阅读说明：本技术 涡轮式流体机械 (Turbo type fluid machine ) 是由 森英文 铃木润也 冈崎和贵 于 2020-02-18 设计创作，主要内容包括：得到抑制从涡轮机室侧向马达室侧的流体侵入并且也抑制壳体内的轴周边的温度上升的涡轮式流体机械。由压缩机叶轮(22)升压后的流体的一部分经由具有入口侧固定节流部(TH1)的入口侧流路(IN)而向马达收容空间(18)导入,导入到马达收容空间(18)的流体经由具有出口侧固定节流部(TH2)的出口侧流路(EN)而从马达收容空间(18)排出。出口侧流路(EN)中的与马达收容空间(18)的连接部,与第2区划壁(15)与轴(21)之间的间隙分开设置,且与入口侧流路(IN)中的与马达收容空间的连接部在轴向上相对于马达(28)位于相反侧。入口侧固定节流部(TH1)及出口侧固定节流部(TH2)构成为马达收容空间的压力比涡轮机叶轮背面区域(39)的压力高。(A turbo fluid machine is provided which suppresses the intrusion of fluid from a turbine casing side to a motor chamber side and also suppresses the temperature rise around a shaft in a casing. A part of the fluid pressurized by the compressor impeller (22) is introduced into the motor housing space (18) through an inlet-side flow path (IN) having an inlet-side fixed throttle (TH1), and the fluid introduced into the motor housing space (18) is discharged from the motor housing space (18) through an outlet-side flow path (EN) having an outlet-side fixed throttle (TH 2). The connection portion with the motor housing space (18) IN the outlet side flow path (EN) is provided separately from the gap between the 2 nd partition wall (15) and the shaft (21), and is located on the opposite side IN the axial direction with respect to the motor (28) from the connection portion with the motor housing space IN the inlet side flow path (IN). The inlet side fixed throttle part (TH1) and the outlet side fixed throttle part (TH2) are configured such that the pressure of the motor accommodating space is higher than the pressure of the turbine wheel back surface area (39).)

1. A turbo fluid machine includes:

a housing including a 1 st partition wall and a 2 nd partition wall, a motor accommodating space being formed between the 1 st partition wall and the 2 nd partition wall in an axial direction, an impeller chamber being formed on a side opposite to the motor accommodating space with respect to the 1 st partition wall, and a turbine chamber being formed on a side opposite to the motor accommodating space with respect to the 2 nd partition wall;

a rotating member including a shaft, a compressor impeller, and a turbine impeller, the shaft being disposed so as to penetrate the 1 st partition wall and the 2 nd partition wall, the compressor impeller being fixed to the shaft and disposed in the impeller chamber to perform a compression action of a fluid, the turbine impeller being fixed to the shaft and disposed in the turbine chamber to perform a regeneration action; and

a motor disposed in the motor accommodating space to rotate the rotating member,

a turbine wheel backface region is formed on the turbine chamber side of the 2 nd partition wall,

a shaft seal portion is disposed between the 2 nd partition wall and the shaft to restrict fluid communication between the motor housing space and the turbine wheel back surface region,

a part of the fluid pressurized by the compressor impeller is introduced into the motor housing space through an inlet-side flow passage having an inlet-side fixed throttle portion,

the fluid introduced into the motor housing space can be discharged from the motor housing space through an outlet side flow path having an outlet side fixed throttle portion,

a connection portion with the motor housing space in the outlet-side flow passage is provided separately from a gap between the 2 nd partition wall and the shaft, and is located on an opposite side in an axial direction with respect to the motor from a connection portion with the motor housing space in the inlet-side flow passage,

the inlet-side fixed throttle portion and the outlet-side fixed throttle portion are configured such that a pressure of the motor housing space is higher than a pressure of the turbine wheel back surface region.

2. The turbo fluid machine according to claim 1,

the casing is further provided with a connection flow path for supplying the fluid having passed through the outlet-side flow path to a suction port on an upstream side of the compressor impeller.

3. The turbo fluid machine according to claim 1 or 2,

the turbo fluid machine further includes a foil bearing for axially supporting the shaft,

the fluid flowing in the motor housing space is configured to pass between the foil bearing and the shaft.

4. A turbo fluid machine according to any one of claims 1 to 3,

the turbo fluid machine further includes a resolver that detects a rotation angle of the shaft,

the resolver includes a resolver rotor fixed to the shaft so as to be integrally rotatable, and a resolver stator fixed to the housing,

the fluid flowing in the motor housing space is configured to pass between the resolver rotor and the resolver stator.

5. The turbo fluid machine according to any one of claims 1 to 4,

a compressor impeller backface region is formed on the impeller chamber side of the 1 st partition wall,

the 1 st partition wall is provided with a partition portion that extends annularly so as to surround the periphery of the shaft and that partitions the compressor impeller back surface region into an inner diameter side space and an outer diameter side space.

