JP2002005089A - Turbo-compressor and refrigeration equipment provided with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve an efficiency of a turbo-compressor by neither making to scale-up its size nor increasing its cost of production, and also to improve the efficiency of a refrigeration equipment provided with this turbo compressor. SOLUTION: This turbo-compressor comprised of a casing 55 being set up with an intake vent and outlet vent, a rotating shaft 41 which is driven by a motor, an impeller 19 which is made as in one body with the rotating shaft 41, and a diffuser portion 46 which is formed by one pair of the first wall portion 56 and the second wall portion 58 around an external periphery of the impeller 19, and is a flow channel of a refrigerant being taken out to the external periphery by rotation of the impeller 19. The refrigerant is sucked from a suction port and compressed by the impeller 19, together with the rotating shaft 41 being rotationally driven by the motor, then is delivered from delivery port through the diffuser portion 46. The width size along the longitudinal axis of the diffuser portion 46 is fixed bigger than the size of diffuser port 46b of external periphery against the size of the suction port 46a which is sending out the refrigerant from the impeller 19.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turbo type compressor for compressing a fluid by a rotating impeller and a refrigeration system having the same.

[0002]

2. Description of the Related Art Conventionally, a turbo compressor has been used as a refrigerant compressor in a refrigeration system. In this turbo type compressor, fluid is compressed by the impeller by rotating a rotation shaft provided with the impeller. Here, the structure of the turbo type compressor will be described by taking the structure shown in FIG. 10 as an example.

As shown in FIG. 1, an impeller 3 having a plurality of blades 2 is fixed to a rotating shaft 1 of the turbo-type compressor at intervals in a circumferential direction, and is rotated together with the rotating shaft 1. It has become. A rotating body (rotor) including the rotating shaft 1 and the impeller 3 is housed in a casing 4. The interior of the casing 4 is partitioned by a partition plate 5 into a diffuser portion 6 and a return flow passage 7, and the diffuser portion 6 and the return flow passage 7 are communicated by a return bend portion 8 formed in a U-shape in cross section. Have been.

The diffuser portion 6 is formed by a first wall portion 4a on the casing 4 side and a second wall portion 5a on the partition plate 5 side. The first wall portion 4a and the second wall portion 5a are
It is perpendicular to the rotation axis 1 and parallel to each other. The return flow path 7 is provided with a plurality of return vanes 9 at intervals in the circumferential direction so as to guide the flowing fluid. And in this turbo type compressor, it is compressed by the impeller 3 and
The fluid sent to the return channel 7 is sent to the return channel 7 via the return bend unit 8.

[0005]

The first wall 4
The diffuser section 6 formed by the second wall section 5a and the second wall section 5a decelerates the flow of the fluid sent out from the impeller 3 and restores most of the dynamic pressure to the static pressure. Is dependent on the shape of the diffuser portion 6. Therefore, it is conceivable to increase the pressure recovery coefficient Cp by improving the area and shape of the fluid inlet 6a and the outlet 6b in the diffuser section 6.

However, at present, as shown in the map of FIG. 11, the pressure recovery coefficient Cp has not reached 0.5, and there is room for further improvement. Therefore, it is required to improve the performance of the turbo-type compressor by improving the pressure recovery coefficient Cp in the diffuser unit 6 without increasing the size.

The pressure recovery coefficient Cp is represented by the aspect ratio and the area ratio at the inlet 6a and the outlet 6b of the diffuser section 6.

Here, the aspect ratio and the area ratio are obtained by the following equations.

Aspect ratio: 2 △ R / b2 = 2 (R2−R1) / b2 (1) Area ratio: AR-1 = (R2b2 / R1b1) -1 (2) where R1: diffuser portion Radius 6 at the inlet 6a R2: Radius at the outlet 6b of the diffuser 6 b1: Width at the inlet 6a of the diffuser 6 b2: Width at the outlet 6b of the diffuser 6

The pressure recovery coefficient Cp in the diffuser section 6 is expressed by the following equation.

