JP2003307197A - Turbo-compressor and refrigerator using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a turbo-compressor having satisfactorily controlled suction flow of fluid for practical use and improved controllability of freezing capacity without increasing the size as a whole, and to provide a refrigerator using the turbo-compressor. <P>SOLUTION: A channel part 101 has an inlet of the fluid in the peripheral direction with respect to a main shaft 2 and leads the incoming fluid from the inlet toward an impeller 3. The channel part 101 is equipped with a movable vane 100 comprising a plurality of blades 100a with variable installation angle to the flow direction of the fluid. The turbo-compressor 20 is adopted for the refrigerator. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turbo compressor for compressing a fluid by a rotating impeller and a refrigerating apparatus using the turbo compressor.

[0002]

2. Description of the Related Art Conventionally, a turbo type compressor has been widely used in various plants, but a turbo type compressor is also used as a refrigerant compressor in a refrigeration system. This turbo compressor is configured to compress a fluid by rotating a rotating shaft provided with an impeller (impeller).

In recent turbo compressors,
For the purpose of controlling the suction flow rate of the impeller, a so-called variable inlet guide vane is provided at the suction port.
The variable inlet guide vane will be briefly described below with reference to the drawings. Here, FIG. 5 is a sectional view of a main part of a turbo compressor provided with a conventional variable inlet guide vane, FIG. 6 is a front view of the variable inlet guide vane in a fully closed state as seen from the upstream side, and FIG. FIG. 6 is a sectional view taken along line AA of FIG. 5.

In FIG. 5, reference numeral 1 denotes a casing, 2
Is a main shaft, 3 is a first impeller, 4 is a diffuser, 5 is a return path, 6 is a flow path partition plate, 7 is a guide vane, 8 is a suction port,
Reference numeral 9 indicates a seal member, and 10 indicates a variable inlet guide vane.

In this case, a multi-stage (two-stage) centrifugal compressor is used as the turbo compressor, and the fluid to be compressed is the first stage (as indicated by the white arrow in the figure). After being sucked from the suction port 8 of the first stage), the impeller 3 is supported by the casing 1 and rotates together with the main shaft 2 by a drive mechanism (not shown). The velocity of gas is reduced to convert kinetic energy into internal energy. After passing through the diffuser 4, the return passage 5 and the guide vane 7 in this order, the pressure is increased and the pressure is guided to the inlet of the next stage (second stage).

A plurality of variable inlet guide vanes 10 having, for example, an airfoil cross section are installed between the outer periphery of the main shaft 2 and the casing 1 at the suction port 8 of such a turbo compressor. This variable inlet guide vane 10
Are rotatably supported so that their installation angles can be changed with respect to the flow direction (white arrow) of the fluid to be pressurized.

That is, by appropriately adjusting the opening between the fully opened position which is substantially parallel to the flow direction and the fully closed position where the suction port 8 is completely closed, the blade of the fluid for changing the valve opening and increasing the pressure. The refrigeration capacity can be controlled by adjusting the inflow angle to the car. Further, the fluid sucked into the impeller 3 is given a swirling flow when throttled while flowing in the axial direction.

Incidentally, FIG. 7A shows a state in which the variable inlet guide vane 10 is in a half-open position and is capable of sucking fluid, and FIG. 7B shows a rear edge side of the variable inlet guide vane 10. It shows a state in which the end portions 10a are in a fully closed position in which they are in close contact with the leading edge side negative pressure surfaces 10b of the adjacent guide vanes.

[0009]

By the way, in such a turbo compressor, the variable inlet guide vane 10 as described above can be arranged in the suction port 8 of the first stage, but it is in the second stage. It is difficult to install the suction port (not shown) due to a space problem, and if it is installed, there is a problem that the entire turbo compressor is enlarged.

Therefore, even though the suction flow rate of the fluid in the impeller 3 is controlled by the suction port 8 of the first stage,
Since the suction flow rate of the fluid cannot be controlled by the suction port of the second stage, the turbo compressor as a whole has an insufficient mechanism of controlling only the suction flow rate of the first stage, and it is difficult to sufficiently control the refrigeration capacity. Met.

