CN101078570A - Ejector type refrigerating cycle device - Google Patents
Ejector type refrigerating cycle device Download PDFInfo
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- CN101078570A CN101078570A CN 200710002365 CN200710002365A CN101078570A CN 101078570 A CN101078570 A CN 101078570A CN 200710002365 CN200710002365 CN 200710002365 CN 200710002365 A CN200710002365 A CN 200710002365A CN 101078570 A CN101078570 A CN 101078570A
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Abstract
An ejector refrigerant cycle device includes a radiator for radiating heat of high-temperature and high-pressure refrigerant discharged from a compressor, a branch portion for branching a flow of refrigerant on a downstream side of the radiator into a first stream and a second stream, an ejector that includes a nozzle portion for decompressing and expending refrigerant of the first stream from the branch portion, a decompression portion for decompressing and expanding refrigerant of the second stream from the branch portion, and an evaporator for evaporating refrigerant on a downstream side of the decompression portion. The evaporator has a refrigerant outlet coupled to the refrigerant suction port of the ejector. Furthermore, a refrigerant radiating portion is provided for radiating heat of refrigerant while the decompression portion decompresses and expands refrigerant. For example, the refrigerant radiating portion is provided in an inner heat exchanger.
Description
Technical field
The present invention relates to a kind of ejector type refrigerating cycle device with injector.
Background technology
JP-A-2005-308380 (corresponding to U.S. 2005/0268644A1) discloses a kind of ejector type refrigerating cycle device.In this ejector type refrigerating cycle device, cold-producing medium stream is split into two a fluid streams in the downstream of radiator and in the branching portion office of the upstream side of the nozzle segment of injector, one of them flows to nozzle segment, and another flows to the refrigerant suction port of injector.
In the ejector type refrigerating cycle device of the document, first evaporimeter is placed on the downstream of the diffusion part of injector.Between the component and refrigerant suction port of injector, be provided with throttle mechanism, described throttle mechanism is as the decompressor refrigeration that makes the cold-producing medium decompression, and be provided with second evaporimeter, described second evaporimeter is used to evaporate the cold-producing medium that is depressurized, and is inhaled into the refrigerant suction port of injector with the cold-producing medium that allows to be evaporated.
The cold-producing medium evaporating pressure (cold-producing medium evaporating temperature just) that the pressure increase effect of the diffusion part of injector has increased by first evaporimeter makes its cold-producing medium evaporating pressure than second evaporimeter big, and cold-producing medium can be sentenced different temperature range evaporations at first and second evaporimeters like this.In addition, the downstream of first evaporimeter is connected to the compressor suction side, and the pressure of the cold-producing medium that will be aspirated by compressor increases, thereby has reduced driven compressor power and improved cycle efficieny (cycle performance COP just).
In order further to improve cycle efficieny, except the structure of disclosed ejector type refrigerating cycle device in JP-A-2005-308380, the present inventor has attempted a kind of ejector refrigerant circulation, the circulation of this ejector refrigerant comprises inner heat exchanger, is used for the heat between the low-temperature low-pressure refrigerant of the high-temperature high-pressure refrigerant in exchange radiator downstream and compressor suction side.In this case, the enthalpy that flows into the cold-producing medium in each first and second evaporimeter is lowered by the heat exchange of the cold-producing medium in inner heat exchanger, the difference of the enthalpy (refrigerating capacity) of the cold-producing medium between refrigerant inlet in each first and second evaporimeter and the outlet is increased thus, thereby compare with disclosed circulation in JP-A-2005-308380, improved cycle efficieny.
Yet, when the ejector type refrigerating cycle device that is provided with inner heat exchanger is activated practically, do not make the cold-producing medium decompression fully at the throttle mechanism of the upstream side of second evaporimeter.Thereby, running when ejector type refrigerating cycle device reduces with respect to the cold-producing medium evaporating pressure of first evaporimeter fully through the cold-producing medium evaporating pressure of second evaporimeter of being everlasting.If cold-producing medium circulates in such state and turned round, then second evaporimeter can not provide sufficient refrigerating capacity.
Summary of the invention
The present inventor has been found that this problem is due to the fact that and causes: promptly, the cold-producing medium that enters supercooled state in inner heat exchanger after the heat radiation flow in the throttle mechanism.This be because, the cold-producing medium in flowing into throttle mechanism is when supercooled state (liquid phase state), the density of cold-producing medium has been increased, and causes the increase by the refrigerant mass fluxes of throttle mechanism.In other words, the resistance that the increase of the refrigerant mass fluxes by throttle mechanism causes cold-producing medium to pass through the passage of throttle mechanism wherein reduces, and the amount that reduces of the refrigerant pressure that is caused by throttle mechanism reduces thus.
In addition, in order suitably to make the cold-producing medium decompression by decompressor, based on by ASHRAEResearch, " 2002 ASHRAE HANDBOOK REFRIGERATION SI Edition ", USA, American Society of Heating, Refrigerating and Air-ConditioningEngineers, Inc.edition, June 2002, report and empirical formula that p45.23 describes in the p45.30, the inventor as calculated as the relation between the flow of the shape of the throttle mechanism of decompressor and the cold-producing medium by the mechanism of decompressor.