6. The turbo fluid machine according to claim 5,

the inlet-side fixed throttle portion is formed by the partition portion.

7. The turbo fluid machine according to claim 5,

the fluid is introduced into the motor accommodating space by connecting a discharge port on a downstream side of the compressor impeller with a space formed at the motor side of the 2 nd partition wall,

the outlet-side fixed throttle is formed between the 1 st division wall and the shaft,

the housing is further provided with a flow path that connects the inner diameter side space to a space other than the outer diameter side space so that the pressure of the inner diameter side space is lower than the pressure of the outer diameter side space when fluid is pressure-fed.

8. The turbo fluid machine according to claim 5,

the fluid is introduced into the motor accommodating space by connecting a discharge port on a downstream side of the compressor impeller with a shaft hole at an outer periphery of the shaft in the 1 st partition wall,

the housing is further provided with a flow path that connects the inner diameter side space to a space other than the outer diameter side space so that the pressure of the inner diameter side space is lower than the pressure of the outer diameter side space when fluid is pressure-fed.

Technical Field

The present specification relates to a turbo fluid machine.

Background

As disclosed in patent document 1, in a fluid machine (fluid pump) including a motor, when a fluid enters a motor chamber, the motor is likely to rust, and therefore it is desirable to suppress the entry of the fluid into the motor chamber.

Disclosure of Invention

Problems to be solved by the invention

In a turbo fluid machine, a rotating member including a compressor wheel, a turbine wheel, and a shaft is disposed in a casing. Such a rotating member is rotated by a motor. By generating a differential pressure by the internal pressure of a flow path or the like formed in the casing, it is possible to suppress the intrusion of the fluid from the turbine chamber side to the motor chamber side.

Here, the temperature around the shaft in the housing is likely to rise. In particular, when the intrusion of the fluid into the motor chamber is suppressed, the temperature around the shaft in the housing is more likely to increase due to the suppression of the flow of the fluid, and suppression of the temperature increase is desired. In the case where the fluid is moved to generate a differential pressure by the internal pressure of a flow path or the like formed in the housing, it is preferable that the temperature rise around the shaft in the housing can also be suppressed.

An object of the present invention is to provide a turbo fluid machine having a structure capable of suppressing the intrusion of a fluid from a turbine casing side to a motor chamber side and also suppressing the temperature rise around a shaft in a casing.

Means for solving the problems

The turbo fluid machine according to the present disclosure includes: a housing including a 1 st partition wall and a 2 nd partition wall, a motor accommodating space being formed between the 1 st partition wall and the 2 nd partition wall in an axial direction, an impeller chamber being formed on a side opposite to the motor accommodating space with respect to the 1 st partition wall, and a turbine chamber being formed on a side opposite to the motor accommodating space with respect to the 2 nd partition wall; a rotating member including a shaft, a compressor impeller, and a turbine impeller, the shaft being disposed so as to penetrate the 1 st partition wall and the 2 nd partition wall, the compressor impeller being fixed to the shaft and disposed in the impeller chamber to perform a compression action of a fluid, the turbine impeller being fixed to the shaft and disposed in the turbine chamber to perform a regeneration action; and a motor disposed in the motor housing space to rotate the rotary member, wherein a turbine impeller back surface region is formed on the turbine chamber side of the 2 nd partition wall, a shaft seal portion is disposed between the 2 nd partition wall and the shaft to restrict communication of fluid between the motor housing space and the turbine impeller back surface region, a part of fluid pressurized by the compressor impeller is introduced into the motor housing space through an inlet-side flow passage having an inlet-side fixed throttle portion, fluid introduced into the motor housing space is discharged from the motor housing space through an outlet-side flow passage having an outlet-side fixed throttle portion, a connection portion of the outlet-side flow passage to the motor housing space is provided separately from a gap between the 2 nd partition wall and the shaft, and the connection portion of the inlet-side flow passage to the motor housing space is located on an opposite side in an axial direction to the motor The inlet-side fixed throttle portion and the outlet-side fixed throttle portion are configured such that a pressure of the motor accommodating space is higher than a pressure of the turbine wheel back surface region.

According to the turbo fluid machine, the pressure in the motor housing space is higher than the pressure in the region on the back surface of the turbine wheel by the differential pressure generated by the internal pressure of the flow passage formed in the housing. Therefore, the fluid can be suppressed from entering from the turbine casing side to the motor chamber side. Further, the connection portion with the motor housing space in the inlet-side flow path and the connection portion with the motor housing space in the outlet-side flow path are located on opposite sides of the motor. Since the fluid flows from the inlet side to the outlet side opposite thereto via the motor, a heat radiation effect of the fluid to the space around the shaft can be obtained, and the temperature rise around the shaft in the case can also be suppressed.

