JP2011185221A - Turbo compressor and turbo refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a turbo compressor which reduces manufacturing labor hours and cost while improving its workability during assembling a flow control part and a power transmission shaft together, and to provide a turbo refrigerator. <P>SOLUTION: The turbo compressor includes the flow control part 42 for controlling a flow amount of gas to be introduced into an impeller 21a, a driving part 43 for driving the flow control part 42, and the power transmission shaft 44 for transmitting power generated by the driving part 43 to the flow control unit 42, wherein a frame 45 is provided around the flow control unit 42. The frame 45 includes a suction port 45a for gas to be introduced into the impeller 21a, and a hole portion 45b through which the power transmission shaft 44 passes. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

 The present invention relates to a turbo compressor and a turbo refrigerator.

 As a refrigerator that cools or freezes an object to be cooled such as water, a turbo refrigerator that includes a turbo compressor that compresses and discharges refrigerant gas is known. A turbo compressor included in such a turbo chiller may be provided with a flow rate adjusting unit that adjusts the flow rate of refrigerant gas introduced into a rotating impeller, for example, as shown in Patent Document 1. By adjusting the flow rate of the refrigerant gas by the flow rate adjustment unit, it is possible to adjust the compression performance of the turbo compressor, the cooling / refrigeration performance of the turbo refrigerator, and the like. The flow rate adjustment unit includes a flow rate adjustment unit including a plurality of vanes (blades), a drive unit such as a motor that drives the flow rate adjustment unit, and a power transmission shaft that transmits power generated by the drive unit to the flow rate adjustment unit. And.

JP 2007-177695 A

By the way, the power transmission shaft is provided through a hole formed in the casing of the turbo compressor, and connects a flow rate adjusting unit and a driving unit provided inside and outside the casing, respectively. In assembling the flow rate adjusting unit and the power transmission shaft, it is necessary to first install the flow rate adjusting unit inside the casing, and then to connect the power transmission shaft to the flow rate adjusting unit through the hole.
However, since the connection location between the flow rate adjusting unit and the power transmission shaft installed inside the casing cannot be confirmed from the outside, the assembly work of the flow rate adjusting unit and the power transmission shaft is difficult, and the workability of the assembly is reduced. It was. As a result, there has been a problem that the labor and cost of manufacturing a turbo compressor and a centrifugal chiller including such a flow rate adjusting unit and a power transmission shaft increase.

 The present invention has been made in consideration of the above points. A turbo compressor and a centrifugal chiller capable of improving the workability of assembling the flow rate adjusting unit and the power transmission shaft and reducing the manufacturing effort and cost. The purpose is to provide.

In order to solve the above problems, the present invention employs the following means.
A turbo compressor according to the present invention transmits a flow rate adjusting unit that adjusts a flow rate of a gas introduced into an impeller, a drive unit that drives the flow rate adjusting unit, and power generated by the drive unit to the flow rate adjusting unit. A turbo compressor comprising a power transmission shaft, comprising a frame provided so as to surround a flow rate adjusting portion, wherein the frame has a suction port for a gas introduced into the impeller and a hole provided through the power transmission shaft. The structure which comprises a part is employ | adopted.
According to the present invention, the power transmission shaft is provided through the hole formed in the frame, and connects the flow rate adjusting unit and the driving unit provided inside and outside the frame, respectively. In assembling the flow rate adjusting unit and the power transmission shaft, before the frame is fixed to the casing of the turbo compressor, the power transmission shaft can be passed through the hole of the frame and connected to the flow rate adjusting unit. In other words, the assembly can be performed while confirming the connection portion between the flow rate adjusting unit and the power transmission shaft from the outside, and the workability of the assembly of the flow rate adjusting unit and the power transmission shaft is improved.

 In addition, the turbo compressor according to the present invention employs a configuration in which the frame is provided in an annular shape so as to surround the flow rate adjusting portion and has an outer diameter that decreases as the distance from the impeller increases.