Figure 24 shows the chart of the result of calculation of relation above-mentioned.In this calculated, capillary was used as throttle mechanism.In Figure 24, transverse axis is the index l/d (length l capillaceous is to the ratio of inside diameter d capillaceous) of representative shape capillaceous, and the longitudinal axis has shown when the pressure at the cold-producing medium of porch capillaceous is in predetermined value the flow of cold-producing medium (mass flow).
In addition, Figure 24 also illustrates two kinds of result of calculations under the situation by curve table, and wherein two kinds of situations are respectively: flow to cold-producing medium capillaceous and be in supercooled state, and cold-producing medium is in the gas-liquid two-phase state.At this, the mass dryness fraction of the cold-producing medium in calculating under the gas-liquid two-phase state is set between 0.03 to 0.25.This mass dryness fraction is corresponding to the mass dryness fraction of the cold-producing medium at the place, downstream of the radiator in the common ejector type refrigerating cycle device.
With reference to Figure 24, when flowing into cold-producing medium capillaceous and become supercooled state, compare with the situation of cold-producing medium in the gas-liquid two-phase state, the flow of cold-producing medium has been increased, and the increase of the value of l/d does not cause the flow of cold-producing medium to be reduced to being lower than predetermined value.In other words, the change of shape capillaceous can not increase the amount that pressure reduces and makes the pressure reduction more than predetermined value.
Therefore, Figure 24 illustrates: use flow into the cold-producing medium in the gas-liquid two-phase state capillaceous and compares with the situation of using the cold-producing medium in supercooled state, can increase the decrease of the pressure of the cold-producing medium in the capillary effectively.Yet, the cold-producing medium in the gas-liquid two-phase state flow in the throttle mechanism flow and the cold-producing medium in supercooled state flow into mobile comparing in the throttle mechanism, trend towards causing flowing into the increase of the enthalpy of the cold-producing medium in the evaporimeter.Therefore, when the cold-producing medium in the gas-liquid two-phase state flow in the throttle mechanism, cycle efficieny was lowered probably.
Consider problem above-mentioned, the decompressor that the objective of the invention is the upstream side by being arranged in evaporimeter suitably makes the cold-producing medium decompression, and can not cause the reduction of cycle efficieny, and wherein said evaporimeter is coupled to the refrigerant suction port of injector.
Another object of the present invention provides a kind of ejector type refrigerating cycle device with new loop structure, and this ejector type refrigerating cycle device can improve its cycle efficieny effectively.
According to a first aspect of the invention, ejector type refrigerating cycle device comprises: compressor, this compressor are used for compression and refrigerant emission; Radiator is used for distributing the heat of the high-temperature high-pressure refrigerant that is discharged out from compressor; Component, this component be used for the cold-producing medium diverting flow in the radiator downstream gain the first rank the bundle and second a fluid stream; And injector, this injector has nozzle segment, is used to make the cold-producing medium decompression and the expansion of first a fluid stream that comes from component; And refrigerant suction port, the high velocity stream inspiration of the cold-producing medium that cold-producing medium is ejected from nozzle segment from described refrigerant suction port.In addition, ejector type refrigerating cycle device comprises: decompressor is used to make the cold-producing medium decompression and the expansion of second a fluid stream that comes from component.
Thus, even when the cold-producing medium at the radiator outlet place is in the gas-liquid two-phase state, the cycle efficieny of ejector type refrigerating cycle device also can be increased effectively.
Normally, in ejector type refrigerating cycle device, when the cold-producing medium at the radiator outlet place was in the state of gas-liquid two-phase, the cold-producing medium that is in the gas-liquid two-phase state in the radiator downstream can flow in the decompressor.This compares from the situation that radiator flow into the decompressor with the cold-producing medium in supercooled state, can increase the decrease of the pressure of cold-producing medium greatly.Yet, in ejector type refrigerating cycle device, when decompressor makes the cold-producing medium decompression, the refrigerant loses heat device distributes the heat of cold-producing medium, and it can for example not only reduce the pressure of cold-producing medium but also reduce its enthalpy by the straight line of ordering to J from the D point in the Mollier diagram shown in Figure 2 in the shown time period.
As a result, this can increase the difference of enthalpy (refrigerating capacity) of the refrigerant inlet and the cold-producing medium between the outlet of evaporimeter, thereby cold-producing medium is suitably reduced pressure and does not cause the reduction of cycle efficieny.
Thus, even the mass dryness fraction of the cold-producing medium of gas-liquid two-phase very little (for example, mass dryness fraction is 0.03), the decrease that flow into the pressure of the cold-producing medium in the decompressor also can be increased fully by decompressor.
For example, the refrigerant loses heat device is an inner heat exchanger, and this inner heat exchanger is at the cold-producing medium by decompressor and will be sucked into heat-shift between the cold-producing medium of compressor.
