CN1383477A - Turbo comprssor and refringerator with compressor - Google Patents
Turbo comprssor and refringerator with compressor Download PDFInfo
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- CN1383477A CN1383477A CN01801641A CN01801641A CN1383477A CN 1383477 A CN1383477 A CN 1383477A CN 01801641 A CN01801641 A CN 01801641A CN 01801641 A CN01801641 A CN 01801641A CN 1383477 A CN1383477 A CN 1383477A
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- mentioned
- impeller
- turbocompressor
- diffusion portion
- outlet
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- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
- F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
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- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- 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
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/52—Outlet
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- 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
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- 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
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- 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
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
- F25B31/008—Cooling of compressor or motor by injecting a liquid
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A turbo-type compressor having an improved performance which may be produced without increasing its size or cost, and the performance of a refrigeration unit is also improved when it is provided with such a turbo-type compressor. The turbo-type compressor includes a casing 55 provided with an intake opening and a discharge opening; a rotation shaft (41) operated by a driving mechanism; an impeller (19) provided integrally with the rotation shaft (41); a diffuser section 46 constituted by a pair of a first wall section (56) and a second wall section (58), located at the outer periphery side of the impeller 19 to serve as a fluid passage for a refrigerant driven towards the outer side by the rotation action of the impeller 19. The refrigerant is drawn in through the intake opening, by the action of the impeller (19) which is rotated together with the rotation shaft 41 and driven by a motor, to be compressed and discharged through the outlet opening. In this compressor, the diffuser section 46 is constructed in such a way that the width dimension in the axial direction of the outlet opening 46b is made larger than the width dimension of the inlet opening (46a).
Description
Technical field
The present invention relates to the turbocompressor of the impeller compressed fluid that rotates and the refrigeration plant that has this turbocompressor.
Background technique
Before, in refrigeration plant, adopt the compressor of turbocompressor as refrigeration agent.This turbocompressor by making the running shaft rotation that is provided with impeller, is used the impeller compressed fluid.
Below, be example with compressor shown in Figure 10, the structure of this turbocompressor is described.
As shown in the figure, the running shaft 1 upper edge Zhou Fangxiang devices spaced apart of this turbocompressor fixing impeller 3 with a plurality of blades 2, make it with running shaft 1 rotation.The solid of rotation (rotor) that is made of this running shaft 1 and impeller 3 is housed in the housing 4.
In the housing 4, marking off diffusion portion 6 and backflow road 7 with demarcation strip 5, is that the return bend portion 8 of U font is communicated with between diffusion portion 6 and the backflow road 7, by section.
Diffusion portion 6 is formed by the 1st 4a of wall portion of housing 4 sides and the 2nd 5a of wall portion of demarcation strip 5 sides, and the 1st 4a of wall portion and the 2nd 5a of wall portion are parallel to each other and perpendicular to running shaft 1.In backflow road 7, along the Zhou Fangxiang devices spaced apart be provided with a plurality of reflux blades 9, be used for the fluid of pilot flow.
In this turbocompressor, sent into the fluid of diffusion portion 6 after impeller 3 compressions, passed out to backflow road 7 by return bend portion 8.
The diffusion portion 6 that forms by the 1st 4a of wall portion and the 2nd 5a of wall portion the mobile deceleration of the fluid of sending from impeller 3 after, make most of dynamic pressure revert back to static pressure, represent the pressure recovery factor Cp of turbocompressor performance be subjected to diffusion portion 6 shape about.
Therefore, by fluid input 6a that improves this diffusion portion 6 and area and the shape that exports 6b, can intensified pressure recovery factor Cp.
But its present situation is shown in the plotted curve of Figure 11, and pressure recovery factor Cp does not reach 0.5, still awaits improving.For this reason, under the prerequisite that does not cause maximizing, require to improve the pressure recovery factor Cp of diffusion portion 6, improve the performance of turbocompressor.
In addition, pressure recovery factor Cp can represent with the inlet 6a of diffusion portion 6, Elongation and the area ratio of outlet 6b.
Elongation and area are tried to achieve than available following formula.
Elongation: 2 Δ R/b2=2 (R2-R1)/b2 ... (1)
Area ratio: AR-1=(R2b2/R1b1)-1 ... (2)
In the formula, R1: the radius of the inlet 6a of diffusion portion 6
R2: the radius of the outlet 6b of diffusion portion 6
B1: the width dimensions of the inlet 6a of diffusion portion 6
B2: the width dimensions of the outlet 6b of diffusion portion 6
In addition, the pressure recovery factor Cp of diffusion portion 6 can be represented by the formula.
