TURBO COMPRESSOR AND TURBO REFRIGERATOR

Abstract

A turbo compressor according to the present invention supports a rotational shaft fixed to an impeller by a bearing in a freely rotatable manner, and supplies the lubricant oil to a plurality of sliding portions that are slid due to the rotation of the rotational shaft. Furthermore, the turbo compressor includes a oil supply nozzle in which a first injection hole, which injects the lubricant oil toward a predetermined first fueling place among a plurality of sliding portions to be supplied with the lubricant oil, and a second injection hole, which injects the lubricant oil toward a second fueling place different from the first fueling place, are provided. According to the present invention, it is possible to provide a turbo compressor capable of reducing the labor and the costs of manufacturing and a turbo refrigerator including the same.

Description

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a turbo compressor and a turbo refrigerator. Priority is claimed on Japanese Patent Application No. 2010-51930, filed Mar. 9, 2010, the content of which is incorporated herein by reference.

2. Description of Related Art

As a refrigerator that cools or refrigerates a cooling object such as water, there is known a turbo refrigerator including a turbo compressor which compresses and discharges a refrigerant by the rotation of an impeller. For example, as disclosed in Japanese Patent Application, First publication No. 2007-177695, the turbo compressor included in the turbo refrigerator includes a motor generating rotational power, an impeller to which the rotational power of the motor is transmitted and which rotates, and a pair of gears that transmits the rotational power of the motor to the impeller. The impeller and one of the gears are provided on a rotational shaft, and the rotational shaft is supported by a bearing in a freely rotatable manner.

Incidentally, in the aforementioned turbo compressor, a lubricant oil supply structure is provided which supplies lubricant oil for the lubricant and the cooling to a sliding portion such as a bearing or an engagement portion of a pair of gears. The lubricant oil supply structure includes a supply pump which delivers the lubricant oil, a plurality of nozzles that are respectively provided near the bearing or the engagement portion of the pair of gears, and inject the lubricant oil to the sliding portions, and supply pipes that respectively connect each nozzle with the supply pump.

However, since the plurality of nozzles are used, the number of components constituting the lubricant oil supply structure increase and the assembly thereof requires much labor, whereby the labor and the costs for manufacturing the turbo compressor increase.

The present invention was made in view of the above problems, and an object thereof is to provide a turbo compressor capable of reducing the labor and the costs of manufacturing and a turbo refrigerator including the same.

SUMMARY OF THE INVENTION

In order to solve the above problems, the present invention adopts the following means:

In the turbo compressor according to the present invention, a rotational shaft fixed to an impeller is supported by a bearing in a freely rotatable manner, and the lubricant oil is supplied to a plurality of sliding portions that are slid due to the rotation of the rotational shaft. Furthermore, the turbo compressor includes an oil supply nozzle in which a first injection hole, which injects the lubricant oil toward a predetermined first fueling place among a plurality of sliding portions to be supplied with the lubricant oil, and a second injection hole, which injects the lubricant oil toward a second fueling place different from the first fueling place, are provided.

In the present invention, since the oil supply nozzle can supply the plurality of sliding portions with the lubricant oil, it is needless to respectively provide nozzles for supplying the lubricant oil near the plurality of sliding portions. Furthermore, the number of supply pipes or the like to be connected to the nozzles are also reduced by the use of the oil supply nozzle of the present invention. Thus, the number of nozzles or supply pipes for supplying the plurality of sliding portions with the lubricant oil is reduced.

Furthermore, it is preferable that the turbo compressor according to the present invention includes a driving portion that generates the rotational power, and a pair of gears that transmits the rotational power of the driving portion to the rotational shaft; and the first fueling place is a bearing, and the second fueling place is an engagement portion of the pair of gears.

Furthermore, in the turbo compressor according to the present invention, it is preferable that a rolling bearing is used as the bearing and the first fueling place is an inner ring of the rolling bearing.

Furthermore, in the turbo compressor according to the present invention, it is preferable that the oil supply nozzle includes a first plane orthogonal to the extension direction of the first injection hole, and a second plane orthogonal to the extension direction of the second injection hole, the first injection hole is opened to the first plane, and the second injection hole is opened to the second plane.