The present invention has been made in view of the above problems, and does not increase the size as a whole.
It is an object of the present invention to provide a turbo compressor that can sufficiently control the suction flow rate of a fluid in practical use and can significantly improve the controllability of refrigeration capacity, and a refrigeration apparatus using the turbo compressor.

[0012]

In order to solve the above problems, the present invention employs the following means. Claim 1
The invention described in (1), a casing provided with a suction port and a discharge port, a main shaft rotatably supported in the casing, an impeller provided in multiple stages on the main shaft, and a downstream side of the impeller. In the turbo compressor having the diffuser and the drive mechanism for the main shaft, the pressure of the fluid sucked from the suction port is increased and the fluid is discharged from the discharge port,
An inlet for the fluid is provided in the circumferential direction with respect to the main shaft, and a passage portion that guides the fluid introduced from the inlet to the impeller and the passage portion have an installation angle with respect to the flow direction of the fluid. It is characterized in that it comprises a movable vane comprising a plurality of blades that are variably provided.

According to the present invention, the fluid introduced by the movable vane from the inlet provided in the circumferential direction with respect to the main shaft is introduced by adjusting the flow rate by a plurality of blades whose installation angle with respect to the flow direction is variable. It is possible to sufficiently control the suction flow rate of the fluid in practical use without increasing the overall size. Moreover, by introducing the fluid from the movable vanes in the circumferential direction with respect to the main shaft, a larger swirling flow can be generated and the axial flow resistance can be increased as compared with the case where the movable vane is mounted at the position shown in FIG.

The invention described in claim 2 is the same as claim 1
In the turbo compressor, the movable vane is characterized in that each of the blades is provided with a link mechanism that collectively changes the installation angle with respect to the flow direction of the fluid.

According to this turbo compressor, since the movable vanes collectively change the installation angle of each blade with respect to the flow direction of the fluid by the link mechanism, the amount of fluctuation of these blades can be kept uniform. The suction flow rate of the fluid can be adjusted accurately.

According to a third aspect of the present invention, a casing provided with a suction port and a discharge port, a main shaft rotatably supported in the casing, an impeller provided in multiple stages on the main shaft, and the blade. A turbo compressor that has a diffuser provided on the downstream side of the vehicle and a drive mechanism for the main shaft, and that boosts the pressure of the fluid sucked from the suction port to flow out from the discharge port; and condenses and liquefies the fluid. A condenser for cooling, a throttle mechanism for depressurizing the fluid condensed and liquefied by the condenser, and a heat exchange between the fluid depressurized by the throttle mechanism and the object to be cooled to cool the object to be cooled. In addition, in a refrigerating apparatus including an evaporator that evaporates and vaporizes the fluid, the turbo compressor has an inlet for the fluid in a circumferential direction with respect to the main shaft, and the fluid introduced through the inlet. The above feather And the flow path portion leading to the car, in the flow path unit, is characterized by comprising a movable vane comprising and a plurality of blades provided an installation angle to the flow direction of the fluid to freely change.

According to this refrigeration system, the fluid introduced by the movable vanes from the inlet provided in the circumferential direction with respect to the main shaft is introduced by adjusting the flow rate by a plurality of blades whose installation angle is variable with respect to the flow direction. Therefore, the suction flow rate of the fluid can be sufficiently controlled practically without increasing the overall size. In addition, the movable vanes introduce the fluid in the circumferential direction with respect to the main shaft, so that a swirl flow can be generated to increase the flow resistance in the axial direction.

The invention described in claim 4 is the same as claim 3
In the refrigerating apparatus, the movable vane is provided with a link mechanism in which the blades collectively change the installation angle with respect to the flow direction of the fluid.

According to this refrigerating apparatus, since the movable vanes provided in the turbo-type compressor collectively change the installation angle of each blade with respect to the fluid flow direction by the link mechanism,
The fluctuation amount of these blades can be kept uniform, and the suction flow rate of the fluid can be adjusted accurately.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of a turbo compressor and a refrigerating apparatus using the same according to the present invention will be described in detail below with reference to the drawings.

