CN101608642A - Sparger - Google Patents
Sparger Download PDFInfo
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- CN101608642A CN101608642A CNA2009101493429A CN200910149342A CN101608642A CN 101608642 A CN101608642 A CN 101608642A CN A2009101493429 A CNA2009101493429 A CN A2009101493429A CN 200910149342 A CN200910149342 A CN 200910149342A CN 101608642 A CN101608642 A CN 101608642A
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- Prior art keywords
- fluid
- suction
- passage area
- nozzle
- sparger
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Classifications
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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
- F04F5/02—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid
- F04F5/04—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being liquid displacing elastic fluids
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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
- F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
- F04F5/46—Arrangements of nozzles
- F04F5/461—Adjustable nozzles
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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
- F25B41/00—Fluid-circulation arrangements
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
Abstract
A kind of sparger comprises nozzle (151), main body (152) and supercharging part (153).Described main body (152) has fluid intake (152b) and fluid suction channel (152d), flow from described fluid intake (152b) withdrawn fluid from the fluid jet that described nozzle (151) sprays, mobile by described fluid suction channel (152d) when flowing to change from the fluid that described fluid intake (152b) extracts.Described fluid suction channel (152d) has the notch portion of being pumped into (152f), suction space part (152g) and suction exit portion (152h), from described suction space partly the fluid of (152g) flow out from described suction exit portion along the injection direction (100) of described jet fluid.The described fluid passage area that is pumped into notch portion is less than the opening area of described fluid intake and the fluid passage area of described suction space part, and the fluid passage area of described suction exit portion is less than the fluid passage area of described fluid space parts.
Description
Technical field
The present invention relates to a kind of sparger, in described sparger, by utilizing pumping action from the high velocity jet fluid of nozzle ejection from the fluid intake withdrawn fluid.
Background technique
Patent documentation JP 2004-270460A (corresponding to US2004/0172966A1) has proposed a kind of sparger, and this sparger comprises: nozzle is used for the high velocity jet fluid; Fluid intake, the pumping action by utilizing the high velocity jet fluid that sprays from the fluid jet mouth of nozzle is from described fluid intake withdrawn fluid; With supercharging part (for example diffuser (diffuser)), wherein, the fluid of described jet fluid and described extraction is mixed, and the pressure of the fluid of described mixing is increased.In addition, described sparger is provided with the taper pin, and described taper pin extends to the outside with the fluid jet mouth of the concentrical described nozzle in fluid passage of described nozzle from the inside of the fluid passage of described nozzle.The point of described pin is tapered towards downstream along the injection direction of the fluid in the nozzle.
In above-mentioned sparger, described fluid sprays with the Surface runoff along described pin from the fluid jet mouth of described nozzle, makes described jet fluid have the shape of suitable expansion, thereby has improved the nozzle efficiency of described sparger.Described nozzle efficiency is the energy conversion efficiency in the nozzle, and is defined as the ratio of the enthalpy difference (expansion energy) between the fluid at jetburner place of the fluid of inlet of the speed energy of jet fluid and nozzle and nozzle.
Yet,,, also be difficult to make the supercharging amount of the fluid in the diffuser to increase amount corresponding to the increasing amount of nozzle efficiency even under the situation that increases described nozzle efficiency according to the applicant's inventor's research.
In order fully to improve the supercharging amount of the fluid in the diffuser, not only need to improve nozzle efficiency, but also the mixed tensor that need reduce to cause loses when mixing described jet fluid and described withdrawn fluid.
The flow direction of the fluid in being drawn into described sparger (suction direction) with as the injection direction of fluid in above-mentioned sparger not simultaneously, be easy to cause described mixed tensor loss.Differ from one another in sparger if suck direction and injection direction, when mixing described suction fluid and jet fluid, the flow direction that sucks fluid need change to the injection direction of jet fluid, thereby has caused sucking the velocity distribution of fluid.
When the suction fluid with velocity distribution mixed with jet fluid, the fluid-mixing of jet fluid and suction fluid became uneven state, thereby has reduced the supercharging amount in the diffuser.
Summary of the invention
Consider the problems referred to above, an object of the present invention is to provide a kind of sparger, the energy loss that described sparger can reduce at the mixing jetting fluid and cause when sucking fluid, thus increase supercharging amount in the supercharging part of described sparger.
According to an aspect of the present invention, a kind of sparger comprises: the nozzle, main body and the supercharging part that are configured to decompression and jet fluid.Described main body has fluid intake and fluid suction channel, by from the jet flow of the fluid of described nozzle ejection from described fluid intake withdrawn fluid, the described fluid that extracts from described fluid intake is flowing to the reformed fluid suction channel that flows through simultaneously.In described supercharging part, flow through the fluid of described fluid suction channel and be increased from the pressure of the fluid mixture of the fluid of described nozzle ejection from described fluid intake.In described sparger, described fluid suction channel be configured to have the notch portion of being pumped into, suction space part and suction exit portion, flow into from the described fluid of described fluid intake and to be pumped into notch portion, the flow direction of the fluid that flows out from described fluid intake is changed described suction space part, and flows out from the injection direction of described fluid from the suction exit portion along described jet fluid of described suction space part.In addition, the described notch portion that is pumped into has than the opening area of described fluid intake and the little fluid passage area of fluid passage area of described suction space part, and the fluid passage area of described suction exit portion is less than the fluid passage area of described suction space part.