Pressure recovery coefficient Cp = (Ps 2 −Ps 1) / (Pt 1 −Ps 1) where Ps 1: static pressure at the inlet 6 a of the diffuser section 6 Ps 2: static pressure at the outlet 6 b of the diffuser section 6 Pt 1: inlet of the diffuser section 6 Total pressure at 6a

In other words, as the pressure recovery coefficient Cp increases, the dynamic pressure of the fluid compressed and sent out by the impeller 3 is restored to the static pressure satisfactorily.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to provide a high-efficiency turbo-type compressor having improved performance without increasing the size and a refrigeration apparatus including the same. .

[0014]

According to a first aspect of the present invention, there is provided a turbo-type compressor comprising: a casing provided with a suction port and a discharge port; and a rotating shaft rotatably driven by a driving mechanism. An impeller provided integrally with the rotating shaft, and a diffuser portion formed by a pair of walls on an outer peripheral side of the impeller and serving as a flow path of a fluid sent to an outer peripheral side by rotation of the impeller. A turbo-type compressor that sucks fluid from the suction port and compresses the fluid by the impeller rotated with the rotation shaft by the drive mechanism, and discharges the fluid from the discharge port through the diffuser unit. The diffuser portion is characterized in that the width dimension along the axial direction is such that the outlet on the outer peripheral side is larger than the inlet of the fluid sent out from the impeller.

As described above, since the width of the diffuser portion along the axial direction on the inlet side and the outlet side is larger on the outlet side than on the inlet side, the aspect ratio between the inlet side and the outlet side is slightly smaller. As a result, the area ratio is increased, and the pressure recovery coefficient in the diffuser portion can be increased. In other words, the dynamic pressure of the compressed fluid sent out from the impeller can be efficiently restored to the static pressure at the diffuser without using a complicated structure, thereby increasing the size and complexity. Thus, a turbo-type compressor excellent in compression efficiency can be obtained.

According to a second aspect of the present invention, there is provided a turbo-type compressor according to the first aspect, wherein the width of the outlet relative to the width of the inlet is unchanged without changing the area ratio between the inlet and the outlet of the diffuser portion. It is characterized in that the width dimension is increased.

As described above, without changing the area ratio between the inlet and the outlet of the diffuser portion, the width of the outlet is made larger than the width of the inlet, that is, the width of the outlet is increased by the width of the outlet. Since the diameter is reduced, the outer diameter can be reduced in size and the cost can be reduced. In addition, since the width at the outlet is larger than that at the inlet without changing the area ratio between the inlet and the outlet, the aspect ratio is reduced, the pressure recovery coefficient is increased, and the performance is surely improved. be able to.

According to a third aspect of the present invention, in the turbo type compressor according to the first or second aspect, the pair of walls forming the diffuser portion are gradually separated from the inlet to the outlet. It is characterized in that it is formed in a tapered shape.

That is, by forming the pair of walls forming the diffuser portion into a tapered shape, the width of the outlet with respect to the inlet can be very easily increased, and the performance can be improved. Further, since the wall portion has a tapered shape, it is possible to eliminate a problem that the fluid sent out from the impeller is separated at the diffuser portion.

According to a fourth aspect of the present invention, there is provided a turbo type compressor according to the first or second aspect, wherein one of the pair of walls forming the diffuser portion has an inlet. It is characterized in that it has a tapered shape that is gradually separated from the other wall portion toward the outlet.

That is, by forming only one of the pair of walls forming the diffuser portion into a tapered shape, the width of the outlet with respect to the inlet can be very easily increased to improve the performance. . Also, since only one of the walls needs to be tapered, the performance can be more simply improved. In particular, by making the wall on the front side of the impeller which has some space in comparison with the rear side of the impeller having the downstream flow path connected to the diffuser part tapered, compactness in the axial direction can be reduced. Can be planned.

According to a fifth aspect of the present invention, there is provided a turbo-type compressor according to any one of the first to fourth aspects, further comprising a plurality of the impellers, wherein a fluid sucked from a suction port is upstream. It is characterized in that it is a multi-stage type that compresses sequentially from the side impeller.

That is, in the multistage type having a plurality of impellers, the pressure recovery coefficient in the diffuser portion, which is the flow path of the fluid sent out from each impeller, is increased, so that the performance of each impeller is enhanced. A highly efficient turbo compressor can be provided.