Pressure recovery factor Cp=(Ps2-Ps1)/(Pt1-Ps2)
In the formula, Ps1: the static pressure of the inlet 6a of diffusion portion 6
Ps2: the static pressure of the outlet 6b of diffusion portion 6
Pt1: the total head of the inlet 6a of diffusion portion 6
That is,, then correspondingly, can be reverted back to static pressure well by the dynamic pressure of the fluid of sending after impeller 3 compressions if pressure coefficient Cp increases.
The present invention makes in view of the above problems, its objective is under the prerequisite that does not cause maximizing, and high turbocompressor of a kind of performance height, efficient and the refrigeration plant that has this turbocompressor are provided.
Summary of the invention
To achieve these goals, turbocompressor of the present invention has housing, running shaft, impeller, diffusion portion; Above-mentioned housing is provided with suction port and exhaust port; Above-mentioned running shaft driven-mechanism rotary driving; Above-mentioned impeller is located on this running shaft integratedly; Above-mentioned diffusion portion is formed by a pair of wall portion at above-mentioned impeller outer circumferential side, is stream from the rotation of above-mentioned impeller to outer circumferential side that send fluid by; Also rotation together of above-mentioned impeller during the rotation of above-mentioned running shaft driven-mechanism, by the impeller of this rotation with fluid from above-mentioned suction port suck and compression after, discharge from above-mentioned exhaust port by above-mentioned diffusion portion; It is characterized in that above-mentioned diffusion portion is the inlet of the outlet of outer circumferential side greater than the fluid of being sent by above-mentioned impeller along its axial width dimensions.
Like this and since the width dimensions axially of the inlet side of diffusion portion and outlet side be outlet side greater than inlet side, so inlet side reduces with the vertical wide ratio of outlet side, area can strengthen the pressure recovery factor of diffusion portion than increase simultaneously.That is, do not need complicated structure, just can revert back to static pressure to the dynamic pressure of the compressed fluid of sending from impeller expeditiously by diffusion portion, like this, do not cause maximizing with complicated prerequisite under can realize the turbocompressor that compression efficiency is high.
The turbocompressor of another embodiment of the present invention is characterized in that, does not change the inlet of above-mentioned diffusion portion and the area ratio of outlet, and the width dimensions of outlet is greater than the width dimensions of inlet.
Like this, owing to do not change the inlet of above-mentioned diffusion portion and the area ratio of outlet, the width dimensions of outlet promptly, adds the width dimensions of large outlet greater than the width dimensions of inlet, correspondingly reduces the diameter that exports, so, can realize the miniaturization of external diameter, reduce cost.
Even, also make the width dimensions of the width dimensions of outlet, so by reducing vertical wide ratio, the intensified pressure recovery factor can improve performance conscientiously greater than inlet owing to do not change the inlet of above-mentioned diffusion portion and the area ratio of outlet.
The turbocompressor of another embodiment of the present invention is characterized in that, a pair of wall portion that forms above-mentioned diffusion portion forms the taper that separates gradually towards outlet from inlet.
That is,, can make the outlet width dimensions easy as can, can improve performance greater than the throat width size by a pair of wall portion that forms above-mentioned diffusion portion is formed taper.In addition, because wall portion is taper, so the fluid that can avoid being sent by impeller is peeled off in diffusion portion.
The turbocompressor of another embodiment of the present invention is characterized in that, either party the wall portion that forms in a pair of wall portion of above-mentioned diffusion portion forms the taper of leaving the opposing party's wall portion from inlet towards outlet gradually.
That is, only either party the wall portion in a pair of wall portion that forms above-mentioned diffusion portion is formed taper, can make the outlet width dimensions easy as can, can improve performance greater than the throat width size.In addition, get final product owing to only side's wall portion is formed taper, so, performance can be improved more simply.
Especially, the place ahead side wall portion of impeller (front side of this wall portion has more space than the rear side of the impeller with the downstream side stream that links to each other with diffusion portion) is done when tapered, can be realized axial miniaturization.
The turbocompressor of another embodiment of the present invention is characterized in that, is the multistage with a plurality of impellers, will compress successively from the upstream side impeller from the fluid that suction port sucks.
That is, in having the multistage of a plurality of impellers since can strengthen the fluid of sending from each impeller stream, be the pressure recovery factor of diffusion portion, so, each impeller performance is improved, can realize the turbocompressor of extreme efficiency.
Refrigeration plant of the present invention has compressor, condenser, throttle mechanism, vaporizer; Above-mentioned compressor flows out the refrigeration agent compression back that sucks from suction port from exhaust port; Above-mentioned condenser after above-mentioned condensation of refrigerant, liquefaction, is sent liquid refrigerant; Above-mentioned throttle mechanism is with this liquid refrigerant decompression; Above-mentioned vaporizer makes condensation and post-decompression liquid refrigerant and cooled object carry out heat exchange, with this cooled object cooling, simultaneously, makes the evaporation of aforesaid liquid refrigeration agent, gasification; It is characterized in that above-mentioned compressor is to adopt any turbocompressor of above-mentioned record.