FIG. 1 is a schematic block diagram showing the refrigerating apparatus according to the present embodiment as a whole in perspective, and FIG. 2 is a system diagram thereof. This refrigeration system includes a turbo compressor 20 that pressurizes (compresses) the gas refrigerant sucked from the suction port and flows out from the discharge port, and a condenser 30 that condenses and liquefies the refrigerant compressed in the turbo compressor 20. A throttle mechanism 40 for reducing the pressure of the liquefied refrigerant in the condenser 30, and an evaporator 50 for cooling the cold water by exchanging heat between the refrigerant and the cold water (object to be cooled) and evaporating and vaporizing the refrigerant. It is configured to include.

In the illustrated refrigerating apparatus, the intercooler 60 for temporarily storing and cooling the refrigerant liquefied in the condenser 30 and a part of the refrigerant liquefied in the condenser 30 are used. An oil cooler 70 for cooling the lubricating oil of the turbo compressor 20 is provided. A drive mechanism 23 including a motor 21 that serves as a drive source and a power transmission mechanism 22 is connected to the turbo compressor 20.

The turbo compressor 20, the condenser 30, the throttle mechanism 40, the evaporator 50 and the intercooler 60 are connected by a main pipe 81 so as to form a closed system for circulating the refrigerant.

As the turbo compressor 20, for example, a two-stage centrifugal compressor is adopted. The first-stage impeller 3a compresses a gas refrigerant, and the refrigerant is introduced into the second-stage impeller 3b. After further compressing, it is sent to the condenser 30.

Further, the suction port 8 of the turbo compressor 20
The variable inlet guide vane 10 is provided for controlling the suction flow rate by changing the installation angle with respect to the flow direction of the fluid (gas refrigerant) that is sucked in to increase the pressure. Along with this, this turbo compressor 20
Immediately before the second-stage impeller 3b, when the fluid introduced from the first-stage impeller 3a is introduced from the circumferential direction with respect to the main shaft 2 described later, and the introduced fluid is guided to the second-stage impeller 3b. In addition, the movable vane 10 that controls the suction flow rate by changing the installation angle of the plurality of blades with respect to the flow direction of the fluid
0 is provided.

The condenser 30 comprises a main condenser 30a and an auxiliary condenser 30b called a subcooler, and the main condenser 3
The refrigerant is introduced in the order of 0a and the subcooler 30b, but a part of the refrigerant cooled in the main condenser 30a is introduced into the oil cooler 70 without passing through the subcooler 30b to cool the lubricating oil. Separately from this, a part of the refrigerant cooled in the main condenser 30a is introduced into the casing of the electric motor 21 without passing through the subcooler 30b, and cools a stator and a coil (not shown).

The throttling mechanism 40 is provided between the condenser 30 and the intercooler 60, and between the intercooler 60 and the evaporator 50, and the refrigerant liquefied in the condenser 30 is stepwise. Depressurize to. The structure of the intercooler 60 is the same as that of a hollow container, and the refrigerant cooled in the main condenser 30a and the subcooler 30b and depressurized in the expansion mechanism 40 is temporarily stored and further cooled. The gas phase component in the intercooler 60 passes through the bypass pipe 82 without passing through the evaporator 50 and the second-stage impeller 3b of the turbo compressor 20.
Will be introduced to.

FIG. 3 shows the turbo compressor 2 described above.
As an example of No. 0, the configuration of a two-stage compression centrifugal compressor is shown. In this turbo compressor 20, reference numeral 1 is a casing, 2 is a main shaft, 3 is an impeller (impeller),
4 is a diffuser, 5 is a return path, 6 is a flow path partition, 7 is a guide vane, 8 is a suction port, 10 is a variable inlet guide vane, 21 is an electric motor, 22 is a power transmission mechanism, 23 is a drive mechanism, and 24 is The discharge port 100 is a movable vane.

The turbo compressor 20 is a two-stage compression impeller 3 including a first-stage impeller 3a and a second-stage impeller 3b.
Is provided on the main shaft 2, and the impeller 3 is rotated by the drive mechanism 23 including the electric motor 21 and the power transmission mechanism 22 to pressurize the fluid (gas) such as the gas refrigerant sucked from the suction port 8 and discharge it from the discharge port 24. It is configured to drain. The power transmission mechanism 22 in this case includes the first gear 22a that rotates integrally with the rotary shaft 21a of the electric motor 21.
The second gear 22b that rotates integrally with the main shaft 2 meshes with the speed increasing mechanism, but the present invention is not limited to this.

