CN102037245B - Methods and systems for injecting liquid into screw compressor for noise suppression - Google Patents
Methods and systems for injecting liquid into screw compressor for noise suppression Download PDFInfo
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- CN102037245B CN102037245B CN200980118281.8A CN200980118281A CN102037245B CN 102037245 B CN102037245 B CN 102037245B CN 200980118281 A CN200980118281 A CN 200980118281A CN 102037245 B CN102037245 B CN 102037245B
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- compressor
- refrigeration agent
- venturi tube
- pressure
- condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
- F04C29/0035—Equalization of pressure pulses
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/54—Installations characterised by use of jet pumps, e.g. combinations of two or more jet pumps of different type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
- F04C18/165—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type having more than two rotary pistons with parallel axes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/13—Noise
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Jet Pumps And Other Pumps (AREA)
Abstract
A screw compressor (12) for use in a chiller assembly (10) includes cooperating screw rotors (22, 24, 26) configured to increase the pressure of a vaporized refrigerant flowing through the compressor (12), a venturi tube (50) arranged in a flow path of the refrigerant in the compressor (129) downstream of the rotors (22, 24, 26), and an inlet port (46) in fluid communication with a throat of the venturi tube (50) and configured to deliver liquid refrigerant from a condenser (16) of the chiller assembly (10) to the flow path of the refrigerant in the compressor (12). The venturi tube (50) is configured to cause a pressure drop in the refrigerant in the compressor (12). The liquid refrigerant delivered from the condenser (16) reduces pulsations in the pressure of the refrigerant discharged from the compressor (12).
Description
Technical field
The present invention relates to the noise that suppresses to produce in mechanical system.Particularly, the noise suppression in the screw compressor that the present invention relates to use in commercial and industrial air-conditioning and refrigeration system.
Background technique
Using compression-type water-cooled refrigerator is the commonsense method of cooling-air in medium-sized or large scale business, industry or mechanism's building.Compression-type water-cooled refrigerator is driven by electricity usually, but also can be driven by combustion engine or other power source.Adopted multiple compressor in the water-cooled refrigerator.A kind of common compression molding machine is screw compressor, and it uses rotary-type positive displacement machine (positive displacement mechanism) to come compression working fluid, for example refrigeration agent.
The water-cooled refrigerator used in air-conditioning and refrigeration system need to meet strict noise level requirement, such as the requirement by Occupational health and safety association (OSHA) defined.Yet the screw type cold device has the tendency that produces serious noise during operation.In the refrigerator of these types, the main source of the noise that produces is the pressure pulsation from compressor, and it produces the vibration of noise and adjacent components.Except screw compressor, also there is a plurality of secondary noise source, such as vaporizer, condenser and vapor economizer (economizer).
Existing screw compressor design has adopted various device and method to suppress the noise produced by compressor, such as the baffler and the baffle plate that are arranged in drain chamber.In addition, existing refrigerator is injected into liquid refrigerant the gas refrigerant stream of compressor discharge, to suppress the noise produced from pressure pulsation from condenser.But, under many operational conditions, these existing refrigerator designs need pressure application devices (such as pump) to compensate the negative pressure differential between condenser and compressor.The increase of pump or miscellaneous equipment has improved cost and the complexity of system.
Summary of the invention
The screw compressor used in refrigerator assembly comprises: the screw rotor of cooperation, and it is configured to improve the pressure of the vaporizing system cryogen that flows through compressor; Venturi tube (venturi tube), it is disposed in the downstream that is positioned at rotor in the flow path of the refrigeration agent in compressor; And input port, it is communicated with throat's fluid of Venturi tube and is configured to liquid refrigerant is transported to the flow path of the refrigeration agent compressor from the condenser of refrigerator assembly.Described Venturi tube is configured to cause the pressure decreased of the refrigeration agent in compressor.The liquid refrigerant of carrying from condenser has reduced the pulsation from the pressure of the refrigeration agent of compressor discharge.
The accompanying drawing explanation
Fig. 1 is the perspective view according to screw type cold device assembly of the present invention.
Fig. 2 is the axial section that is included in the screw compressor in the refrigerator assembly of Fig. 1.
Fig. 3 is the schematic diagram of the screw type cold device assembly of Fig. 1, shows the refrigeration agent stream through described system.