Furthermore, a turbo refrigerator according to the present invention includes a condenser that cools and liquefies a compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes vaporization heat from a cooling object to cool the cooling object, and a compressor that compresses the refrigerant evaporated by the evaporator and supplies the refrigerant to the condenser, and, as the compressor, any one of the aforementioned turbo compressors is employed.

According to the present invention, it is possible to reduce the number of nozzles, the supply pipes or the like for supplying the plurality of sliding portions with the lubricant oil. For that reason, it is possible to reduce the labor and the costs of manufacturing in the turbo compressor and the turbo refrigerator including the same.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a block diagram that shows a schematic configuration of a turbo refrigerator in an embodiment of the present invention.

FIG. 2 is a horizontal cross-sectional view of a turbo compressor in an embodiment of the present invention.

FIG. 3 is a cross-sectional view taken along line A-A of FIG. 2.

FIG. 4 is a cross-sectional view taken along line B-B of FIG. 3.

FIG. 5 is an enlarged plan view of a spur gear and a pinion gear which are included in a turbo compressor in an embodiment of the present invention.

FIG. 6A is a vertical cross-sectional view that schematically shows a oil supply nozzle in an embodiment of the present invention.

FIG. 6B is a bottom view that schematically shows a oil supply nozzle in an embodiment of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 to 6B. In addition, in the respective drawings used in the following description, in order to make the respective members realizable sizes, the scales of the respective members are suitably changed.

FIG. 1 is a block diagram that shows a schematic configuration of a turbo refrigerator S1 in the present embodiment. The turbo refrigerator S1 in the present embodiment is installed in a building, a factory or the like, for example, in order to create cooling water for air-conditioning. As shown in FIG. 1, the turbo refrigerator S1 includes a condenser 1, an economizer 2, an evaporator 3, and a turbo compressor 4.

The condenser 1 is supplied with a compressed refrigerant gas X1 which is a refrigerant in a compressed gas state, and converts the compressed refrigerant gas X1 into a refrigerant liquid X2 by a cooling liquefaction. As shown in FIG. 1, the condenser 1 is connected to the turbo compressor 4 via a flow path R1 through which the compressed refrigerant gas X1 flows, and is connected to the economizer 2 via a flow path R2 through which a refrigerant liquid X2 flows. In addition, in the flow path R2, an expansion valve 5 for decompressing the refrigerant liquid X2 is installed.

The economizer 2 temporarily stores the refrigerant liquid X2 that was 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, and is connected to the turbo compressor 4 via a flow path R4 through which a gaseous phase component X3 of the refrigerant generated by the economizer 2 flows. In addition, in the flow path R3, an expansion valve 6 for further decompressing the refrigerant liquid X2 is installed. Moreover, the flow path R4 is connected to the turbo compressor 4 so as to supply a second compression stage 22 described later included in the turbo compressor 4 with the gaseous phase component X3.

The evaporator 3 evaporates the refrigerant liquid X2 and cools a cooling object by removing the vaporization heat from the cooling object 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 the evaporation of the refrigerant liquid X2 flows. In addition, flow path R5 is connected to a first compression state 21, described later, included in the turbo compressor 4.

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

In the turbo refrigerant S1 configured as above, the compressed refrigerant gas X1 supplied to the evaporator 1 via the flow path R1 is liquefied and cooled by the evaporator 1 and becomes the refrigerant liquid X2.

The refrigerant liquid X2 is decompressed by the expansion valve 5 when being supplied to the economizer 2 via the flow path R2 and is temporarily stored in the economizer 2 in the decompressed state, and then, the refrigerant liquid X2 is further decompressed by the expansion valve 6 when being supplied to the evaporator 3 via the flow path R3 and is supplied to the evaporator 3 in the further decompressed state.

The refrigerant liquid X2 supplied to the evaporator 3 is evaporated by the evaporator 3, becomes the refrigerant gas X4, and is supplied to the turbo compressor 4 via the flow path R5.

The refrigerant liquid X4 supplied to the turbo compressor 4 is compressed by the turbo compressor 4, becomes the compressed refrigerant gas X1, and is supplied to the condenser 1 via the flow path R1 again.

In addition, the gaseous 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, is compressed together with the refrigerant gas X4, and is supplied to the condenser 1 via the flow path R1 as the compressed refrigerant gas X1.

Moreover, in the turbo refrigerator S1, when the refrigerant liquid X2 is evaporated in the evaporator 3, the cooling or the refrigeration of the cooling object is performed by removing the vaporization heat from the cooling object.