Because the described opening area that is pumped into the fluid passage area of notch portion less than described fluid intake, so be pumped into the suction flow rate of fluid that notch portion flow into the described suction space part and compare and to be increased with the described suction flow rate of fluid that extracts from described fluid intake from described.Therefore, can increase from described and be pumped into the dynamic pressure that notch portion flow into the suction fluid the described suction space part.Therefore, described fluid is stirred in described suction space part, thus in the suction space part of described sparger fluid-mixing effectively.In addition, because the velocity ratio of described suction fluid has just flow into more that flow rate of fluid in the suction space part is lowered after flowing into described suction space part, so the dynamic pressure that sucks fluid is converted into the static pressure of described suction fluid in partly in suction space.Therefore, described suction space part can be used to the pressure of balance from the fluid of described suction exit portion outflow.In addition, because the fluid passage area of described suction exit portion flows out from described suction exit portion so can prevent fluid before reducing the velocity flow profile difference less than the fluid passage area of the part of the suction space in the sparger.As a result, described sparger can reduce the energy loss that causes when mixing described jet fluid and sucking fluid, thereby increases the supercharging amount in the described supercharging part.
Described fluid intake can be connected to the fluid suction pipe, and the fluid that is drawn in the described fluid intake is flowed in described fluid suction pipe.In this case, the described fluid passage area that is pumped into the fluid passage area of notch portion less than described fluid suction pipe.In addition, the fluid passage area of described fluid suction pipe can reduce gradually towards described fluid intake.
For example, the described notch portion that is pumped into can be a throttle orifice.Alternatively/additionally, the elongation line of the flow direction of the fluid that extracts from described fluid intake can intersect vertically with the elongation line from the injection direction of the fluid of described nozzle ejection.Described suction space part can be arranged on the outer circumferential side of described nozzle.
In described sparger, the described fluid passage area that is pumped into notch portion can be equal to or less than 0.5 with the ratio of the opening area of described fluid intake, or/and the ratio of the described fluid passage area that is pumped into notch portion and the maximum fluid aisle spare of described fluid suction pipe can be equal to or less than 0.5, or/and the ratio of the fluid passage area of described suction exit portion and the fluid passage area of described suction space part can be equal to or less than 0.5.
For example, described suction space part can be arranged on the passage of the substantial cylindrical on the outer circumferential side of nozzle, with described nozzle axially on extend, described suction exit portion can be extended with the cylindrical channel of described suction space part and be tapered downstream coaxially.In addition, described nozzle can be positioned to be projected into coaxially the described suction exit portion with described cylindrical channel from the suction space part, and the described notch portion that is pumped into can be in the axial direction upper shed that is approximately perpendicular to described nozzle to described columniform passage.
Description of drawings
Other purpose and advantage of the present invention will become more obvious by following detailed description and the accompanying drawing to preferred embodiment.In described accompanying drawing:
Fig. 1 is the schematic representation that shows according to the refrigerant cycle apparatus with sparger that is used for heat pump water heater of the first embodiment of the present invention;
Fig. 2 is the schematic cross-section that shows according to first embodiment's sparger; With
Fig. 3 is the schematic cross-section that shows sparger according to a second embodiment of the present invention.
Embodiment
(first embodiment)
With reference to Fig. 1 and 2, will be to according to the sparger 15 of the first embodiment of the present invention with comprise that the refrigerant cycle apparatus 10 of described sparger 15 is described.In the present embodiment, the refrigerant cycle apparatus 10 with sparger 15 typically is used for the heat pump water heater 1 that shows at Fig. 1.
Described heat pump water heater 1 comprises the water-flow circuit 20 that makes the water cycle in the water tank 21 and is configured to the refrigerant cycle apparatus 10 that heating will be stored in the water in the water tank 21.Water tank 21 is used for the interim hot water that stores 10 heating of cooled dose of circulation means.In the present embodiment, circulate in refrigerant cycle apparatus 10 as the refrigeration agent of an example of fluid, and carbon dioxide (CO2) is as described refrigeration agent.At carbon dioxide during, become than the critical pressure height of refrigeration agent from the pressure of the on high-tension side refrigeration agent of compressor 11 dischargings as the refrigeration agent in the refrigerant cycle apparatus 10.
At first, will be described water-flow circuit 20.Water tank 21 is hot water storage boxes of being made by the metal with thermal insulation structure (for example stainless steel), and wherein, high-temperature-hot-water can be stored for a long time.Usually, water tank 21 is made by the metal with enough corrosion resistancies.
How be stored in water in the water tank 21 and be by hot water outlet and be supplied to the outside from the top that is arranged on water tank 21.Hot water from the hot water outlet of water tank 21 suitably can be mixed with tap water by the serviceability temperature modulating valve, afterwards, be supplied to place to use (for example kitchen, bathroom or similarly local) with it.Water intake is arranged on the bottom of water tank 21, makes that for example the water of tap water can be supplied to water tank 21 from the water intake of water tank 21.
Make the electric pump 22 of water cycle be arranged in water-flow circuit 20.Control the operation of electric pump 22 by the control signal of electric control system (not shown) output.When electric control system made electric pump 22 operations, water was circulated to water channel 12a, water storage box 21 and the electric pump 22 of water-refrigerant heat exchanger 12 successively from electric pump 22.
Secondly, will be described refrigerant cycle apparatus 10.Described refrigerant cycle apparatus 10 comprises the compressor 11 that is configured to extraction and compressed refrigerant and discharges described refrigerant compressed.For example, described compressor 11 is electric power compressors, the motor 11b that it comprises the compressing mechanism 11a with fixed discharge capacity and is used to drive described compressing mechanism 11a.Various types of compressing mechanisms (for example, eddy type, blade type, rotary-piston type) can be used as described compressing mechanism 11a.
Because the operation of motor 11b (for example rotational speed of motor 11b) is controlled by the control signal of electric control system output, so can use Wechselstrommotor or direct current motor.By the rotational speed of control motor 11b, can change the refrigeration agent discharge capacity (discharge capacity) of compressing mechanism 11a.Therefore, motor 11b can be used as discharge capacity and change part, is used to change the refrigeration agent discharge capacity of compressing mechanism 11a.