Fig. 4 A and Fig. 4 B are the schematic diagram according to two embodiments of the compressor of the refrigerator assembly of Fig. 1.
Embodiment
Fig. 1 is the perspective view of screw type cold device assembly 10, and described screw type cold device assembly 10 comprises screw compressor 12, variable frequency driver 14, condenser 16 and vaporizer 18.In Fig. 1, the inlet opening of compressor 12 is connected with vaporizer 18 fluids, and the delivery outlet of compressor 12 is connected with condenser 16 fluids.Condenser 16 is connected with vaporizer 18 fluids.Variable frequency driver 14 is assemblied on condenser 16.
Fig. 2 is the axial section of the screw compressor 12 of Fig. 1, and described compressor 12 comprises compressor housing 20, drive screw 22, two relative screw rods 24,26, bearing housing 28, discharge housing 30, drain chamber 32, discharge port 34 and motors 48.Housing 20 receives center driven screw rod 22 screw rod 24 and 26 relative with two.Housing 20 is connected to motor 48, described motor 48 is configured to drive screw 22,24 and 26.Bearing housing 28 receives screw-bearing 28a, and described screw-bearing 28a promotes the low friction rotation of drive screw 22 and relative screw rod 24,26.Bearing housing 28 also receives the refrigeration agent of compression from pressing chamber 36, and the refrigeration agent of this compression is transported to the drain chamber 32 in discharge housing 30 through the discharge port 34 in bearing housing 28.The size of drain chamber 32 is along with the interior perimeter surface 38 of discharge housing 30 forms the contraction of neck shape.
Fig. 3 is the schematic diagram of the refrigerator assembly of Fig. 1, shows the refrigeration agent stream through described system.Refrigerator assembly 10 is closed-loop systems, and refrigeration agent passes through this system with various cycle of states, such as liquid and steam.As any starting point in a way in the refrigerator assembly 10 of Fig. 1-4, by fluid hose 42 (such as steel pipe) or other pipeline, the overheated gas refrigeration agent of low temperature, low pressure is drawn into screw compressor 12 from vaporizer 18.Under the control of variable frequency driver 14 by motor 48 drive compression machines 12.Variable frequency driver 14 is controlled the frequency of the alternating current (AC) that offers motor 48, controls thus the speed of motor 48 and the output of compressor 12.By input port 40, refrigeration agent is drawn in compressor 12, and compresses described refrigeration agent between screw rod 22,24 and 22,26, and the discharge port 34 in bearing housing 28 is transported described refrigeration agent.The refrigeration agent of compression enters drain chamber 32 by discharge port 34.After refrigeration agent is compressed, from compressor 12, by fluid hose 42, the overheated gas of high temperature, high pressure is discharged into to condenser 16.Refrigerator assembly 10 can also comprise the oil separator (not shown) between compressor 12 and condenser 16, and it separated compressor lubricant and refrigeration agent before refrigeration agent is transported to condenser 16.In condenser 16, gas refrigerant provides heat and is condensed into liquid along with it.Overheated gas refrigerant enters condenser 16, and the gas refrigerant cooling that this is overheated by heat exchanging process, condensation and excessively cold (sub-cooled), and this heat exchanging process for example utilizes the water that flows through condenser 16 to absorb heat.Liquid refrigerant is discharged into metering equipment 44 from condenser 16, and described metering equipment 44 can, liquid-steam mixture of saturated that be low temperature by higher temperature, high pressure, excessively cold liquid transition.Described low temperature, saturated liquid-steam refrigerating agent composition enters vaporizer 18 from metering equipment 44 by fluid hose 42.Environment under low pressure in vaporizer 18 makes refrigeration agent that state is changed to overheated gas, and absorbs the needed heat of gasification from cooling water, thereby reduces the temperature of water.Then, low area overheat gas is inhaled into the inlet opening of compressor 12, and repeats continuously this circulation.Then, by distribution system by cooling water circulation to cooling worm, for providing air conditioning or for other purpose.
