Patent Application
20200102964
This application claims priority to Japanese Patent Application No. 2018-185311 filed on Sep. 28, 2018, the entire disclosure of which is incorporated herein by reference.
The present disclosure relates to a centrifugal compressor.
A centrifugal compressor includes a low-speed shaft, an impeller integrally rotating with a high-speed shaft to compress gas, and a speed increaser transmitting power of the low-speed shaft to the high-speed shaft. A housing of the centrifugal compressor has therein an impeller chamber accommodating the impeller and a speed increaser chamber accommodating the speed increaser. The impeller chamber is separated from the speed increaser chamber by a separation wall. The separation wall has a shaft insertion hole extending therethrough. The high-speed shaft extends from the speed increaser chamber into the impeller chamber through the shaft insertion hole.
Japanese Patent Application Publication No. 2016-186238 discloses the above-described centrifugal compressor, in which oil is supplied to the speed increaser to prevent friction and seizure of a sliding area between the high-speed shaft and the speed increaser. The centrifugal compressor includes an oil pan for storing therein oil to be supplied to the speed increaser chamber, an oil supply passage through which the oil stored in the oil pan is supplied to the speed increaser chamber, and an oil return passage through which the oil in the speed increaser chamber is returned to the oil pan. The oil is supplied to the speed increaser in the speed increaser chamber from the oil pan through the oil supply passage, stored in the speed increaser chamber, and returned to the oil pan through the oil return passage. A seal member is disposed between the outer circumferential surface of the high-speed shaft and the inner circumferential surface of the shaft insertion hole. The seal member prevents leakage of the oil stored in the speed increaser chamber into the impeller chamber through the shaft insertion hole.
However, pressure in the impeller chamber is increased as gas is compressed with rotation of the impeller, so that gas may leak from the impeller chamber into the speed increaser chamber through a gap between the outer circumferential surface of the high-speed shaft and the inner circumferential surface of the shaft insertion hole. This leakage increases the pressure in the speed increaser chamber. Then, under the circumstances where pressure of the impeller chamber is lower than that of the speed increaser chamber, for example, the impeller rotates at a low speed or the operation of the centrifugal compressor stops, oil in the speed increaser chamber may leak into the impeller chamber through the gap between the outer circumferential surface of the high-speed shaft and the inner circumferential surface of the shaft insertion hole.
One idea to restrict an increase of the pressure in the speed increaser chamber is to form a pressure reduction passage communicating with the oil pan and the outside in the centrifugal compressor. For example, in the case where the oil supply passage and the oil return passage are filled with oil during stoppage of operation of the centrifugal compressor, the speed increaser chamber becomes a closed space. Then, when the temperature in the speed increaser chamber increases, the oil in the speed increaser chamber is pushed out by gas expanded in the speed increaser chamber and flows out to the oil return passage. The oil flows into the oil pan through the oil return passage, increasing the level of the oil in the oil pan. As the oil level in the oil pan increases, the oil may leak into the outside through the pressure reduction passage, thereby reducing an amount of oil supplied to the speed increaser.
The present disclosure has been made in view of the above circumstances and is directed to providing a centrifugal compressor that restricts the reduction of an amount of oil supplied to a speed increaser in addition to restricting an increase of the pressure in the speed increaser chamber.
In accordance with an aspect of the present disclosure, there is provided a centrifugal compressor that includes a low-speed shaft, an impeller, a speed increaser, a housing, a separation wall, a shaft insertion hole, a seal member, an oil pan, an oil supply passage, an oil return passage, and a pressure reduction passage. The impeller is integrally rotated with a high-speed shaft to compress gas. The speed increaser transmits power of the low-speed shaft to the high-speed shaft. The housing has therein an impeller chamber accommodating the impeller and a speed increaser chamber accommodating the speed increaser. The separation wall separates the impeller chamber from the speed increaser chamber. The shaft insertion hole through which the high-speed shaft is inserted is formed in the separation wall. The seal member is disposed between an outer circumferential surface of the high-speed shaft and an inner circumferential surface of the shaft insertion hole. The oil pan stores therein oil supplied to the speed increaser. Oil stored in the oil pan is supplied to the speed increaser chamber through the oil supply passage. Oil in the speed increaser chamber is returned to the oil pan through the oil return passage. The pressure reduction passage communicates with the oil pan and the outside. The centrifugal compressor includes a bypass passage having a first end communicating with the speed increaser chamber and a second end communicating with the oil pan.