The coolant channel 12b of water-refrigerant heat exchanger 12 is connected to the refrigeration agent waste side of compressor 11.Water-refrigerant heat exchanger 12 is the heat exchangers that wherein have coolant channel 12b and water channel 12a, flow by described coolant channel 12b from the high temperature and high pressure refrigeration agent of described compressor 11 dischargings, water flows to carry out and the heat exchange of flowing through the refrigeration agent of described coolant channel 12b by described water channel 12a.Therefore, the water from the heat radiation of the high temperature and high pressure refrigeration agent of described compressor 11 dischargings to described water-refrigerant heat exchanger 12 makes described water be heated and described refrigeration agent is cooled in described water-refrigerant heat exchanger 12.In the present embodiment, described water-refrigerant heat exchanger 12 is the refrigeration and heat radiators that are used to cool off from the refrigeration agent of described compressor 11 dischargings.
In the present embodiment, because described refrigerant cycle apparatus 10 is operated with the supercritical refrigerant state, so described refrigeration agent (for example, carbon dioxide) is not condensed when passing the coolant channel 12b of water-refrigerant heat exchanger 12.
The end of the first refrigerant pipe 14a is connected to a refrigerant outlet of component 13, the other end of the first refrigerant pipe 14a is connected to the refrigerant inlet side of the nozzle 151 of sparger 15, makes the first refrigeration agent at component 13 punishment streams flow into the refrigerant inlet side of the nozzle 151 of sparger 15 by the first refrigerant pipe 14a.The end of the second refrigerant pipe 14b is connected to another refrigerant outlet of component 13, the other end of the second refrigerant pipe 14b is connected to the refrigerant inlet side of electric powered expansion valve 17, makes second refrigeration agent that flows at component 13 punishment streams flow into the refrigerant inlet side of described electric powered expansion valve 17 by the second refrigeration agent 14b.
Sparger 15 usefulness act in the refrigeration agent decompression part of nozzle 151 place's reduced-pressure refrigerant and with acting on the kinetic energy pumping unit that makes refrigerant cycle by utilization from the pumping action of the ejector refrigeration agent of nozzle 151 injections.Secondly, will be described with reference to the concrete structure of 2 pairs of spargers 15 of figure.
As shown in Figure 2, sparger 15 comprises nozzle 151, main body 152, diffuser 153, pin 154, drive part 155 or similar device.Nozzle 151 is configured so that the decompression of constant entropy ground flow into the refrigeration agent of nozzle 151 inside by the first refrigerant pipe 14a.Nozzle 151 can be formed by modes such as boring or cuttings by the metal parts with substantial cylindrical.For example, can make nozzle 151 by for example stainless steel.
For example, by forming nozzle 151 in conjunction with two cylindrical members coaxially with different-diameter.Just, nozzle 151 comprises major diameter part 151a and small diameter portion 151b.The outer surface of major diameter part 151a is press-fitted to main body 152.Major diameter part 151a is provided with nozzle inlet 151d, and by described nozzle inlet, the refrigeration agent that flows out from the first refrigerant pipe 14a flow among the coolant channel 151c that is arranged on the nozzle 151.
Described coolant channel 151c is arranged in the nozzle 151, makes refrigeration agent pass through the side of coolant channel 151c from the effluent of major diameter part 151a to small diameter portion 151b.And coolant channel 151c extends axially along nozzle 151, makes the coolant channel area of coolant channel 151c of nozzle 151 reduce gradually in the downstream part of coolant channel 151c (that is the side of small diameter portion 151b).Therefore, the refrigeration agent by coolant channel 151c is depressurized in small diameter portion, and the refrigeration agent of decompression such as arrow 100 show injectedly from refrigerant injection mouth 151e, and refrigerant injection mouth 151e is arranged on the location downstream of coolant channel 151c.
For example, drive part 155 is to be used to drive and the motor actuator of mobile pin 154, and be configured to have coil 155a, rotor 155b and shell 155c.The control signal that coil 155a is configured to according to electric control system output produces rotation magnetic force, makes that rotor 155b can be around the axle rotation of nozzle 151.
Threaded piece 158 is depressed in the nozzle 151 by dress, and pin 154 is inserted in the inner-diameter portion whose of described threaded piece 158 slidably.An end at the pin 154 of drive part 155 1 sides is connected to rotor 155b via packing ring 156.Rotor 155b has the cylindrical body that the inboard is provided with female thread portion, and the female thread portion of rotor 155b is tightened with the outside thread on the outer surface that is arranged on threaded piece 158.Therefore, when rotor 155b rotated, rotor 155b and pin 154 were at the axial top offset of pin 154.Shell 155c is the cup-shaped metal shell 155c that is made by nonmagnetic metal, and is the housing structure that is used to accommodate rotor 155b.Shell 155c soldered and be fixed to main body 152 axially on one distolateral.Spring 157 is arranged between packing ring 156 and the threaded piece 158, and biased to promote rotor 155b along the axial direction opposite with nozzle side.
The outlet of diffuser 153 as being connected on the refrigerant inlet side of first vaporizer 15 afterwards with describing.The various open pores that are arranged in the main body 152 are: the refrigerant inlet part 152a that is communicated with the nozzle inlet 151d of nozzle 151; Refrigerant suction port 152b extracts the refrigeration agent that flows out from suction side vaporizer (i.e. second vaporizer) 18 by described refrigerant suction port 152b; And refrigerant outlet 152c, flow out as the refrigeration agent that mixes from the refrigeration agent of refrigerant suction port 152b extraction with from the refrigeration agent that refrigerant injection mouth 151e sprays by described refrigerant outlet 152c.
The various coolant channels that are arranged in the main body 152 comprise: refrigeration agent suction channel 152d and be used for the cylindrical hybrid channel 152e that the quilt of refrigeration agent suction channel 152d is provided with continuously, guided by the refrigerant injection mouth 151e towards nozzle 151 from the refrigeration agent that refrigerant suction port 152b extracts by refrigeration agent suction channel 152d, the refrigeration agent that mixes by described cylindrical hybrid channel is directed to refrigerant outlet 152c.Herein, the refrigeration agent of mixing is the mixture of the refrigeration agent that sprays from refrigerant injection mouth 151e and the refrigeration agent that extracts from refrigerant suction port 152b.