Next, the turbo compressor 4, which is a characteristic portion of the present embodiment, will be described in more detail.

FIG. 2 is a horizontal cross-sectional view of the turbo compressor 4 in the present embodiment. FIG. 3 is a cross-sectional view taken from line A-A of FIG. 2. FIG. 4 is a cross-sectional view taken from line B-B of FIG. 3. Furthermore, FIG. 5 is an enlarged plan view of a spur gear 31 and a pinion gear 32 included in the turbo compressor 4 in the present embodiment. Moreover, FIGS. 6A and 6B are schematic views of an oil supply nozzle 35 in the present embodiment, FIG. 6A is a vertical cross-sectional view of the oil supply nozzle 35, and FIG. 6B is a bottom view of the oil supply nozzle 35. In addition, all of the spur gear 31, the pinion gear 32 and a gear casing 33 in FIG. 4 and the oil supply nozzle 35 in FIG. 5 are indicated by imaginary lines.

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 a motor 12 (a driving portion) which has an output shaft 11 and becomes a driving source for driving the compressor unit 20, and a motor casing 13 which surrounds the motor 12 and in which the motor 12 is installed. In addition, the driving force, which drives the compressor unit 20, is not limited to the motor 12, but may be, for example, an internal combustion engine.

The output shaft 11 of the motor 12 is supported by a first bearing 14 and a second bearing motor 15 fixed to the motor casing 13 in a freely rotatable manner.

The compressor unit 20 includes a first compression stage 21 which takes in and compresses the refrigerant gas X4 (see FIG. 1), and a second compression stage 22 which further compresses the refrigerant gas X4 compressed in the first compression stage 21 and discharges the same as the compressed refrigerant gas X1 (see FIG. 1).

As shown in FIG. 3, the first compression stage 21 includes a first impeller 21a (an impeller) which gives velocity energy to the refrigerant gas X4 to be supplied from a thrust direction and discharges the same in a radial direction, a first diffuser 21b which compresses the refrigerant gas X4 by converting the velocity energy given to the refrigerant gas X4 by the first impeller 21a into pressure energy, a first scroll chamber 21c which leads the refrigerant gas X4 compressed by the first diffuser 21b to the outside of the first compression stage 21, and an inlet port 21d which takes in the refrigerant gas X4 and supplies the same to the first impeller 21a.

In addition, a part of the first diffuser 21b, the first scroll chamber 21c and the inlet port 21d is formed by a first impeller casing 21e that surrounds the first impeller 21a.

In the compressor unit 20, a rotational shaft 23 extending over the first compression stage 21 and the second compression stage 22 is provided. The first impeller 21a is fixed to the rotational shaft 23 and is rotated by the transmission of the rotational power of the motor 12 (see FIG. 2) to the rotational shaft 23.

Furthermore, in the inlet port 21d of the first compression stage 21, a plurality of inlet guide vanes 21f for adjusting the inlet capacity of the first compression stage 21 are installed. The respective inlet guide vanes 21f are freely rotatable so that an exterior area from a flow direction of the refrigerant gas X4 can be changed by the driving mechanism 21g fixed to the first impeller casing 21e. Furthermore, at the outside of the first impeller casing 21e, a vane driving portion 24 (see FIG. 2) is installed which is connected to the driving mechanism 21g to rotate the respective inlet guide vanes 21f.

The second compression stage 22 includes a second impeller 22a (an impeller) that gives velocity energy to the refrigerant gas X4, which is compressed in the first compression stage 21 and then is supplied from a thrust direction, and discharges the refrigerant gas X4 in a radial direction, a second diffuser 22b which compresses the refrigerant gas X4 by converting the velocity energy given to the refrigerant gas X4 by the second impeller 22a into pressure energy and discharges the refrigerant gas X4 as the compressed refrigerant gas X1, a second scroll chamber 22c which leads the compression refrigerant gas X1 discharged from the second diffuser 22b to the outside of the second compression stage 22, and an introduction scroll chamber 22d which leads the refrigerant gas X4 compressed in the first compression stage 21 to the second impeller 22a.

In addition, a part of the second diffuser 22b, the second scroll chamber 22c and the introduction scroll chamber 22d is formed by a second impeller casing 22e that surrounds the second impeller 22a.