As shown in FIG. 4A and FIG. 4B which is a sectional view of the movable vane 100, the movable vane 100 has a fluid inlet port in the circumferential direction with respect to the main shaft 2 (that is, on the extension of the return path 5).
Nozzle plate 1 that has the above-mentioned structure and guides the fluid introduced from the inlet to the impeller 3 (in this case, the second impeller 3b).
04 and the nozzle mount 105.
01 and a plurality of blades 100a whose installation angle with respect to the flow direction of the fluid is variable in the flow path portion 101.

In addition, each movable vane 100 has a blade 1
00a, a lever plate 102 that is fitted and linked to each blade 100a, a link plate 103 that is provided concentrically with the main shaft 2 and that rotatably holds each lever plate 102, and a nozzle plate And a nozzle support 106 that supports the nozzle plate 104 and the nozzle mount 105 and that is provided between the nozzle plate 104 and the nozzle mount 105. The link mechanism allows the blades 100a to collectively change the installation angle with respect to the fluid flow direction. Are configured. Therefore, the movable vane 100 can uniformly vary the blades 100a (that is, keep the variation amount uniform), and thus the suction flow rate of the fluid can be accurately adjusted.

The fluid sucked into the first stage impeller 3a from the suction port 8 through the variable inlet guide vane 10 has a setting angle with respect to the flow direction of the variable inlet guide vane 10 from the fully open position to the fully closed position. The suction flow rate corresponding to the operation of the turbo compressor 20 is selectively controlled by appropriately changing the value within the range. Then, the speed and pressure of the impeller 3a passing therethrough are increased, and the speed of the diffuser 4 passing therethrough is reduced to convert the kinetic energy into internal energy, and further passes through the return path 5 and the guide vane 7 in this order. After being pressurized, it is guided to the entrance of the second-stage impeller 3b.

The fluid introduced to the inlet of the second-stage impeller 3b is the blades 10 of the movable vane 100.
The installation angle with respect to the flow direction of 0a is the link mechanism 100.
By appropriately changing the range from the fully open position to the fully closed position by b, the suction flow rate corresponding to the operation of the turbo compressor 20 is selectively controlled. And
The introduced fluid goes through the same process as in the case of the first-stage impeller 3a described above when passing through the second-stage impeller 3b,
After the pressure is further increased, it flows out from the discharge port 24.

As described above, in the turbo compressor 20, the movable vane 1 provided at the inlet of the second-stage impeller 3b.
00, the suction flow rate of the fluid is adjusted and introduced, so that the suction flow rate of the fluid can be sufficiently controlled practically.

The shape of the movable vane 100 can be reduced by introducing the fluid from the circumferential direction with respect to the main shaft 2, so that it is possible to avoid increasing the size of the turbo compressor 20 as a whole. can do.

Further, the movable vane 100 can generate a swirling flow by introducing the fluid from the circumferential direction with respect to the main shaft 2 to increase the flow resistance in the axial direction.

In the above-mentioned embodiment,
The case where the movable vane 100 is provided at the inlet of the second stage impeller 3b has been described, but the present invention is not limited to this, and the movable vane 100 may be provided at the suction port 8 of the first stage impeller 3a, for example. However, in this case, there is an advantage that the entire turbo compressor can be further downsized.

[0038]

As described above, according to the first aspect of the present invention, a plurality of fluid vanes, whose movable vanes are introduced from the inlet provided in the circumferential direction with respect to the main shaft, can be set at various installation angles with respect to the flow direction. Since the flow rate is adjusted and introduced by the blades, the suction flow rate of the fluid can be sufficiently controlled practically without increasing the overall size, and thus the controllability of the refrigeration capacity can be significantly improved. Can be realized. In addition, the movable vanes introduce the fluid in the circumferential direction with respect to the main shaft, so that a swirl flow can be generated to increase the flow resistance in the axial direction.

Further, according to the invention of claim 2, since the movable vanes collectively change the installation angles of the blades with respect to the flow direction of the fluid by the link mechanism, the fluctuation amounts of these blades can be kept uniform. Therefore, the suction flow rate of the fluid can be adjusted accurately.