In addition, can be provided for cold-producing medium is separated into the gas/liquid separative element of vapor phase refrigerant and liquid phase refrigerant in the downstream of radiator.In this case, component will be gained the first rank by the liquid phase refrigerant shunting that the gas/liquid separative element is separated and restraint and second a fluid stream.
Alternatively, decompressor can be used as the first decompression part, and can be provided for making the second decompression part of the cold-producing medium decompression of second a fluid stream that comes from component further.In this case, the second decompression part is positioned at the downstream position of component and the upstream position of the first decompression part, and, make the cold-producing medium decompression of second a fluid stream of being shunted from component in the gas-liquid two-phase state along the cold-producing medium of second a fluid stream stream, at the upstream side place of the first decompression part.
Alternatively, the second decompression part can be positioned at the upstream position of component and the downstream position of radiator along cold-producing medium stream, and makes the cold-producing medium decompression in the gas-liquid two-phase state.In this case, the second decompression part can be a variable restrictor mechanism, and along with the increase in the degree of supercooling of the cold-producing medium in radiator downstream, this variable restrictor mechanism reduces its throttling passage area.
Alternatively, the second decompression part can be set, be used for after cold-producing medium is by the first decompression part decompression, making its decompression.In this case, the second decompression part is positioned at the downstream position of the first decompression part and the upstream position of evaporimeter, and along the cold-producing medium of second a fluid stream stream, at the upstream side place of the second decompression part, the first decompression part makes the cold-producing medium decompression of second a fluid stream of being shunted from component in the gas-liquid two-phase state.
According to another aspect of the present invention, a kind of ejector type refrigerating cycle device comprises: compressor, this compressor are used for compression and refrigerant emission; Radiator, this radiator are used for distributing the heat of the high-temperature high-pressure refrigerant that is discharged out from compressor; Component, this component be used for the cold-producing medium diverting flow in the radiator downstream gain the first rank the bundle and second a fluid stream; Injector, this injector comprises nozzle segment, is used to make the cold-producing medium decompression of first a fluid stream that comes from component and expands, and also comprises refrigerant suction port, is sucked into from the high velocity stream by the cold-producing medium that is ejected from nozzle segment of cold-producing medium here; First decompressor, this first decompressor are used to make the cold-producing medium decompression of second a fluid stream of being shunted from component and expand; Evaporimeter, this evaporimeter are used to evaporate the cold-producing medium in the first decompressor downstream, and the refrigerant outlet with the refrigerant suction port that is connected to injector; And second decompressor, this second decompressor is positioned at the downstream of component and the upstream of first decompressor along the cold-producing medium stream of second a fluid stream, is used for making the cold-producing medium decompression at second a fluid stream of gas-liquid two-phase state.Even in this case, the cycle efficieny of ejector type refrigerating cycle device still can be increased effectively by using first decompressor and second decompressor.
Description of drawings
To the following detailed description of preferred embodiment, more purpose of the present invention and advantage will be more readily understood in conjunction with the drawings, in the accompanying drawings:
Fig. 1 is a schematic diagram, shows the ejector type refrigerating cycle device of first embodiment according to the invention;
Fig. 2 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of first embodiment;
Fig. 3 is a schematic diagram, shows the ejector type refrigerating cycle device according to second embodiment of the present invention;
Fig. 4 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of second embodiment;
Fig. 5 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 3rd embodiment of the present invention;
Fig. 6 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of the 3rd embodiment;
Fig. 7 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 4th embodiment of the present invention;
Fig. 8 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of the 4th embodiment;
Fig. 9 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 5th embodiment of the present invention;
Figure 10 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of the 5th embodiment;
Figure 11 is a schematic diagram, shows ejector type refrigerating cycle device according to a sixth embodiment of the present;
Figure 12 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of the 6th embodiment;
Figure 13 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 7th embodiment of the present invention;
Figure 14 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of the 7th embodiment;
Figure 15 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 8th embodiment of the present invention;
Figure 16 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of the 8th embodiment;
Figure 17 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 9th embodiment of the present invention;
Figure 18 is a schematic diagram, shows the ejector type refrigerating cycle device according to the of the present invention ten embodiment;
Figure 19 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 11 embodiment of the present invention;
Figure 20 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 12 embodiment of the present invention;
Figure 21 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of the 12 embodiment;
Figure 22 is a schematic diagram, shows the ejector type refrigerating cycle device according to the 13 embodiment of the present invention;
Figure 23 is a Mollier diagram, shows the running according to the ejector type refrigerating cycle device of the 13 embodiment;
Figure 24 is a chart, shows the relation between the flow of the shape of throttle mechanism and the cold-producing medium by throttle mechanism.
The specific embodiment
(first embodiment)
With reference to figure 1 and Fig. 2, will be described below first embodiment of the present invention.Fig. 1 shows the configured in one piece figure of example, and wherein the ejector type refrigerating cycle device of first embodiment is applied to the refrigeration plant of vehicle.The refrigeration plant that is used for vehicle of this embodiment is to be used for cool room is cooled to low-down temperature, for example, and approximately-20 ℃.