Like this, after the refrigeration agent compression, send into the compressor of condenser, be that employing has pressure recovery factor height, can bring into play the high efficiency turbocompressor of the diffusion portion of superperformance, so, can increase substantially cooling effectiveness, like this, can realize the refrigeration plant that cold performance is good.
Description of drawings
Fig. 1 is the stereogram of refrigeration plant, with the turbocompressor of the explanation embodiment of the invention and have the formation and the structure of the refrigeration plant of this turbocompressor.
Fig. 2 is the summary piping diagram of refrigeration plant, the turbocompressor of the embodiment of the invention is described and has the formation of the refrigeration plant of this turbocompressor.
Fig. 3 is the sectional view of turbocompressor, and the structure of the turbocompressor of the embodiment of the invention is described.
Fig. 4 is the sectional view of press part, and the structure of the turbocompressor of the embodiment of the invention is described.
Fig. 5 is a plotted curve, the performance of the diffusion portion of the turbocompressor of the expression embodiment of the invention.
Fig. 6 is the sectional view of press part, and the structure of the turbocompressor of another embodiment of the present invention is described.
Fig. 7 is a plotted curve, the performance of the diffusion portion of the turbocompressor of expression another embodiment of the present invention.
Fig. 8 is the sectional view of press part, and the structure of the turbocompressor of another embodiment of the present invention is described.
Fig. 9 is the sectional view of press part, and the structure of the turbocompressor of another embodiment of the present invention is described.
Figure 10 is the sectional view of press part, and the structure of turbocompressor before is described.
Figure 11 is a plotted curve, the pressure recovery factor of expression diffusion portion.
The concrete form of implementation of invention
Below, with reference to the turbocompressor of the description of drawings embodiment of the invention with have the refrigeration plant of this turbocompressor.
The integral body that refrigeration plant is described that sees figures.1.and.2 earlier constitutes.
Illustrated refrigerator has vaporizer 11, compressor 12, condenser 13, throttle valve 14, interstage cooler 15, oil cooler 16.Vaporizer 11 makes refrigeration agent and cold water carry out heat exchange, with the cold water cooling, simultaneously with refrigeration agent evaporation gasification.Compressor 12 is the refrigeration agent compression of having gasified in vaporizer 11.Condenser 13 is compressed condensation of refrigerant, liquefaction in compressor 12.The refrigeration agent that 14 pairs of throttle valve have liquefied in condenser 13 reduces pressure.Interstage cooler 15 temporarily accumulates in the refrigeration agent that liquefied in the condenser 13 and it is cooled off.Oil cooler 16 utilizes the lubricant oil cooling of the part of the refrigeration agent that is cooled with compressor 12 in condenser 13.
In addition, on compressor 12, connecting the motor (driving mechanism) 17 that drives this compressor 12.
Vaporizer 11, compressor 12, condenser 13, throttle valve 14 and interstage cooler 15 are connected by main pipe arrangement 18, thereby constitute the locking system that makes refrigerant cycle.
In addition, the part of the refrigeration agent that is cooled in main condenser 13a imports without supplementary cooler 13b ground in the housing 31 of aftermentioned motor 17, and stator or coil that figure is not shown cool off.
The structure of interstage cooler 15 is identical with hollow container, temporarily accumulate in be cooled among main condenser 13a, the supplementary cooler 13b, by throttle valve 14 post-decompression refrigeration agents, further cool off.The gaseous component of interstage cooler 15 imports the 2nd grade of impeller 19b of compressor 12 without vaporizer 11 by bypass pipe arrangement 23.
Below, describe the turbocompressor 12 that above-mentioned refrigeration plant has in detail.
As shown in Figure 3, on turbocompressor 12, be provided with said motor 17 integratedly, driven by the rotary driving force of this motor 17.
The rotating force of the running shaft 35 of motor 17 passes to the running shaft 41 that constitutes turbocompressor 12 by the transmission gear 36,37 that is being meshing with each other, and like this, the running shaft 41 of this turbocompressor 12 is driven in rotation.
This turbocompressor 12, one is distolateral to be suction port 42, refrigeration agent is admitted to suction port 42 from vaporizer 11.Be provided with suction blade 40 at this suction port 42, carry out the control of the refrigeration agent inlet capacity in the suction port 42 by this suction blade 40.
On turbocompressor 12, be provided with the 1st grade of press part 43, the 2nd grade of press part 44 successively from suction port 42.Be provided with the 1st grade of above-mentioned impeller 19a, the 2nd grade of impeller 19b at these the 1st grade of press part 43, the 2nd grade of press part 44.
