US20110219809A1 - Turbo compressor and turbo refrigerator - Google Patents
Turbo compressor and turbo refrigerator Download PDFInfo
- Publication number
- US20110219809A1 US20110219809A1 US13/042,609 US201113042609A US2011219809A1 US 20110219809 A1 US20110219809 A1 US 20110219809A1 US 201113042609 A US201113042609 A US 201113042609A US 2011219809 A1 US2011219809 A1 US 2011219809A1
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- Prior art keywords
- refrigerant
- injection hole
- compressor
- turbo
- evaporator
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000002347 injection Methods 0.000 claims abstract description 59
- 239000007924 injection Substances 0.000 claims abstract description 59
- 239000000314 lubricant Substances 0.000 claims abstract description 51
- 239000003507 refrigerant Substances 0.000 claims description 95
- 238000001816 cooling Methods 0.000 claims description 24
- 238000009834 vaporization Methods 0.000 claims description 9
- 230000008016 vaporization Effects 0.000 claims description 9
- 238000005096 rolling process Methods 0.000 claims description 6
- 238000004519 manufacturing process Methods 0.000 abstract description 7
- 239000007789 gas Substances 0.000 description 47
- 230000006835 compression Effects 0.000 description 41
- 238000007906 compression Methods 0.000 description 41
- 239000007788 liquid Substances 0.000 description 15
- 239000007792 gaseous phase Substances 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000004308 accommodation Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/18—Lubricating arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/005—Adaptations for refrigeration plants
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/06—Lubrication
- F04D29/063—Lubrication specially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2300/00—Materials; Properties thereof
- F05D2300/20—Oxide or non-oxide ceramics
- F05D2300/22—Non-oxide ceramics
- F05D2300/226—Carbides
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
Definitions
- 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.
- the turbo refrigerator including a turbo compressor which compresses and discharges a refrigerant by the rotation of an impeller.
- 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.
- a lubricant oil supply structure 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.
- 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.
- the present invention adopts the following means:
- 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.
- 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.
- 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.
- 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.
- a rolling bearing is used as the bearing and the first fueling place is an inner ring of the rolling bearing.
- 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.
- a turbo refrigerator 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.
- 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.
- 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.
- FIG. 1 is a block diagram that shows a schematic configuration of a turbo refrigerator S 1 in the present embodiment.
- the turbo refrigerator S 1 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.
- the turbo refrigerator S 1 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 X 1 which is a refrigerant in a compressed gas state, and converts the compressed refrigerant gas X 1 into a refrigerant liquid X 2 by a cooling liquefaction.
- the condenser 1 is connected to the turbo compressor 4 via a flow path R 1 through which the compressed refrigerant gas X 1 flows, and is connected to the economizer 2 via a flow path R 2 through which a refrigerant liquid X 2 flows.
- an expansion valve 5 for decompressing the refrigerant liquid X 2 is installed in the flow path R 2 .
- the economizer 2 temporarily stores the refrigerant liquid X 2 that was decompressed by the expansion valve 5 .
- the economizer 2 is connected to the evaporator 3 via a flow path R 3 through which the refrigerant liquid X 2 flows, and is connected to the turbo compressor 4 via a flow path R 4 through which a gaseous phase component X 3 of the refrigerant generated by the economizer 2 flows.
- an expansion valve 6 for further decompressing the refrigerant liquid X 2 is installed in the flow path R 3 .
- the flow path R 4 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 X 3 .
- the evaporator 3 evaporates the refrigerant liquid X 2 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 R 5 through which a refrigerant gas X 4 generated by the evaporation of the refrigerant liquid X 2 flows.
- flow path R 5 is connected to a first compression state 21 , described later, included in the turbo compressor 4 .
- the turbo compressor 4 compresses the refrigerant gas X 4 and converts the same into the compressed refrigerant gas X 1 .
- the turbo compressor 4 is connected to the condenser 1 via the flow path R 1 through which the compressed refrigerant gas X 1 flows as mentioned above, and is connected to the evaporator 3 via the flow path R 5 through which the refrigerant gas X 4 flows.
- the compressed refrigerant gas X 1 supplied to the evaporator 1 via the flow path R 1 is liquefied and cooled by the evaporator 1 and becomes the refrigerant liquid X 2 .
- the refrigerant liquid X 2 is decompressed by the expansion valve 5 when being supplied to the economizer 2 via the flow path R 2 and is temporarily stored in the economizer 2 in the decompressed state, and then, the refrigerant liquid X 2 is further decompressed by the expansion valve 6 when being supplied to the evaporator 3 via the flow path R 3 and is supplied to the evaporator 3 in the further decompressed state.