At first, in ejector type refrigerating cycle device 10, compressor 11 inspirations, the compression and refrigerant emission, and have from vehicle travel the engine (not shown) via belt wheel and belt be delivered to the there driving force, thereby can drive with being rotated.In addition, in this embodiment, a kind of known rotating sloping disk type variable volume compressor is used as compressor 11, and this compressor can be controlled discharge volume changeably and continuously by the control signal from the outside.
Discharge volume is represented the geometric volume of apron space, and cold-producing medium is sucked into and compresses in described apron space, and is illustrated in the top dead-centre of stroke of piston of compressor and the cylinder volume between the bottom dead centre particularly.By changing discharge volume, the discharge capacity of compressor 11 can be adjusted.Thereby the variation of discharge volume is to be done by the stroke that the inclination angle that the pressure P c that is controlled at the wobbler chamber (not shown) that form in the compressor 11 changes wobbler changes piston.
The pressure P c of wobbler chamber is by using by subsequently with the long-pending control valve 11a of output signal electromagnet driven of the conditioning control unit 23 that is described, and controlled, wherein refrigerant emission pressure P d and suction refrigerant pressure Ps are introduced in the wobbler chamber change refrigerant emission pressure P d for the ratio that sucks refrigerant pressure Ps.By like this, compressor 11 can change discharge volume continuously in about scope of 0% to 100%.
In addition, because compressor 11 can change discharge volume continuously in about scope of 0% to 100%, therefore, arrive near 0% by reducing discharge volume, compressor 11 can be brought into the running halted state basically.Therefore, this embodiment has adopted the formation of no-clutch, and wherein the rotating shaft of compressor 11 is coupled to vehicle all the time via belt wheel and belt and travels on the engine.
Certainly, variable displacement compressor even can be constituted as has via electromagnetic clutch from the vehicle power that engine transmits that travels.In addition, when fixed volume formula compressor is used as compressor 11, also recommend to carry out by electromagnetic clutch turn round off and on the switch control of compressor, with the control running rate, just, the open operation of compressor is to the ratio of shutoff operation, thus the discharge capacity of the cold-producing medium of control compressor.Alternatively, can use the motor compressor that is rotatably driven by electro-motor.In this case, the rotation number of electro-motor is controlled by the FREQUENCY CONTROL or the similar control of transverter (inverter), thus the discharge capacity of the cold-producing medium of control compressor.
The ejector type refrigerating cycle device of this embodiment constitutes subcritical cycle, and wherein the pressure of high-pressure refrigerant can not be increased on the supercritical pressure of cold-producing medium, and radiator 12 is used as condenser, is used for cooling and condensating refrigerant.The cold-producing medium that is cooled off by radiator 12 reaches the gas-liquid two-phase state in normal running.For example, when outdoor temperature was low in winter, cold-producing medium often became supercooled state.
The component A that is used to shunt the cold-producing medium stream that comes from radiator 12 is set at the downstream of radiator 12.A cold-producing medium a fluid stream of being shunted at component A place is introduced into nozzle segment side pipe road 13, and this nozzle segment side pipe road 13 connects component A and subsequently with the upstream side of the nozzle segment 16a of the injector 16 that is described.Another cold-producing medium a fluid stream of being shunted at component A place is introduced into suction inlet side pipe road 14, and this suction inlet side pipe road 14 connects the refrigerant suction port 16b of component A and injector 16.
In being branched the cold-producing medium inflow nozzle segment side pipe road 13 wherein of part A shunting, variable restrictor mechanism 15 is set up.The refrigerant flow Ge that variable restrictor mechanism 15 is used to determine to flow to suction inlet side pipe road 14 is for the flow rate ratio η that flows to the refrigerant flow Gnoz in nozzle segment side pipe road 13 from component A (η=Ge/Gnoz).
More specifically, in this embodiment, known thermal expansion valve is used as variable restrictor mechanism 15, and flow through the flow of the cold-producing medium of variable restrictor mechanism 15 by the extent of opening adjustment that changes the valve body (not shown), wherein the degree of superheat of the cold-producing medium at the outlet side place of the extent of opening correspondence of valve body second evaporimeter 21 that will be described subsequently.Flow rate ratio η is set as suitable value, thus in the degree of superheat of the cold-producing medium of second evaporimeter, 21 outlet sides near predetermined value.Be noted that the description of the parts of thermal expansion valve (such as responsive to temperature cylinder or balance pipe) will be omitted for the ease of diagram.
As variable restrictor mechanism 15, a kind of electric throttling mechanism can be used.Temperature and pressure at the cold-producing medium of the outlet side of second evaporimeter 21 can be detected, and can be calculated based on these detected values in the degree of superheat of the cold-producing medium of the outlet side of second evaporimeter 21.In this case, the flow of cold-producing medium can be adjusted, and the process degree of making is a predetermined value.In addition, perhaps alternatively, the temperature and pressure of the cold-producing medium that flows out from radiator 12 can be detected.In this case, the flow of cold-producing medium can be adjusted, and makes the temperature and pressure of the cold-producing medium that flows out from radiator 12 be based on the predetermined value that these detected value.