The second impeller 22a is fixed to the rotational shaft 23 so that a rear surface thereof faces the first impeller 21a, and is rotated by the transmission of the rotational power of the motor 12 to the rotational shaft 23.

The second scroll chamber 22c is connected to the flow path R1 (see FIG. 1) for supplying the condenser 1 with the compressed refrigerant gas X1 and supplies the flow path R1 with the compressed refrigerant gas X1 led from the second compression stage 22.

In addition, the first scroll chamber 21c of the first compression stage 21 and the introduction scroll chamber 22d of the second compression stage 22 are connected to each other via an external piping (not shown) which is provided separately from the first compression stage 21 and the second compression stage 22, and the refrigerant gas X4 compressed in the first compression stage 21 via the external piping is supplied to the second compression stage 22. The above-mentioned flow path R4 (see FIG. 1) is connected to the external piping, and the gaseous phase component X3 of the refrigerant generated in the economizer 2 is supplied to the second compression stage 22 via an external piping.

The rotational shaft 23 is supported by a third bearing 26 in freely rotatable manner, which is fixed to the second impeller casing 22e in a space 25 between the first compression stage 21 and the second compression stage 22, and a fourth bearing 27 (bearing) which is fixed to an end portion of a casing protruding portion 22f protruding from the second impeller casing 22e to the gear unit 30 side. In the rotational shaft 23, a labyrinth seal 23a for suppressing the flow of the refrigerant gas X4 from the introduction scroll seal 22d to the gear unit 30 side is provided.

Furthermore, as shown in FIG. 2, the gear unit 30 includes a spur gear 31 (gear) which is fixed to the output shaft 11, a pinion gear 32 (gear) which is fixed to the rotational shaft 23 and is engaged with the spur gear 31, and a gear casing which accommodates the spur gear 31 and the pinion gear 32, and transmits the rotational power of the output shaft 11 of the motor 12 to the rotational shaft 23. In addition, the gear unit 30 includes a lubricant oil supply portion 34 for supplying the lubricant oil to a plurality of sliding portions which slides due to the rotation of the rotational shaft 23.

An outer diameter of the spur gear 31 is greater than that of the pinion gear 32, and the rotational power of the motor 12 is transmitted to the rotational shaft 23 so that the revolution of the rotation shaft 23 increases relative to that of the output shaft 11 by the cooperation between the spur gear 31 and the pinion gear 32. In addition, at the time the rotational power of the motor 12 is transmitted to the rotational shaft 23, the diameters of the plurality of gears may be set so that the revolution of the rotational shaft 23 is identical to that of the output shaft 11 or reduces without being limited to the transmission method.

The gear casing 33 is molded separately from the motor casing 13 and the second impeller casing 22e and connects them to each other. In an inner part of the gear casing 33, an accommodation space 33a for accommodating the spur gear 31, the pinion gear 32 and the lubricant oil supply portion 34 is formed. The gear casing 33 and the second impeller casing 22e are fixed to each other using a plurality of bolts 33b. Furthermore, in the gear casing 33, an oil tank 33c is provided in which the lubricant oil to be supplied to the sliding portion of the turbo compressor 4 is collected and stored.

The lubricant oil supply portion 34 supplies the lubricant oil for the lubrication and the cooling to the fourth bearing 27, which is a sliding portion accompanied by the rotation of the output shaft 11 and the rotational shaft 23, and an engagement portion 38 (see FIG. 4) between the spur gear 31 and the pinion gear 32. The lubricant oil supply portion 34 includes a oil supply nozzle 35 which injects and supplies the lubricant oil to the plurality of sliding portions, and a supply pipe 36 which is connected to the oil supply nozzle 35 and supplies the lubricant oil.

The supply tube 36 is connected to the supply pump 37 delivering the lubricant oil stored in the oil tank 33c, via a supply flow path (not shown) provided outside the gear casing 33. The supply pump 37 is installed on an external surface of the oil tank 33c.

In addition, another supply portion may be provided which supplies the lubricant oil not only to the lubricant oil supply portion 34 but also to other sliding portions (for example, the first bearing 14).

As shown in FIG. 3, the oil supply nozzle 35 is provided on the upper side of the pinion gear 32 and is fixed to the casing protruding portion 22f of the second compression stage 22. In addition, in the casing protruding portion 22f, an oil discharging port 22g is formed which is situated at the lower part side of the pinion gear 32 to discharge the lubricant oil supplied from the oil supply nozzle 35.