For the noise that the pressure pulsation suppressed from compressor 12 produces, refrigerator assembly 10 comprises the liquid refrigerant pipe 46 shown in Fig. 3.Pipe 46 is configured to liquid refrigerant is transported to the overheated gas refrigeration agent stream compressor 12 from condenser 16.Especially, manage 46 liquid refrigerants that are configured to self cooling condenser 16 in future and be transported to compressor 12 in the downstream of the pressing chamber 36 shown in Fig. 2.For example, manage 46 and liquid refrigerant can be transported to the passage in bearing housing 28, described passage is transported to drain chamber 32 by discharge port 34 from pressing chamber 36 by overheated gas refrigerant.Noise in gas refrigerant in compressor 12 causes by the pressure pulsation with range of audibility frequency, and this scope can be from about 20Hz to 20,000Hz.Can reduce noise level by the amplitude that reduces this pressure pulsation.The purpose that gas refrigerant is incorporated in the gas refrigerant stream compressor 12 from condenser 16 is by energy being reduced from the gas transfer to the liquid phase to the intensity of pressure pulsation.When liquid refrigerant droplets is injected in gas refrigerant stream, three mechanism are facilitated reduction pressure pulsation: a) viscous drag between the liquids and gases refrigeration agent; B) the heat transmission between the liquids and gases refrigeration agent; And c) the quality transmission (mass transfer) to the gasification of gas from liquid refrigerant.Generally speaking, the amplitude of noise attentuation depends on drop size and the mass velocity of the liquid refrigerant of carrying from condenser 16.The noise suppression of transmitting due to viscous drag and heat is all the function of liquid size.Because the noise suppression of quality transmission is the function of mass velocity.Viscous drag and heat are transmitted reduction effective especially higher than the noise of the frequency of 10,000Hz, and gasify (being the quality transmission) is effective to lower frequency.
For liquid refrigerant is transported to the overheated gas refrigeration agent stream compressor 12 from condenser 16, the pressure in condenser 16 must be greater than the pressure in compressor 12.Yet, in the downstream of pressing chamber 36, the overheated gas refrigeration agent has the pressure higher than the pressure of the liquid refrigerant in condenser 16 usually.Therefore, embodiments of the invention provide such method and system, it,, in the stream of the overheated gas refrigeration agent at compressor 12, introducing pressure decreased, is enough to the pressure in compressor 12 is reduced under the pressure in condenser 16, and to system, does not increase extra work (work).
Fig. 4 A and Fig. 4 B are two embodiments' of compressor 12 schematic diagram, and it is configured to introducing pressure decreased from compressor 12 the overheated gas refrigeration agent stream by bearing housing 28 and drain chamber 32 discharges.In Fig. 4 A and Fig. 4 B, compressor 12 comprises compressor housing 20, bearing housing 28, discharge housing 30, motor 48 and Venturi tube 50.Pressing chamber 36 is arranged in compressor housing 20, and described chamber 36 comprises drive screw 22 and two relative screw rods 24,26 (as shown in Figure 2).Venturi tube 50 (also being called as convergent-divergent or Laval nozzle) is included in along the direction of stream tapered portion and the flaring part that throat connects.The throat of Venturi tube 50 defines the position of smallest cross-sectional, and is communicated with by pipe 46 fluids with condenser 16, and described pipe 46 can be steel pipe for example.In the embodiment of Fig. 4 A, Venturi tube 50 is disposed in bearing housing 28, and is configured to refrigeration agent stream 52 is directed to the drain chamber 32 discharge housing 30 from compressor 12.
When refrigeration agent stream 52 during through Venturi tube 50, flow 52 speed and rise along with the reduction of the pressure of stream 52.The throat of Venturi tube 50 not only limits the position of smallest cross-sectional, and limits the position of the pressure minimum of refrigeration agent stream 52.Thus, Venturi tube 50 has been introduced pressure decreased in refrigeration agent stream 52, and described refrigeration agent stream 52 is discharged into condenser 16 from compressor 12 by bearing housing 28 and drain chamber 32.In an embodiment of the present invention, Venturi tube 50 is configured to introduce pressure decreased in refrigeration agent stream 52, is enough to the pressure of the stream 52 at the throat of Venturi tube 50 place is reduced under the pressure of the liquid refrigerant that is guided through pipe 46 from condenser 16.Therefore, can freely from condenser 16, flow to compressor 12 from condenser 16 and for the liquid refrigerant of the noise that suppresses compressor 12, and to system, not increase extra work, for example not use the pressure application devices of similar pump.