In addition, injector 16 comprises mixing portion 16c, this mixing portion is positioned in the downstream of nozzle segment 16a and refrigerant suction port 16b, and will mix mutually with suction cold-producing medium from the high speed cold-producing medium of nozzle segment 16a ejection from refrigerant suction port 16b inspiration, and described injector 16 comprises diffusion part 16d, described diffusion part 16d is positioned in the downstream of mixing portion 16c, increase part as pressure, be used to reduce the speed of cold-producing medium stream, thereby increase the pressure of cold-producing medium.
In addition, the vapor phase refrigerant outlet is set at jar top of shape reservoir 18.The vapor phase refrigerant outlet is connected on the inner heat exchanger 19, and this inner heat exchanger 19 has the refrigerant outlet side of the suction side that is connected to compressor 11.
Next, inner heat exchanger 19, the second fixed restriction device 20 and second evaporimeter 21 are placed in the suction inlet side pipe road 14, wherein are branched another cold-producing medium that part A shunts and flow in this suction inlet side pipe road 14.
In addition, the coolant channel of the inner heat exchanger 19 that provides in suction inlet side pipe road 14 comprises the first fixed restriction device 19a, as throttle mechanism the cold-producing medium in component A downstream is reduced pressure and expansion, wherein the cold-producing medium in component A downstream is by described coolant channel.Therefore, in this embodiment, the first fixed restriction device 19a is used to make at the cold-producing medium decompression in component A downstream and the decompressor that expands, and inner heat exchanger 19 also is the refrigerant loses heat device.
More specifically, the first fixed restriction device 19a of inner heat exchanger 19 is made of capillary.Inner heat exchanger 19 is formed by this way: make win fixed restriction device 19a be in the same place by hard solder mutually at the refrigerant tubing of the suction side of compressor 11.Be understandable that, any other method of attachment, for example welding, pressure welding or soft soldering or the like can be used to form inner heat exchanger.Therefore, in this embodiment, constituted by one as the first fixed restriction device 19a of decompressor with as the inner heat exchanger of refrigerant loses heat device, this shows the effect of the size that reduces to circulate.
The capillary that is used as the first fixed restriction device 19a in inner heat exchanger 19 is by the restriction of coolant channel area and the friction in coolant channel being made the cold-producing medium decompression, and therefore has the elongated shape with pre-customized cryogen passage length.Like this, the capillary heat exchange area of refrigerant pipe during that make it possible to guarantee at an easy rate compressor 11 suction sides as the use of the first fixed restriction device 19a by hard solder.As a result, the cold-producing medium by the first fixed restriction device 19a trend towards having it by distribute heat.
The second fixed restriction device 20 is to be used to make by first fixed restriction device 19a decompression and further decompression of cold-producing medium of expanding and the decompressor that expands.More specifically, although in this embodiment, the second fixed restriction device 20 is made of capillary, and it can be made of throttle orifice.Here be noted that in this embodiment the second fixed restriction device 20 can be used as the assisted decompression device of first throttle device 19a, but can be omitted.
Like this, the air that is blown out by air blast 17a above-mentioned flows on the direction of arrow B, and at first by 17 coolings of first evaporimeter, is cooled off once more by second evaporimeter 21 then.In other words, the first evaporimeter 17 single space (identical space) that 21 coolings will be cooled with second evaporimeter.
In addition, the different operating signal that comes from the detection signal of one group of various types of sensor and come from the guidance panel (not shown) is imported in the conditioning control unit 23.Particularly, as one group of sensor, be provided with the extraneous air sensor or the similar sensor of the temperature (the outer air themperature of vehicle chamber just) that is used to detect extraneous air.In addition, guidance panel is provided with the console switch that is used to operate refrigeration plant, be used to set the temperature setting switch of the chilling temperature in the space that will be cooled, and similar switch.
Next, the running of ejector type refrigerating cycle device that below description is had first embodiment of said structure.Be illustrated in the Mollier diagram of operating condition at Fig. 2 of the cold-producing medium in this cold-producing medium circulation.
At first, when vehicle travels engine when being started, rotary driving force is transferred to compressor 11 from the vehicle engine that travels.Further, when the operation signal of console switch when guidance panel is imported into conditioning control unit 23, based on the control program of storage formerly, output signal is output to electromagnetism volume control valve 11a from conditioning control unit 23.
The discharge volume of compressor 11 is determined by this output signal.The vapor phase refrigerant that compressor 11 inspirations are flowed via inner heat exchanger 19 from reservoir 18, and compression and discharge vapor phase refrigerant.The confined state of the cold-producing medium of this moment is corresponding to the some C among Fig. 2.The HTHP vapor phase refrigerant that is discharged out from compressor 11 flow into the radiator 12, to be cooled off by extraneous air, cold-producing medium is brought into gas-liquid two-phase state (corresponding to a D) like this.In the state of gas-liquid two-phase, and has the mass dryness fraction that allows second evaporimeter 21 to have suitable cooling capacity corresponding to the cold-producing medium of Fig. 2 mid point D.