- the refrigerant liquid X 2 supplied to the evaporator 3 is evaporated by the evaporator 3 , becomes the refrigerant gas X 4 , and is supplied to the turbo compressor 4 via the flow path R 5 .
- the refrigerant liquid X 4 supplied to the turbo compressor 4 is compressed by the turbo compressor 4 , becomes the compressed refrigerant gas X 1 , and is supplied to the condenser 1 via the flow path R 1 again.
- the gaseous phase component X 3 of the refrigerant generated when the refrigerant liquid X 2 is stored in the economizer 2 is supplied to the turbo compressor 4 via the flow path R 4 , is compressed together with the refrigerant gas X 4 , and is supplied to the condenser 1 via the flow path R 1 as the compressed refrigerant gas X 1 .
- the cooling or the refrigeration of the cooling object is performed by removing the vaporization heat from the cooling object.
- 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 .
- 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.
- 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 .
- 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.
- 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.
- 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 X 4 (see FIG. 1 ), and a second compression stage 22 which further compresses the refrigerant gas X 4 compressed in the first compression stage 21 and discharges the same as the compressed refrigerant gas X 1 (see FIG. 1 ).
- the first compression stage 21 includes a first impeller 21 a (an impeller) which gives velocity energy to the refrigerant gas X 4 to be supplied from a thrust direction and discharges the same in a radial direction, a first diffuser 21 b which compresses the refrigerant gas X 4 by converting the velocity energy given to the refrigerant gas X 4 by the first impeller 21 a into pressure energy, a first scroll chamber 21 c which leads the refrigerant gas X 4 compressed by the first diffuser 21 b to the outside of the first compression stage 21 , and an inlet port 21 d which takes in the refrigerant gas X 4 and supplies the same to the first impeller 21 a.
- a first impeller 21 a an impeller
- first diffuser 21 b a part of the first diffuser 21 b , the first scroll chamber 21 c and the inlet port 21 d is formed by a first impeller casing 21 e that surrounds the first impeller 21 a.
- a rotational shaft 23 extending over the first compression stage 21 and the second compression stage 22 is provided.
- the first impeller 21 a 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 .
- a plurality of inlet guide vanes 21 f for adjusting the inlet capacity of the first compression stage 21 are installed.
- the respective inlet guide vanes 21 f are freely rotatable so that an exterior area from a flow direction of the refrigerant gas X 4 can be changed by the driving mechanism 21 g fixed to the first impeller casing 21 e .
- a vane driving portion 24 is installed which is connected to the driving mechanism 21 g to rotate the respective inlet guide vanes 21 f.
- the second compression stage 22 includes a second impeller 22 a (an impeller) that gives velocity energy to the refrigerant gas X 4 , which is compressed in the first compression stage 21 and then is supplied from a thrust direction, and discharges the refrigerant gas X 4 in a radial direction, a second diffuser 22 b which compresses the refrigerant gas X 4 by converting the velocity energy given to the refrigerant gas X 4 by the second impeller 22 a into pressure energy and discharges the refrigerant gas X 4 as the compressed refrigerant gas X 1 , a second scroll chamber 22 c which leads the compression refrigerant gas X 1 discharged from the second diffuser 22 b to the outside of the second compression stage 22 , and an introduction scroll chamber 22 d which leads the refrigerant gas X 4 compressed in the first compression stage 21 to the second impeller 22 a.
- a second impeller 22 a an impeller
- a part of the second diffuser 22 b , the second scroll chamber 22 c and the introduction scroll chamber 22 d is formed by a second impeller casing 22 e that surrounds the second impeller 22 a.
- the second impeller 22 a is fixed to the rotational shaft 23 so that a rear surface thereof faces the first impeller 21 a , and is rotated by the transmission of the rotational power of the motor 12 to the rotational shaft 23 .
- the second scroll chamber 22 c is connected to the flow path R 1 (see FIG. 1 ) for supplying the condenser 1 with the compressed refrigerant gas X 1 and supplies the flow path R 1 with the compressed refrigerant gas X 1 led from the second compression stage 22 .
- first scroll chamber 21 c of the first compression stage 21 and the introduction scroll chamber 22 d 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 X 4 compressed in the first compression stage 21 via the external piping is supplied to the second compression stage 22 .