According to a sixth aspect of the present invention, there is provided a refrigerating apparatus comprising: a compressor for compressing a refrigerant sucked from a suction port and flowing out from a discharge port; a condenser for condensing and liquefying the refrigerant to send out a liquid refrigerant; A throttle mechanism for depressurizing the refrigerant, and an evaporator for cooling the object to be cooled by performing heat exchange between the condensed and decompressed liquid refrigerant and the object to be cooled, and evaporating and vaporizing the liquid refrigerant. 6. The compressor according to claim 1, wherein the compressor is provided.
The turbo type compressor according to any one of the above items is used.

As described above, a high-efficiency turbo-type compressor having a diffuser portion having a high pressure recovery coefficient and exhibiting good performance is used as a compressor for compressing a refrigerant and sending it to a condenser. In addition, the cooling efficiency can be greatly improved, and a refrigeration apparatus having excellent cooling performance can be provided.

[0026]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A turbo compressor according to an embodiment of the present invention and a refrigeration apparatus having the same will be described below with reference to the drawings. First, the overall configuration of the refrigeration apparatus will be described with reference to FIGS.

In the refrigerator shown in the figure, heat is exchanged between the refrigerant and the chilled water to cool the chilled water and evaporate the refrigerant.
An evaporator 11 for vaporizing, a compressor 12 for compressing the refrigerant vaporized in the evaporator 11, a condenser 13 for condensing and liquefying the refrigerant compressed in the compressor 12, and a condenser 13
A throttle valve 14 for decompressing the refrigerant liquefied in the above, an intercooler 15 for temporarily storing and cooling the refrigerant liquefied in the condenser 13, and utilizing a part of the refrigerant cooled in the condenser 13. And an oil cooler 16 for cooling the lubricating oil of the compressor 12. Also, the compressor 12 includes:
A motor (drive mechanism) 17 for driving this is connected.

The evaporator 11, the compressor 12, the condenser 13,
The throttle valve 14 and the intercooler 15 are connected by a main pipe 18 so as to form a closed system for circulating the refrigerant.

The compressor 12 employs a two-stage (multi-stage) centrifugal compressor, a so-called turbo compressor. The turbo compressor 12 is provided with a plurality of impellers 19. The refrigerant is compressed by the first-stage impeller 19a on the upstream side of the impeller 19, and the refrigerant is further introduced into the second-stage impeller 19b, further compressed, and then sent to the condenser 13.

The condenser 13 comprises a main condenser 13a and a subcooler 13b as an auxiliary condenser.
The refrigerant is introduced in the order of a and the subcooler 13b, but a part of the refrigerant cooled in the main condenser 13a is introduced into the oil cooler 16 without passing through the subcooler 13b to cool the lubricating oil. Apart from that, a part of the refrigerant cooled in the main condenser 13a is introduced into a casing 31 of the motor 17 described later without passing through the subcooler 13b, and cools a stator and a coil (not shown).

The throttle valve 14 is disposed between the condenser 13 and the intercooler 15 and between the intercooler 15 and the evaporator 11, respectively. Reduce the pressure.

The structure of the intercooler 15 is the same as that of a hollow container, and the refrigerant cooled in the main condenser 13a and the subcooler 13b and temporarily decompressed in the throttle valve 14 is temporarily stored to further cool. The gas phase component of the intercooler 15 is introduced into the second stage impeller 19 b of the compressor 12 through the bypass pipe 23 without passing through the evaporator 11.

Next, the turbo compressor 12 provided in the refrigeration system will be described in more detail. As shown in FIG. 3, the above-described motor 17 is provided integrally with the turbo-type compressor 12, and is driven by the rotational driving force of the motor 17.

The rotating force of the rotating shaft 35 of the motor 17 is transmitted to the rotating shaft 41 of the turbo compressor 12 by the transmission gears 36 and 37 meshed with each other. Rotary shaft 41 of compressor 12
Are driven to rotate.

One end of the turbo-type compressor 12 is a suction port 42, and a refrigerant is sent from the evaporator 11 to the suction port 42. The suction port 42 is provided with a suction vane 40, and the suction vane 40 controls the suction capacity of the refrigerant in the suction port 42. The turbo-type compressor 12 is provided with a first-stage compression section 43 and a second-stage compression section 44 in this order from the suction port 42 side.
The second stage compression section 44 includes the first stage impeller 19a described above,
A second stage impeller 19b is provided.