 In addition, the turbo compressor according to the present invention employs a configuration including an output shaft that outputs the power of the drive unit and a connecting portion that connects the power transmission shaft.

 In addition, the turbo compressor according to the present invention employs a configuration in which a seal member that keeps a hole portion through which the power transmission shaft passes is provided airtight.

 The turbo refrigerator according to the present invention includes a condenser that cools and liquefies the compressed refrigerant, an evaporator that cools the object to be cooled by evaporating the liquefied refrigerant and taking heat of vaporization from the object to be cooled, A compressor that compresses the refrigerant evaporated in the evaporator and supplies the compressed refrigerant to the condenser, comprising the turbo compressor according to any one of claims 1 to 4 as a compressor. The configuration is adopted.

According to the present invention, the following effects can be obtained.
ADVANTAGE OF THE INVENTION According to this invention, it can assemble while confirming the connection location of a flow volume adjustment part and a power transmission shaft from the outside, and the workability | operativity of an assembly with a flow volume adjustment part and a power transmission shaft improves. Therefore, there is an effect that it is possible to reduce manufacturing effort and cost in a turbo compressor and a centrifugal chiller including such a flow rate adjusting unit and a power transmission shaft.

It is a block diagram which shows schematic structure of the turbo refrigerator in embodiment of this invention. It is a horizontal sectional view of a turbo compressor in an embodiment of the present invention. It is a horizontal sectional view of a flow rate adjustment unit in an embodiment of the present invention. It is A arrow directional view of FIG.

 Hereinafter, embodiments of the present invention will be described with reference to FIGS. In each drawing used for the following description, the scale of each member is appropriately changed to make each member a recognizable size.

FIG. 1 is a block diagram showing a schematic configuration of a turbo refrigerator S1 in the present embodiment.
The turbo chiller S1 in the present embodiment is installed in a building, a factory, or the like, for example, to generate cooling water for air conditioning. As shown in FIG. 1, the condenser 1, the economizer 2, and the evaporation And a turbo compressor 4.

 The condenser 1 is supplied with a compressed refrigerant gas X1, which is a compressed gaseous refrigerant, and cools and liquefies the compressed refrigerant gas X1 to obtain a refrigerant liquid X2. As shown in FIG. 1, the condenser 1 is connected to the turbo compressor 4 through a flow path R1 through which the compressed refrigerant gas X1 flows, and is connected to the economizer 2 through a flow path R2 through which the refrigerant liquid X2 flows. Has been. In addition, the expansion valve 5 for decompressing the refrigerant liquid X2 is installed in the flow path R2.

 The economizer 2 temporarily stores the refrigerant liquid X2 decompressed by the expansion valve 5. The economizer 2 is connected to the evaporator 3 via a flow path R3 through which the refrigerant liquid X2 flows. It is connected. Note that an expansion valve 6 for further reducing the pressure of the refrigerant liquid X2 is installed in the flow path R3. Further, the flow path R4 is connected to the turbo compressor 4 so as to supply a gas phase component X3 to a second compression stage 22 described later included in the turbo compressor 4.

 The evaporator 3 cools the object to be cooled by evaporating the refrigerant liquid X2 and removing the heat of vaporization from the object to be cooled such as water. The evaporator 3 is connected to the turbo compressor 4 via a flow path R5 through which a refrigerant gas X4 generated by evaporating the refrigerant liquid X2 flows. The flow path R5 is connected to a first compression stage 21 (described later) included in the turbo compressor 4.

 The turbo compressor 4 compresses the refrigerant gas X4 into a compressed refrigerant gas X1. The turbo compressor 4 is connected to the condenser 1 through the flow path R1 through which the compressed refrigerant gas X1 flows as described above, and is connected to the evaporator 3 through the flow path R5 through which the refrigerant gas X4 flows. Yes.