Furthermore, the oil supply nozzle 35 includes a hole portion 35a connected to the supply pipe 36 extending in a vertical direction, a first injection hole 35b and a second injection hole 35c which communicate with the hole portion 35a and are opened toward the outside (with regard to the second injection hole 35c, see FIG. 4).

The first injection hole 35b is opened toward the fourth bearing 27 which is set as a first supply place among a plurality of sliding portions to be supplied with the lubricant oil. In addition, the fourth bearing 27 is a so-called rolling bearing, includes an inner ring 27a, an outer ring 27b, and a plurality of rolling bodies 27c disposed between the inner ring 27a and the outer ring 27b, and the first injection hole 35b is opened toward the inner ring 27a. That is, more specifically, the above-mentioned first supply place is the inner ring 27a of the fourth bearing 27.

Since the first injection hole 35b is opened toward the fourth bearing 27, the lubricant oil can be supplied from the first injection hole 35b to the fourth bearing 27, which can lubricate and cool the fourth bearing 27. Furthermore, since the first injection hole 35b is opened toward the inner ring 27a, it is possible to actively lubricate and cool the inner ring 27a having a large heating value due to the sliding.

As shown in FIG. 4, the second injection hole 35c is opened to the engagement portion 38 between the spur gear 31 and the pinion gear 32, which is a second supply place among the plurality of sliding portions to be supplied with the lubricant oil. For that reason, the lubricant oil can be injected and supplied from the second injection hole 35c to the engagement portion 38, which can lubricate and cool the spur gear 31 and the pinion gear 32 in the engagement portion 38.

In addition, an end side of the supply pipe 35 is connected to the hole portion 35a of the oil supply nozzle 35 and the other end side thereof is connected to the inner surface of the gear casing 33.

Furthermore, as shown in FIG. 5, the second injection hole 35c is opened toward the center portion in a width direction (left and right direction in FIG. 5) of the engagement portion 38. For that reason, it is possible to effectively spread the lubricant oil over the width direction of the engagement portion 38. In addition, the opening direction of the first injection hole 35b may be suitably tilted to a circumferential direction of the inner ring 27a so as to follow the rotational direction of the rotational shaft 23.

As mentioned above, the oil supply nozzle 35 includes the first injection hole 35b and the second injection hole 35c. As a result, it is possible to supply the lubricant oil to any one of the fourth bearing 27 and the engagement portion 38 slid along with the rotation of the output shaft 11 and the rotational shaft 23 by a single oil supply nozzle 35. For that reason, in the present embodiment, there is needless to provide nozzles for supplying the lubricant oil near the fourth bearing 27 and the engagement portion 38, respectively, and the number of supply pipes or the like to be connected to the nozzle also decreases. Thus, it is possible to reduce the number of nozzles, the supply pipes or the like for supplying the lubricant oil to the fourth bearing 27 and the engagement portion 38, which can reduce the labor and the costs of manufacturing in the turbo compressor 4.

As shown in FIGS. 6A and 6B, the first injection hole 35b and the second injection hole 35c of the oil supply nozzle 35 connect the front end side (a lower part side of FIG. 6A) of the oil supply nozzle 35 to the inner peripheral surface of the hole portion 35a formed of a cylindrical shape. Furthermore, the extension direction of the first injection hole 35b and the second injection hole 35c is tilted relative to the extension direction of the hole portion 35a at a predetermined angle. In addition, as shown in FIG. 6B, the first injection hole 35b and the second injection hole 35c branch off in a radial direction around the axis of the hole portion 35a.

Furthermore, the oil supply nozzle 35 includes a first plane 35d orthogonal to the extension direction of the first injection hole 35b, and a second plane 35e orthogonal to the extension direction of the second injection hole 35c. The first injection hole 35b is opened to the first plane 35d and the second injection hole 35c is opened to the second plan 35e. As a result, the first plane 35d and the second plane 35e are tilted to the proximal end side with respect to the front end surface (a lower end surface in FIG. 6A) of the oil supply nozzle 35 at a predetermined angle and form a slope surface facing the fourth bearing 27 or the engagement portion 38.