- the above-mentioned flow path R 4 (see FIG. 1 ) is connected to the external piping, and the gaseous phase component X 3 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 22 e 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 22 f protruding from the second impeller casing 22 e to the gear unit 30 side.
- a labyrinth seal 23 a for suppressing the flow of the refrigerant gas X 4 from the introduction scroll seal 22 d to the gear unit 30 side is provided.
- 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 .
- 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 .
- 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 22 e and connects them to each other.
- an accommodation space 33 a 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 22 e are fixed to each other using a plurality of bolts 33 b .
- an oil tank 33 c 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 33 c , 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 33 c.
- 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 ).
- the oil supply nozzle 35 is provided on the upper side of the pinion gear 32 and is fixed to the casing protruding portion 22 f of the second compression stage 22 .
- an oil discharging port 22 g 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 .
- the oil supply nozzle 35 includes a hole portion 35 a connected to the supply pipe 36 extending in a vertical direction, a first injection hole 35 b and a second injection hole 35 c which communicate with the hole portion 35 a and are opened toward the outside (with regard to the second injection hole 35 c , see FIG. 4 ).
- the first injection hole 35 b 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.
- the fourth bearing 27 is a so-called rolling bearing, includes an inner ring 27 a , an outer ring 27 b , and a plurality of rolling bodies 27 c disposed between the inner ring 27 a and the outer ring 27 b , and the first injection hole 35 b is opened toward the inner ring 27 a . That is, more specifically, the above-mentioned first supply place is the inner ring 27 a of the fourth bearing 27 .
- the lubricant oil can be supplied from the first injection hole 35 b to the fourth bearing 27 , which can lubricate and cool the fourth bearing 27 . Furthermore, since the first injection hole 35 b is opened toward the inner ring 27 a , it is possible to actively lubricate and cool the inner ring 27 a having a large heating value due to the sliding.
- the second injection hole 35 c 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 35 c to the engagement portion 38 , which can lubricate and cool the spur gear 31 and the pinion gear 32 in the engagement portion 38 .
- an end side of the supply pipe 35 is connected to the hole portion 35 a of the oil supply nozzle 35 and the other end side thereof is connected to the inner surface of the gear casing 33 .
- the second injection hole 35 c 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 .
- the opening direction of the first injection hole 35 b may be suitably tilted to a circumferential direction of the inner ring 27 a so as to follow the rotational direction of the rotational shaft 23 .
- the oil supply nozzle 35 includes the first injection hole 35 b and the second injection hole 35 c .
- the oil supply nozzle 35 includes the first injection hole 35 b and the second injection hole 35 c .
- the first injection hole 35 b and the second injection hole 35 c 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 35 a formed of a cylindrical shape. Furthermore, the extension direction of the first injection hole 35 b and the second injection hole 35 c is tilted relative to the extension direction of the hole portion 35 a at a predetermined angle. In addition, as shown in FIG. 6B , the first injection hole 35 b and the second injection hole 35 c branch off in a radial direction around the axis of the hole portion 35 a.
- the oil supply nozzle 35 includes a first plane 35 d orthogonal to the extension direction of the first injection hole 35 b , and a second plane 35 e orthogonal to the extension direction of the second injection hole 35 c .
- the first injection hole 35 b is opened to the first plane 35 d
- the second injection hole 35 c is opened to the second plan 35 e .
- the first plane 35 d and the second plane 35 e 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 .
- the main body of the oil supply nozzle 35 and the hole portion 35 a are formed by the mechanical working (a cutting working and a drill working).
- the first plane 35 d and the second plane 35 e are formed by the mechanical working (the cutting working and the drill working)
- the first injection hole 35 b and the second injection hole 35 c are formed by the mechanical working (the drill working).
- 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 21 a and the second impeller 22 a of the compressor unit 20 are rotated.
- the inlet port 21 d of the first compression stage 21 enters a negative pressure state, and the refrigerant gas X 4 flows from the flow path R 5 into the first compression stage 21 via the inlet port 21 d.
- This refrigerant gas X 4 is provided with the velocity energy by the first impeller 21 a , and is discharged in the radial direction.
- the refrigerant gas X 4 discharged from the first impeller 21 a is compressed by converting the velocity energy to the pressure energy by the first diffuser 21 b.
- the refrigerant gas X 4 discharged from the first diffuser 21 b is led to the outside of the first compression stage 21 via the first scroll chamber 21 c.
- the refrigerant gas X 4 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 X 4 supplied to the second compression stage 22 flows into the second impeller 22 a via the introduction scroll chamber 22 d in the thrust direction.