According to the third aspect of the present invention, the flow rate of the fluid introduced by the movable vane from the inlet provided in the circumferential direction with respect to the main shaft is adjusted by a plurality of blades whose installation angle is variable with respect to the flow direction. Since it is introduced, it is possible to sufficiently control the suction flow rate of the fluid in practical use without increasing the size as a whole, and thus it is possible to realize a turbo compressor that can remarkably improve the controllability of the refrigerating capacity. In addition, the movable vanes introduce the fluid in the circumferential direction with respect to the main shaft, so that a swirl flow can be generated to increase the flow resistance in the axial direction.

Further, according to the invention of claim 4, the movable vanes provided in the turbo-type compressor collectively change the installation angles of the respective blades with respect to the flow direction of the fluid by the link mechanism. The fluctuation amount can be kept uniform, and the suction flow rate of the fluid can be adjusted accurately.

[Brief description of drawings]

FIG. 1 is a perspective view showing a configuration example of a refrigerating apparatus according to the present invention.

FIG. 2 is a system diagram showing a configuration example of a refrigerating apparatus according to the present invention.

FIG. 3 is a cross-sectional view showing a configuration of a centrifugal compressor as an embodiment of a turbo compressor according to the present invention.

FIG. 4 is an enlarged view of a main part of a turbo compressor according to the present invention, (a) is a top view showing a schematic configuration of a movable vane, and (b) is an AA line of (a). It is sectional drawing of the movable vane which follows the line.

FIG. 5 is a cross-sectional view of essential parts showing a conventional turbo compressor.

FIG. 6 is a front view of the variable inlet guide vane in a fully closed position as seen from the outside of the suction port.

7A and 7B are cross-sectional views of the variable inlet guide vane taken along the line AA in FIG. 5, where FIG. 7A is a partially opened state and FIG. 7B is a fully closed state.

[Explanation of symbols]

1 casing 2 spindles 3 impeller 3a 1st stage impeller 3b Second stage impeller 4 diffuser 5 Return 20 turbo compressor 23 Drive mechanism 30 condenser 50 evaporator 100 movable vanes 100a wings 101 flow path 102 lever plate 103 link plate 104 nozzle plate 105 nozzle mount

Claims (4)

[Claims] 1. A casing having a suction port and a discharge port, and a main shaft rotatably supported in the casing.
It has an impeller provided in multiple stages on the main shaft, a diffuser provided on the downstream side of the impeller, and a drive mechanism for the main shaft, and pressurizes the fluid sucked from the suction port to increase the pressure from the discharge port. In the turbo compressor for outflow, there is an inlet port for the fluid in the circumferential direction with respect to the main shaft, and a channel part for guiding the fluid introduced from the inlet port to the impeller; A turbo compressor comprising: a movable vane having a plurality of blades whose installation angle is variable with respect to a fluid flow direction. 2. The turbo compressor according to claim 1, wherein the movable vane is provided with a link mechanism in which the blades collectively change the installation angle with respect to the flow direction of the fluid. . 3. A casing having a suction port and a discharge port, and a main shaft rotatably supported in the casing.
It has an impeller provided in multiple stages on the main shaft, a diffuser provided on the downstream side of the impeller, and a drive mechanism for the main shaft, and pressurizes the fluid sucked from the suction port to increase the pressure from the discharge port. A turbo type compressor to flow out, a condenser to condense and liquefy the fluid, a throttle mechanism to depressurize the fluid condensed and liquefied by the condenser, a fluid depressurized by the throttle mechanism and an object to be cooled. In a refrigerating apparatus including an evaporator that evaporates and vaporizes the fluid while cooling the object to be cooled by performing heat exchange between the turbocompressor and an inlet for the fluid with respect to the main shaft. A flow passage portion that has a circumferential direction and guides the fluid introduced from the introduction port to the impeller, and a plurality of blades provided in the flow passage portion such that the installation angle with respect to the flow direction of the fluid is variable. Movable bed equipped with A refrigerating device characterized by comprising a heater. 4. The refrigerating apparatus according to claim 3, wherein the movable vane is provided with a link mechanism in which the blades collectively change the installation angle with respect to the flow direction of the fluid.