In some applications, the spatial constraints in compressor 12 may not allow Venturi tube 50 is arranged in bearing housing 28.In alternate embodiment (Fig. 4 B), Venturi tube 50 is disposed in the drain chamber 32 of discharge housing 30.In the embodiment of Fig. 4 B, refrigeration agent stream 52 enters the Venturi tube 50 in drain chamber 32 through bearing housing 28 by discharge port 34.Through Venturi tube 50, in refrigeration agent stream 52, introduce pressure decreased along with refrigeration agent, described Pressure Drop low energy makes liquid refrigerant freely flow through pipe 46 and flow to compressor 12 from condenser 16, and not to system increase work.
Embodiments of the invention provide the method and system of introducing pressure decreased in the overheated gas refrigeration agent stream for the screw compressor at refrigerator assembly, described pressure decreased is enough to the pressure in compressor is reduced under the pressure in condenser, and to system, does not increase extra work.Introducing Pressure Drop low energy in compressor refrigerant stream makes liquid refrigerant freely flow to compressor and not use the pressure application devices such as pump from condenser.Thus, embodiments of the invention suppress by the gas refrigerant stream that liquid is injected into compressor from condenser the noise that the pressure pulsation from screw compressor produces, and the cost of not obvious increase refrigerator assembly and complexity.
Although the present invention has been described with reference to preferred embodiment, it will be appreciated by those skilled in the art that in the situation that can change form without departing from the spirit and scope of the present invention and details.
Claims (20)
1. the screw compressor used in refrigerator assembly, described compressor comprises:
The screw rotor of a plurality of cooperations, it is configured to improve the pressure of the vaporizing system cryogen that flows through described compressor;
The first Venturi tube, it is disposed in the first-class path of the described refrigeration agent in described compressor and is positioned at described rotor downstream, for causing the pressure decreased of described refrigeration agent; And
The first input end mouth, it is communicated with throat's fluid of described the first Venturi tube and is configured to liquid refrigerant is transported to the described flow path of the described refrigeration agent described compressor from the condenser of described refrigerator assembly, for reducing the pulsation the pressure of the described refrigeration agent from described compressor discharge.
2. compressor as claimed in claim 1, wherein, described the first Venturi tube is arranged in the bearing housing of described compressor.
3. compressor as claimed in claim 1, wherein, described the first Venturi tube is arranged in the discharge housing of described compressor.
4. compressor as claimed in claim 1 also comprises:
The second Venturi tube, it is disposed in the second path of the described refrigeration agent in described compressor; And
The second input port, it is communicated with throat's fluid of described the second Venturi tube and is configured to liquid refrigerant is transported to the described second path of the described refrigeration agent described compressor from described condenser.
5. compressor as claimed in claim 1, wherein, described the first Venturi tube is reduced to the pressure of the described refrigeration agent in described compressor under the pressure of the described refrigeration agent in described condenser.
6. a refrigerator assembly comprises:
Screw compressor;
Condenser, it is connected to described screw compressor;
The first Venturi tube, it is disposed in the first-class path through the refrigeration agent of described compressor, and wherein, described the first Venturi tube is included in the tapered portion that throat is connected to the flaring part; And
The first pipe, it is connected between the throat and described condenser of described the first Venturi tube, and be configured to liquid refrigerant is transported to the described first-class path of the described refrigeration agent described compressor from described condenser, for reducing the pulsation the refrigeration agent of the compression of discharging from described compressor.
7. assembly as claimed in claim 6, wherein, described screw compressor comprises:
The screw rotor of a plurality of cooperations, it is configured to improve the pressure of the described refrigeration agent that flows through described compressor, and wherein, described the first Venturi tube is disposed in the downstream of described screw rotor.
8. assembly as claimed in claim 7, wherein, described the first Venturi tube is arranged in the bearing housing of described compressor.
9. assembly as claimed in claim 7, wherein, described first Venturi tube of described drain chamber is arranged in the discharge housing of described compressor.
10. assembly as claimed in claim 6 also comprises:
The second Venturi tube, it is disposed in the second path of the described refrigeration agent in described compressor, and wherein, described the second Venturi tube is included in the tapered portion that throat is connected to the flaring part; And
The second pipe, it is connected between the throat and described condenser of described the second Venturi tube, and is configured to liquid refrigerant is transported to the described second path of the described refrigeration agent described compressor from described condenser.
11. assembly as claimed in claim 6, wherein, described the first Venturi tube is reduced to the pressure of the described refrigeration agent in described compressor under the pressure of the described refrigeration agent in described condenser.