- This refrigerant gas X 4 is provided with the velocity energy by the second impeller 22 a , and is discharged in the radial direction.
- the refrigerant gas X 4 discharged from the second impeller 22 a is further compressed by converting the velocity energy into the pressure energy by the second diffuser 22 b and becomes the compressed refrigerant gas X 1 .
- the compression refrigerant gas X 1 discharged from the second diffuse 22 b is led to the outside of the second compression stage 22 via the second scroll chamber 22 c.
- the compressed refrigerant gas X 1 led to the outside of the second compression stage 22 is supplied to the condenser 1 via the flow path R 1 .
- 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.
- 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 S 1 , it is possible to obtain an effect capable of reducing the labor and the costs of manufacturing.
- 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.
- first injection hole 35 b and the second injection hole 35 c are titled toward the front end side in the extension direction of the hole portion 35 a at a predetermined angle, and branch off around the axis of the hole portion 35 a 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 35 a is powerfully injected from the first injection hole 35 b and the second injection hole 35 c 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 .
- first injection hole 35 b and the second injection hole 35 c are opened vertically to the first plane 35 d and the second plane 35 e facing the fourth bearing 27 or the engagement portion 38 , it is difficult for the lubricant oil injected from the first injection hole 35 b and the second injection hole 35 c to be adversely affected by the first plane 35 d and the second plane 35 e.
- 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.
- the oil supply nozzle 35 includes the first injection hole 35 b and the second injection hole 35 c
- the oil supply nozzle 35 may have a configuration including, for example, three or more injection holes.
- 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.
- turbo compressor 4 in the above embodiment is used in the turbo refrigerator S 1 , for example, the turbo compressor 4 may be used, for example, as a supercharger that supplies an internal combustion engine with the compressed air.
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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
- 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.
- 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.
-
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 ofFIG. 2 . -
FIG. 4 is a cross-sectional view taken along line B-B ofFIG. 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. - 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 inFIG. 1 , the turbo refrigerator S1 includes acondenser 1, aneconomizer 2, an evaporator 3, and aturbo 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 inFIG. 1 , thecondenser 1 is connected to theturbo compressor 4 via a flow path R1 through which the compressed refrigerant gas X1 flows, and is connected to theeconomizer 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. Theeconomizer 2 is connected to the evaporator 3 via a flow path R3 through which the refrigerant liquid X2 flows, and is connected to theturbo compressor 4 via a flow path R4 through which a gaseous phase component X3 of the refrigerant generated by theeconomizer 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 theturbo compressor 4 so as to supply asecond compression stage 22 described later included in theturbo 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 afirst compression state 21, described later, included in theturbo compressor 4. - The
turbo compressor 4 compresses the refrigerant gas X4 and converts the same into the compressed refrigerant gas X1. Theturbo compressor 4 is connected to thecondenser 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 theevaporator 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 theeconomizer 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 theturbo compressor 4, becomes the compressed refrigerant gas X1, and is supplied to thecondenser 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 theturbo compressor 4 via the flow path R4, is compressed together with the refrigerant gas X4, and is supplied to thecondenser 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 theturbo compressor 4 in the present embodiment.FIG. 3 is a cross-sectional view taken from line A-A ofFIG. 2 .FIG. 4 is a cross-sectional view taken from line B-B ofFIG. 3 . Furthermore,FIG. 5 is an enlarged plan view of aspur gear 31 and apinion gear 32 included in theturbo compressor 4 in the present embodiment. Moreover,FIGS. 6A and 6B are schematic views of anoil supply nozzle 35 in the present embodiment,FIG. 6A is a vertical cross-sectional view of theoil supply nozzle 35, andFIG. 6B is a bottom view of theoil supply nozzle 35. In addition, all of thespur gear 31, thepinion gear 32 and agear casing 33 inFIG. 4 and theoil supply nozzle 35 inFIG. 5 are indicated by imaginary lines. - As shown in