During running shaft 41 rotations, these the 1st grade of impeller 19a, the 2nd grade of impeller 19b rotate respectively, come the refrigeration agent of from evaporator drier 11 to be inhaled into the 1st grade of press part 43 from suction port 42, after the 1st grade of impeller 19a compression of the 1st grade of press part 43, by have diffusion portion 46, go back to elbow portion 47, the backflow road 49 of rotary vane 48 is admitted to the 2nd grade of press part 44, after the 2nd grade of impeller 19b compression of the 2nd grade of press part 44, pass diffusion portion 46, by the stream along Zhou Fangxiang formation is scroll portion 52, discharge from exhaust port 53, pass out to condenser 13.
As previously mentioned, the refrigeration agent of sending into from middle cooler 15 is admitted to the 2nd grade of press part 44, with being compressed by the 2nd grade of impeller 19b of the 2nd grade of press part 44 from the 1st grade of refrigeration agent that press part 43 is sent into, with similarly aforementioned, pass diffusion portion 46, by the stream along Zhou Fangxiang formation is scroll portion 52, discharges from exhaust port 53, passes out to condenser 13.
Below, be the structure that example illustrates the diffusion portion 46 in the 1st grade of press part 43, the 2nd grade of press part 44 with the diffusion portion 46 of the 1st grade of press part 43.
As shown in Figure 4, in diffusion portion 46, the 1st wall portion 56 (the 1st wall portion 56 is made of the housing 55 of turbocompressor 12) and the 2nd wall portion 58 (the 2nd wall portion 58 is made of demarcation strip 57) that form this diffusion portion 46 are towards the separated shape of radial direction foreign side, like this, this diffusion portion 46 forms from inlet 46a towards the outlet 46b taper of expanding out gradually, strengthens gradually towards radial direction foreign side along the axial width dimensions of diffusion portion 46.
Like this, this turbocompressor 12, (b1＜b2), so the inlet 46a of diffusion portion 46 reduces with the Elongation at outlet 46b place, area is than increase simultaneously greater than the width dimensions b1 of its inlet 46a for the width dimensions b2 of the outlet 46b of its diffusion portion 46.
Like this, as shown in Figure 5, turbocompressor 12 with this diffusion portion 46 is compared with having before the turbocompressor of diffusion portion 6 (the inlet 46a of this diffusion portion 6, outlet 46b are same width dimensions), and pressure recovery factor Cp is the point of left oblique upper, has surpassed 0.5.Like this, the performance of diffusion portion 46 improves, and the efficient of turbocompressor 12 improves.
In addition, therewith similarly, in the diffusion portion 46 of the 2nd grade of press part 44, pressure recovery factor Cp also improves.
In the above-mentioned example, be that 2 grades of formulas (multistage) turbocompressor with the 1st grade of impeller 19a and the 2nd grade of impeller 19b is described, but also be applicable to single-stage turbocompressor with an impeller.
As mentioned above, turbocompressor 12 according to above-mentioned structure, the axle direction width dimensions of the inlet 46a side of diffusion portion 46 and outlet 46b side is that outlet 46b side is greater than inlet 46a side, so, inlet 46a side reduces some with the length ratio of outlet 46b side, area can strengthen the pressure recovery factor Cp of diffusion portion 46 than increasing.
Promptly, do not need complicated structure, by diffusion portion 46, can revert back to static pressure to the dynamic pressure of sending from the 1st grade of impeller 19a, the 2nd grade of impeller 19b that is compressed the back refrigeration agent expeditiously, like this, do not cause maximizing and complicated prerequisite under, can realize the turbocompressor that compression efficiency is high.
In addition, by a pair of wall portion that forms diffusion portion 46, promptly the 1st wall portion 56 and the 2nd wall portion 58 form taper, the width dimensions that makes outlet easy as can improve performance greater than the throat width size.In addition, because the 1st wall portion 56 and the 2nd wall portion 58 form taper, so, can not peel off from the 1st grade of impeller 19a, the 2nd grade of refrigeration agent that impeller 19b sends in diffusion portion 46.
In addition, above-mentioned turbocompressor 12, be 2 grades of formulas (multistage) with the 1st grade of impeller 19a and the 2nd grade of impeller 19b, because from the stream of the 1st grade of impeller 19a and the 2nd grade of refrigeration agent that impeller 19b sends respectively is that pressure recovery factor Cp the diffusion portion 46 is big, so, at each the 1st grade of impeller 19a and the 2nd grade of impeller 19b, performance is enhanced, and can realize the turbocompressor of extreme efficiency.