Refrigeration agent suction channel 152d is by being pumped into notch portion 152f, suction space part 152g and aspirating exit portion 152h and construct, from the suction flow of refrigerant of refrigerant suction port 152b by the described notch portion 152f that is pumped into, pass through suction space part 152g from the suction flow of refrigerant that is pumped into notch portion 152f introducing, and flow among the described hybrid channel 152e by suction exit portion 152h from the suction refrigeration agent of described suction space part 152g.
Be pumped into notch portion 152f and refrigerant suction port 152b in identical direction upper shed, make to be pumped into the access portal area of the access portal area of notch portion 152f less than refrigerant suction port 152b.For example, in the present embodiment, the access portal area that is pumped into notch portion 152f can be set equal to the ratio of the opening area of refrigerant suction port 152b or less than 0.5.
As shown in Figure 2, the access portal area that is pumped into notch portion 152f is significantly smaller than the largest passages opening area of the 3rd refrigerant pipe (suction refrigerant pipe) 14c.In the present embodiment, being pumped into notch portion 152f is made up by throttle orifice.Being pumped into notch portion 152f can make up by directly form throttle orifice in main body 152, maybe can be installed in the main body by another member that will have throttle orifice to make up.
Just, the coolant channel area of suction space part 152g is at the cross sectional area perpendicular to the suction space part 152g in the cross section of the flow direction of the refrigeration agent that flows through suction space part 152g.Therefore, if change the flow direction of the suction refrigeration agent that flows through suction space part 152g, so also change the coolant channel area of suction space part 152g.
In the present embodiment, the minimum coolant channel area of the coolant channel area of suction space part 152g is set to greater than the coolant channel area that is pumped into notch portion 152f.Just, be pumped into the minimum coolant channel area of the coolant channel area of notch portion 152f less than suction space part 152g.For example, the ratio that is pumped into the minimum coolant channel area of the coolant channel area of notch portion 152f and the 3rd refrigerant pipe (suction refrigerant pipe) 14c is equal to or less than 0.5.
Diffuser 153 is the supercharging parts in the sparger 15, and the flow velocity of refrigeration agent is lowered and the pressure of refrigeration agent is increased in this supercharging part.Can form diffuser 153 by making metal tube (copper pipe) plastic deformation, make that the coolant channel area of diffuser 153 is increased towards downstream gradually.Therefore, refrigeration agent is decelerated and the pressure of refrigeration agent is increased in diffuser 153, makes the speed energy of refrigeration agent be converted into the pressure energy of refrigeration agent.As shown in Figure 2, make coolant channel area constant on the suction side of diffuser 153 and outlet side.As shown in Figure 1, the refrigerant outlet side of diffuser 153 is connected to the refrigerant inlet side of first vaporizer 16.
For example, first vaporizer 16 is endothermic heat exchangers, and the refrigeration agent that flows into wherein from diffuser 153 is evaporated by the heat that absorbs the outside air that is blowed by blower 16a.Just, flow into the outside air that refrigeration agent first vaporizer 16 and blower 16a blow from diffuser 153 and carry out heat exchange, to be evaporated.Described blower 16a can be the electric power blower, and wherein, fan revolution speed is by the control Control of Voltage of electric control system output.The refrigerant outlet side of first vaporizer 16 is connected to the refrigerant suction port of compressor 11.
As shown in Figure 1, electric powered expansion valve 17 is connected to the second refrigerant pipe 14b, makes that second stream at the refrigeration agent of component 13 punishment stream flow in the electric powered expansion valve 17 by the second refrigerant pipe 14b.Electric powered expansion valve 17 is to be configured to decompression and to expand to flow into the decompressing unit of the refrigeration agent among the second refrigerant pipe 14b.Can control the operation of electric powered expansion valve 17 by the control signal of electric control system output.As shown in Figure 1, electric powered expansion valve 17 comprises valve portion 17a and the motor portion 17b that is used for the valve opening degree of control valve part 17a.Come the valve opening degree of control valve part 17a according to the control signal of electric control system output by motor portion 17b.
Second vaporizer 18 (suction vaporizer) is connected to the refrigerant outlet side of the valve portion 17a of electric power dilation 17.For example, second vaporizer 18 is endothermic heat exchangers, and the refrigeration agent that flows into wherein from electric powered expansion valve 17 is evaporated by the heat that absorbs by the outside air that blows after first vaporizer 16 and by blower 16a.Just, flow into refrigeration agent and the outside air heat exchange that blows by blower 16a second vaporizer 18 from electric powered expansion valve 17, to be evaporated.Among Fig. 1, second vaporizer 18 is positioned at the downstream of first vaporizer 16 on the air-flow direction 200, yet second vaporizer 18 can be provided with discretely with first vaporizer 16.The refrigerant outlet side of second vaporizer 18 is connected to the refrigerant suction port 152b of sparger 15 via the 3rd refrigerant pipe 14c.
In the example of Fig. 1, make up first vaporizer 16 and second vaporizer 18 by the heat exchange unit of one with fin and tubular construction.For example, first vaporizer 16 and second vaporizer 18 can be configured to has common heat-exchange fin, has independently tubular construction simultaneously.In the structure of the one of first vaporizer 16 and second vaporizer 18, the tubular construction that tubular construction that the refrigeration agent that flows out from sparger 15 flows therein and the refrigeration agent that flows out from electric powered expansion valve 17 flow therein is provided with independently of one another.
Therefore, the heat of the air that is blowed by blower 16a is at first absorbed by the refrigeration agent of first vaporizer 16, is absorbed by the refrigeration agent of second vaporizer 18 afterwards.