FIG. 2 , theturbo compressor 4 in the present embodiment includes amotor unit 10, acompressor unit 20, and agear unit 30. - The
motor unit 10 includes a motor 12 (a driving portion) which has anoutput shaft 11 and becomes a driving source for driving thecompressor unit 20, and amotor casing 13 which surrounds themotor 12 and in which themotor 12 is installed. In addition, the driving force, which drives thecompressor unit 20, is not limited to themotor 12, but may be, for example, an internal combustion engine. - The
output shaft 11 of themotor 12 is supported by afirst bearing 14 and asecond bearing motor 15 fixed to themotor casing 13 in a freely rotatable manner. - The
compressor unit 20 includes afirst compression stage 21 which takes in and compresses the refrigerant gas X4 (seeFIG. 1 ), and asecond compression stage 22 which further compresses the refrigerant gas X4 compressed in thefirst compression stage 21 and discharges the same as the compressed refrigerant gas X1 (seeFIG. 1 ). - As shown in
FIG. 3 , thefirst compression stage 21 includes afirst impeller 21 a (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, afirst diffuser 21 b which compresses the refrigerant gas X4 by converting the velocity energy given to the refrigerant gas X4 by thefirst impeller 21 a into pressure energy, afirst scroll chamber 21 c which leads the refrigerant gas X4 compressed by thefirst diffuser 21 b to the outside of thefirst compression stage 21, and aninlet port 21 d which takes in the refrigerant gas X4 and supplies the same to thefirst impeller 21 a. - In addition, a part of the
first diffuser 21 b, thefirst scroll chamber 21 c and theinlet port 21 d is formed by afirst impeller casing 21 e that surrounds thefirst impeller 21 a. - In the
compressor unit 20, arotational shaft 23 extending over thefirst compression stage 21 and thesecond compression stage 22 is provided. Thefirst impeller 21 a is fixed to therotational shaft 23 and is rotated by the transmission of the rotational power of the motor 12 (seeFIG. 2 ) to therotational shaft 23. - Furthermore, in the
inlet port 21 d of thefirst compression stage 21, a plurality ofinlet guide vanes 21 f for adjusting the inlet capacity of thefirst compression stage 21 are installed. The respectiveinlet guide vanes 21 f are freely rotatable so that an exterior area from a flow direction of the refrigerant gas X4 can be changed by thedriving mechanism 21 g fixed to thefirst impeller casing 21 e. Furthermore, at the outside of thefirst impeller casing 21 e, a vane driving portion 24 (seeFIG. 2 ) is installed which is connected to thedriving mechanism 21 g to rotate the respectiveinlet guide vanes 21 f. - The
second compression stage 22 includes asecond impeller 22 a (an impeller) that gives velocity energy to the refrigerant gas X4, which is compressed in thefirst compression stage 21 and then is supplied from a thrust direction, and discharges the refrigerant gas X4 in a radial direction, asecond diffuser 22 b which compresses the refrigerant gas X4 by converting the velocity energy given to the refrigerant gas X4 by thesecond impeller 22 a into pressure energy and discharges the refrigerant gas X4 as the compressed refrigerant gas X1, asecond scroll chamber 22 c which leads the compression refrigerant gas X1 discharged from thesecond diffuser 22 b to the outside of thesecond compression stage 22, and anintroduction scroll chamber 22 d which leads the refrigerant gas X4 compressed in thefirst compression stage 21 to thesecond impeller 22 a. - In addition, a part of the
second diffuser 22 b, thesecond scroll chamber 22 c and theintroduction scroll chamber 22 d is formed by a second impeller casing 22 e that surrounds thesecond impeller 22 a. - The
second impeller 22 a is fixed to therotational shaft 23 so that a rear surface thereof faces thefirst impeller 21 a, and is rotated by the transmission of the rotational power of themotor 12 to therotational shaft 23. - The
second scroll chamber 22 c is connected to the flow path R1 (seeFIG. 1 ) for supplying thecondenser 1 with the compressed refrigerant gas X1 and supplies the flow path R1 with the compressed refrigerant gas X1 led from thesecond compression stage 22. - In addition, the
first scroll chamber 21 c of thefirst compression stage 21 and theintroduction scroll chamber 22 d of thesecond compression stage 22 are connected to each other via an external piping (not shown) which is provided separately from thefirst compression stage 21 and thesecond compression stage 22, and the refrigerant gas X4 compressed in thefirst compression stage 21 via the external piping is supplied to thesecond compression stage 22. The above-mentioned flow path R4 (seeFIG. 1 ) is connected to the external piping, and the gaseous phase component X3 of the refrigerant generated in theeconomizer 2 is supplied to thesecond compression stage 22 via an external piping. - The