12. the screw compressor used in refrigerator assembly, described compressor comprises:
The screw rotor bearing housing;
The first Venturi tube, it is disposed in described bearing housing and is disposed in the first-class path be transported through the refrigeration agent of described bearing housing, for reducing the pressure of described refrigeration agent; And
The first input end mouth, it is communicated with throat's fluid of described the first Venturi tube, and is configured to liquid refrigerant is transported to the described first-class path of the described refrigeration agent described bearing housing from the condenser of described refrigerator assembly.
13. compressor as claimed in claim 12 also comprises:
The second Venturi tube, it is disposed in described bearing housing and is disposed in the second path be transported through the refrigeration agent of described bearing housing; And
The second input port, it is communicated with throat's fluid of described the second Venturi tube, and is configured to liquid refrigerant is transported to the described second path of the described refrigeration agent described bearing housing from described condenser.
14. compressor as claimed in claim 12, wherein, described Venturi tube is reduced to the pressure of the described refrigeration agent in described bearing housing under the pressure of the described refrigeration agent in described condenser.
15. the screw compressor used in refrigerator assembly, described compressor comprises:
The discharge housing;
The first Venturi tube, it is disposed in described discharge housing, and is disposed in the first-class path be transported through the refrigeration agent of described discharge housing, for reducing the pressure of described refrigeration agent; And
The first input end mouth, it is communicated with throat's fluid of described Venturi tube, and is configured to liquid refrigerant is transported to the described first-class path of the described refrigeration agent described discharge housing from the condenser of described refrigerator assembly.
16. compressor as claimed in claim 15 also comprises:
The second Venturi tube, it is disposed in described discharge housing, and is disposed in the second path be transported through the refrigeration agent of described discharge housing; And
The second input port, it is communicated with throat's fluid of described the second Venturi tube, and is configured to liquid refrigerant is transported to the described second path of the described refrigeration agent described discharge housing from described condenser.
17. compressor as claimed in claim 15, wherein, described the first Venturi tube is reduced to the pressure of the described refrigeration agent in described discharge housing under the pressure of the described refrigeration agent in described condenser.
18. the method for the noise in a screw compressor that suppresses refrigerator assembly, described compressor comprises: the screw rotor of a plurality of cooperations, and it is configured to improve the pressure of the vaporizing system cryogen that flows through described compressor; The first Venturi tube, it is disposed in the first-class path of the described refrigeration agent in described compressor and is positioned at described rotor downstream, for causing the pressure decreased of described refrigeration agent; And first input end mouth, it is communicated with throat's fluid of described the first Venturi tube and is configured to liquid refrigerant is transported to the described flow path of the described refrigeration agent described compressor from the condenser of described refrigerator assembly, for reducing the pulsation the pressure of the described refrigeration agent from described compressor discharge, described method comprises:
Liquid refrigerant is incorporated into the compressed gas refrigerant that flows through described screw compressor from the condenser of described refrigerator assembly, to reduce the pulsation in described refrigeration agent; And
In the situation that do not increase work, the pressure of the gas refrigerant in described compressor is reduced under the pressure of the liquid refrigerant in described condenser, with promotion, described liquid refrigerant is incorporated in described gas refrigerant.
19. method as claimed in claim 18, wherein, reduce the pressure of described gas refrigerant by making described gas refrigerant through one or more Venturi tubes.