In the turbo chiller S1 configured as described above, the compressed refrigerant gas X1 supplied to the condenser 1 via the flow path R1 is liquefied and cooled by the condenser 1 to become a refrigerant liquid X2.
The refrigerant liquid X2 is decompressed by the expansion valve 5 when supplied to the economizer 2 via the flow path R2, and is temporarily stored in the economizer 2 in a decompressed state, and then evaporated via the flow path R3. When supplied to the evaporator 3, the pressure is further reduced by the expansion valve 6, and the pressure is further reduced and supplied to the evaporator 3.
The refrigerant liquid X2 supplied to the evaporator 3 is evaporated by the evaporator 3 to become the refrigerant gas X4, and is supplied to the turbo compressor 4 via the flow path R5.
The refrigerant gas X4 supplied to the turbo compressor 4 is compressed by the turbo compressor 4 into the compressed refrigerant gas X1, and is supplied again to the condenser 1 via the flow path R1.
Note that the gas phase component X3 of the refrigerant generated when the refrigerant liquid X2 is stored in the economizer 2 is supplied to the turbo compressor 4 via the flow path R4, and is compressed together with the refrigerant gas X4 to be compressed refrigerant gas X1. Is supplied to the condenser 1 through the flow path R1.
And in such turbo refrigerator S1, when the refrigerant | coolant liquid X2 evaporates in the evaporator 3, it cools or refrigerates a cooling target object by taking heat of vaporization from a cooling target object.

Subsequently, the turbo compressor 4 including the characteristic part of the present embodiment will be described in more detail. FIG. 2 is a horizontal sectional view of the turbo compressor 4 in the present embodiment.
As shown in FIG. 2, the turbo compressor 4 in the present embodiment includes a motor unit 10, a compressor unit 20, and a gear unit 30.

The motor unit 10 includes an output shaft 11 and a motor 12 serving as a drive source for driving the compressor unit 20, and a motor casing 13 that surrounds the motor 12 and in which the motor 12 is installed. The drive source for driving the compressor unit 20 is not limited to the motor 12 and may be, for example, an internal combustion engine.
The output shaft 11 of the motor 12 is rotatably supported by a first bearing 14 and a second bearing 15 that are fixed to the motor casing 13.

 The compressor unit 20 sucks and compresses the refrigerant gas X4 (see FIG. 1), and further compresses the refrigerant gas X4 compressed in the first compression stage 21 to compress the compressed refrigerant gas X1 ( As shown in FIG. 1, a second compression stage 22 that discharges, and a rotary shaft 23 that extends across the first compression stage 21 and the second compression stage 22 are provided.

The first compression stage 21 imparts velocity energy to the refrigerant gas X4 supplied from the thrust direction and discharges it in the radial direction, and the velocity imparted to the refrigerant gas X4 by the first impeller 21a. A first diffuser 21b that compresses energy by converting it into pressure energy, and a first scroll chamber 21c that guides the refrigerant gas X4 compressed by the first diffuser 21b to the outside of the first compression stage 21 are provided. The first diffuser 21b and the first scroll chamber 21c are formed by a first impeller casing 21e that surrounds the first impeller 21a.
The first impeller 21 a is fixed to the rotary shaft 23 and is driven to rotate when the rotational power of the motor 12 is transmitted to the rotary shaft 23.

 The first compression stage 21 includes a flow rate adjusting unit 40 that adjusts the flow rate of the refrigerant gas X4 introduced into the first impeller 21a. The flow rate adjusting unit 40 is airtightly fixed to the first impeller casing 21e. Further, the flow rate adjusting unit 40 includes a suction port 41 for the refrigerant gas X4. The suction port 41 penetrates in the axial direction of the rotating shaft 23.