Other aspects and advantages of the disclosure will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the disclosure.
The disclosure, together with objects and advantages thereof, may best be understood by reference to the following description of the embodiments together with the accompanying drawings in which:
The following will describe an embodiment of a centrifugal compressor with reference to
Referring to
The motor housing 12 is formed in a bottomed cylindrical shape, and has a disk-like bottom wall 12a and a circumferential wall 12b cylindrically extending from the outer circumferential edge of the bottom wall 12a. The speed increaser housing 13 is formed in a bottomed cylindrical shape, and has a disk-like bottom wall 13a and a circumferential wall 13b cylindrically extending from the outer circumferential edge of the bottom wall 13a.
An end portion of the circumferential wall 12b located on the opposite side to the bottom wall 12a in the motor housing 12 is connected to the bottom wall 13a of the speed increaser housing 13. In addition, an opening formed by the circumferential wall 12b and located on the opposite side to the bottom wall 12a in the motor housing 12 is closed by the bottom wall 13a of the speed increaser housing 13. The bottom wall 13a has at the central part thereof a hole 13h.
An end portion of the circumferential wall 13b located on the opposite side to the bottom wall 13a in the speed increaser housing 13 is connected to the plate 14. In addition, an opening formed by the circumferential wall 13b and located on the opposite side to the bottom wall 13a in the speed increaser housing 13 is closed by the plate 14. The plate 14 has at the central part thereof a shaft insertion hole 14h.
The compressor housing 15 is connected to the opposite surface of the plate 14 to the speed increaser housing 13. The compressor housing 15 has an intake port 15a through which air corresponding to gas is sucked in. The intake port 15a is an opening located at a central part of an end surface of the compressor housing 15 on the opposite side to the plate 14, and extends from such central part in the axial direction of the housing 11.
The centrifugal compressor 10 includes a low-speed shaft 16 and an electric motor 17 rotating the low-speed shaft 16. The housing 11 has therein a motor chamber 12c accommodating the electric motor 17. The motor chamber 12c is defined by the inner surface of the bottom wall 12a, the inner circumferential surface of the circumferential wall 12b of the motor housing 12, and the outer surface of the bottom wall 13a of the speed increaser housing 13. The motor housing 12 accommodates the low-speed shaft 16, which is coaxial with the motor housing 12. The low-speed shaft 16 is made of metallic materials, such as iron and alloy.
A cylindrical boss portion 12f protrudes from the inner surface of the bottom wall 12a of the motor housing 12. A first end portion of the low-speed shaft 16 near the boss portion 12f is inserted in the boss portion 12f. A first bearing 18 is disposed between the first end portion of the low-speed shaft 16 and the boss portion 12f. Thus, the first end portion of the low-speed shaft 16 is rotatably supported by the bottom wall 12a of the motor housing 12 via the first bearing 18.
A second end portion of the low-speed shaft 16 near the speed increaser housing 13 is inserted in the hole 13h. A second bearing 19 is disposed between the second end portion of the low-speed shaft 16 and the hole 13h. Thus, the second end portion 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. Accordingly, the low-speed shaft 16 is rotatably supported in the housing 11. The second end portion of the low-speed shaft 16 extends from the motor chamber 12c into the speed increaser housing 13 through the hole 13h.