When the rotary shaft 41 is rotated, the first stage impeller 19a and the second stage impeller 19b are rotated.
Are rotated, the refrigerant from the evaporator 11 is sucked from the suction port 42 into the first-stage compression section 43, compressed by the first-stage impeller 19 a of the first-stage compression section 43, and further diffused by the diffuser section 46. , Through a return channel 49 having a return bend portion 47 and a return vane 48, and sent to the second stage compression portion 44.
After being compressed by the step impeller 19 b, the compressed air is then discharged from the discharge port 53 through the diffuser section 46 through the scroll section 52, which is a flow path formed along the circumferential direction, and sent out to the condenser 13. ing.

As mentioned above, the intercooler 15
Is sent to the second-stage compression section 44, and is compressed by the second-stage impeller 19b of the second-stage compression section 44 together with the refrigerant sent from the first-stage compression section 43. The liquid is discharged from the discharge port 53 to the condenser 13 through the scroll part 52, which is a flow path formed along the circumferential direction, through the diffuser part 46.

Next, the structure of the diffuser section 46 in the first-stage compression section 43 and the second-stage compression section 44 will be described by taking the diffuser section 46 of the first-stage compression section 43 as an example.

As shown in FIG. 4, the diffuser section 46
In this configuration, the first wall portion 56 formed of the casing 55 of the turbo-type compressor 12 forming the diffuser portion 46 and the second wall portion 58 formed of the partition plate 57 are separated from each other radially outward. Thereby, the diffuser portion 46 is formed in a tapered shape that gradually widens from the inlet 46a to the outlet 46b, and the diffuser portion 46 is formed.
The width dimension along the axial direction is gradually increased outward in the radial direction.

As described above, this turbo type compressor 12
Is the width dimension b of the inlet 46a of the diffuser 46.
Since the width dimension b2 of the outlet 46b is larger than that of (1) (b1 <b2), the inlet 46a of the diffuser 46 is
The aspect ratio at the outlet 46b is slightly reduced, and the area ratio is increased.

Thus, as shown in FIG. 5, in the case of the turbo compressor 12 having the diffuser section 46,
The pressure recovery coefficient Cp is a point that exceeds the diagonally upper left of 0.5 with respect to the case of the turbo-type compressor having the conventional diffuser section 6 in which the widths of the inlet 46a and the outlet 46b are the same. The performance of the diffuser section 46 is improved, and the efficiency of the turbo compressor 12 is improved. Similarly, in the diffuser section 46 of the second stage compression section 44, the pressure recovery coefficient Cp is improved.

In the above example, the first stage impeller 19
Although a two-stage (multi-stage) turbo-type compressor having a and a second-stage impeller 19b has been described, a single-stage turbo-type compressor having one impeller can also be applied. Of course.

As described above, according to the turbo-type compressor 12 having the above structure, the inlet 4 of the diffuser section 46
Since the width dimension in the axial direction between the 6a side and the outlet 46b side is larger on the outlet 46b side than the inlet 46a side, the aspect ratio between the inlet 46a side and the outlet 46b side is slightly reduced and the area ratio is reduced. The pressure recovery coefficient Cp in the diffuser portion 46 can be increased by increasing the pressure recovery coefficient Cp.

That is, the dynamic pressure of the compressed refrigerant discharged from the first stage impeller 19a and the second stage impeller 19b is efficiently recovered to the static pressure by the diffuser section 46 without making the structure complicated. As a result, the turbo-type compressor 12 having excellent compression efficiency can be obtained without increasing the size and complexity.

Further, by forming the pair of walls forming the diffuser section 46 as the first wall section 56 and the second wall section 58 in a tapered shape, the width dimension of the outlet with respect to the inlet can be very easily increased. Performance can be improved. Further, since the first wall portion 56 and the second wall portion 58 are tapered, there is a problem that the refrigerant discharged from the first stage impeller 19a and the second stage impeller 19b is separated at the diffuser portion 46. Can be lost.