In addition, the cold-producing medium from radiator 12 outflows in the gas-liquid two-phase state is branched part A and is divided into two streams, and one of them flow into nozzle segment side pipe road 13, and another flow into suction inlet side pipe road 14a.The flow Gnoz that flow into the cold-producing medium in nozzle segment side pipe road 13 from component A is adjusted by variable restrictor mechanism 15 with the flow Ge that flow into the cold-producing medium in suction inlet side pipe road 14, and flow rate ratio η is near appropriate value above-mentioned thus.
Then, the cold-producing medium that has been divided to nozzle segment side pipe road 13 from component A flow into the nozzle segment 16a of injector 16.The cold-producing medium that flow into nozzle segment 16a is reduced pressure by nozzle segment 16a and expand (among Fig. 2 from a D to an E).On the time point of this decompression and expansion, the pressure of cold-producing medium can be converted into the speed energy, and cold-producing medium comes out from the refrigerant injection mouth of nozzle segment 16a is at full speed injected thus.
From the cold-producing medium suction effect of the high speed cold-producing medium stream of the jet of nozzle segment 16a by refrigerant suction port 16b inspiration the cold-producing medium by second evaporimeter 21.The cold-producing medium that is ejected from nozzle segment 16a and mixed, flow into diffusion part 16d by the mixing portion 16c in nozzle segment 16a downstream from the indrawn cold-producing medium of refrigerant suction port 16b.In this diffusion part 16d, the speed of cold-producing medium can be converted into the pressure energy by enlarging aisle spare, and the pressure of cold-producing medium has been increased (the some E from Fig. 2 arrives some G then to a F) thus.
The cold-producing medium that flows out from the diffusion part 16d of injector 16 flow into first evaporimeter 17, and low pressure refrigerant evaporates (the some G from Fig. 2 is to a H) from the absorption of air heat that blown out by air blast 17a therein.The cold-producing medium by first evaporimeter 17 flow in the reservoir 18, to be divided into vapor phase refrigerant and liquid phase refrigerant.
The low-pressure vapor phase cold-producing medium that flows out from reservoir 18 flow in the inner heat exchanger 19, and carries out exchange heat (the some H from Fig. 2 is to an I) with the high-pressure refrigerant that flows out to suction inlet side pipe road 14 from component A.The vapor phase refrigerant of heat exchanger 19 outflows internally is by compressor 11 inspirations and compression once more.
The gas-liquid two-phase cold-producing medium that flows out to suction inlet side pipe road 14 from component A flow into the first fixed restriction device 19a of inner heat exchanger 19.Be depressurized during the first fixed restriction device 19a of the cold-producing medium of the first fixed restriction device 19a that flow into inner heat exchanger 19 by inner heat exchanger 19 and expand, thus simultaneously with cold-producing medium heat-shift distribute heat (the some D from Fig. 2 is to a J) in the suction side of compressor 11.Because the cold-producing medium that comes under the gas-liquid two-phase state of radiator 12 flows to the first fixed restriction device 19a, so cold-producing medium can suitably be reduced pressure by the first fixed restriction device 19a.
When the cold-producing medium of the first fixed restriction device 19a that flows out inner heat exchanger 19 is depressurized during by the second fixed restriction device 20, flow into then (the some J from Fig. 2 is to a K) in second evaporimeter 21.In second evaporimeter 21, the low pressure refrigerant that flows further absorbs heat and evaporates (the some K from Fig. 2 is to a L) from the air that air blast 17a blows out, and wherein said low pressure refrigerant is by 17 coolings of first evaporimeter.
And, cold-producing medium in second evaporimeter, 21 places evaporations is sucked among the refrigerant suction port 16b of injector 16 via suction inlet side pipe road 14, and by mixing portion 16c mix (the some L from Fig. 2 is to a F) with liquid phase refrigerant by nozzle segment 16a, to flow out to first evaporimeter 17.
As mentioned above, in this embodiment, the cold-producing medium under the gas-liquid two-phase state of being in radiator 12 downstreams flow among the first fixed restriction device 19a in the coolant channel that is placed in inner heat exchanger 19, and cold-producing medium can suitably be reduced pressure by the first fixed restriction device 19a thus.As a result, the cold-producing medium evaporating temperature with second evaporimeter 21 of first evaporimeter 17 can be set in the different temperature ranges, allows second evaporimeter 21 to apply sufficient refrigerating capacity simultaneously.
In addition, in the first fixed restriction device 19a, the cold-producing medium at place, the downstream of component A is depressurized and expands, and distributes the heat of cold-producing medium simultaneously.Like this, as in the Mollier diagram of Fig. 2 from a D to the straight line of a J shown, the pressure of cold-producing medium and enthalpy can side by side be reduced, and the difference of the enthalpy (refrigerating capacity) of the cold-producing medium between the refrigerant inlet of second evaporimeter 21 and outlet can be increased like this.As a result, the cycle efficieny of spray type refrigerating circulation can be enhanced.