In the embodiment in figure 1, first vaporizer 16 and second vaporizer 18 in series are provided with on air-flow direction 200, to form as one.Yet first vaporizer 16 separated from one another and second vaporizer 18 can in series be provided with on air-flow direction 200.Alternatively, first vaporizer 16 and second vaporizer 18 can be set separated from one anotherly on diverse location.
Secondly, will the electric control system according to first embodiment's refrigerating circulatory device be described.Electric control system is microprocessor and the constructed control gear of circumference circuit that wherein has CPU, ROM and RAM etc. by known.The outlet side of electric control system is connected to the various actuators of the motor 11b of compressor 11 for example, the drive part 155 of sparger 15, the motor of blower 16a, motor 17b of electric powered expansion valve 17 etc., so that control described parts.
The input side of electric control system is connected to sensor groups, operation panel etc.Sensor groups comprise be configured to detection at the water temperature sensor of the temperature of the water of the heating of the water out side of the water channel 12a of water-refrigerant heat exchanger 12, be configured to the external air temperature sensor of the temperature of the air (for example, outside air) that detection blows by blower 16a.Described operation panel is connected to the input side of electric control system, and the operation signal of the actuating signal of feasible for example water heater 1 and the water temperature setting signal of stop signal and water heater 1 is imported into electric control system.
Secondly, with the operation of describing according to first embodiment's heat pump water heater 1.Be input to the electrical control division timesharing from the outside supply capability of heat pump water heater 1 and the operation commencing signal of water heater 1 from operation panel, electric control system is carried out the expectant control program be stored among the ROM, thereby parts 11b, 155, the 16a, 17 of refrigerant cycle apparatus 10,22 etc. are operated.
The water that flow into the coolant channel 12b of water-refrigerant heat exchanger 12 to flow into the water channel 12a of water-refrigerant heat exchanger 12 with downside from water tank 21 from the high temperature and high pressure refrigeration agent of compressor 11 discharging carries out heat exchange.Water is incorporated into the water channel 12a by the downside of electric pump 12 from water tank 21, and carries out heat exchange with the high-temperature high-pressure refrigerant of the coolant channel 12b that flows through water-refrigerant heat exchanger 12.Therefore, water is heated when the water channel 12a by water-refrigerant heat exchanger 12, and the water of heating is stored in the upside of water tank 21.
The high-pressure refrigerant that flows out from the coolant channel 12b of water-refrigerant heat exchanger 12 flow into the refrigeration agent component 13, and is split into first-class and second flows.The first refrigeration agent of being shunted at component 13 places flow into the nozzle segment 151 of sparger 15 via the first refrigerant pipe 14a, and is reduced pressure by constant entropy ground in nozzle 151.In nozzle 151, sprayed from refrigerant injection mouth 151e at high speed by the refrigeration agent of constant entropy ground decompression.
Control the drive part 155 of sparger 15 by the control signal of electric control system output, so that the coolant channel 151c of control sparger 15 and the coolant channel area of refrigerant injection mouth 151e make to be drawn into the degree of superheat of the refrigeration agent in the compressor 11 near predetermined value.Therefore, can prevent that liquid refrigerant is returned to compressor 11.
The refrigeration agent that flows out from second vaporizer 18 is drawn into the sparger 15 from refrigerant suction port 152b.And ejector refrigeration agent of spraying from refrigerant injection mouth 151e and the suction refrigeration agent that extracts from refrigerant suction port 152b are mixed in suction side and the hybrid channel 152 of hybrid channel 152e, and afterwards, the refrigeration agent of mixing flow into and is diffused in 153.
Because the aisle spare of diffuser 153 increases towards downstream gradually, so become the pressure energy of refrigeration agent to increase the pressure of refrigeration agent by the speed transformation of energy with refrigeration agent.The refrigeration agent that flows out from the diffuser 153 of sparger 15 flow into first vaporizer 16, and is evaporated by absorbing heat from the outside air that is blowed by blower 16a.Afterwards, the refrigeration agent that flows out from first vaporizer 16 is drawn into compressor 11 and is compressed compressor 11.
The refrigeration agent of second stream of being shunted at component 13 places is depressurized and is inflated at electric powered expansion valve 17 places, and flow into second vaporizer 18 afterwards.The refrigeration agent that flow in second vaporizer 18 is evaporated by absorbing heat from outside air, and the vaporized gas refrigeration agent that flows out from second vaporizer 18 is drawn into the sparger 15 from refrigerant suction port 152b.
Change the throttling passage area (that is, the valve opening degree) of electric powered expansion valve 17 according to the control signal of electric control system output, make that the refrigerant pressure on the high pressure side of refrigeration cycle is near goal pressure before being depressurized.According to the temperature of the refrigeration agent that flows out from the coolant channel 12b of water-refrigerant heat exchanger 12, described goal pressure is determined, and makes performance of refrigeration circulation coefficient (COP) roughly near maximum value.Therefore, refrigerant cycle apparatus 10 can move under the situation of the COP of very high value.
In refrigerant cycle apparatus 10, pressurized refrigeration agent flow in first vaporizer 16 in the diffuser 153.On the contrary, because second vaporizer 18 is connected to refrigerant suction port 152b, so the refrigeration agent evaporating pressure in second vaporizer 18 is corresponding to the minimum pressure that is right after after the refrigerant injection mouth 151e of nozzle 151.
Therefore, can make refrigeration agent evaporating pressure (refrigeration agent evaporating temperature) in second vaporizer 18 be lower than the refrigeration agent evaporating pressure (refrigeration agent evaporating temperature) in first vaporizer 16.The result, even when second vaporizer 18 is located at the downstream of first vaporizer 16 on the air flow 200, also can be simultaneously first vaporizer 16 and second vaporizer, 18 places set refrigeration agent and the air that blows by blower 16a between the temperature difference that is fit to, thereby refrigeration agent can all can absorb heat effectively at first vaporizer 16 and second vaporizer, 18 places from air.