A seal member 20 is disposed between the second end portion of the low-speed shaft 16 and the hole 13h. The seal member 20 is located closer to the motor chamber 12c than the second bearing 19 is located, interposed between the second end portion of the low-speed shaft 16 and the hole 13h. The seal member 20 seals a gap between the outer circumferential surface of the low-speed shaft 16 and the inner circumferential surface of the hole 13h.
The electric motor 17 is configured of a cylindrical stator 21 and a rotor 22 disposed inside the stator 21. The rotor 22 is fixed to the low-speed shaft 16 and integrally rotates with the low-speed shaft 16. The stator 21 is disposed to surround the rotor 22. The rotor 22 has a cylindrical rotor core 22a attached fixedly to the low-speed shaft 16 and a plurality of permanent magnets (not shown) disposed in the rotor core 22a. The stator 21 has a cylindrical stator core 21a fixed to the inner circumferential surface of the circumferential wall 12b of the motor housing 12 and a coil 21b wound around the stator core 21a. When electric current flows through the coil 21b, the rotor 22 rotates integrally with the low-speed shaft 16.
The centrifugal compressor 10 includes a high-speed shaft 31 and a speed increaser 30 transmitting power of the low-speed shaft 16 to the high-speed shaft 31. The housing 11 has therein a speed increaser chamber 13c accommodating the speed increaser 30. The speed increaser chamber 13c is defined by the inner surface of the bottom wall 13a, the inner circumferential surface of the circumferential wall 13b of the speed increaser housing 13, and the plate 14. Oil is stored in the speed increaser chamber 13c. The seal member 20 prevents leakage of the oil stored in the speed increaser chamber 13c into the motor chamber 12c through the gap between the outer circumferential surface of the low-speed shaft 16 and the inner circumferential surface of the hole 13h.
The high-speed shaft 31 is made of metallic materials, such as iron or alloy. The speed increaser chamber 13c accommodates the high-speed shaft 31, which is coaxial with the speed increaser housing 13. An end portion of the high-speed shaft 31 on the opposite side to the motor housing 12 extends into the compressor housing 15 through the shaft insertion hole 14h of the plate 14. The high-speed shaft 31 is coaxial with the low-speed shaft 16.
The centrifugal compressor 10 includes an impeller 24 attached to the high-speed shaft 31. The housing 11 has therein an impeller chamber 15b accommodating the impeller 24. The impeller chamber 15b is defined by the compressor housing 15 and the plate 14. The plate 14 corresponding to the separation wall of the present disclosure separates the impeller chamber 15b from the speed increaser chamber 13c. The shaft insertion hole 14h through which the high-speed shaft 31 is inserted is formed in the plate 14 corresponding to the separation wall.
A seal member 23 is disposed between the outer circumferential surface of the high-speed shaft 31 and the inner circumferential surface of the shaft insertion hole 14h. The seal member 23 is, for example, a mechanical seal. The seal member 23 seals the gap between the outer circumferential surface of the high-speed shaft 31 and the inner circumferential surface of the shaft insertion hole 14h. The seal member 23 prevents leakage of the oil stored in the speed increaser chamber 13c into the impeller chamber 15b through the gap between the outer circumferential surface of the high-speed shaft 31 and the inner circumferential surface of the shaft insertion hole 14h.
The impeller chamber 15b is in communication with the intake port 15a. The impeller chamber 15b is a substantially truncated conical hollow the diameter of which expands gradually as distanced away from the intake port 15a in the axial direction of the housing 11. A projecting end portion of the high-speed shaft 31 projects into the compressor housing 15, specifically into the impeller chamber 15b.
The impeller 24 has a substantially truncated conical shape the diameter of which decreases gradually as extending from a rear surface 24a of the impeller 24 toward a distal end surface 24b of the impeller 24. The impeller 24 has a hole 24c through which the high-speed shaft 31 is inserted. The hole 24c extends in a direction of the rotational axis of the impeller 24. In the impeller 24, the projecting end portion of the high-speed shaft 31 projects into the compressor housing 15 through the hole 24c. The impeller 24 is attached to the high-speed shaft 31 so as to be rotatable integrally with the high-speed shaft 31. With this configuration, the impeller 24 is rotated with the rotation of the high-speed shaft 31, so that air sucked from the intake port 15a is compressed. Therefore, the impeller 24 is integrally rotated with the high-speed shaft 31 to compress air.