According to first embodiment, inner heat exchanger 19 comprises the first coolant channel part that is provided with the first fixed restriction device 19a, with the second coolant channel part, wherein cold-producing medium flows towards the cold-producing medium suction side of compressor 11 by described second coolant channel part from the downstream of the outlet side of injector 16.In addition, only when the cold-producing medium that comes from component A in first coolant channel part, be cooled, when cold-producing medium is reduced pressure by the first fixed restriction device 19a simultaneously, first coolant channel part and second coolant channel with first fixed restriction device 19a partly can suitably be constituted in inner heat exchanger 19.In addition, in this embodiment, because first evaporimeter 17 and reservoir 18 are set at from the downstream part of the refrigerant outlet of injector 16, the separated vapor phase refrigerant in reservoir 18 is introduced in the second coolant channel part of inner heat exchanger 19.Yet in the cold-producing medium circulation of the ejector type refrigerating cycle device of first embodiment, one in first evaporimeter 17 and the reservoir 18 may be omitted, and perhaps first evaporimeter 17 and reservoir 18 all may be left in the basket.
(second embodiment)
The first above-mentioned embodiment by the example that the first fixed restriction device 19a constitutes, has explained the employing of inner heat exchanger 19 as the coolant channel in the suction inlet wing passage 14.That is to say, the cold-producing medium that flow into inner heat exchanger 19 from component A when being cooled by throttling.Yet in second embodiment, as shown in Figure 3, a kind of do not have the inner heat exchanger 24 of throttling function to be used.Inner heat exchanger 24 only has at the cold-producing medium in component A downstream and carry out the function of exchange heat between the cold-producing medium of compressor 11 suction sides, and the coolant channel of wherein said inner heat exchanger 24 is not to be made of throttle mechanism.
Be used as decompressor be used to make cold-producing medium decompression and expand and the first fixed restriction device 25 that it is brought into the gas-liquid two-phase state is set at the upstream side of the inner heat exchanger 24 in the suction inlet side pipe road 14 and at the upstream side of the second fixed restriction device 20.More specifically, as an example, the first fixed restriction device 25 is made of throttle orifice.
Therefore, in this embodiment, the first fixed restriction device 25 makes the cold-producing medium of locating in the downstream of component A be in the gas-liquid two-phase state as the decompressor at the upstream side place that is arranged on the second fixed restriction device 20.Then, the second fixed restriction device 20 further makes the cold-producing medium decompression of flowing out from the first fixed restriction device 25.
Though the first fixed restriction device 25 is made of throttle orifice in this embodiment, the obvious first fixed restriction device 25 can be made of capillary.Other parts of this embodiment can have same structure with those parts among first embodiment.
Next, the running of this embodiment will be described below.Be illustrated in the Mollier diagram of state at Fig. 4 of the cold-producing medium in this circulation.In Fig. 4, used same drawing reference numeral to represent the same refrigerant condition that goes out as shown in Figure 2.
At first, similar with first embodiment, compressor 11 is come compressed refrigerant by running, and cold-producing medium is by radiator 12 coolings (the some C from Fig. 4 is to a D) then.In this embodiment, the cold-producing medium that is cooled off by radiator 12 becomes as at the shown gas-liquid two-phase state of Fig. 4 mid point D.
In addition, similar with first embodiment, the cold-producing medium the gas-liquid two-phase state that flows out from radiator 2 is branched part A and is divided into two streams, one of them sequentially flow into nozzle segment side pipe road 13, flow to then injector 16 nozzle segment 16a, mixing portion 16c, diffusion part 16d, first evaporimeter 17 and reservoir 18 (just in Fig. 4 from a D to an E, the some F, the some G and the some H order).
The low-pressure vapor phase cold-producing medium that flows out from reservoir 18 flow in the inner heat exchanger 24, and and flows out to the high-pressure refrigerant heat-shift (the some H from Fig. 4 is to an I) in suction inlet side pipe road 14 from component A.The vapor phase refrigerant of heat exchanger 24 outflows internally is by compressor 11 inspirations and compression once more.On the other hand, the cold-producing medium that flows out to suction inlet side pipe road 14 from component A flow into the inner heat exchanger 24, and with at the cold-producing medium heat-shift of the suction side of compressor 11, reach supercooled state (the some D from Fig. 4 is to a M) with distribute heat.The cold-producing medium in supercooled state of heat exchanger 24 outflows is internally reduced pressure to by the first fixed restriction device 25 and becomes gas-liquid two-phase state (the some M from Fig. 4 is to a N).
Cold-producing medium in the gas-liquid two-phase state flow in the second fixed restriction device 20, and here it further is depressurized and expand (the some N from Fig. 4 is to a K).The second fixed restriction device 20 makes the cold-producing medium decompression in the gas-liquid two-phase state at the place, downstream of the first fixed restriction device 25, can suitably make the cold-producing medium decompression thus.