According to the refrigeration plant that has this turbocompressor 12, the compressor of sending into condenser 13 after the refrigeration agent compression, be to adopt the high efficiency turbocompressor 12 that has high pressure recovery factor Cp, brings into play the diffusion portion 46 of superperformance, so, can increase substantially cooling effectiveness, like this, can realize the refrigeration plant that cooling performance is good.
Below, other embodiment is described.
As shown in Figure 6, this diffusion portion 46 similarly, the 1st wall portion 56 (the 1st wall portion 56 is made of the housing 55 of turbocompressor 12) and the 2nd wall portion 58 (the 2nd wall portion 58 is made of demarcation strip 57) that form this diffusion portion 46 form the separated shape towards radial direction foreign side, like this, this diffusion portion 46 forms the taper that enlarges gradually towards outlet 46b from inlet 46a, and the width dimensions of diffusion portion 46 is to strengthen gradually towards radial direction foreign side.
But in this diffusion portion 46, by reducing to export the radius R 2 of 46b, inlet 46a is preceding identical with improvement with the area ratio of outlet 46b.
That is, this turbocompressor 12, the area ratio remains unchanged, and vertical wide ratio reduces.Like this, as shown in Figure 7, the turbocompressor 12 with this diffusion portion 46 is compared with having before the turbocompressor of diffusion portion, and its pressure recovery factor Cp is the point that moves towards the left side, has surpassed 0.5.Like this, the performance of diffusion portion 46 improves, and the efficient of turbocompressor 12 improves.
The turbocompressor 12 of above-mentioned structure, as previously mentioned, do not change the area ratio of inlet 46a side with the outlet 46b side of diffusion portion 46, width dimensions axially is that outlet 46b side is greater than inlet 46a side, so, inlet 46a side reduces with the vertical wide ratio of outlet 46b side, can strengthen the pressure recovery factor Cp of diffusion portion 46.
Promptly, do not need complicated structure, just can be compressed afterwards that the dynamic pressure of refrigeration agent reverts back to static pressure effectively to what send by diffusion portion 46, like this from the 1st grade of impeller 19a, the 2nd grade of impeller 19b, do not cause maximization and complicated, can realize the turbocompressor that compression efficiency is high.
And, do not change the inlet 46a of diffusion portion 46 and the area ratio of outlet 46b, make the width dimensions b1 of the width dimensions b2 of outlet 46b greater than inlet 46a, promptly, the width dimensions b2 that adds large outlet 46b correspondingly reduces to export the radius R 2 of 46b, so, can realize the miniaturization of external diameter, can reduce cost.
In addition,, make the width dimensions b1 of the width dimensions b2 of outlet 46b greater than inlet 46a owing to do not change inlet 46a and the area ratio that exports 46b, so, make vertical wide ratio reduce intensified pressure recovery factor Cp.Can improve performance conscientiously.
In addition, in the above-mentioned example, all be that the 1st wall portion 56 (the 1st wall portion 56 is made of the housing 55 of turbocompressor 12) and the 2nd wall portion 58 (the 2nd wall portion 58 is made of demarcation strip 57) that form diffusion portion 46 are separated from each other towards radial direction foreign side, become the structure that diffusion portion 46 enlarges towards outlet 46b gradually from inlet 46a, the width dimensions of diffusion portion 46 is become the structure that enlarges gradually towards radial direction foreign side, but under the prerequisite that liquid stream is not peeled off in diffusion portion 46, as long as make the width dimensions of the width dimensions of outlet 46b side greater than inlet 46a, just can improve pressure recovery factor Cp, improve the efficient of turbocompressor 12.
In the example shown in Figure 8, be only the 2nd wall portion 58 that is made of demarcation strip 57 to be inclined to taper.In example shown in Figure 9, be only the 1st wall portion 56 that is made of housing 55 to be inclined to taper.Transport two kinds of situations and all form the taper that the liquid stream in the diffusion portion 46 is not peeled off.
According to Fig. 8 or diffusion portion 46 shown in Figure 9, only the either party in the 1st wall portion 56 or the 2nd wall portion 58 is formed taper, the opposing party is perpendicular to the vertical surface of running shaft 41, so, compare when the 1st wall portion 56 is all formed taper with the 2nd wall portion 58, construct simplyr, can reduce cost.
When the 2nd wall portion 58 that is made of demarcation strip 57 is become taper, go back to the curvature that elbow portion 47 keeps liquid stream not peel off in order to make, demarcation strip 57 also needs to tilt rearward itself.But in the example shown in Figure 9, because the 2nd wall portion 58 that is made of demarcation strip 57 is perpendicular to running shaft 41, so, can avoid in order to remain on the curvature that the liquid stream that goes back to elbow portion 47 places do not peel off and demarcation strip 57 to be tilted rearward, thereby avoid increasing the axle direction size.Like this, can not increase the axle direction size of turbocompressor 12, raise the efficiency.