The centrifugal compressor 10 includes a diffuser passage 25 into which the air compressed by the impeller 24 flows and a discharge chamber 26 into which the air passing through the diffuser passage 25 flows.
The diffuser passage 25 is defined by the plate 14 and the surface of the compressor housing 15 facing the plate 14. The diffuser passage 25 is located radially outward of the impeller chamber 15b relative to the high-speed shaft 31, and in communication with the impeller chamber 15b. The diffuser passage 25 is annularly formed to surround the impeller 24 and the impeller chamber 15b.
The discharge chamber 26 is located radially outward of the diffuser passage 25 relative to of the high-speed shaft 31, and in communication with the diffuser passage 25. The discharge chamber 26 has an annular shape. The impeller chamber 15b is in communication with the discharge chamber 26 via the diffuser passage 25. The air compressed by the impeller 24 is further compressed by passing through the diffuser passage 25. Then, the air flows into the discharge chamber 26 and is subsequently discharged from the discharge chamber 26.
The speed increaser 30 transmits rotation of the low-speed shaft 16 to the high-speed shaft 31, so that the high-speed shaft 31 rotates at a higher speed than the low-speed shaft 16 rotates. The speed increaser 30 is of a so-called traction drive type (friction roller type). The speed increaser 30 includes a ring member 32 connected to the second end portion of the low-speed shaft 16. The ring member 32 is made of metal. The ring member 32 rotates with rotation of the low-speed shaft 16. The ring member 32 is formed in a bottomed cylindrical shape, and has a disk-like base 33 connected to the second end portion of the low-speed shaft 16 and a cylindrical portion 34 cylindrically extending from the outer edge portion of the base 33. The base 33 extends in the radial direction of the low-speed shaft 16 relative to the low-speed shaft 16. The cylindrical portion 34 is coaxial with the low-speed shaft 16.
Referring to
Referring to
Referring to
The supporting member 39 has three bolt insertion holes 45 through which bolts 44 are inserted. The bolt insertion holes 45 are formed to pass through the corresponding three stand walls 41 in a direction of the rotational axis of the rollers 35. Referring to
The surface 14a of the plate 14 facing the supporting member 39 has three first recesses 51 (only one recess 51 is illustrated in
The surface 40a of the supporting base 40 facing the plate 14 has three second recesses 53 (only one recess 53 is illustrated in
The first protrusions 35c of the rollers 35 are inserted into the first roller bearings 52 in the first recesses 51, and rotatably supported by the plate 14 via the first roller bearings 52. The second protrusions 35e of the rollers 35 are inserted into the second roller bearings 54 in the second recesses 53, and rotatably supported by the supporting member 39 via the second roller bearings 54.
The high-speed shaft 31 has a pair of flange portions 31f that is opposed to and distanced from each other in the axial direction of the high-speed shaft 31. The roller portions 35a of the three rollers 35 are held between the pair of flange portions 31f. This restricts misalignment between the high-speed shaft 31 and the roller portions 35a of the three rollers 35 in the axial direction of the high-speed shaft 31.
Referring to
Pushing loads are applied to ring-side contact areas Pa where the outer circumferential surfaces of the roller portions 35a of the three rollers 35 are in contact with the inner circumferential surface of the cylindrical portion 34. In addition, pushing loads are applied to shaft-side contact areas Pb where the outer circumferential surfaces of the roller portions 35a of the three rollers 35 are in contact with the outer circumferential surface of high-speed shaft 31. The ring-side contact areas Pa and the shaft-side contact areas Pb extend in the axial direction of the high-speed shaft 31.