At the time of the production of the oil supply nozzle 35, the main body of the oil supply nozzle 35 and the hole portion 35a are formed by the mechanical working (a cutting working and a drill working). Next, after the first plane 35d and the second plane 35e are formed by the mechanical working (the cutting working and the drill working), the first injection hole 35b and the second injection hole 35c are formed by the mechanical working (the drill working).

Next, the operation of the turbo compressor 4 in the present embodiment will be described.

Firstly, the rotational power of the motor 12 is transmitted to the rotational 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 rotated.

When the first impeller 21a is rotated, the inlet port 21d of the first compression stage 21 enters a negative pressure state, and the refrigerant gas X4 flows from the flow path R5 into the first compression stage 21 via the inlet port 21d.

The refrigerant gas X4 flowed into the inner portion of the first compression stage 21 flows into the first impeller 21a in the thrust direction. This refrigerant gas X4 is provided with the 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 the velocity energy to the pressure energy by the first diffuser 21b.

The refrigerant gas X4 discharged from the first diffuser 21b is led to the outside of the first compression stage 21 via the first scroll chamber 21c.

Moreover, the refrigerant gas X4 led to the outside of the first compression stage 21 is supplied to the second compression stage 22 via an external piping (not shown).

The refrigerant gas X4 supplied to the second compression stage 22 flows into the second impeller 22a via the introduction scroll chamber 22d in the thrust direction. This refrigerant gas X4 is provided with the velocity energy by the second impeller 22a, and is discharged in the radial direction.

The refrigerant gas X4 discharged from the second impeller 22a is further compressed by converting the velocity energy into the pressure energy by the second diffuser 22b and becomes the compressed refrigerant gas X1.

The compression refrigerant gas X1 discharged from the second diffuse 22b is led to the outside of the second compression stage 22 via the second scroll chamber 22c.

The compressed refrigerant gas X1 led to the outside of the second compression stage 22 is supplied to the condenser 1 via the flow path R1.

Furthermore, the turbo compressor 4 in the present embodiment includes the above-mentioned lubricant oil supply portion 34. For that reason, it is possible to supply the lubricant oil to any one of the fourth bearing 27 and the engagement portion 38 slid due to the output shaft 11 and the rotational shaft 23, thereby performing the lubrication and the cooling.

As mentioned above, the operation of the turbo compressor 4 is finished.

According to the present embodiment, since the same oil supply nozzle 35 supplies the fourth bearing 27 and the engagement portion 38 with the lubricant oil, it is possible to reduce the number of nozzles, supply pipes or the like for supplying oil to the member. As a result, in the turbo compressor 4 and the turbo refrigerator S1, it is possible to obtain an effect capable of reducing the labor and the costs of manufacturing.

Furthermore, since the structure of the oil supply nozzle 35 is simple and the oil supply nozzle 35 can be produced by a simple mechanical working, the effect can be further improved.

In addition, the first injection hole 35b and the second injection hole 35c are titled toward the front end side in the extension direction of the hole portion 35a at a predetermined angle, and branch off around the axis of the hole portion 35a in the radial direction. For that reason, the lubricant oil supplied from the supply pipe 36 toward the front end side of the hole portion 35a is powerfully injected from the first injection hole 35b and the second injection hole 35c which are titled toward the front end side and branch off, with the result that it is possible to effectively lubricate and cool the fourth bearing 27 and the engagement portion 38. Furthermore, since the first injection hole 35b and the second injection hole 35c are opened vertically to the first plane 35d and the second plane 35e facing the fourth bearing 27 or the engagement portion 38, it is difficult for the lubricant oil injected from the first injection hole 35b and the second injection hole 35c to be adversely affected by the first plane 35d and the second plane 35e.

As mentioned above, although a preferable embodiment according to the present invention has been described with reference to the drawings, it is needless to say that the present invention is not limited to the related art. Overall shapes, combinations or the like of the respective members shown in the aforementioned example are examples, and can be variously changed in a scope of not departing from the gist of the present invention based on the design request or the like.

For example, although the oil supply nozzle 35 in the above-mentioned embodiment supplies the fourth bearings 27 and the engagement portion 38 with the lubricant toil, the oil supply nozzle may be a nozzle which supplies a plurality of other sliding portions with the lubricant oil without being limited thereto. Furthermore, although the oil supply nozzle 35 includes the first injection hole 35b and the second injection hole 35c, the oil supply nozzle 35 may have a configuration including, for example, three or more injection holes.