That is, according to above-mentioned turbocompressor 12, only a pair of wall portion that forms diffusion portion 46, promptly one in the 1st wall portion 56 and the 2nd wall portion 58 squarely becomes taper, can make the width dimensions of the width dimensions of outlet 46b greater than inlet 46a easy as can, the raising performance.In addition, because as long as the either party in the 1st wall portion 56 or the 2nd wall portion 58 is formed taper, so, performance can be improved more simply.
Especially in the example shown in Figure 9, as previously mentioned, because the place ahead side wall portion is that the 1st wall portion 56 (front side of the 1st wall portion 56 has more space than impeller 19 rear sides with the downstream side stream that links to each other with diffusion portion 46) does tapered, so, can realize axial miniaturization.
In addition, the structure of Fig. 8 and diffusion portion 46 shown in Figure 9 also is applicable to Fig. 4 and diffusion cage structure shown in Figure 6.
In the above-mentioned example, the on-bladed formula diffusion portion that blade is not set in diffusion portion 46 has been described, this diffusion portion 46 also can be provided with blade.
Industrial applicibility
As mentioned above, according to turbocompressor of the present invention with have this turbocompressor Refrigerating plant, have following effect.
According to the turbocompressor of claim 1 record and since the entrance side of diffusion section with go out The width dimensions axially of mouthful side, be outlet side greater than entrance side, so, entrance side Reduce with the vertical wide ratio of outlet side, Area Ratio increases simultaneously, and the pressure that can strengthen diffusion section returns Complex coefficient. That is, do not need complicated structure, just can be sending from impeller by diffusion section The dynamic pressure of compressed rear fluid effectively revert back to static pressure, like this, do not cause maximizing and Complicated, can realize the turbocompressor that compression efficiency is high.
According to the turbocompressor of claim 2 record, do not change the entrance of above-mentioned diffusion section With the Area Ratio of outlet, the width dimensions of outlet is greater than the width dimensions of entrance, that is, and add The width dimensions of large outlet correspondingly reduces the radius that exports, so, can realize the little of external diameter Type reduces cost.
Owing to do not change the Area Ratio of entrance and outlet, the width dimensions of outlet is greater than entrance Width dimensions, so, reducing vertical wide ratio, the intensified pressure recovery factor improves performance conscientiously.
According to the turbocompressor of claim 3 record, a pair of wall section of formation diffusion section Form taper, can make easy as can the outlet width dimensions greater than the throat width size, can carry High-performance. In addition, because wall section is taper, so, can avoid the fluid of being sent by impeller Section peels off at diffusion.
According to the turbocompressor of claim 4 record, only a pair of wall that forms diffusion section Either party's wall section in the section forms taper, can make easy as can the outlet width dimensions greater than entering The mouth width dimensions can improve performance. In addition, owing to as long as side's wall section is formed taper Get final product, so, performance can be improved more simply.
Especially, (front side of wall section is than having and diffusion the place ahead side wall portion of impeller The rear side of the impeller of the downstream side stream that section links to each other has more space) do when tapered, Can realize axial miniaturization.
According to the turbocompressor of claim 5 record, owing to have the many of a plurality of impellers In the level formula, strengthen the fluid that each impeller sends stream, be the pressure recovery factor of diffusion section, So, each impeller performance is improved, can realize the turbocompressor of extreme efficiency.
According to the refrigerating plant of claim 6 record, as sending into condensation behind the refrigerant compression The compressor of device is to adopt the diffusion section that has pressure recovery factor height, can bring into play superperformance The high efficiency turbocompressor, so, can improve cooling effectiveness in amplitude, like this, can Realize the good refrigerating plant of cooling performance.
Modification according to the 19th of treaty
1. refrigeration plant has compressor, condenser, throttle mechanism, vaporizer; Above-mentioned compressor flows out the refrigeration agent compression back that sucks from suction port from exhaust port; Above-mentioned condenser with above-mentioned condensation of refrigerant, liquefaction after send liquid refrigerant; Above-mentioned throttle mechanism is with this liquid refrigerant decompression; Above-mentioned vaporizer makes condensation and post-decompression liquid refrigerant and cooled object carry out heat exchange, with this cooled object cooling, simultaneously, makes the evaporation of aforesaid liquid refrigeration agent, gasification;
Above-mentioned compressor is a turbocompressor, has housing, running shaft, impeller, diffusion portion; Above-mentioned housing is provided with suction port and exhaust port; Above-mentioned running shaft driven-mechanism rotary driving; Above-mentioned impeller is located on this running shaft integratedly; Above-mentioned diffusion portion is formed by a pair of wall portion at the impeller outer circumferential side, is stream from the rotation of impeller to outer circumferential side that send fluid by; During the rotation of above-mentioned running shaft driven-mechanism, impeller is rotation together also, by the impeller of this rotation, fluid is sucked and compresses from above-mentioned suction port, discharges from above-mentioned exhaust port by above-mentioned diffusion portion; It is characterized in that the width dimensions axially of above-mentioned diffusion portion is that the width dimensions of outlet of outer circumferential side is greater than the width dimensions of the inlet of the fluid of being sent by impeller.