In the present embodiment, refrigeration agent suction channel 152d is by being pumped into notch portion 152f, suction space part 152g and suction exit portion 152h structure.Secondly, will be to the line description that is configured into of the sparger 15 that comprises refrigeration agent suction channel 152d.
In the present embodiment, because be pumped into the opening area of the coolant channel area of notch portion 152f, so compare and to be increased with the flow velocity of the suction refrigeration agent that extracts by refrigerant suction port 152b from being pumped into the flow velocity that notch portion 152f flow into the suction refrigeration agent of suction space part 152g less than refrigerant suction port 152b.Therefore, can increase effectively from being pumped into the dynamic pressure that notch portion 152f flow into the suction refrigeration agent the suction space part 152g.
Because described dynamic pressure, the refrigeration agent that flow among the suction space part 152g is stirred, so the refrigeration agent that flow among the suction space part 152g can be mixed effectively.And, because the flow velocity that sucks refrigeration agent (suction fluid) after flowing into suction space part 152g is reduced with comparing at the flow velocity of the suction refrigeration agent (suction fluid) when being pumped into notch portion 152f and just having flow into suction space part 152g, be converted into static pressure so suck the dynamic pressure of refrigeration agent.Therefore, suction space part 152g can be used to the pressure of balance from the refrigeration agent of suction exit portion 152h outflow, thereby can reduce the current difference on the velocity flow profile.
In addition, because the flow channel area of suction exit portion 152h (promptly, flow path cross sectional area) less than the flow channel area of suction space part 152g, from suction exit portion 152h, flows out so before reducing the current difference of velocity flow profile, can prevent refrigeration agent.
Therefore, the mixed pressure loss that causes when ejector refrigeration agent and suction refrigeration agent are mixed can be reduced, thereby the supercharging amount in hybrid channel 152e and diffuser 153 can be increased.Therefore, the electric power that consumes in the compressor 11 can be reduced, thereby has increased the COP in the refrigeration cycle.
In the present embodiment, made up by throttle orifice because be pumped into notch portion 152f, to flow into the flow velocity of the refrigeration agent the suction space part 152g faster than being drawn into the flow velocity that is pumped into the refrigeration agent the notch portion 152f from refrigerant suction port 152b effectively from being pumped into notch portion 152f so can make.Therefore, can relatively reduce the length of refrigeration agent suction channel 152d.
Because cylindrical suction space part 152g is arranged on the outer circumferential side of nozzle 151, can on the whole outer circumferential side of ejector refrigeration agent, mixes equably so suck refrigeration agent, thereby reduce the mixed pressure loss effectively.
The suction exit portion 152h that is communicated with the cylindrical suction space part 152g of the small diameter portion 151b that centers on nozzle 151 is arranged on the upstream of hybrid channel 152e, and the refrigerant injection mouth 151e of nozzle 151 is positioned on the radial center zone of suction exit portion 152d.Therefore, among cylindrical suction space part 152g, turn to and flow into afterwards suction exit portion 152h from the refrigeration agent that is pumped into notch portion 152f extraction.Therefore, enter into the flow direction of the refrigeration agent that aspirates exit portion 152h roughly corresponding to the injection of refrigerant direction 100 that is injected into hybrid channel 152e from refrigerant injection mouth 151e via suction exit portion 152h from suction space part 152g.Therefore, the mixed pressure loss can be reduced more effectively.
In first embodiment, the present invention is applied to sparger 15, and wherein, the flow direction of the suction refrigeration agent that extracts from refrigerant suction port 152b intersects with the elongation line approximate vertical of the injection of refrigerant direction of spraying from refrigerant injection mouth 151e.In this case, in the ejector refrigeration agent with suck the mixed pressure loss that refrigeration agent causes when mixed can more effectively be reduced in sparger 15.
(second embodiment)
To be described with reference to 3 pairs of second embodiment of the present invention of figure.In the first above-mentioned embodiment, the 3rd refrigerant pipe (suction refrigerant pipe) 14c that is connected to refrigerant suction port 152b is the common tube with constant channel area.Yet in a second embodiment, as shown in Figure 3, the 3rd refrigerant pipe (suction refrigerant pipe) 14c that is connected to refrigerant suction port 152b is configured to has the channel cross sectional area that reduces gradually towards refrigerant suction port 152b.
In a second embodiment, the feasible channel cross sectional area of the channel cross sectional area of notch portion 152f that be pumped into less than the 3rd refrigerant pipe 14c.Therefore, be pumped into the largest passages cross sectional area of the channel cross sectional area of notch portion 152f less than the 3rd refrigerant pipe 14c.As second embodiment's a example, the cross-sectional area of comparable the 3rd refrigerant pipe 14c of channel cross sectional area that is pumped into notch portion 152f is little.In a second embodiment, other parts of sparger 15 can be similar to other parts of first embodiment's sparger 15.
According to a second embodiment of the present invention, when heat pump water heater 1 was operated, the flow velocity of the refrigeration agent by the 3rd refrigerant pipe 14c increased gradually towards refrigerant suction port 152b.Therefore, can increase from being pumped into the dynamic pressure that notch portion 152f flow into the refrigeration agent the suction space part 152g.
As a result, can reduce the current difference on the velocity flow profile of the suction refrigeration agent that flows out from suction exit portion 152h, thus the mixed pressure loss that reduces in the ejector refrigeration agent and cause when sucking refrigerant mixed.In addition, the flow velocity that flows through the refrigeration agent of the 3rd refrigerant pipe 14c is increased gradually, thereby reduces generating noise.
Though with reference to the accompanying drawings and in conjunction with the preferred embodiments of the present invention the present invention has been carried out describing all sidedly, should note various changes and revise and to become clearly for a person skilled in the art.