The turbo type compressor 12 has a first stage impeller 19a and a second stage impeller in a two-stage type (multistage type) having a first stage impeller 19a and a second stage impeller 19b. Since the pressure recovery coefficient Cp in the diffuser portion 46, which is the flow path of the refrigerant sent out from each of the first stage impellers 19b, is increased, the performance in each of the first stage impellers 19a and the second stage impellers 19b is extremely high and the efficiency is extremely high. It can be a turbo compressor.

According to the refrigerating apparatus provided with the turbo type compressor 12, as a compressor for compressing the refrigerant and sending the compressed refrigerant to the condenser 13, the diffuser section having a high pressure recovery coefficient Cp and exhibiting good performance. Since the high-efficiency turbo-type compressor 12 having 46 is used, the cooling efficiency can be greatly increased, and as a result, a refrigeration apparatus having excellent cooling performance can be obtained.

Next, another embodiment will be described. As shown in FIG. 6, also in the case of the diffuser section 46, the first wall section 56 formed of the casing 55 of the turbo-type compressor 12 and the second wall section 58 formed of the partition plate 57 forming the diffuser section 46 are formed. The diffuser portion 4 is formed so as to be spaced apart from each other in a radially outward direction.
6 is formed in a tapered shape that gradually widens from the inlet 46a to the outlet 46b, and the width dimension of the diffuser portion 46 is gradually widened radially outward.

However, in this diffuser section 46,
By reducing the radius R2 at the outlet 46b,
The area ratio between the inlet 46a and the outlet 46b is the same as before the improvement.

That is, in the turbo type compressor 12, the aspect ratio is reduced while the area ratio is kept as it is. As a result, as shown in FIG. 7, the turbo type compressor having the diffuser section 46 is provided. In the case of 12, the pressure recovery coefficient Cp moves to the left and exceeds 0.5 with respect to the case of the current turbo-type compressor having the conventional diffuser section, so that the diffuser section 4
6 is improved, and the efficiency of the turbo compressor 12 is improved.

As described above, in the case of the turbo compressor 12 having the above structure, as described above, the width dimension along the axial direction is maintained without changing the area ratio between the inlet 46a side and the outlet 46b side of the diffuser section 46. However, since the outlet 46b side is larger than the inlet 46a side, the aspect ratio between the inlet 46a side and the outlet 46b side is reduced, and the pressure recovery coefficient Cp in the diffuser section 46 can be increased.

That is, the dynamic pressure of the compressed refrigerant delivered from the first stage impeller 19a and the second stage impeller 19b is efficiently recovered to the static pressure by the diffuser section 46 without having a complicated structure. As a result, the turbo-type compressor 12 having excellent compression efficiency can be obtained without increasing the size and complexity.

In addition, the entrance 46 of the diffuser section 46
a and the outlet 46b without changing the area ratio.
The width b2 of the outlet 46b is made larger than the width b1 of a, that is, the diameter R2 at the outlet 46b is made smaller by increasing the width b2 of the outlet 46b. And cost can be reduced. In addition, the entrance 46a and the exit 4
Since the width b2 of the outlet 46b is made larger than that of the inlet 46a without changing the area ratio with respect to the inlet 6a, the aspect ratio is reduced, the pressure recovery coefficient Cp is increased, and the performance is surely improved. be able to.

In each of the above examples, the first wall portion 56 formed of the casing 55 of the turbo-type compressor 12 forming the diffuser portion 46 and the second wall portion formed of the partition plate 57 are provided.
The diffuser portion 46 is tapered so as to gradually expand from the inlet 46a to the outlet 46b by separating the wall portion 58 from each other radially outward, and the width dimension of the diffuser portion 46 is radially outward. Although the structure gradually widens, the outlet 46b is positioned closer to the inlet 46a so that the flow does not separate in the diffuser section 46.
If the width of the side is widened, the pressure recovery coefficient Cp can be increased, and the efficiency of the turbo compressor 12 can be increased.

Here, the one shown in FIG.
In FIG. 9, only a second wall portion 58 made of a casing 55 is tapered and only a first wall portion 56 made of a casing 55 is tapered and a diffuser is shown. The tapered shape is such that the flow in the portion 46 does not separate.