When the electric motor 17 is driven and the low-speed shaft 16 and the ring member 32 are rotated, the torque of the ring member 32 is transmitted to the three rollers 35 through the ring-side contact areas Pa to rotate the three rollers 35. A sum of the torque of the three rollers 35 is transmitted to the high-speed shaft 31 through the shaft-side contact areas Pb. In consequence, the high-speed shaft 31 is rotated. At this time, the ring member 32 rotates at the same speed as that of the low-speed shaft 16, and the three rollers 35 rotate at a higher speed than the low-speed shaft 16 rotates. The high-speed shaft 31 rotates at a higher speed than the three rollers 35 rotate because the outer diameter of the high-speed shaft 31 is smaller than that of the three rollers 35. Accordingly, the speed increaser 30 causes the high-speed shaft 31 to rotate at a higher speed than the low-speed shaft 16 rotates.
Referring to
The centrifugal compressor 10 includes an oil pump 57 and an oil supply passage 56 through which oil stored in the oil pan 55 is supplied to the speed increaser chamber 13c. The oil pump 57 that pumps up and discharges the oil stored in the oil pan 55 is disposed in the oil supply passage 56. The oil pump 57 is formed in the bottom wall 12a of the motor housing 12. The oil pump 57 is, for example, a trochoid pump. The oil pump 57 is connected to the first end portion of the low-speed shaft 16. The oil pump 57 is driven with rotation of the low-speed shaft 16.
The oil supply passage 56 has a first connecting passage 56a connecting the oil pan 55 to the oil pump 57, and a second connecting passage 56b connecting the oil pump 57 to the speed increaser chamber 13c. The first connecting passage 56a is formed in the motor housing 12. A first end of the first connecting passage 56a extends into the oil pan 55. A second end of the first connecting passage 56a is connected to an oil intake port 57a of the oil pump 57. The second connecting passage 56b passes through the motor housing 12 and the speed increaser housing 13. A first end of the second connecting passage 56b is connected to an oil discharge port 57b of the oil pump 57. A second end of the second connecting passage 56b opens at an upper portion of the speed increaser chamber 13c in the gravity direction.
The centrifugal compressor 10 includes an oil return passage 58 through which the oil in the speed increaser chamber 13c is returned to the oil pan 55, and an oil cooler 59 cooling the oil flowing through the oil return passage 58. The oil cooler 59 has a bottomed cylindrical cover member 59a attached to the outer circumferential surface of the circumferential wall 12b of the motor housing 12. The inner surface of the cover member 59a and the outer circumferential surface of the circumferential wall 12b of the motor housing 12 cooperate to define a space 59b. The oil cooler 59 also has a cooling pipe 59c disposed in the space 59b. The opposite end portions of the cooling pipe 59c are supported by the motor housing 12. The cooling pipe 59c forms a part of the oil return passage 58.
The cover member 59a has an introduction pipe 59d and a discharge pipe 59e. Low-temperature fluid is introduced into the space 59b from the introduction pipe 59d. The low-temperature fluid introduced into the space 59b is discharged through the discharge pipe 59e, and then cooled down by a cooling device (not shown). After that, the low-temperature fluid is introduced into the space 59b again through the introduction pipe 59d. In one example, the low-temperature fluid is water.
The oil return passage 58 has a third connecting passage 58a connecting the speed increaser chamber 13c to the oil cooler 59, and a fourth connecting passage 58b connecting the oil cooler 59 to the oil pan 55. The third connecting passage 58a passes through the speed increaser housing 13, and extends into the circumferential wall 12b of the motor housing 12. A first end of the third connecting passage 58a opens at a lower portion of the speed increaser chamber 13c in the gravity direction. A second end of the third connecting passage 58a is connected to a first end of the cooling pipe 59c. The fourth connecting passage 58b is formed in the motor housing 12. A first end of the fourth connecting passage 58b is connected to a second end of the cooling pipe 59c. A second end of the fourth connecting passage 58b opens at the oil pan 55.