rotational shaft 23 is supported by athird bearing 26 in freely rotatable manner, which is fixed to the second impeller casing 22 e in aspace 25 between thefirst compression stage 21 and thesecond compression stage 22, and a fourth bearing 27 (bearing) which is fixed to an end portion of acasing protruding portion 22 f protruding from the second impeller casing 22 e to thegear unit 30 side. In therotational shaft 23, alabyrinth seal 23 a for suppressing the flow of the refrigerant gas X4 from theintroduction scroll seal 22 d to thegear unit 30 side is provided. - Furthermore, as shown in
FIG. 2 , thegear unit 30 includes a spur gear 31 (gear) which is fixed to theoutput shaft 11, a pinion gear 32 (gear) which is fixed to therotational shaft 23 and is engaged with thespur gear 31, and a gear casing which accommodates thespur gear 31 and thepinion gear 32, and transmits the rotational power of theoutput shaft 11 of themotor 12 to therotational shaft 23. In addition, thegear unit 30 includes a lubricantoil supply portion 34 for supplying the lubricant oil to a plurality of sliding portions which slides due to the rotation of therotational shaft 23. - An outer diameter of the
spur gear 31 is greater than that of thepinion gear 32, and the rotational power of themotor 12 is transmitted to therotational shaft 23 so that the revolution of therotation shaft 23 increases relative to that of theoutput shaft 11 by the cooperation between thespur gear 31 and thepinion gear 32. In addition, at the time the rotational power of themotor 12 is transmitted to therotational shaft 23, the diameters of the plurality of gears may be set so that the revolution of therotational shaft 23 is identical to that of theoutput shaft 11 or reduces without being limited to the transmission method. - The
gear casing 33 is molded separately from themotor casing 13 and the second impeller casing 22 e and connects them to each other. In an inner part of thegear casing 33, anaccommodation space 33 a for accommodating thespur gear 31, thepinion gear 32 and the lubricantoil supply portion 34 is formed. Thegear casing 33 and the second impeller casing 22 e are fixed to each other using a plurality ofbolts 33 b. Furthermore, in thegear casing 33, anoil tank 33 c is provided in which the lubricant oil to be supplied to the sliding portion of theturbo compressor 4 is collected and stored. - The lubricant
oil supply portion 34 supplies the lubricant oil for the lubrication and the cooling to thefourth bearing 27, which is a sliding portion accompanied by the rotation of theoutput shaft 11 and therotational shaft 23, and an engagement portion 38 (seeFIG. 4 ) between thespur gear 31 and thepinion gear 32. The lubricantoil supply portion 34 includes aoil supply nozzle 35 which injects and supplies the lubricant oil to the plurality of sliding portions, and asupply pipe 36 which is connected to theoil supply nozzle 35 and supplies the lubricant oil. - The
supply tube 36 is connected to thesupply pump 37 delivering the lubricant oil stored in theoil tank 33 c, via a supply flow path (not shown) provided outside thegear casing 33. Thesupply pump 37 is installed on an external surface of theoil tank 33 c. - 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 , theoil supply nozzle 35 is provided on the upper side of thepinion gear 32 and is fixed to thecasing protruding portion 22 f of thesecond compression stage 22. In addition, in thecasing protruding portion 22 f, anoil discharging port 22 g is formed which is situated at the lower part side of thepinion gear 32 to discharge the lubricant oil supplied from theoil supply nozzle 35. - Furthermore, the
oil supply nozzle 35 includes ahole portion 35 a connected to thesupply pipe 36 extending in a vertical direction, afirst injection hole 35 b and asecond injection hole 35 c which communicate with thehole portion 35 a and are opened toward the outside (with regard to thesecond injection hole 35 c, seeFIG. 4 ). - The
first injection hole 35 b is opened toward thefourth 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, thefourth bearing 27 is a so-called rolling bearing, includes aninner ring 27 a, anouter ring 27 b, and a plurality of rollingbodies 27 c disposed between theinner ring 27 a and theouter ring 27 b, and thefirst injection hole 35 b is opened toward theinner ring 27 a. That is, more specifically, the above-mentioned first supply place is theinner ring 27 a of thefourth bearing 27. - Since the
first injection hole 35 b is opened toward thefourth bearing 27, the lubricant oil can be supplied from thefirst injection hole 35 b to thefourth bearing 27, which can lubricate and cool thefourth bearing 27. Furthermore, since thefirst injection hole 35 b is opened toward theinner ring 27 a, it is possible to actively lubricate and cool theinner ring 27 a having a large heating value due to the sliding. - As shown in