In the turbo fluid machine, the casing may be further provided with a connection flow path for supplying the fluid passing through the outlet side flow path to the suction port on the upstream side of the compressor impeller.

According to the turbo fluid machine, when the turbo fluid machine is used as an air compressor in a fuel cell system, for example, the air flow meter can measure or control how much air is supplied to a stack (stack) of the fuel cell system. The flow rate of air supplied for differential pressure formation and heat dissipation can be minimized.

The turbo fluid machine may further include a foil bearing (hereinafter, referred to as "foil") for supporting the shaft, and the fluid flowing in the motor housing space may pass through a gap between the foil bearing and the shaft.

According to the turbo fluid machine, the heat radiation efficiency to the foil bearing can be improved.

The turbo fluid machine may further include a resolver that detects a rotation angle of the shaft, the resolver may include a resolver rotor that is integrally rotatably fixed to the shaft and a resolver stator that is fixed to the housing, and the fluid flowing through the motor housing space may pass between the resolver rotor and the resolver stator.

According to the turbo fluid machine, the heat radiation efficiency of the rotary transformer can be improved.

In the turbo fluid machine, a compressor impeller back surface region may be formed on the impeller chamber side of the 1 st partition wall, and a partition portion may be provided on the 1 st partition wall, the partition portion extending annularly so as to surround the periphery of the shaft and dividing the compressor impeller back surface region into an inner diameter side space and an outer diameter side space.

According to the turbo fluid machine, the increase in the back load of the compressor impeller is suppressed by the presence of the inner diameter side space, and the displacement of the compressor impeller toward the inlet side of the suction port is also suppressed.

In the turbo fluid machine, the inlet side fixed throttle portion may be formed by the partition portion.

According to the turbo fluid machine, the partition portion that partitions the compressor wheel back surface region into the inner diameter side space and the outer diameter side space in order to reduce the back surface load of the compressor wheel can function as a means for forming the inlet side fixed throttle portion, and high utilization efficiency in layout can be obtained.

In the turbo fluid machine, a discharge port on a downstream side of the compressor impeller may be connected to a space formed on the motor side of the 2 nd partition wall, so that the fluid is introduced into the motor housing space, the outlet side fixed throttle portion may be formed between the 1 st partition wall and the shaft, and the casing may further include a flow path that connects the inner diameter side space to a space other than the outer diameter side space so that a pressure of the inner diameter side space is lower than a pressure of the outer diameter side space when the fluid is pressure-fed.

With the turbo fluid machine, it is possible to suppress the intrusion of the fluid from the turbine casing side to the motor chamber side, and it is also possible to obtain the heat radiation effect of the fluid to the peripheral space of the shaft.

In the turbo fluid machine, the fluid may be introduced into the motor housing space by connecting a discharge port on a downstream side of the compressor impeller to a shaft hole in the 1 st partition wall on an outer periphery of the shaft, and the casing may further include a flow path connecting the inner diameter side space to a space other than the outer diameter side space so that a pressure of the inner diameter side space is lower than a pressure of the outer diameter side space when the fluid is pressure-fed.

According to the turbo fluid machine, even if the pressure in the motor housing space is set to a high value, the effect thereof is suppressed from directly causing an increase in the back load of the compressor impeller. The displacement of the compressor impeller toward the inlet side of the suction port can be further suppressed.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the turbo fluid machine disclosed in the present specification, it is possible to suppress the intrusion of the fluid from the turbine casing side to the motor chamber side, and also to suppress the temperature increase around the shaft in the casing.

Drawings

Fig. 1 is a sectional view showing a turbo fluid machine 101 according to embodiment 1.

Fig. 2 is a cross-sectional view showing a state during operation of the turbo fluid machine 101 according to embodiment 1.

Fig. 3 is a graph showing a pressure distribution during operation of the turbo fluid machine 101 according to embodiment 1.

Fig. 4 is a sectional view showing the turbo fluid machine 102 according to embodiment 2.

Fig. 5 is a sectional view showing the turbo fluid machine 103 according to embodiment 3.

Fig. 6 is a cross-sectional view showing a state in operation of the turbo fluid machine 103 according to embodiment 3.

Fig. 7 is a sectional view showing the turbo fluid machine 104 according to embodiment 4.

Fig. 8 is a sectional view showing a state in operation of the turbo fluid machine 104 according to embodiment 4.