20. method as claimed in claim 18, wherein, reduce the pressure of described gas refrigerant in one of the bearing housing in described compressor or discharge housing.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US12846708P | 2008-05-21 | 2008-05-21 | |
| US61/128467 | 2008-05-21 | ||
| US61/128,467 | 2008-05-21 | ||
| PCT/US2009/044567 WO2009151895A2 (en) | 2008-05-21 | 2009-05-19 | Methods and systems for injecting liquid into a screw compressor for noise suppression |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102037245A CN102037245A (en) | 2011-04-27 |
| CN102037245B true CN102037245B (en) | 2013-12-25 |
Family
ID=41417344
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980118281.8A Expired - Fee Related CN102037245B (en) | 2008-05-21 | 2009-05-19 | Methods and systems for injecting liquid into screw compressor for noise suppression |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20110016895A1 (en) |
| EP (1) | EP2307733A4 (en) |
| CN (1) | CN102037245B (en) |
| WO (1) | WO2009151895A2 (en) |
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|---|---|---|---|---|
| US11859881B2 (en) | 2020-07-31 | 2024-01-02 | Carrier Corporation | Refrigeration system and control method therefor |
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| CN102022870B (en) * | 2010-12-09 | 2014-02-19 | 海尔集团公司 | Method for improving supercooling degree of screw machine set and screw machine set adopting same |
| JP6380091B2 (en) | 2014-12-26 | 2018-08-29 | セイコーエプソン株式会社 | Head-mounted display device, head-mounted display device control method, and computer program |
| US10704549B2 (en) * | 2015-03-31 | 2020-07-07 | Hitachi Industrial Equipment Systems Co., Ltd. | Screw compressor having a discharging passage with enlarged cross section area |
| BE1025222B1 (en) * | 2017-05-04 | 2018-12-13 | Atlas Copco Airpower Naamloze Vennootschap | Transmission and compressor or vacuum pump provided with such transmission |
| CN109139464A (en) * | 2018-09-20 | 2019-01-04 | 李桂君 | A kind of double helix supercharging device and the engine comprising the double helix supercharging device |
| CN112334662B (en) | 2018-10-02 | 2022-08-12 | 开利公司 | Multi-stage resonator for compressor |
| CN112334660A (en) * | 2019-05-20 | 2021-02-05 | 开利公司 | Direct drive refrigerant screw compressor with refrigerant lubricated bearings |
| CN110566457B (en) * | 2019-09-03 | 2020-07-10 | 乐清市芮易经济信息咨询有限公司 | Gas-liquid mixing and conveying device with three-jaw rotor |
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| JP2580020B2 (en) * | 1988-12-05 | 1997-02-12 | 住友重機械工業株式会社 | Lubrication method for air compressor |
| EP1657445A2 (en) * | 2004-10-21 | 2006-05-17 | Ingersoll-Rand Company | Compressor discharge pulsation dampener |
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| US2967410A (en) * | 1959-12-21 | 1961-01-10 | Gen Electric | Motor cooling arrangement for hermetically sealed refrigerant compressor unit |
| US3402571A (en) * | 1966-10-20 | 1968-09-24 | Whirlpool Co | Liquid injection cooling for compressor |
| US4045975A (en) * | 1976-08-11 | 1977-09-06 | General Electric Company | Combination motor cooler and storage coil for heat pump |
| JPH0849682A (en) * | 1994-08-04 | 1996-02-20 | Ebara Corp | Screw fluid machinery |
| US6443711B1 (en) * | 2000-11-14 | 2002-09-03 | Carrier Corporation | Inlet bearing lubrication for a screw machine |
| US6826926B2 (en) * | 2002-01-07 | 2004-12-07 | Carrier Corporation | Liquid injection for reduced discharge pressure pulsation in compressors |
| JP2006037895A (en) * | 2004-07-29 | 2006-02-09 | Matsushita Electric Ind Co Ltd | Compressor |
| US7121814B2 (en) * | 2004-09-30 | 2006-10-17 | Carrier Corporation | Compressor sound suppression |
-
2009
- 2009-05-19 CN CN200980118281.8A patent/CN102037245B/en not_active Expired - Fee Related
- 2009-05-19 US US12/933,729 patent/US20110016895A1/en not_active Abandoned
- 2009-05-19 WO PCT/US2009/044567 patent/WO2009151895A2/en active Application Filing
- 2009-05-19 EP EP09763186.5A patent/EP2307733A4/en not_active Withdrawn
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2580020B2 (en) * | 1988-12-05 | 1997-02-12 | 住友重機械工業株式会社 | Lubrication method for air compressor |
| EP1657445A2 (en) * | 2004-10-21 | 2006-05-17 | Ingersoll-Rand Company | Compressor discharge pulsation dampener |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11859881B2 (en) | 2020-07-31 | 2024-01-02 | Carrier Corporation | Refrigeration system and control method therefor |
Also Published As
| Publication number | Publication date |
|---|---|
| US20110016895A1 (en) | 2011-01-27 |
| WO2009151895A3 (en) | 2010-04-22 |
| EP2307733A2 (en) | 2011-04-13 |
| CN102037245A (en) | 2011-04-27 |
| WO2009151895A2 (en) | 2009-12-17 |
| EP2307733A4 (en) | 2014-07-02 |
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