from moving in the axial direction of the high-speed side shaft 31.

A first annular gap S1 is formed between the outer peripheral surface of the first large diameter portion 101 of the collar member 100 and the inner peripheral surface of the second large diameter portion 141h, and the first small diameter portion of the collar member 100 is formed. A second annular gap S2 is formed between the outer peripheral surface of 102 and the inner peripheral surface of the second small diameter portion 142h. Further, a third annular gap S3 is formed between the outer peripheral surface of the seal inner cylinder portion 103 of the color member 100 and the first inner peripheral wall 74b of the cartridge 74.

Further, a first communication gap M1 is formed between the first connection surface 104 of the collar member 100 and the first step surface 151 of the shaft insertion hole 14h. The first communication gap M1 communicates the first annular gap S1 and the second annular gap S2. A second communication gap M2 is formed between the second connection surface 105 of the color member 100 and the bottom wall 74a of the cartridge 74. The second communication gap M2 communicates the second annular gap S2 and the third annular gap S3.

The dimensions of the first annular gap S1 along the radial direction of the high-speed side shaft 31, the dimensions of the second annular gap S2, and the dimensions of the third annular gap S3 are all equal or substantially equal, and are in the axial direction of the high-speed side shaft 31. The dimensions of the first communication gap M1 and the dimensions of the second communication gap M2 along the same are equal or substantially equal. Then, the dimensions of the first to third annular gaps S1 to S3 along the radial direction of the high-speed side shaft 31 and the dimensions of the first and second communication gaps M1 and M2 along the axial direction of the high-speed side shaft 31 are equal to or equal to each other. Approximately equal.

A throttle passage 110 is formed between the collar member 100 and the plate 14 in the radial direction. Specifically, the throttle passage 110 is formed between the outer peripheral surface of the collar member 100, the inner peripheral surface of the plate 14 forming the shaft insertion hole 14h, and a part of the inner peripheral surface of the cartridge 74. The throttle passage 110 is formed radially outside the collar member 100.

The throttle passage 110 has a first annular gap S1 in which the first large diameter portion 101 and the second large diameter portion 141h face each other, and a second small diameter portion 102 and the second small diameter portion 142h facing each other. An annular gap S2 is provided. Further, in the present embodiment, the throttle passage 110 includes a third annular gap S3 and a second inner peripheral wall 74d in which the first inner peripheral wall 74b and the seal inner cylinder portion 103 face each other, and the peripheral surface of the high-speed side shaft 31. The seal inner gap 76 is provided so as to face each other. That is, the throttle passage 110 is formed by communicating the first annular gap S1, the second annular gap S2, the third annular gap S3, and the seal inner gap 76. The first annular gap S1 constituting the throttle passage 110 is open to the first back gap K1.

The throttle passage 110 communicates the seal inner gap 76 with the first back surface gap K1. The seal inner gap 76 communicates with the communication portion 144h via between the rotating ring 81 and the fixed ring 91 of the mechanical seal 71. Therefore, the gap 76 in the seal and the communication portion 144h communicate with each other. Since the communication portion 144h and the speed increaser chamber 13c communicate with each other, the first back gap K1 and the speed increaser chamber 13c communicate with each other via the throttle passage 110 and the communication portion 144h.

The throttle passage 110 communicates the speed increaser chamber 13c with the first rear gap K1, while stepwise from the impeller 24 side toward the speed increaser chamber 13c side along the axial direction of the high speed side shaft 31. The diameter is reduced to. Further, the throttle passage 110 has a constant passage width at any position connecting the communication portion 144h and the first back surface gap K1.

The dimensions of the first to third annular gaps S1 to S3, which are the passage widths of the throttle passage 110, and the dimensions of the first and second communication gaps M1 and M2 are smaller than the narrowest passage width in the first back gap K1. Is also narrow. The narrowest passage width of the first back gap K1 is the dimension between the annular surface 14k and the flat surface 24c. Therefore, the air flowing from the first back gap K1 toward the speed increaser 30 is throttled by the throttle passage 110. The throttle passage 110 makes the flow rate of air in the shaft insertion hole 14h smaller than the flow rate of air in the first back gap K1.

Next, the operation of this embodiment will be described.
When the electric motor 17 is driven, the oil pump 57 is driven by the rotation of the low-speed side shaft 16, the oil circulates in the oil supply passage 60, and the oil slides between the seal member 20 and the low-speed side shaft 16. It is supplied to the moving portion and the sliding portion between the second bearing 19 and the low-speed side shaft 16, and the lubrication of each sliding portion becomes good. Further, the oil is supplied to the mechanical seal 71 and the roller 35. As a result, the lubrication of the sliding portion between the roller 35 and the high-speed side shaft 31 becomes good. The oil supplied to the outer peripheral surfaces of the mechanical seal 71 and the roller 35 is returned to the speed increaser chamber 13c.