In the sparger 15 of the above embodiments, the elongation line of the injection direction 100 of the ejector refrigeration agent that the flow direction of the suction refrigeration agent that extracts from refrigerant suction port 152b and the refrigerant injection mouth 151e from nozzle 151 spray intersects vertically.Yet the injection direction 100 of the flow direction of the suction refrigeration agent that extracts from refrigerant suction port 152b and the ejector refrigeration agent of spraying from the refrigerant injection mouth 151e of nozzle 151 can be set on the different directions from each other.
For example, because be changed among suction space part 152g from the flow direction that is pumped into the suction refrigeration agent that notch portion 152f flows out, the refrigeration agent among the suction space part 152g flows out from suction exit portion 152h afterwards, so can reduce the mixed pressure loss effectively.
In the above-described embodiments, changed the coolant channel area of nozzle 151, make the degree of superheat of the refrigeration agent on the refrigerant outlet side of first vaporizer 16 become the target degree of superheat, and changed the throttling passage area of electric powered expansion valve 17, made that the refrigerant pressure on the high pressure side in the refrigeration cycle becomes desired value.Yet the control of the control of nozzle 151 and electric powered expansion valve 17 can be carried out on the contrary.
Just, the throttling passage area of electric powered expansion valve 17 can be changed, make the degree of superheat of the refrigeration agent on the refrigerant outlet side of first vaporizer 16 become the target degree of superheat, and the coolant channel area of nozzle 151 is changed, and makes that the refrigerant pressure on the high pressure side in the refrigeration cycle becomes desired value.
In the above-described embodiment, carbon dioxide is as refrigeration agent.Yet, can use known fluid, for example carbon hydride (carbon hydride) refrigeration agent, Fu Longji (flon-based) refrigeration agent.In addition, the sparger 15 of the above embodiments can be used to subcritical refrigerant cycle apparatus, and wherein, the refrigerant pressure on the high pressure side is less than the critical pressure of refrigeration agent.
In the above-described embodiment, the electric power compressor is as compressor 11.Yet known compressor (for example by compressor driven such as engines) can be used as compressor 11.In addition, fixed displacement compressing mechanism or compressor with variable displacement structure can be used as compressing mechanism 11a.
In the above-described embodiment, nozzle 151 is variable nozzles, is configured to the feasible coolant channel that can change nozzle 151.Yet nozzle 151 can not be variable nozzle, is configured to make that the coolant channel of nozzle 151 is fixed.
In the above-described embodiment, refrigerant cycle apparatus 10 is used for heat pump water heater 1.Yet refrigerant cycle apparatus 10 can be used for fixing air regulator, automotive air conditioner of type etc.In this case, first vaporizer 16 and second vaporizer 18 can be used as inner heat exchanger, and radiator 12 is as external heat exchanger.
These variations and modification should be understood that to drop in the scope of the present invention as defined by the appended claims.
Claims (14)
1. sparger comprises:
Nozzle (151) is configured to decompression and jet fluid;
Main body (152), described main body has fluid intake (152b) and fluid suction channel (152d), from described fluid intake (152b) withdrawn fluid, the fluid that extracts from described fluid intake is flowing to the reformed described fluid suction channel (152d) that flows through simultaneously from the jet flow of the fluid of described nozzle ejection; With
Supercharging part (153) in described supercharging part, flows through the fluid of described fluid suction channel and is increased from the pressure of the fluid mixture of the fluid of described nozzle ejection from described fluid intake, wherein,
Described fluid suction channel is configured to have the notch portion of being pumped into (152f), suction space part (152g) and suction exit portion (152h), fluid from described fluid intake flows into described being pumped in the notch portion (152f), the flow direction of the fluid that flows out from described fluid intake is changed described suction space part (152g), and, the injection direction of fluid from described suction exit portion (152h) along jet fluid from described suction space part flows out
Described be pumped into notch portion have than the little fluid passage area of the fluid passage area of the opening area of described fluid intake and described suction space part and
The described fluid passage area of described suction exit portion is less than the fluid passage area of described suction space part.
2. sparger according to claim 1, wherein
Described fluid intake (152b) is connected to fluid suction pipe (14c), will be drawn into that fluid in the described fluid intake flows in described fluid suction pipe (14c) and
The described fluid passage area that is pumped into the fluid passage area of notch portion less than described fluid suction pipe.
3. sparger according to claim 2, wherein, the fluid passage area of described fluid suction pipe reduces gradually towards described fluid intake.
4. according to each described sparger among the claim 1-3, wherein, the described notch portion that is pumped into is a throttle orifice.
5. according to each described sparger among the claim 1-3, wherein, the elongation line of the flow direction of the fluid that extracts from described fluid intake intersects vertically with elongation line from the injection direction of the fluid of described nozzle ejection.
6. according to each described sparger among the claim 1-3, wherein, described suction space part (152g) is arranged on the outer circumferential side of described nozzle.
7. according to each described sparger among the claim 1-3, wherein, the described fluid passage area that is pumped into notch portion is equal to or less than 0.5 with the ratio of the opening area of described fluid intake.
8. according to claim 2 or 3 described spargers, wherein, the described fluid passage area that is pumped into notch portion is equal to or less than 0.5 with the ratio of the maximum fluid aisle spare of described fluid suction pipe.
9. according to each described sparger in the claim 1 to 3, wherein, the fluid passage area of described suction exit portion is equal to or less than 0.5 with the ratio of the fluid passage area of described suction space part.
10. according to each described sparger in the claim 1 to 3, wherein
The outer circumferential side that described suction space partly is arranged on nozzle with the passage of the upwardly extending substantial cylindrical of axle of nozzle and
The cylindrical channel of described suction exit portion and described suction space part extends coaxially and is tapered towards downstream.