When the electric motor 17 is driven, the low-speed shaft 16 is rotated to drive the oil pump 57. The oil stored in the oil pan 55 is pumped up into the oil pump 57 through the first connecting passage 56a and the oil intake port 57a, and then, discharged to the second connecting passage 56b from the oil discharge port 57b. The oil pump 57 is driven such that an amount of oil discharged from the oil discharge port 57b is linearly increased as the number of rotation of the low-speed shaft 16 increases. The oil discharged to the second connecting passage 56b flows therethrough into the speed increaser chamber 13c, and is supplied to the outer circumferential surfaces of the roller portions 35a and the like. The oil supplied to the outer circumferential surfaces of the roller portions 35a improves lubrication of sliding areas between the roller portions 35a and the high-speed shaft 31.
The oil having contributed to the lubrication of the sliding areas between the roller portions 35a and the high-speed shaft 31 is stored in the speed increaser chamber 13c. The oil stored in the speed increaser chamber 13c flows into the third connecting passage 58a, and then, passes through the third connecting passage 58a, the cooling pipe 59c, and the fourth connecting passage 58b. While passing through the cooling pipe 59c, the oil is cooled by heat exchange with the low-temperature fluid introduced to the space 59b of the oil cooler 59. Then, the oil cooled by the oil cooler 59 is stored in the oil pan 55.
The centrifugal compressor 10 includes a pressure reduction passage 60 communicating with the oil pan 55 and the outside. The pressure reduction passage 60 has a connecting passage 60a, a buffer chamber 60b, and a discharge hole 60c. The buffer chamber 60b is formed in the bottom wall 12a of the motor housing 12. The connecting passage 60a is formed in the bottom wall 12a of the motor housing 12. The connecting passage 60a is in communication with the oil pan 55 and the buffer chamber 60b. A first end of the connecting passage 60a opens at an upper portion of the oil pan 55 in the gravity direction. A second end of the connecting passage 60a opens at a lower portion of the buffer chamber 60b in the gravity direction. The discharge hole 60c is formed in the bottom wall 12a of the motor housing 12. A first end of the discharge hole 60c opens at an upper portion of the buffer chamber 60b in the gravity direction. A second end of the discharge hole 60c opens at the outer surface of the bottom wall 12a of the motor housing 12 and is in communication with the outside.
The centrifugal compressor 10 includes a bypass passage 61. The bypass passage 61 passes through the speed increaser housing 13 and the motor housing 12. A first end of the bypass passage 61 opens at an upper portion of the speed increaser chamber 13c in the gravity direction. A second end of the bypass passage 61 opens at an upper portion of the oil pan 55 in the gravity direction. Thus, the speed increaser chamber 13c and the oil pan 55 are in communication with each other via the bypass passage 61. Specifically, the bypass passage 61 has the first end communicating with the speed increaser chamber 13c and the second end communicating with the oil pan 55.
The following will describe functions according to the present embodiment.
While the centrifugal compressor 10 is operated, even when air leaks from the impeller chamber 15b into the speed increaser chamber 13c through the gap between the outer circumferential surface of the high-speed shaft 31 and the inner circumferential surface of the shaft insertion hole 14h, air in the speed increaser chamber 13c is discharged to the outside through the oil return passage 58, the oil pan 55, and the pressure reduction passage 60. This restricts an increase of pressure in the speed increaser chamber 13c. Thus, even under the circumstances where pressure of the impeller chamber 15b is lower than that of the speed increaser chamber 13c, for example, the impeller 24 rotates at a low speed or the operation of the centrifugal compressor 10 stops, the difference between the pressure of the speed increaser chamber 13c and the pressure of the impeller chamber 15b becomes smaller. This means that the oil in the speed increaser chamber 13c is restricted from leaking into the impeller chamber 15b through the gap between the outer circumferential surface of the high-speed shaft 31 and the inner circumferential surface of the shaft insertion hole 14h.