According to the diffuser portion 46 shown in FIG. 8 or FIG. 9, only one of the first wall portion 57 and the second wall portion 58 has a tapered shape, and the other has a tapered shape. The first wall 57
As compared with the case where both the second wall portion 58 and the second wall portion 58 have a tapered shape, the cost can be reduced due to the simplification of the structure.

Here, the second wall 5 made of the partition plate 57
8 is tapered, the partition plate 57 itself must also be tilted rearward in order to secure a curvature at which the flow does not separate at the return bend portion 47. However, the partition plate 57 shown in FIG. Since the second wall portion 58 is perpendicular to the rotation shaft 41, the partition plate 57 is tilted rearward to secure a curvature at which the flow does not separate at the return bend portion 47. It is possible to eliminate a problem that the size is increased. Thereby, efficiency can be improved without increasing the axial dimension of the turbo compressor 12.

That is, according to the turbo-type compressor 12, only one of the first wall portion 56 and the second wall portion 58, which are a pair of walls forming the diffuser portion 46, is tapered. Makes it very easy to
, The width b2 of the outlet 46b can be increased to improve the performance. In addition, since only one of the first wall portion 56 and the second wall portion 58 may have a tapered shape, the performance can be more simply improved.

In particular, as shown in FIG. 9, as described above, the wall on the front side, which has some space in comparison with the rear side of the impeller 19 having the downstream flow path connected to the diffuser portion 46, has a margin. Since the first wall portion 56, which is a portion, has a tapered shape, it is possible to reduce the size in the axial direction.

The structure of the diffuser section 46 shown in FIGS. 8 and 9 can be applied to any of the structures of the diffuser section 46 shown in FIGS. 4 and 6. is there. Further, in the above-described example, the vaneless type having no vanes has been described as the diffuser section 46. However, the diffuser section 46 may be a type having vanes.

[0061]

As described above, according to the turbo type compressor of the present invention and the refrigerating apparatus having the same, the following effects can be obtained. According to the turbo type compressor of the first aspect, the width dimension along the axial direction on the inlet side and the outlet side of the diffuser portion is larger on the outlet side than on the inlet side. Is slightly reduced and the area ratio is increased, so that the pressure recovery coefficient in the diffuser portion can be increased. In other words, the dynamic pressure of the compressed fluid sent out from the impeller can be efficiently restored to the static pressure by the diffuser without using a complicated structure.
A turbo compressor having excellent compression efficiency can be provided without increasing the size and complexity.

According to the turbo compressor of the second aspect, the width of the outlet is made larger than the width of the inlet without changing the area ratio between the inlet and the outlet of the diffuser, that is, the outlet. Since the diameter at the outlet is reduced by an increase in the width dimension, the outer diameter can be made compact and the cost can be reduced. In addition, since the width at the outlet is larger than that at the inlet without changing the area ratio between the inlet and the outlet, the aspect ratio is reduced, the pressure recovery coefficient is increased, and the performance is surely improved. be able to.

According to the third aspect of the present invention, the width of the outlet with respect to the inlet is very easily increased by tapering the pair of walls forming the diffuser, thereby improving the performance. Can be achieved. Further, since the wall portion has a tapered shape, it is possible to eliminate a problem that the fluid sent out from the impeller is separated at the diffuser portion.

According to the turbo-type compressor of the fourth aspect, by forming only one of the pair of walls forming the diffuser portion into a tapered shape, it is possible to very easily
The performance can be improved by increasing the width of the outlet with respect to the inlet. Also, since only one of the walls needs to be tapered, the performance can be more simply improved. In particular, by making the wall on the front side of the impeller which has some space in comparison with the rear side of the impeller having the downstream flow path connected to the diffuser part tapered, compactness in the axial direction can be reduced. Can be planned.

According to the turbo compressor of the fifth aspect, in the multistage type having a plurality of impellers, the pressure recovery coefficient in the diffuser portion, which is the flow path of the fluid sent out from each impeller, is increased. In addition, it is possible to provide an extremely high-efficiency turbo-type compressor with improved performance in each impeller.