Description of the reference numerals

10 casing, 11 compressor casing, 11a suction port, 11b impeller chamber, 11c discharge chamber, 11d discharge port, 12 st division wall, 12a, 15a shaft hole, 12b division part, 13, 14 center casing, 15 nd division wall, 2 nd division wall, 16 turbine casing, 16b turbine casing, 17 motor chamber, 18 motor housing space, 19 shaft seal part, 20 rotating member, 21 shaft, 21a large diameter part, 21b, 21c inner ring, 22 compressor impeller, 22a, 23a base plate, 22b, 23b blade, 22c, 23c back surface part, 23 turbine impeller, 24 thrust bearing, 25, 26 radial foil bearing, 27 resolver, 27a resolver rotor, 27b resolver stator, 28 motor, 28a stator, 28b rotor, 29 connecting flow path, flow passages 29a and 29b, a compressor wheel back surface region 30, an inner diameter side space 31, an outer diameter side space 32, a space 37 and 38, a turbine wheel back surface region 39, an air flow meter 40, a fuel cell stack 50, a turbo fluid machine 100, 101, 102, 103, and 104, a CN communication passage, an EN outlet side flow passage, an ENa and INa connection part, an IN inlet side flow passage, a TH1 inlet side fixed throttle part, and a TH2 outlet side fixed throttle part.

Detailed Description

Hereinafter, a turbo fluid machine according to an embodiment will be described with reference to the drawings. In the following description, the same reference numerals are given to the same components and corresponding components, and repeated description may not be repeated.

[ embodiment 1]

(turbo type fluid machine 101)

As shown in fig. 1, the turbo fluid machine 101 includes a casing 10, a rotary member 20, and a motor 28. The housing 10 includes a compressor housing 11, a 1 st partition wall 12, center housings 13, 14, a 2 nd partition wall 15, and a turbine housing 16. These members constituting the housing 10 are coupled in the axial direction (the direction in which the central axis of the shaft 21 extends).

A motor housing space 18 including a motor chamber 17 is formed between the 1 st partition wall 12 and the 2 nd partition wall 15 in the axial direction. A motor 28 (a stator 28a and a rotor 28b) is disposed in the motor housing space 18, more specifically, in the motor chamber 17. An impeller chamber 11b is formed on the opposite side of the motor housing space 18 with respect to the 1 st partition wall 12. A turbine chamber 16b is formed on the opposite side of the motor housing space 18 from the 2 nd partition wall 15. A shaft hole 12a is formed in the 1 st partition wall 12, and a shaft hole 15a is formed in the 2 nd partition wall 15. A shaft seal 19 is disposed between the 2 nd partition wall 15 (inner peripheral portion of the shaft hole 15 a) and the shaft 21. The shaft seal portion 19 has, for example, a C-shaped configuration, and is provided with a notch in a part in the circumferential direction.

The rotating member 20 includes a shaft 21, a compressor wheel 22, and a turbine wheel 23. The shaft 21 has a large diameter portion 21a and inner rings 21b and 21c, and is disposed so as to penetrate the shaft holes 12a and 15 a. The compressor impeller 22 is fixed to one end of the shaft 21 and disposed in the impeller chamber 11 b. The turbine wheel 23 is fixed to the other end of the shaft 21 and is disposed in the turbine chamber 16 b.

The compressor wheel 22 performs a compression action of the fluid. The turbine wheel 23 performs a regeneration action of recovering energy from the fluid compressed by the compressor wheel 22. Compressor impeller 22 includes a disk-shaped base plate 22a and blades 22b formed on one side of base plate 22a, and a rear surface portion 22c is formed on the opposite side of base plate 22a from blades 22 b. Similarly, the turbine wheel 23 has a disk-shaped base plate 23a and blades 23b formed on one side of the base plate 23a, and the opposite side of the base plate 23a from the blades 23b is referred to as a back surface portion 23 c.

A thrust foil bearing 24 and radial foil bearings 25 and 26 are provided inside the housing 10. The shaft 21 is supported by these bearings. The thrust foil bearing 24 and the large diameter portion 21a are disposed in a space 37 defined by the 1 st partition wall 12 and the center housing 13. The shaft 21 is rotated together with the compressor wheel 22 and the turbine wheel 23 by the motor 28. The shaft 21 can be rotated by receiving power from the motor 28 alone, or can be rotated not only by the motor 28 but also by receiving power assisted by the turbine wheel 23.

The 1 st partition wall 12 faces the back surface portion 22c of the compressor impeller 22 with a gap. By disposing the compressor wheel 22 in the wheel chamber 11b, the compressor wheel back region 30 is formed between the 1 st partition wall 12 and the compressor wheel 22 in the axial direction (on the wheel chamber 11b side of the 1 st partition wall 12).

The 2 nd partition wall 15 faces the back surface portion 23c of the turbine wheel 23 with a space. By disposing the turbine wheel 23 in the turbine chamber 16b, a turbine wheel rear surface region 39 is formed between the 2 nd partition wall 15 and the turbine wheel 23 in the axial direction (on the turbine chamber 16b side of the 2 nd partition wall 15). A space 38 is formed on the motor chamber 17 side of the 2 nd partition wall 15. A resolver 27 for detecting the rotation angle of the shaft 21 is preferably provided in the space 38. The resolver 27 includes a resolver rotor 27a fixed to the shaft 21 as the rotating member 20 so as to be rotatable integrally, and a resolver stator 27b fixed to the center housing 14. The space 37, the motor chamber 17, and the space 38 are arranged in series and connected to each other, forming a motor housing space 18. The motor housing space 18 forms a space defined by the shaft seal portion 19 and a partition portion 12b described later. The communication of fluid between the motor housing space 18 and the turbine wheel back surface region 39 is restricted by the shaft seal portion 19.