11. sparger according to claim 10, wherein
Described nozzle be positioned be projected into coaxially from suction space part and described cylindrical channel the described suction exit portion and
Described be pumped into notch portion in the axial direction upper shed that is approximately perpendicular to described nozzle to described columniform passage.
12., further comprise according to each described sparger in the claim 1 to 3
Be arranged on the cylindrical hybrid channel (152e) between described suction exit portion (152h) and the described diffuser (153) coaxially.
13. a sparger comprises:
Nozzle (151) is configured to decompression and jet fluid;
Main body (152), described main body has fluid intake (152b) and fluid suction channel (152d), from described fluid intake (152b) withdrawn fluid, the fluid that extracts from described fluid intake is flowing to the reformed described fluid suction channel (152d) that flows through simultaneously from the jet flow of the fluid of described nozzle ejection; With
Supercharging part (153) in described supercharging part, flows through the fluid of described fluid suction channel and is increased from the pressure of the fluid mixture of the fluid of described nozzle ejection from described fluid intake, wherein,
Described fluid intake is connected to the fluid suction pipe, and the fluid that will be drawn in the described fluid intake flows in described fluid suction pipe,
Described fluid suction channel is configured to have the notch portion of being pumped into (152f), suction space part (152g) and suction exit portion (152h), flow into from the fluid of described fluid intake and to be pumped in the notch portion (152f), the flow direction of the fluid that flows out from described fluid intake is changed described suction space part (152g), and the injection direction of fluid from described suction exit portion (152h) along described jet fluid from described suction space part flows out
Described be pumped into notch portion have than the little fluid passage area of the fluid passage area of the fluid passage area of described fluid suction pipe and described suction space part and
The fluid passage area of described suction exit portion is less than the fluid passage area of described suction space part.
14. sparger according to claim 13, wherein
The fluid passage area of described fluid suction pipe towards described fluid intake reduce gradually and
The described minimum fluid passage area that is pumped into the fluid passage area of notch portion less than described fluid suction pipe.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008156331A JP2009299609A (en) | 2008-06-16 | 2008-06-16 | Ejector |
| JP2008156331 | 2008-06-16 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101608642A true CN101608642A (en) | 2009-12-23 |
Family
ID=41414976
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2009101493429A Pending CN101608642A (en) | 2008-06-16 | 2009-06-16 | Sparger |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20090311111A1 (en) |
| JP (1) | JP2009299609A (en) |
| CN (1) | CN101608642A (en) |
| DE (1) | DE102009024712A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102297704A (en) * | 2010-06-23 | 2011-12-28 | 罗伯特·博世有限公司 | Apparatus for determining fluid medium characteristics |
| CN105363582A (en) * | 2015-12-16 | 2016-03-02 | 山东大学 | Needle control device capable of adjusting area of ejector nozzle and ejector |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ITMI20112261A1 (en) * | 2011-12-14 | 2013-06-15 | Eni Spa | MULTI-PHASE VARIABLE-SET EJECTOR FOR WELL-HEAD PRODUCTION RECOVERY |
| EP3099987B1 (en) | 2014-01-30 | 2022-07-20 | Carrier Corporation | Ejector and method of manufacture therefor |
| DK3099988T3 (en) * | 2014-01-30 | 2022-05-16 | Carrier Corp | STEAM COMPRESSION SYSTEM AND OPERATING METHODS |
| CN104196769B (en) * | 2014-08-18 | 2017-11-07 | 连云港久盛电力辅机有限公司 | A kind of environment-friendly type multi-path water jet air extractor |
| CN104958817B (en) * | 2015-07-15 | 2017-07-11 | 深圳市安保科技有限公司 | The empty oxygen mixing device and method of a kind of lung ventilator |
| ITUA20162684A1 (en) | 2016-04-18 | 2017-10-18 | Carel Ind Spa | EJECTOR FOR REFRIGERATED MACHINE |
| DE102017220800A1 (en) * | 2017-11-21 | 2019-05-23 | Robert Bosch Gmbh | Jet pump unit with a metering valve for controlling a gaseous medium |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6021600U (en) * | 1983-07-22 | 1985-02-14 | 石川島播磨重工業株式会社 | Vacuum suction device |
| DE3563918D1 (en) * | 1984-10-12 | 1988-09-01 | Nordson Corp | Venturi powder pump |
| US5979889A (en) * | 1997-04-15 | 1999-11-09 | Heidelberger, Druckmaschinen Ag | Apparatus for generating a vacuum |
| JP4232484B2 (en) | 2003-03-05 | 2009-03-04 | 株式会社日本自動車部品総合研究所 | Ejector and vapor compression refrigerator |
-
2008
- 2008-06-16 JP JP2008156331A patent/JP2009299609A/en active Pending
-
2009
- 2009-06-12 DE DE102009024712A patent/DE102009024712A1/en not_active Withdrawn
- 2009-06-15 US US12/456,334 patent/US20090311111A1/en not_active Abandoned
- 2009-06-16 CN CNA2009101493429A patent/CN101608642A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102297704A (en) * | 2010-06-23 | 2011-12-28 | 罗伯特·博世有限公司 | Apparatus for determining fluid medium characteristics |
| CN102297704B (en) * | 2010-06-23 | 2016-12-07 | 罗伯特·博世有限公司 | For detecting the device of the characteristic of the fluid media (medium) of flowing |
| CN105363582A (en) * | 2015-12-16 | 2016-03-02 | 山东大学 | Needle control device capable of adjusting area of ejector nozzle and ejector |
| CN105363582B (en) * | 2015-12-16 | 2018-06-12 | 山东大学 | A kind of nozzle needle control device and injector that can adjust injector nozzle area |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2009299609A (en) | 2009-12-24 |
| DE102009024712A1 (en) | 2010-05-12 |
| US20090311111A1 (en) | 2009-12-17 |
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Open date: 20091223 |