FIG. 4 , thesecond injection hole 35 c is opened to theengagement portion 38 between thespur gear 31 and thepinion 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 thesecond injection hole 35 c to theengagement portion 38, which can lubricate and cool thespur gear 31 and thepinion gear 32 in theengagement portion 38. - In addition, an end side of the
supply pipe 35 is connected to thehole portion 35 a of theoil supply nozzle 35 and the other end side thereof is connected to the inner surface of thegear casing 33. - Furthermore, as shown in
FIG. 5 , thesecond injection hole 35 c is opened toward the center portion in a width direction (left and right direction inFIG. 5 ) of theengagement portion 38. For that reason, it is possible to effectively spread the lubricant oil over the width direction of theengagement portion 38. In addition, the opening direction of thefirst injection hole 35 b may be suitably tilted to a circumferential direction of theinner ring 27 a so as to follow the rotational direction of therotational shaft 23. - As mentioned above, the
oil supply nozzle 35 includes thefirst injection hole 35 b and thesecond injection hole 35 c. As a result, it is possible to supply the lubricant oil to any one of thefourth bearing 27 and theengagement portion 38 slid along with the rotation of theoutput shaft 11 and therotational shaft 23 by a singleoil supply nozzle 35. For that reason, in the present embodiment, there is needless to provide nozzles for supplying the lubricant oil near thefourth bearing 27 and theengagement 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 thefourth bearing 27 and theengagement portion 38, which can reduce the labor and the costs of manufacturing in theturbo compressor 4. - As shown in
FIGS. 6A and 6B , thefirst injection hole 35 b and thesecond injection hole 35 c of theoil supply nozzle 35 connect the front end side (a lower part side ofFIG. 6A ) of theoil supply nozzle 35 to the inner peripheral surface of thehole portion 35 a formed of a cylindrical shape. Furthermore, the extension direction of thefirst injection hole 35 b and thesecond injection hole 35 c is tilted relative to the extension direction of thehole portion 35 a at a predetermined angle. In addition, as shown inFIG. 6B , thefirst injection hole 35 b and thesecond injection hole 35 c branch off in a radial direction around the axis of thehole portion 35 a. - Furthermore, the
oil supply nozzle 35 includes afirst plane 35 d orthogonal to the extension direction of thefirst injection hole 35 b, and asecond plane 35 e orthogonal to the extension direction of thesecond injection hole 35 c. Thefirst injection hole 35 b is opened to thefirst plane 35 d and thesecond injection hole 35 c is opened to thesecond plan 35 e. As a result, thefirst plane 35 d and thesecond plane 35 e are tilted to the proximal end side with respect to the front end surface (a lower end surface inFIG. 6A ) of theoil supply nozzle 35 at a predetermined angle and form a slope surface facing thefourth bearing 27 or theengagement portion 38. - At the time of the production of the
oil supply nozzle 35, the main body of theoil supply nozzle 35 and thehole portion 35 a are formed by the mechanical working (a cutting working and a drill working). Next, after thefirst plane 35 d and thesecond plane 35 e are formed by the mechanical working (the cutting working and the drill working), thefirst injection hole 35 b and thesecond injection hole 35 c 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 therotational shaft 23 via thespur gear 31 and thepinion gear 32, whereby thefirst impeller 21 a and thesecond impeller 22 a of thecompressor unit 20 are rotated. - When the
first impeller 21 a is rotated, theinlet port 21 d of thefirst compression stage 21 enters a negative pressure state, and the refrigerant gas X4 flows from the flow path R5 into thefirst compression stage 21 via theinlet port 21 d. - The refrigerant gas X4 flowed into the inner portion of the
first compression stage 21 flows into thefirst impeller 21 a in the thrust direction. This refrigerant gas X4 is provided with the velocity energy by thefirst impeller 21 a, and is discharged in the radial direction. - The refrigerant gas X4 discharged from the
first impeller 21 a is compressed by converting the velocity energy to the pressure energy by thefirst diffuser 21 b. - The refrigerant gas X4 discharged from the
first diffuser 21 b is led to the outside of thefirst compression stage 21 via thefirst scroll chamber 21 c. - Moreover, the refrigerant gas X4 led to the outside of the
first compression stage 21 is supplied to thesecond compression stage 22 via an external piping (not shown). - The refrigerant gas X4 supplied to the
second compression stage 22 flows into thesecond impeller 22 a via theintroduction scroll chamber 22 d in the thrust direction. This refrigerant gas X4 is provided with the velocity energy by thesecond impeller 22 a, and is discharged in the radial direction. - The refrigerant gas X4 discharged from the