The casing 10 is provided with an inlet-side flow passage IN, an outlet-side flow passage EN, and a communication passage CN. The inlet-side flow path IN includes an inlet-side fixed restriction TH 1. The inlet-side fixed throttle TH1 is formed on the turbine wheel 23 side in the axial direction with respect to the position of the compressor wheel 22.

In the present embodiment, the 1 st partition wall 12 is provided with a partition portion 12 b. The partition portion 12b extends annularly so as to surround the shaft 21, and divides the compressor wheel back surface region 30 into an inner diameter side space 31 and an outer diameter side space 32. In the present embodiment, the inlet side fixed throttle TH1 is formed by the partition portion 12 b. The inlet-side flow passage IN includes an inlet-side fixed throttle TH1 and an inner-diameter-side space 31, and is connected to the motor accommodating space 18 through the shaft hole 12 a.

The inner diameter side space 31 is connected to the external space via the shaft hole 12a, the motor chamber 17, the space 38, and the outlet side flow path EN. The inner diameter side space 31 communicates with an outer space, which is a space other than the outer diameter side space 32, so as not to pass through the outer diameter side space 32. That is, a part of the fluid pressurized by the compressor impeller 22 is introduced into the motor accommodating space 18 through the inlet side flow passage IN having the inlet side fixed throttle TH 1. With the throttle structure of the inlet side fixed throttle TH1, the pressure in the inner diameter side space 31 is lower than the pressure in the outer diameter side space 32 when the fluid is pumped.

The outlet-side flow passage EN includes an outlet-side fixed restriction TH 2. The outlet-side fixed throttle TH2 is formed on the compressor wheel 22 side in the axial direction with respect to the position of the turbine wheel 23. The fluid introduced into the motor housing space 18 can be discharged from the motor housing space 18 through an outlet side flow passage EN having an outlet side fixed throttle TH 2. A connection portion ENa with the motor housing space 18 in the outlet-side flow path EN is provided separately from a gap between the 2 nd partition wall 15 and the shaft 21. A connection portion ENa with the motor housing space 18 IN the outlet-side flow path EN and a connection portion INa with the motor housing space 18 IN the inlet-side flow path IN are located on opposite sides with respect to the motor 28 IN the axial direction. In the present embodiment, the outlet-side flow passage EN is provided in the center housing 14, and communicates the space 38 with the external space. The communication passage CN is formed to connect the inlet-side passage IN and the outlet-side passage EN and to communicate with the space 38 located on the motor chamber 17 side of the 2 nd partition wall 15.

Fig. 2 is a cross-sectional view showing a state of the turbo fluid machine 101 during operation. Fluid is taken in from the suction port 11a and is pressurized by the compressor impeller 22. A part of the fluid after the pressure increase passes through the diffuser and moves toward the discharge chamber 11 c. Another part of the fluid after the pressure increase passes through the outer diameter side space 32 and the inlet side fixed throttle TH 1. The pressure is reduced by passing through the inlet-side fixed throttle TH1 (see a portion a in fig. 3).

The fluid having passed through the inlet-side flow passage IN (the inlet-side fixed throttle TH1) then passes through the communication passage CN toward the side opposite to the inlet-side fixed throttle TH1 across the motor 28 so as to flow along at least a part of the shaft 21. In the present embodiment, the communication path CN is formed so that the fluid flowing in the motor housing space 18 passes through a position between the shaft hole 12a and the shaft 21, a position between the thrust foil bearing 24 and the large diameter portion 21a, a position between the radial foil bearing 25 and the inner ring 21b, a position between the stator 28a and the rotor 28b, a position between the radial foil bearing 26 and the inner ring 21c, and a position between the resolver rotor 27a and the resolver stator 27 b. The pressure therebetween is substantially constant or slightly reduced (see section B in fig. 3). The fluid having passed through the communication passage CN, that is, the fluid having reached the space 38 further passes through the outlet-side flow passage EN. The pressure is further reduced by the outlet side fixed throttle TH2 of the outlet side flow path EN (see the portion C in fig. 3), and the pressure becomes a pressure value corresponding to the intake pressure.

As shown IN fig. 3, the pressure of the communication passage CN is increased by the pressure supplied from the inlet-side passage IN to the communication passage CN (portion B IN fig. 3). That is, the inlet-side fixed throttle TH1 and the outlet-side fixed throttle TH2 are configured such that the pressure of the motor housing space 18 (portion B in fig. 3), which is the space 38 formed on the motor chamber 17 side of the 2 nd partition wall 15, is higher than the pressure of the turbine wheel back surface region 39.