According to the refrigeration apparatus of the present invention, as a compressor for compressing the refrigerant and sending it to the condenser, a high-efficiency turbo compression having a diffuser portion having a high pressure recovery coefficient and exhibiting good performance. Machine is used,
The cooling efficiency can be greatly increased, and as a result, a refrigeration apparatus having excellent cooling performance can be provided.

[Brief description of the drawings]

FIG. 1 is a perspective view of a refrigeration apparatus illustrating a configuration and a structure of a turbo type compressor and a refrigeration apparatus including the same according to an embodiment of the present invention.

FIG. 2 is a schematic piping diagram of a refrigeration apparatus illustrating a configuration of a turbo compressor according to an embodiment of the present invention and a refrigeration apparatus including the same.

FIG. 3 is a cross-sectional view of the turbo-type compressor illustrating the structure of the turbo-type compressor according to the embodiment of the present invention.

FIG. 4 is a cross-sectional view of a compression section illustrating a structure of a turbo type compressor according to an embodiment of the present invention.

FIG. 5 is a graph showing the performance of the diffuser unit of the turbo compressor according to the embodiment of the present invention.

FIG. 6 is a cross-sectional view of a compression section illustrating a structure of a turbo type compressor according to another embodiment of the present invention.

FIG. 7 is a graph showing the performance of a diffuser unit of a turbo compressor according to another embodiment of the present invention.

FIG. 8 is a cross-sectional view of a compression section illustrating a structure of a turbo type compressor according to another embodiment of the present invention.

FIG. 9 is a cross-sectional view of a compression section illustrating a structure of a turbo type compressor according to another embodiment of the present invention.

FIG. 10 is a cross-sectional view of a compression section illustrating a structure of a conventional turbo type compressor.

FIG. 11 is a map diagram showing a pressure recovery coefficient in a diffuser section.

[Explanation of symbols]

 Reference Signs List 11 evaporator 12 turbo-type compressor 13 condenser 14 throttle valve (throttle mechanism) 17 motor (drive mechanism) 19 impeller 19a first-stage impeller (impeller) 19b second-stage impeller (impeller) 41 rotating shaft 42 inlet 46 diffuser 46a inlet 46b outlet 53 outlet 55 casing 56 first wall (wall) 58 second wall (wall) b1 inlet width b2 outlet width

Claims (6)

[Claims] A casing provided with a suction port and a discharge port, a rotating shaft rotatably driven by a driving mechanism, an impeller provided integrally with the rotating shaft, and an outer peripheral side of the impeller. A diffuser portion formed by a pair of wall portions and serving as a flow path of a fluid sent to an outer peripheral side by rotation of the impeller, wherein the suction port is rotated by the impeller by the drive mechanism together with the rotation shaft. A turbo-type compressor that sucks fluid from, compresses, and discharges from the discharge port through the diffuser portion, wherein the diffuser portion has a width dimension along an axial direction of the fluid that is sent out from the impeller. A turbo compressor, wherein an outlet on the outer peripheral side is made larger than an inlet. 2. The turbo compression according to claim 1, wherein the width of the outlet is made larger than the width of the inlet without changing the area ratio between the inlet and the outlet of the diffuser portion. Machine. 3. The turbo-type compression according to claim 1, wherein the pair of walls forming the diffuser portion are formed in a tapered shape that gradually separates from an inlet to an outlet. Machine. 4. A method according to claim 1, wherein one of the pair of wall portions forming the diffuser portion has a tapered shape that gradually separates from the other wall portion from the inlet to the outlet. The turbo compressor according to claim 1 or 2, wherein 5. A multi-stage type comprising a plurality of the impellers, wherein a fluid sucked from a suction port is sequentially compressed from an upstream impeller. The turbo compressor as described. 6. A compressor for compressing a refrigerant sucked from a suction port and flowing out from a discharge port, a condenser for condensing and liquefying the refrigerant and sending out a liquid refrigerant, and a throttle mechanism for reducing the pressure of the liquid refrigerant. Cooling the cooled object by causing heat exchange between the condensed and decompressed liquid refrigerant and the cooled object,
A refrigerating apparatus comprising: an evaporator for evaporating and vaporizing the liquid refrigerant, wherein the turbo-type compressor according to any one of claims 1 to 5 is used as the compressor.