second impeller 22 a is further compressed by converting the velocity energy into the pressure energy by thesecond diffuser 22 b and becomes the compressed refrigerant gas X1. - The compression refrigerant gas X1 discharged from the second diffuse 22 b is led to the outside of the
second compression stage 22 via thesecond scroll chamber 22 c. - The compressed refrigerant gas X1 led to the outside of the
second compression stage 22 is supplied to thecondenser 1 via the flow path R1. - Furthermore, the
turbo compressor 4 in the present embodiment includes the above-mentioned lubricantoil supply portion 34. For that reason, it is possible to supply the lubricant oil to any one of thefourth bearing 27 and theengagement portion 38 slid due to theoutput shaft 11 and therotational 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 thefourth bearing 27 and theengagement 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 theturbo 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 theoil supply nozzle 35 can be produced by a simple mechanical working, the effect can be further improved. - In addition, the
first injection hole 35 b and thesecond injection hole 35 c are titled toward the front end side in the extension direction of thehole portion 35 a at a predetermined angle, and branch off around the axis of thehole portion 35 a in the radial direction. For that reason, the lubricant oil supplied from thesupply pipe 36 toward the front end side of thehole portion 35 a is powerfully injected from thefirst injection hole 35 b and thesecond injection hole 35 c which are titled toward the front end side and branch off, with the result that it is possible to effectively lubricate and cool thefourth bearing 27 and theengagement portion 38. Furthermore, since thefirst injection hole 35 b and thesecond injection hole 35 c are opened vertically to thefirst plane 35 d and thesecond plane 35 e facing thefourth bearing 27 or theengagement portion 38, it is difficult for the lubricant oil injected from thefirst injection hole 35 b and thesecond injection hole 35 c to be adversely affected by thefirst plane 35 d and thesecond plane 35 e. - 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 thefourth bearings 27 and theengagement 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 theoil supply nozzle 35 includes thefirst injection hole 35 b and thesecond injection hole 35 c, theoil 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 thefirst compression stage 21 and thesecond 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 theturbo compressor 4 in the above embodiment is used in the turbo refrigerator S1, for example, theturbo compressor 4 may be used, for example, as a supercharger that supplies an internal combustion engine with the compressed air.
Claims (12)
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.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JPP2010-051930 | 2010-03-09 | ||
JP2010051930A JP5577762B2 (en) | 2010-03-09 | 2010-03-09 | Turbo compressor and turbo refrigerator |
Publications (1)
Publication Number | Publication Date |
---|---|
US20110219809A1 true US20110219809A1 (en) | 2011-09-15 |
Family
ID=44558630
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/042,609 Abandoned US20110219809A1 (en) | 2010-03-09 | 2011-03-08 | Turbo compressor and turbo refrigerator |
Country Status (3)
Country | Link |
---|---|
US (1) | US20110219809A1 (en) |
JP (1) | JP5577762B2 (en) |
CN (1) | CN102192146A (en) |
Cited By (7)
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---|---|---|---|---|
US20160138835A1 (en) * | 2013-06-04 | 2016-05-19 | Daikin Industries, Ltd. | Turbo refrigerator |
US20160237964A1 (en) * | 2015-02-16 | 2016-08-18 | Borgwarner Inc. | Heat transfer system and method of making and using the same |
WO2016188819A1 (en) * | 2015-05-22 | 2016-12-01 | Nuovo Pignone Tecnologie Srl | Subsea compressor with device for cleaning the motor cooling fan and/or auxiliary bearings |
US20180274544A1 (en) * | 2014-10-31 | 2018-09-27 | Trane International Inc. | Systems and methods to provide lubricant to a bearing |
US10570776B2 (en) | 2016-06-07 | 2020-02-25 | United Technologies Corporation | Nozzle for delivering fluid to a component |
WO2022119709A1 (en) * | 2020-12-03 | 2022-06-09 | Danfoss A/S | Refrigerant compressor including diffuser with grooves |
US11359642B2 (en) | 2018-07-20 | 2022-06-14 | Ihi Corporation | Electric compressor |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP6102589B2 (en) * | 2013-07-10 | 2017-03-29 | ダイキン工業株式会社 | Turbo compressor and turbo refrigerator |
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Also Published As
Publication number | Publication date |
---|---|
JP5577762B2 (en) | 2014-08-27 |
JP2011185175A (en) | 2011-09-22 |
CN102192146A (en) | 2011-09-21 |
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Owner name: IHI CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:KURIHARA, KAZUAKI;REEL/FRAME:026185/0307 Effective date: 20110408 |
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