(action and Effect)

The turbo fluid machine 101 is used in a fuel cell system as an air compressor, for example. The compressor impeller 22 is driven to rotate by the motor 28 and the turbine impeller 23, air as an external fluid is sucked into the compressor, and the air compressed by the compressor impeller 22 is pressure-fed to the discharge chamber 11 c. The high-pressure air in the discharge chamber 11c is supplied to the stack of the fuel cell system. The turbine wheel 23 is rotated by air discharged from a fuel cell stack (FC stack)50 (fig. 1), and assists the rotation of the shaft 21.

As the fluid is pumped, the pressure in the compressor impeller back surface region 30 (impeller back surface pressure) increases. The back pressure acts as a back load to displace the compressor impeller 22 toward the inlet side of the suction port 11 a. In the present embodiment, the inlet side fixed throttle TH1 is formed by the partition portion 12b, and the compressor wheel back region 30 is divided into the low-pressure inner diameter side space 31 and the high-pressure outer diameter side space 32 by the inlet side fixed throttle TH 1. The increase in the back load is suppressed by the presence of the inner diameter side space 31, and the displacement of the compressor impeller 22 toward the inlet side of the suction port 11a is also suppressed. The thrust foil bearing 24 is also inhibited from receiving an excessive force from the large diameter portion 21a of the shaft 21. Since the inlet-side fixed throttle TH1 is formed by the partition 12b, the partition 12b that divides the compressor impeller back surface region 30 into the inner diameter-side space 31 and the outer diameter-side space 32 in order to reduce the back surface load of the compressor impeller 22 can function as a means for forming the inlet-side fixed throttle TH1, and high use efficiency in layout can also be obtained.

The rotary member 20 is rotated by a motor 28. By generating a differential pressure by the internal pressure of the flow path formed in the casing 10, the pressure of the space 38 formed on the motor chamber 17 side of the 2 nd partition wall 15 (portion B in fig. 3) is higher than the pressure of the turbine wheel back surface region 39. Therefore, the fluid can be suppressed from entering from the turbine chamber 16b side to the motor chamber 17 side (see arrow D in fig. 3).

By adopting a structure in which the pressure is reduced at least at 2 points of the inlet-side fixed throttle TH1 and the outlet-side fixed throttle TH2, the differential pressure as described above can be easily formed. The differential pressure can be easily formed by adjusting the size and/or ratio of the flow passage cross-sectional area of the inlet side fixed throttle TH1 to the flow passage cross-sectional area of the outlet side fixed throttle TH2, and for example, the flow passage cross-sectional area of the inlet side fixed throttle TH1 is preferably larger than the flow passage cross-sectional area of the outlet side fixed throttle TH 2. With this configuration, the pressure in the motor chamber 17 can be easily made higher than the average of the back pressure of the turbine wheel 23 and the atmospheric pressure, and the pressure in the space 38 (portion B in fig. 3) formed on the motor chamber 17 side of the 2 nd partition wall 15 can be easily made higher than the pressure in the turbine wheel back surface region 39. The cross-sectional flow area when the fluid leaks and passes between the 2 nd partition wall 15 and the shaft seal portion 19 (the notch formed in the shaft seal portion 19) is smaller than the cross-sectional flow areas of the inlet-side fixed throttle portion TH1 and the outlet-side fixed throttle portion TH 2.

In embodiment 1 described above, the downstream side of the outlet side fixed throttle TH2 is set to a pressure value corresponding to the intake pressure, but the downstream side of the outlet side fixed throttle TH2 may be set to a pressure value corresponding to the atmospheric pressure or a pressure value corresponding to the exhaust pressure of the turbine impeller 23 as long as the pressure difference can be formed within the above-described range. IN the formation of the differential pressure as described above, a valve function may be disposed at an arbitrary position (for example, an arbitrary position of the inlet-side flow passage IN, the communication passage CN, and the outlet-side flow passage EN) IN addition to the inlet-side fixed throttle TH1 and the outlet-side fixed throttle TH2, and the differential pressure formation may be assisted by the valve function.