Here, the flow rate adjustment unit 40 which is a characteristic part of the present embodiment will be described in more detail. FIG. 3 is a horizontal sectional view of the flow rate adjusting unit 40 in the present embodiment. FIG. 4 is a view taken in the direction of arrow A in FIG. For the sake of explanation, in FIG. 3, the first impeller 21a and the rotating shaft 23 are represented by phantom lines.
As shown in FIGS. 3 and 4, the flow rate adjustment unit 40 includes a flow rate adjustment unit 42, a drive unit 43, a power transmission shaft 44, and a suction frame 45 (frame).

 The flow rate adjusting unit 42 adjusts the flow rate of the refrigerant gas X4 (see FIG. 1) introduced into the first impeller 21a, and includes a plurality of vanes 42a that are blade members. The plurality of vanes 42a are rotatably provided on a vane frame 42b formed in a substantially circular shape, and are arranged side by side in the circumferential direction on the inner peripheral surface side of the vane frame 42b. The inner peripheral surface side of the vane frame 42 b forms a part of the suction port 41. Therefore, the apparent area from the upstream side of the suction port 41 is adjusted by the plurality of vanes 42a rotating in synchronization. The vane frame 42b is fixed to the suction frame 45 by a plurality of screw members 42c.

 A drive-side crank arm 42d is fixed to one of the plurality of vanes 42a. The drive-side crank arm 42 d is provided on the outer peripheral surface side of the vane frame 42 b and is connected to the power transmission shaft 44. The drive side crank arm 42d is connected to the drive ring 42f via the drive side rod 42e. The drive-side crank arm 42d includes an arm portion that protrudes in a direction intersecting with the rotation axis thereof, and the drive-side rod 42e is connected to the arm portion.

The drive ring 42f rotates the plurality of vanes 42a in synchronization, is formed in an annular shape, and is provided so as to surround the vane frame 42b. The drive ring 42f is rotatably installed on the outer peripheral surface side of the vane frame 42b via a plurality of rolling elements 42g.
The drive ring 42f is connected to a plurality of driven crank arms 42i via a plurality of driven rods 42h, respectively. The driven-side crank arm 42i includes an arm portion that protrudes in a direction intersecting with the rotation axis thereof, and the driven-side rod 42h is connected to the arm portion. A plurality of vanes 42a are fixed to the plurality of driven crank arms 42i, respectively.

 The drive unit 43 is a motor that generates power for driving the flow rate adjusting unit 42. The drive unit 43 is fixed to the suction frame 45 via a bracket 46. The drive unit 43 is provided with a second output shaft 43a (output shaft) that projects the power. In addition, the drive part 43 is not limited to a motor, For example, the drive part using hydraulic pressure or pneumatic pressure may be sufficient.

 The power transmission shaft 44 is a shaft member for transmitting the power generated by the drive unit 43 to the flow rate adjustment unit 42. The end of the power transmission shaft 44 on the drive unit 43 side is connected to the second output shaft 43 a of the drive unit 43 via a connection plate 46 a (connection unit) provided in the bracket 46. On the other hand, the end of the power transmission shaft 44 on the flow rate adjustment unit 42 side is connected to the drive side crank arm 42d as described above. The drive-side crank arm 42d is formed with a connecting hole, and a power transmission shaft 44 is inserted into and connected to the connecting hole. Further, in order to engage the power transmission shaft 44 with the drive-side crank arm 42d around its axis, a key member 44a is fixed to the end of the power transmission shaft 44 on the flow rate adjusting portion 42 side, and the drive-side crank arm 42d. A groove portion corresponding to the key member 44a is formed in the connecting hole portion.

 The suction frame 45 is a member that surrounds the flow rate adjustment unit 42 and fixes the flow rate adjustment unit 42 and the drive unit 43 to the first impeller casing 21e (see FIG. 2). The suction frame 45 is formed with an opening 45 a (suction port) that forms a part of the suction port 41. The suction frame 45 is provided in an annular shape so as to surround the flow rate adjusting unit 42 and has an outer diameter that decreases as the distance from the first impeller 21a increases. Therefore, the suction frame 45 can be reduced in size and weight as compared with a case where the suction frame 45 is formed in a cylindrical shape, for example.