The speed increaser chamber 13c is in communication with the oil pan 55 via the bypass passage 61. With this configuration, the speed increaser chamber 13c does not become a closed space even when the oil supply passage 56 and the oil return passage 58 are filled with oil, for example, during stoppage of operation of the centrifugal compressor 10. As a result, air in the speed increaser chamber 13c is discharged to the outside through the bypass passage 61, the oil pan 55, and the pressure reduction passage 60, even when the air in the speed increaser chamber 13c is expanded with an increase of the temperature in the speed increaser chamber 13c. In addition, the oil which is stirred by the speed increaser 30 in the speed increaser chamber 13c during the operation of the centrifugal compressor 10 may flow into the bypass passage 61. Even in this case, the oil becomes confluent with the oil stored in the oil pan 55 through the bypass passage 61, with the result that the oil hardly leaks out to the outside through the pressure reduction passage 60.
The above embodiment offers the following effects.
(1) The centrifugal compressor 10 includes the bypass passage 61 having the first end communicating with the speed increaser chamber 13c and the second end communicating with the oil pan 55. With this configuration, even when air in the speed increaser chamber 13c is expanded with an increase in the temperature in the speed increaser chamber 13c, the air in the speed increaser chamber 13c is discharged to the outside through the bypass passage 61, the oil pan 55, and the pressure reduction passage 60. The bypass passage 61 restricts the oil pushed out by the expanded air in the speed increaser chamber 13c from flowing into the oil pan 55 through the oil return passage 58. This restricts increasing a level of oil in the oil pan 55, so that leakage of the oil to the outside through the pressure reduction passage 60 is restricted. Therefore, the reduction of an amount of oil supplied to the speed increaser 30 is restricted.
While the centrifugal compressor 10 is operated, even when air leaks from the impeller chamber 15b into the speed increaser chamber 13c through the gap between the outer circumferential surface of the high-speed shaft 31 and the inner circumferential surface of the shaft insertion hole 14h, air in the speed increaser chamber 13c is discharged to the outside through the oil return passage 58, the oil pan 55 and the pressure reduction passage 60. This restricts an increase of the pressure in the speed increaser chamber 13c. In addition, the oil which is stirred by the speed increaser 30 in the speed increaser chamber 13c during the operation of the centrifugal compressor 10 may flow into the bypass passage 61. Even in this case, the oil becomes confluent with the oil stored in the oil pan 55 through the bypass passage 61. For this reason, the oil hardly leaks out to the outside through the pressure reduction passage 60. Thus, providing the bypass passage 61 in the centrifugal compressor 10 also restricts the reduction of an amount of oil supplied to the speed increaser 30. Therefore, the present disclosure restricts the reduction of the amount of oil supplied to the speed increaser 30 in addition to restricting an increase of pressure in the speed increaser chamber 13c.
(2) In the present embodiment, leakage of oil from the speed increaser chamber 13c to the impeller chamber 15b is restricted. This restricts the oil from being supplied to a fuel cell together with air compressed by the centrifugal compressor 10, avoiding a reduction of the power generation efficiency of the fuel cell.
The above embodiment may be modified as described below. The above embodiment and the following modifications may be combined each other appropriately, as long as there is no technical contradictions.
In the embodiment, the buffer chamber 60b which forms part of pressure reduction passage 60 may not be formed in the motor housing 12.
In the embodiment, for example, the pressure reduction valve which opens when pressure in the speed increaser chamber 13c reaches a predetermined pressure may be formed in the discharge hole 60c of the pressure reduction passage 60. The pressure reduction valve may be a solenoid valve configured to open and close by electrical signals only while the centrifugal compressor 10 is operated.
In the embodiment, the centrifugal compressor 10 may be applied to any unit and compress any gas. For example, the centrifugal compressor 10 may be applied to an air conditioning unit and compress refrigerant gas. In addition, the centrifugal compressor 10 may be mounted to any unit other than a vehicle.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2018-185311 | Sep 2018 | JP | national |