Here, the temperature of the periphery of the shaft 21 in the housing 10 is likely to rise without taking any special measures. In particular, when the intrusion of the fluid into the motor chamber 17 is suppressed, the temperature around the shaft 21 in the housing 10 is more likely to increase due to the suppression of the flow of the fluid. IN the present embodiment, since a differential pressure is generated by the internal pressure of the flow path formed IN the casing 10, the fluid moves to the inlet-side flow path IN, the communication path CN, and the outlet-side flow path EN IN order. Since the fluid from the inlet-side flow passage IN (the connection portion INa) passes through the communication passage CN so as to flow toward the outlet-side flow passage EN (the connection portion ENa) located on the opposite side of the connection portion INa with respect to the motor 28, a heat radiation effect of the fluid to the space around the shaft 21 can be obtained, and an increase IN temperature around the shaft 21 IN the casing 10 can also be suppressed. That is, the outlet-side flow path EN is provided closer to the turbine wheel 23 than the thrust foil bearing 24 and the radial foil bearings 25 and 26, and can radiate or cool heat therefrom, and the outlet-side flow path EN is provided closer to the turbine wheel 23 than the resolver 27, and can radiate or cool heat from the resolver 27.

In embodiment 1 described above, the outlet-side flow passage EN is provided in the center case 14, and communicates the space 38 with the external space. Depending on the specification, it may not be necessary to perform machining on the center housing 14 in order to form the outlet-side flow passage EN. In this case, the cross-sectional flow area of the inlet-side fixed throttle TH1 is preferably larger than the cross-sectional flow area of the outlet-side fixed throttle TH 2.

[ embodiment 2]

Fig. 4 is a sectional view showing the turbo fluid machine 102 according to embodiment 2. In the turbo fluid machine 102, the casing 10 is further provided with a connection flow path 29 for supplying the fluid passing through the outlet side flow path EN to the suction port 11a on the upstream side of the compressor impeller 22.

When the turbo fluid machine 102 is used in a fuel cell system as an air compressor, for example, the air flow meter 40 can measure or control how much air is supplied to a stack of the fuel cell system. By further providing the connection flow path 29 in the turbo fluid machine 102, it is possible to reduce an error in the flow rate that may occur between the measurement value of the air flow meter 40 and the compressed air actually sent out from the discharge chamber 11 c. The flow rate of air supplied for differential pressure formation and heat dissipation can be minimized.

The connection flow passage 29 may be formed in the center housing 13 provided with a water jacket, not shown. The connection flow path 29 is configured to return the compressed fluid to the suction port 11a again, and when this configuration is adopted, the discharge temperature tends to rise. By providing the connection flow path 29 so as to be able to exchange heat with the water jacket, an increase in intake temperature and a decrease in flow rate due to heat generation can be suppressed. In addition, even when an intercooler or the like is provided on the downstream side, the amount of work can be reduced. With this configuration, the heat dissipation efficiency to the thrust foil bearing 24, the radial foil bearings 25 and 26, and the resolver 27 can also be improved.

[ embodiment 3]

Fig. 5 is a sectional view showing the turbo fluid machine 103 according to embodiment 3. In the turbo fluid machine 103, 2 flow paths 29a and 29b are provided in the casing 10. The inlet-side flow path IN is provided inside the flow path 29 a. The inlet-side flow path IN is formed so as to connect the discharge port 11d on the downstream side of the compressor impeller 22 to the space 38 formed on the motor chamber 17 side of the 2 nd partition wall 15.

The outlet side fixed restriction TH2 is formed in a shaft seal portion between the 1 st partition wall 12 (shaft hole 12a) and the shaft 21. The flow path 29b connects the inner diameter side space 31 to a space other than the outer diameter side space 32 (here, the suction port 11a on the upstream side of the compressor impeller 22) so that the pressure of the inner diameter side space 31 is lower than the pressure of the outer diameter side space 32 at the time of pressure-feeding the fluid.

Fig. 6 is a cross-sectional view showing a state of the turbo fluid machine 103 during operation. Fluid is taken in from the suction port 11a and is pressurized by the compressor impeller 22. Most of the fluid after the pressure increase passes through the diffuser and moves toward the discharge chamber 11 c. A part of the fluid having been pressurized and having reached the discharge chamber 11c passes through the discharge port 11d, the flow path 29a, and the inlet-side fixed throttle TH 1. The pressure is reduced by passing through the inlet side fixed throttle TH 1.

The fluid passes through the inlet side flow path IN (inlet side fixed throttle TH 1). Then, the fluid from the inlet-side flow passage IN (connection portion INa) passes through the communication passage CN toward the outlet-side flow passage EN (connection portion ENa) located on the opposite side of the connection portion INa with respect to the motor 28 so as to flow along at least a part of the shaft 21. In the present embodiment, the communication path CN is formed so that the fluid flowing through the communication path CN passes through a position between the radial foil bearing 26 and the inner ring 21c, a position between the stator 28a and the rotor 28b, a position between the radial foil bearing 25 and the inner ring 21b, and a position between the thrust foil bearing 24 and the large diameter portion 21 a. The position of the inlet side fixed throttle TH1 may be set closer to the 2 nd partition wall 15 so that the fluid also passes through a position between the resolver rotor 27a and the resolver stator 27 b. The pressure therebetween is substantially constant or slightly reduced.