2. refrigeration plant as claimed in claim 1 is characterized in that, does not change the inlet of above-mentioned compressor diffusion portion and the area ratio of outlet, and the width dimensions of outlet is greater than the width dimensions of inlet.
3. refrigeration plant as claimed in claim 1 is characterized in that, a pair of wall portion that forms above-mentioned compressor diffusion portion forms the taper that separates gradually towards outlet from inlet.
4. refrigeration plant as claimed in claim 1 is characterized in that, the either party's wall portion that forms in a pair of wall portion of above-mentioned compressor diffusion portion forms the taper of leaving the opposing party's wall portion from inlet towards outlet gradually.
5. refrigeration plant as claimed in claim 1 is characterized in that, above-mentioned compressor is that multistage has a plurality of impellers, and the impeller of the fluid that sucks from suction port from upstream side compressed successively.
Claims (6)
1. turbocompressor has housing, running shaft, impeller, diffusion portion; Above-mentioned housing is provided with suction port and exhaust port; Above-mentioned running shaft driven-mechanism rotary driving; Above-mentioned impeller is located on this running shaft integratedly; Above-mentioned diffusion portion is formed by a pair of wall portion at the impeller outer circumferential side, is stream from the rotation of impeller to outer circumferential side that send fluid by; During the rotation of above-mentioned running shaft driven-mechanism, impeller is rotation together also, by the impeller of this rotation with fluid from above-mentioned suction port suck and compression after, discharge from above-mentioned exhaust port by above-mentioned diffusion portion; It is characterized in that the width dimensions axially of above-mentioned diffusion portion is that the width dimensions of outlet of outer circumferential side is greater than the width dimensions of the inlet of the fluid of being sent by impeller.
2. turbocompressor as claimed in claim 1 is characterized in that, does not change the inlet of above-mentioned diffusion portion and the area ratio of outlet, and the width dimensions of outlet is greater than the width dimensions of inlet.
3. turbocompressor as claimed in claim 1 is characterized in that, a pair of wall portion that forms above-mentioned diffusion portion forms the taper that separates gradually towards outlet from inlet.
4. turbocompressor as claimed in claim 1 is characterized in that, the either party's wall portion that forms in a pair of wall portion of above-mentioned diffusion portion forms the taper of leaving the opposing party's wall portion from inlet towards outlet gradually.
5. turbocompressor as claimed in claim 1 is characterized in that, is the multistage with a plurality of impellers, and the fluid that sucks from suction port is compressed successively from the upstream side impeller.
6. refrigeration plant has compressor, condenser, throttle mechanism, vaporizer; Above-mentioned compressor flows out the refrigeration agent compression back that sucks from suction port from exhaust port; Above-mentioned condenser will be sent liquid refrigerant after above-mentioned condensation of refrigerant, the liquefaction; Above-mentioned throttle mechanism is with this liquid refrigerant decompression; Above-mentioned vaporizer makes condensation and post-decompression liquid refrigerant and cooled object carry out heat exchange, with this cooled object cooling, simultaneously, makes the evaporation of aforesaid liquid refrigeration agent, gasification; It is characterized in that, above-mentioned compressor, be the turbocompressor that adopts any one record in the claim 1～5.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP185239/00 | 2000-06-20 | ||
| JP2000185239A JP2002005089A (en) | 2000-06-20 | 2000-06-20 | Turbo-compressor and refrigeration equipment provided with the same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1383477A true CN1383477A (en) | 2002-12-04 |
Family
ID=18685586
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN01801641A Pending CN1383477A (en) | 2000-06-20 | 2001-06-18 | Turbo comprssor and refringerator with compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20020106278A1 (en) |