Furthermore, although the turbo compressor 4 in the above embodiment is a two-stage compression type of turbo compressor including the first compression stage 21 and the second compression stage 22, the turbo compressor may be a single-stage compression type or a multi-stage type of three stages or more without being limited thereto. Furthermore, although the turbo compressor 4 in the above embodiment is used in the turbo refrigerator S1, for example, the turbo compressor 4 may be used, for example, as a supercharger that supplies an internal combustion engine with the compressed air.

Claims

1. A turbo compressor which supports a rotational shaft to be fixed to an impeller by a bearing in a freely rotatable manner, and supplies a lubricant oil to a plurality of sliding portions that are slid due to the rotation of the rotational shaft, the compressor comprising:

a oil supply nozzle in which a first injection hole, which injects the lubricant oil toward a predetermined first fueling place among a plurality of sliding portions to be supplied with the lubricant oil, and a second injection hole, which injects the lubricant oil toward a second fueling place different from the first fueling place, are provided.

2. The turbo compressor according to claim 1, further comprising:

a driving portion that generates a rotational power, and a pair of gears that transmits the rotational power of the driving portion to the rotational shaft,

wherein the first fueling place is the bearing, and the second fueling place is an engagement portion of the pair of gears.

3. The turbo compressor according to claim 2, wherein a rolling bearing is used as the bearing, and the first fueling place is an inner ring of the rolling bearing.

4. The turbo compressor according to claim 1, wherein the oil supply nozzle includes a first plane orthogonal to the extension direction of the first injection hole, and a second plane orthogonal to the extension direction of the second injection hole, the first injection hole is opened to the first plane, and the second injection hole is opened to the second plane.

5. The turbo compressor according to claim 2, wherein the oil supply nozzle includes a first plane orthogonal to the extension direction of the first injection hole, and a second plane orthogonal to the extension direction of the second injection hole, the first injection hole is opened to the first plane, and the second injection hole is opened to the second plane.

6. The turbo compressor according to claim 3, wherein the oil supply nozzle includes a first plane orthogonal to the extension direction of the first injection hole, and a second plane orthogonal to the extension direction of the second injection hole, the first injection hole is opened to the first plane, and the second injection hole is opened to the second plane.

7. A turbo refrigerator according to the present invention which includes a condenser that cools and liquefies a compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes vaporization heat from a cooling object to cool the cooling object, and a compressor that compresses the refrigerant evaporated by the evaporator and supplies the condenser with the refrigerant, wherein the turbo compressor according to claim 1 is employed as the compressor.

8. A turbo refrigerator according to the present invention which includes a condenser that cools and liquefies a compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes vaporization heat from a cooling object to cool the cooling object, and a compressor that compresses the refrigerant evaporated by the evaporator and supplies the condenser with the refrigerant, wherein the turbo compressor according to claim 2 is employed as the compressor.

9. A turbo refrigerator according to the present invention which includes a condenser that cools and liquefies a compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes vaporization heat from a cooling object to cool the cooling object, and a compressor that compresses the refrigerant evaporated by the evaporator and supplies the condenser with the refrigerant, wherein the turbo compressor according to claim 3 is employed as the compressor.

10. A turbo refrigerator according to the present invention which includes a condenser that cools and liquefies a compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes vaporization heat from a cooling object to cool the cooling object, and a compressor that compresses the refrigerant evaporated by the evaporator and supplies the condenser with the refrigerant, wherein the turbo compressor according to claim 4 is employed as the compressor.

11. A turbo refrigerator according to the present invention which includes a condenser that cools and liquefies a compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes vaporization heat from a cooling object to cool the cooling object, and a compressor that compresses the refrigerant evaporated by the evaporator and supplies the condenser with the refrigerant, wherein the turbo compressor according to claim 5 is employed as the compressor.

12. A turbo refrigerator according to the present invention which includes a condenser that cools and liquefies a compressed refrigerant, an evaporator that evaporates the liquefied refrigerant and removes vaporization heat from a cooling object to cool the cooling object, and a compressor that compresses the refrigerant evaporated by the evaporator and supplies the condenser with the refrigerant, wherein the turbo compressor according to claim 6 is employed as the compressor.