The fluid that has passed through the communication passage CN, that is, the fluid that has reached a position between the shaft hole 12a and the shaft 21 (i.e., the outlet-side fixed restriction TH2) further decreases in pressure by passing through the outlet-side flow passage EN. The fluid further passes through the inner diameter side space 31 and the flow path 29 b. The pressure of the communication passage CN is increased by the pressure supplied from the inlet-side flow passage IN to the communication passage CN, and the pressure of the space 38 (motor housing space 18) formed on the motor chamber 17 side of the 2 nd partition wall 15 is higher than the pressure of the turbine wheel back surface region 39. Therefore, with this configuration, the same operation and effect as those of embodiment 1 described above can be obtained.

[ embodiment 4]

Fig. 7 is a sectional view showing the turbo fluid machine 104 according to embodiment 4. In the turbo fluid machine 104, 2 flow paths 29a and 29b are also provided in the casing 10. The inlet-side flow path IN is provided inside the flow path 29 a. The inlet-side flow path IN is formed so as to connect the discharge port 11d on the downstream side of the compressor impeller 22 to the shaft hole 12a at the outer periphery of the shaft 21 IN the 1 st partition wall 12.

The outlet side fixed throttle TH2 is provided in the center housing 14. The outlet-side fixed throttle TH2 connects the space 38 formed on the motor chamber 17 side of the 2 nd partition wall 15 with a space other than the space 38 so that the pressure of the space 38 (the motor accommodating space 18) formed on the motor chamber 17 side of the 2 nd partition wall 15 becomes higher than the pressure of the turbine wheel back surface region 39 by the pressure supplied from the inlet-side flow passage IN to the communication passage CN. The flow path 29b connects the inner diameter side space 31 to a space other than the outer diameter side space 32 so that the pressure of the inner diameter side space 31 is lower than the pressure of the outer diameter side space 32 at the time of pressure feeding of the fluid.

Fig. 8 is a sectional view showing an operating state of the turbo fluid machine 104. Fluid is taken in from the suction port 11a and is pressurized by the compressor impeller 22. A part of the fluid after the pressure increase passes through the diffuser and moves toward the discharge chamber 11 c. A part of the fluid having been pressurized and having reached the discharge chamber 11c passes through the discharge port 11d, the flow path 29a, and the inlet-side fixed throttle TH 1. The pressure is reduced by passing through the inlet side fixed throttle TH 1.

The fluid passes through the inlet side flow path IN (inlet side fixed throttle TH 1). Then, the fluid from the inlet-side flow passage IN (connection portion INa) passes through the communication passage CN toward the outlet-side flow passage EN (connection portion ENa) located on the opposite side of the connection portion INa with respect to the motor 28 so as to flow along at least a part of the shaft 21. In the present embodiment, the communication path CN is formed so that the fluid flowing through the communication path CN passes through a position between the shaft hole 12a and the shaft 21, a position between the thrust foil bearing 24 and the large diameter portion 21a, a position between the radial foil bearing 25 and the inner ring 21b, a position between the stator 28a and the rotor 28b, a position between the radial foil bearing 26 and the inner ring 21c, and a position between the resolver rotor 27a and the resolver stator 27 b. The pressure therebetween is substantially constant or slightly reduced.

The fluid having passed through the communication passage CN, that is, the fluid having reached the space 38 further passes through the outlet-side flow passage EN. The pressure is further reduced by the outlet side fixed throttle TH2 of the outlet side flow path EN, and the pressure becomes a pressure value corresponding to the intake pressure, for example. The pressure of the communication passage CN is increased by the pressure supplied from the inlet-side passage IN to the communication passage CN, and the pressure of the space 38 formed on the motor chamber 17 side of the 2 nd partition wall 15 is higher than the pressure of the turbine wheel back surface region 39. Therefore, with this configuration, the same operation and effect as those of embodiment 1 described above can be obtained.

As the fluid is pumped, the pressure in the compressor impeller back surface region 30 (impeller back surface pressure) increases. The back pressure acts to displace the compressor impeller 22 toward the inlet side of the suction port 11 a. The back pressure acting in this way is preferably low. On the other hand, the pressure in the space 38 formed on the motor chamber 17 side of the 2 nd partition wall 15 needs to be higher than the pressure in the turbine wheel back surface region 39.

In the present embodiment, the flow path 29b is provided in the 1 st partition wall 12, and the flow path 29b hardly communicates with the space 38. Therefore, even if the pressure of the space 38 is set to a high value, the effect thereof is suppressed from directly causing an increase in the back pressure (back load) of the compressor impeller 22. The displacement of compressor impeller 22 toward the inlet side of suction port 11a can be further suppressed.

While the embodiments have been described above, the above disclosure is in all aspects illustrative and not restrictive. The technical scope of the present invention is defined by the claims, and all changes that come within the meaning and range of equivalency of the claims are intended to be embraced therein.