| JP (1) | JP2002005089A (en) |
| KR (1) | KR20020031409A (en) |
| CN (1) | CN1383477A (en) |
| WO (1) | WO2001098669A1 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100455819C (en) * | 2005-12-23 | 2009-01-28 | 财团法人工业技术研究院 | Compressor jet flow path structure |
| CN103998790A (en) * | 2012-01-17 | 2014-08-20 | 三菱重工业株式会社 | Centrifugal compressor |
| CN104235031A (en) * | 2013-06-19 | 2014-12-24 | 重庆美的通用制冷设备有限公司 | Multistage cantilever compressor |
| CN104764239A (en) * | 2014-01-07 | 2015-07-08 | Lg电子株式会社 | A turbo chiller |
| CN105091380A (en) * | 2014-05-20 | 2015-11-25 | Lg电子株式会社 | Turbo chiller and chiller system including the same |
| CN106662120A (en) * | 2014-09-18 | 2017-05-10 | 三菱重工业株式会社 | Centrifugal compressor |
| CN107709792A (en) * | 2015-10-30 | 2018-02-16 | 三菱重工制冷空调系统株式会社 | The return stream forming portion and centrifugal compressed machinery of centrifugal compressed machinery |
| CN111094874A (en) * | 2017-08-29 | 2020-05-01 | 高效能源有限责任公司 | Heat pump with cooling device for cooling the guide chamber or the suction opening |
| CN114483657A (en) * | 2020-11-13 | 2022-05-13 | Lg电子株式会社 | Compressor and cooling device comprising same |
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| DE102007034236A1 (en) * | 2007-07-23 | 2009-02-05 | Continental Automotive Gmbh | Centrifugal compressor with a diffuser for use with a turbocharger |
| US7975506B2 (en) | 2008-02-20 | 2011-07-12 | Trane International, Inc. | Coaxial economizer assembly and method |
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| US9353765B2 (en) * | 2008-02-20 | 2016-05-31 | Trane International Inc. | Centrifugal compressor assembly and method |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5590798U (en) * | 1978-12-18 | 1980-06-23 | ||
| JPS5736395U (en) * | 1980-08-12 | 1982-02-25 | ||
| JP2000356199A (en) * | 1999-06-15 | 2000-12-26 | Hitachi Ltd | Centrifugal pump |
-
2000
- 2000-06-20 JP JP2000185239A patent/JP2002005089A/en not_active Withdrawn
-
2001
- 2001-06-18 KR KR1020027002006A patent/KR20020031409A/en not_active Application Discontinuation
- 2001-06-18 WO PCT/JP2001/005171 patent/WO2001098669A1/en not_active Application Discontinuation
- 2001-06-18 CN CN01801641A patent/CN1383477A/en active Pending
- 2001-06-18 US US10/048,993 patent/US20020106278A1/en not_active Abandoned
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100455819C (en) * | 2005-12-23 | 2009-01-28 | 财团法人工业技术研究院 | Compressor jet flow path structure |
| CN103998790A (en) * | 2012-01-17 | 2014-08-20 | 三菱重工业株式会社 | Centrifugal compressor |
| CN103998790B (en) * | 2012-01-17 | 2016-10-19 | 三菱重工业株式会社 | Centrifugal compressor |
| CN104235031A (en) * | 2013-06-19 | 2014-12-24 | 重庆美的通用制冷设备有限公司 | Multistage cantilever compressor |
| CN104764239A (en) * | 2014-01-07 | 2015-07-08 | Lg电子株式会社 | A turbo chiller |
| CN104764239B (en) * | 2014-01-07 | 2017-06-23 | Lg电子株式会社 | Cooling turbine unit |
| US9702622B2 (en) | 2014-05-20 | 2017-07-11 | Lg Electronics Inc. | Turbo chiller and chiller system including the same |
| CN105091380A (en) * | 2014-05-20 | 2015-11-25 | Lg电子株式会社 | Turbo chiller and chiller system including the same |
| CN106662120A (en) * | 2014-09-18 | 2017-05-10 | 三菱重工业株式会社 | Centrifugal compressor |
| CN107709792A (en) * | 2015-10-30 | 2018-02-16 | 三菱重工制冷空调系统株式会社 | The return stream forming portion and centrifugal compressed machinery of centrifugal compressed machinery |
| CN111094874A (en) * | 2017-08-29 | 2020-05-01 | 高效能源有限责任公司 | Heat pump with cooling device for cooling the guide chamber or the suction opening |
| CN111094874B (en) * | 2017-08-29 | 2022-04-12 | 高效能源有限责任公司 | Heat pump with cooling device for cooling the guide chamber or the suction opening |
| US11754325B2 (en) | 2017-08-29 | 2023-09-12 | Efficient Energy Gmbh | Heat pump having a cooling device for cooling a guide space or a suction mouth |
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| CN114483657B (en) * | 2020-11-13 | 2024-04-19 | Lg电子株式会社 | Compressor and cooling device comprising same |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2001098669A1 (en) | 2001-12-27 |
| US20020106278A1 (en) | 2002-08-08 |
| JP2002005089A (en) | 2002-01-09 |
| KR20020031409A (en) | 2002-05-01 |
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