During the operation of the pump 10, air is sent as the impeller 24 rotates. The air sent by the impeller 24 is compressed by the diffuser flow path 25 and sent to the discharge chamber 26. The air passing through the diffuser flow path 25 flows into the first back gap K1 and flows into the second back gap K2. At this time, in the second back gap K2, the air flowing into the second back gap K2 collides with the non-contact surface H1 of the collar member 100 and stays in the vicinity of the second back gap K2. Further, even if air flows into the second back gap K2, the flow of air into the shaft insertion hole 14h is suppressed by the throttle passage 110 communicating with the first back gap K1.

According to the above embodiment, the following effects can be obtained.
(1) By colliding the air flowing into the second back gap K2 with the non-contact surface H1 of the collar member 100, the air can be retained in the second back gap K2, and the first back gap K1 can be retained. It is possible to prevent air from flowing into the shaft insertion hole 14h. Further, the throttle passage 110 can suppress the amount of air flowing from the first back surface gap K1 into the shaft insertion hole 14h, and can suppress a decrease in the efficiency of the pump 10. Further, even if the mechanical seal 71 allows the air in the shaft insertion hole 14h to leak to the speed increaser chamber 13c, the amount of air toward the speed increaser chamber 13c is suppressed by the throttle passage 110 to suppress the first back gap. The amount of gas leaking from K1 to the speed increaser chamber 13c can be suppressed. As a result, the amount of gas flowing from the speed increaser chamber 13c to the oil supply passage 60 is suppressed, and when the pressure is released from the depressurization passage 77 to the outside of the pump 10, the amount of air discharged to the outside of the pump 10 is reduced. As a result of being suppressed, the amount of oil discharged with the air is suppressed. Therefore, it is possible to suppress a decrease in the amount of oil circulating in the oil supply passage 60. Further, it is possible to prevent the ventilation membrane 77a from being clogged by the oil mist.

(2) The throttle passage 110 has a stepped shape in which the outer diameter gradually decreases from the impeller 24 side toward the speed increaser chamber 13c side. Therefore, the throttle passage 110 can be formed into a plurality of stages, and air can be prevented from flowing through the throttle passage 110.

(3) In the throttle passage 110, the collar member 100 has a stepped shape, and the shaft insertion hole 14h and the cartridge 74 of the mechanical seal 71 have a stepped shape so as to face the outer peripheral surface of the collar member 100. It is formed. The collar member 100 is a member for restricting the movement of the impeller 24. By using the existing collar member 100, it is possible to suppress the amount of oil discharged to the outside of the pump 10 when the pressure is released from the pressure relief passage 77 to the outside of the pump 10 without increasing the number of parts.

(4) The color member 100 includes a seal inner cylinder portion 103 that enters the cartridge 74 of the mechanical seal 71, and a throttle passage 110 is also provided between the seal inner cylinder portion 103 and the first inner peripheral wall 74b of the cartridge 74. Part is formed. Therefore, the throttle passage 110 can be formed inside the mechanical seal 71, and the length of the throttle passage 110 in the axial direction is lengthened to further increase the amount of air flowing from the first back surface gap K1 into the shaft insertion hole 14h. It can be suppressed.

(5) The throttle passage 110 directly communicates with the first back gap K1. Therefore, the air that has flowed into the first back gap K1 collides with the non-contact surface H1 of the collar member 100 and stays in the second back gap K2, but the staying air stays in the first back gap K2. It becomes difficult for the air to flow from the gap K1 into the shaft insertion hole 14h. Therefore, by using the collar member 100 and the throttle passage 110 together, the amount of air flowing from the first back surface gap K1 into the shaft insertion hole 14h can be further suppressed.

(6) The passage width of the throttle passage 110 is narrower than the width of the first back gap K1. Therefore, the throttle passage 110 makes it difficult for air to flow from the first back gap K1 into the shaft insertion hole 14h.

This embodiment can be modified and implemented as follows. The present embodiment and the following modified examples can be implemented in combination with each other within a technically consistent range.
○ The throttle passage 110 does not have to be inside the mechanical seal 71. The seal inner cylinder portion 103 of the color member 100 may be deleted, and the throttle passage 110 may be composed of the first annular gap S1 and the second annular gap S2.

The collar member 100 may be composed of only the first large diameter portion 101, and the throttle passage 110 may be composed of only the first annular gap S1.
○ The high-speed side shaft 31 itself may be formed into a stepped shape to form a rotating body, and the collar member 100 may be deleted. In this case, the throttle passage 110 is formed by utilizing the step provided on the high-speed side shaft 31.

○ The pump 10 may not be provided with the speed increaser 30, and may have a configuration in which the shaft is directly rotated by the electric motor 17. In this case, the speed-up gear housing 13 of the housing 11 is omitted, and the speed-up gear chamber 13c is also omitted. The drive source is composed of only the electric motor 17, and the drive chamber is composed of only the motor chamber 12c.

Next, the technical idea that can be grasped from the above embodiment and another example will be added below.
(1) The drive source includes an electric motor.