 The suction frame 45 is formed with a hole 45b through which the power transmission shaft 44 is provided. That is, the power transmission shaft 44 is provided through the hole 45 b, and connects the flow rate adjustment unit 42 and the drive unit 43 provided respectively inside and outside the suction frame 45.

 In assembling the flow rate adjusting unit 42 and the power transmission shaft 44, the power transmission shaft 44 is passed through the hole 45b before the suction frame 45 provided with the flow rate adjusting unit 42 is fixed to the first impeller casing 21e. The flow rate adjustment unit 42 can be connected. In other words, the assembly can be performed while confirming from the outside the connection location between the drive side crank arm 42d of the flow rate adjusting unit 42 and the power transmission shaft 44, and the power transmission shaft 44 to which the key member 44a is fixed is connected to the drive side crank arm. It can be easily inserted into the connecting hole 42d. Therefore, the workability of assembling the flow rate adjusting unit 42 and the power transmission shaft 44 is improved.

 The power transmission shaft 44 and the second output shaft 43 a are connected by a connection plate 46 a, and the drive unit 43 is fixed to the suction frame 45 via the bracket 46. Since these connections and fixings can be easily performed, the drive unit 43 may be fixed to the suction frame 45 either before or after the suction frame 45 is fixed to the first impeller casing 21e.

 In order to prevent the refrigerant gas X4 from flowing out through the hole 45b, the flow rate adjustment unit 40 includes a packing 45c (seal member) that keeps the hole 45b provided through the power transmission shaft 44 airtight. ing. For example, V packing is used for the packing 45c.

 The suction frame 45 includes a flange portion 45d, and is fixed to the first impeller casing 21e by a screw member (not shown) provided through the flange portion 45d. In addition, an annular flange packing 45e is provided on the flange portion 45d in order to keep the connecting portion between the flange portion 45d and the first impeller casing 21e airtight.

 The flow rate adjusting unit 40 is provided with an oil cutting plate 47, and the oil cutting plate 47 is fixed to the vane frame 42 b of the flow rate adjusting unit 42. In the oil cutting plate 47, mist-like lubricating oil that flows into the suction frame 45 through a pressure equalizing pipe (not shown) that connects the suction frame 45 and an oil tank 34 (see FIG. 2) described later is used for the first impeller. It is for preventing flowing to the 21a side.

Returning to FIG. 2, the second compression stage 22 includes a second impeller 22a that gives velocity energy to the refrigerant gas X4 supplied from the thrust direction after being compressed in the first compression stage 21 and discharges it in the radial direction. The second diffuser 22b that compresses and discharges the compressed energy gas X1 by converting the velocity energy applied to the refrigerant gas X4 by the second impeller 22a into pressure energy, and the compressed refrigerant gas X1 that is discharged from the second diffuser 22b. Is provided to the outside of the second compression stage 22, and an introduction scroll chamber 22d for introducing the refrigerant gas X4 compressed in the first compression stage 21 to the second impeller 22a.
The second diffuser 22b, the second scroll chamber 22c, and the introduction scroll chamber 22d are formed by a second impeller casing 22e that surrounds the second impeller 22a.

The second impeller 22a is fixed to the rotary shaft 23 so as to be back-to-back with the first impeller 21a, and is driven to rotate when the rotational power of the motor 12 is transmitted to the rotary shaft 23.
The second scroll chamber 22c is connected to a flow path R1 (see FIG. 1) for supplying the compressed refrigerant gas X1 to the condenser 1, and the compressed refrigerant gas X1 derived from the second compression stage 22 is passed through the flow path R1. To supply.