H1 ... non-contact surface, H2 ... contact surface, K1 ... first back gap, K2 ... second back gap, S1 ... first annular gap, S2 ... second annular gap, S3 ... third annular gap, 10 ... Fuel cell vehicle pump, 11 ... Housing, 12c ... Motor chamber constituting the drive chamber, 13c ... Accelerator chamber constituting the drive chamber, 14 ... Plate as a partition wall, 14h ... Shaft insertion hole, 15b ... Impeller chamber, 16 ... Low-speed shaft constituting the shaft, 17 ... Electric motor constituting the drive source, 24 ... Impeller, 24a ... Base end surface forming the back surface, 24b ... Base end side tapered surface forming the back surface, 24c ... Flat surface constituting the back surface, 30 ... Speed increasing machine constituting the drive source, 31 ... High-speed side shaft constituting the shaft, 56 ... Oil pan, 60 ... Oil supply passage, 71 ... Mechanical seal, 74 ... Cartridge, 74b ... 1st inner peripheral wall, 74d ... 2nd inner peripheral wall, 76 ... Seal inner gap, 77 ... Pressure release passage, 81 ... Rotating ring, 91 ... Fixed ring, 100 ... Color member as a rotating body, 101 ... First 1 large diameter portion, 102 ... first small diameter portion, 103 ... seal inner cylinder portion, 110 ... throttle passage, 141h ... second large diameter portion, 142h ... second small diameter portion.

Claims (4)

An impeller fixed to one end of the shaft and
A partition wall including an impeller chamber for accommodating the impeller and a drive chamber for accommodating a drive source for rotating the shaft, and having a shaft insertion hole for partitioning the impeller chamber and the drive chamber and for inserting the shaft. A fuel cell vehicle pump having a housing provided.
A rotating body that is fixed to the shaft and rotates integrally with the shaft is interposed between the shaft insertion hole and the shaft.
The rotating body hits the non-contact surface that faces the back surface of the impeller on the outer peripheral portion and does not abut on the back surface of the impeller, and the back surface of the impeller on the inner peripheral side of the outer peripheral portion. Has a contact surface that comes into contact with
The back surface of the impeller and the wall surface of the partition wall face each other through the first back surface gap, and are opposed to each other.
The back surface of the impeller and the non-contact surface face each other through a second back surface gap, and are opposed to each other.
A pump for a fuel cell vehicle, characterized in that a throttle passage is formed between the rotating body and the partition wall, and the throttle passage is open to the first back gap. The rotating body is a collar member that regulates the movement of the impeller in the axial direction of the shaft.
The collar member has a tubular shape having a first large diameter portion and a first small diameter portion whose outer diameter gradually decreases from the impeller side to the drive chamber side along the axial direction of the shaft. And
The first large diameter portion includes the contact surface and the non-contact surface.
The shaft insertion hole has a second large diameter portion facing the first large diameter portion and a second small diameter portion facing the first small diameter portion.
The throttle passage includes a gap in which the first large-diameter portion and the second large-diameter portion face each other, and a gap in which the first small-diameter portion and the second small-diameter portion face each other, and the shaft. The fuel cell vehicle pump according to claim 1, wherein the diameter is gradually reduced from the impeller side to the drive chamber side along the axial direction of the above. A mechanical seal adjacent to the second small diameter portion is arranged in the shaft insertion hole.
The mechanical seal includes a rotating ring that rotates integrally with the shaft, a fixed ring that is fixed to the shaft insertion hole, and a cylindrical cartridge that covers the fixed ring and is fixed to the shaft insertion hole. However, the cartridge includes a first inner peripheral wall that faces away from the peripheral surface of the shaft, and a second inner peripheral wall that is closer to the peripheral surface of the shaft than the first inner peripheral wall.
The collar member further has a tubular seal inner cylinder portion extending from the peripheral surface of the shaft toward the first inner peripheral wall.
The throttle passage has a gap in which the second inner peripheral wall and the peripheral surface of the shaft face each other, a gap in which the first inner peripheral wall and the seal inner cylinder portion face each other, the first small diameter portion and the first small diameter portion. It is provided with a gap in which the second small diameter portion faces each other and a gap in which the first large diameter portion and the second large diameter portion face each other.
The fuel cell vehicle pump according to claim 2, wherein the throttle passage is gradually reduced in diameter from the impeller side to the drive chamber side along the axial direction of the shaft. The shaft has a low-speed side shaft and a high-speed side shaft.
The housing accommodates a speed increaser as a drive source that accelerates the power of the low speed side shaft and transmits it to the high speed side shaft between the drive chamber and the impeller chamber in the axial direction of the shaft. A speed increaser room as the drive chamber, an oil supply passage communicating with the speed increaser room, an oil pan for storing oil to be supplied to the speed increaser, and a pressure release passage for releasing the pressure of the oil pan. The fuel cell vehicle pump according to any one of claims 1 to 3.

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