 The first scroll chamber 21c of the first compression stage 21 and the introduction scroll chamber 22d of the second compression stage 22 are external pipes provided separately from the first compression stage 21 and the second compression stage 22 (see FIG. The refrigerant gas X4 compressed in the first compression stage 21 is supplied to the second compression stage 22 through the external pipe. The above-described flow path R4 (see FIG. 1) is connected to the external pipe, and the refrigerant gas phase component X3 generated in the economizer 2 is supplied to the second compression stage 22 via the external pipe. It has become.

 The rotation shaft 23 is fixed to the third bearing 26 fixed to the second impeller casing 22e in the space 25 between the first compression stage 21 and the second compression stage 22, and to the gear unit 30 side of the second impeller casing 22e. The fourth bearing 27 is rotatably supported.

 The gear unit 30 is for transmitting the rotational power of the motor 12 to the rotary shaft 23, and is a flat gear 31 fixed to the output shaft 11 and a pinion fixed to the rotary shaft 23 and meshing with the flat gear 31. A gear 32 and a gear casing 33 that accommodates the spur gear 31 and the pinion gear 32 are provided.

 The spur gear 31 has an outer diameter larger than that of the pinion gear 32, and the spur gear 31 and the pinion gear 32 cooperate to increase the rotational speed of the rotary shaft 23 relative to the rotational speed of the output shaft 11. The rotational power of the motor 12 is transmitted to the rotary shaft 23. In addition, it is not limited to such a transmission method, You may set the diameter of a some gear so that the rotation speed of the rotating shaft 23 may be the same number or reduce with respect to the rotation speed of the output shaft 11. FIG.

 The gear casing 33 is formed separately from the motor casing 13 and the second impeller casing 22e, and connects the two. Inside the gear casing 33, an accommodation space 33a for accommodating the spur gear 31 and the pinion gear 32 is formed. Further, the gear casing 33 is provided with an oil tank 34 in which the lubricating oil supplied to the sliding portion of the turbo compressor 4 is collected and stored.

Next, the operation of the turbo compressor 4 in this embodiment will be described.
First, the rotational power of the motor 12 is transmitted to the rotary shaft 23 via the spur gear 31 and the pinion gear 32, whereby the first impeller 21a and the second impeller 22a of the compressor unit 20 are rotationally driven.

When the first impeller 21a is rotationally driven, the suction port 41 of the flow rate adjusting unit 40 is in a negative pressure state, and the refrigerant gas X4 flows from the flow path R5 into the first compression stage 21 through the suction port 41.
At this time, the flow rate adjusting unit 40 adjusts the flow rate of the refrigerant gas X4, whereby the compression performance of the turbo compressor 4, the cooling / refrigeration performance of the turbo chiller S1, and the like can be adjusted. More specifically, first, the drive unit 43 operates, and the second output shaft 43a and the power transmission shaft 44 rotate. As the power transmission shaft 44 rotates, the drive-side crank arm 42d rotates, and one vane 42a fixed to the drive-side crank arm 42d rotates. Further, when the drive-side crank arm 42d rotates, the drive ring 42f connected via the drive-side rod 42e rotates. As the drive ring 42f rotates, the plurality of driven crank arms 42i connected via the plurality of driven rods 42h rotate, and the vanes 42a fixed to the driven crank arms 42i also rotate. As described above, the plurality of vanes 42a are rotated in synchronization with the operation of the drive unit 43, and the apparent area from the upstream side of the suction port 41 can be adjusted. Therefore, the flow rate of the refrigerant gas X4 passing through the suction port 41 can be adjusted by the operation of the drive unit 43.

The refrigerant gas X4 that has passed through the suction port 41 and has flowed into the first compression stage 21 flows into the first impeller 21a from the thrust direction, is given velocity energy by the first impeller 21a, and is discharged in the radial direction. .
The refrigerant gas X4 discharged from the first impeller 21a is compressed by converting velocity energy into pressure energy by the first diffuser 21b.
The refrigerant gas X4 discharged from the first diffuser 21b is led out of the first compression stage 21 through the first scroll chamber 21c.
Then, the refrigerant gas X4 led out of the first compression stage 21 is supplied to the second compression stage 22 via an external pipe (not shown).

The refrigerant gas X4 supplied to the second compression stage 22 flows into the second impeller 22a from the thrust direction through the introduction scroll chamber 22d, and is discharged in the radial direction to which velocity energy is applied by the second impeller 22a.
The refrigerant gas X4 discharged from the second impeller 22a is further compressed into a compressed refrigerant gas X1 by converting velocity energy into pressure energy by the second diffuser 22b.
The compressed refrigerant gas X1 discharged from the second diffuser 22b is led out of the second compression stage 22 through the second scroll chamber 22c.
Then, the compressed refrigerant gas X1 led out of the second compression stage 22 is supplied to the condenser 1 via the flow path R1.
Thus, the operation of the turbo compressor 4 is completed.

 According to the present embodiment, the assembly can be performed while confirming the connection portion between the drive side crank arm 42 d of the flow rate adjusting unit 42 and the power transmission shaft 44 from the outside, and the flow rate adjusting unit 42 and the power transmission shaft 44 can be assembled. Assembling workability is improved. Therefore, there is an effect that it is possible to reduce manufacturing effort and cost in the turbo compressor 4 and the turbo refrigerator S1 including the flow rate adjusting unit 42 and the power transmission shaft 44.

 As described above, the preferred embodiments according to the present invention have been described with reference to the accompanying drawings, but the present invention is not limited to the examples. Various shapes, combinations, and the like of the constituent members shown in the above-described examples are examples, and various modifications can be made based on design requirements and the like without departing from the gist of the present invention.

 For example, the suction frame 45 in the above embodiment has an outer diameter that decreases as the distance from the first impeller 21a increases. However, the present invention is not limited to this, and the suction frame 45 is formed in, for example, a cylindrical shape. May be.

 Moreover, although the turbo compressor 4 in the said embodiment is used in turbo refrigerator S1, it may be used as a supercharger which supplies the compressed air to an internal combustion engine, for example.

DESCRIPTION OF SYMBOLS 1 ... Condenser, 3 ... Evaporator, 4 ... Turbo compressor, 21a ... 1st impeller (impeller), 42 ... Flow volume adjustment part, 43 ... Drive part, 43a ... 2nd output shaft (output shaft), 44 ... Power Transmission shaft, 45 ... suction frame (frame), 45a ... opening (suction port), 45b ... hole, 46a ... connection plate (connection part), 45c ... packing (seal member), S1 ... turbo refrigerator

Claims (5)

Turbo compression comprising: a flow rate adjusting unit that adjusts the flow rate of gas introduced into the impeller; a drive unit that drives the flow rate adjusting unit; and a power transmission shaft that transmits power generated by the drive unit to the flow rate adjusting unit. Machine,
A frame provided to surround the flow rate adjustment unit;
The turbo compressor according to claim 1, wherein the frame includes a suction port for a gas introduced into the impeller, and a hole portion through which the power transmission shaft passes. The turbo compressor according to claim 1, wherein
The turbo compressor is characterized in that the frame is provided in an annular shape so as to surround the flow rate adjusting portion, and has an outer diameter that decreases as the distance from the impeller increases. The turbo compressor according to claim 1 or 2,
A turbo compressor comprising: a connecting portion that connects an output shaft that outputs power of the driving portion and the power transmission shaft. The turbo compressor according to any one of claims 1 to 3,
A turbo compressor, comprising: a seal member that keeps the hole portion through which the power transmission shaft is provided airtight. A condenser that cools and liquefies the compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes heat of vaporization from the object to be cooled, and cools the refrigerant that has evaporated in the evaporator. A turbo chiller comprising a compressor for compressing and supplying to the condenser,
A turbo refrigerator comprising the turbo compressor according to any one of claims 1 to 4 as the compressor.