Similar with first embodiment, the cold-producing medium that flows out from the second fixed restriction device 20 flow in second evaporimeter 21 and absorbs the heat of the air that blows out from air blast 17a, and wherein said cold-producing medium is by 17 coolings of first evaporimeter.Therefore, cold-producing medium is evaporated in second evaporimeter 21, and is sucked among the refrigerant suction port 16b of injector 16, and cold-producing medium mixes with the liquid phase refrigerant by nozzle segment 16a by mixing portion 16c thus.In this cold-producing medium stream, the operating condition of cold-producing medium is changed in proper order with this: the some K among Fig. 4, some L and some F.
As mentioned above, in this embodiment, the cold-producing medium that is under two states of gas-liquid in the first fixed restriction device, 25 downstreams flows in the second fixed restriction device 20, and throttling arrangement 20 suitably reduces pressure thereby cold-producing medium can be fixed.As a result, the cold-producing medium evaporating temperature of first evaporimeter 17 and second evaporimeter 21 can be positioned at different temperature ranges definitely, and second evaporimeter 21 can apply sufficient refrigerating capacity.
In addition, as among Fig. 4 from a D to the operation line of a M shown because the enthalpy of cold-producing medium can be lowered at inner heat exchanger 24 places, therefore, might be increased in the refrigerant inlet of second evaporimeter 21 and the enthalpy difference of cold-producing medium between the outlet fully.This result can improve cycle efficieny.
In addition, the cold-producing medium in supercooled state is changed at the first fixed restriction device, 25 places and is the gas-liquid two-phase state.Therefore, even be in cold excessively state, still can access above-mentioned effect at the cold-producing medium in the exit of radiator 12.In the circulation of this embodiment, inner heat exchanger 24 can be omitted, and can directly flow into the first fixed restriction device 25 from the cold-producing medium that component A flows to suction inlet side pipe road 14.
(the 3rd embodiment)
The first above-mentioned embodiment by the example that the first fixed restriction device 19a constitutes, has explained the employing of inner heat exchanger 19 as the coolant channel in component A downstream.Yet in the 3rd embodiment, as shown in Figure 5, a kind of inner heat exchanger 26 is used, with the inner heat exchanger 19 and the second fixed restriction device 20 that replaces describing in first embodiment.
Pass through in one of them coolant channel at cold-producing medium inner heat exchanger 26, component A downstream, be provided with the first fixed restriction device 26a that constitutes by capillary, and the second fixed restriction device 26b that is positioned in the first fixed restriction device 26a upstream side.For example, the second fixed restriction device 26b is made of throttle orifice or throttling passage.
Similar with the first fixed restriction device 19a of inner heat exchanger 19 in first embodiment, the first fixed restriction device 26a is by the refrigerant tubing of hard solder to compressor 11 suction sides, and be configured to make cold-producing medium decompression and expansion, simultaneously distribute heat in component A downstream.
The second fixed restriction device 26b is positioned at from the upstream of the first fixed restriction device 26a along the cold-producing medium stream that comes from component A.In this embodiment, the refrigerant tubing that the second fixed restriction device 26b is not located to compressor 11 suction sides by hard solder, but separate with the refrigerant tubing of locating in the suction side of compressor 11.Therefore, the second fixed restriction device 26b only have the cold-producing medium decompression that makes component A downstream place and expand, cold-producing medium is brought into the function in the gas-liquid two-phase state.The second fixed restriction device 26b is can be with inner heat exchanger 26 integrally formed or separate with inner heat exchanger 26.
Therefore, in this 3rd embodiment, the first fixed restriction device 26a is used for making decompression of gas-liquid two-phase cold-producing medium and expansion after the second fixed restriction device 26b is depressurized as decompressor.The second fixed restriction device 26b is as decompressor, and this decompressor is set at the upstream side of first throttle device 26a, and is suitable for making the cold-producing medium decompression in component A downstream and expanding, so that it is brought in the gas-liquid two-phase state.Other parts of this embodiment can have same structure with those parts among first embodiment.
Next, the running of this embodiment will be described below.Be illustrated in the Mollier diagram of operating condition at Fig. 6 of the cold-producing medium in this cold-producing medium circulation.In Fig. 6, used same drawing reference numeral to represent the same cold-producing medium mode of operation that goes out as shown in Figure 2.
At first, similar with first embodiment, when the cold-producing medium circulation of the 3rd embodiment was turned round, the cold-producing medium that is discharged out from compressor 11 was cooled off by radiator 12.In addition, the cold-producing medium the gas-liquid two-phase state that flows out from radiator 12 is branched part A and is divided into two streams, one of them sequentially flow into nozzle segment side pipe road 13, arrive then injector 16 nozzle segment 16a, mixing portion 16c, diffusion part 16d, first evaporimeter 17 and reservoir 18 (just in Fig. 6 sequentially from a C to a D, the some E, the some F, the some G and the some H).
The low-pressure vapor phase cold-producing medium that flows out from reservoir 18 flow in the inner heat exchanger 26, and carries out exchange heat (the some H from Fig. 6 is to an I) with the high-pressure refrigerant that flows out to suction inlet side pipe road 14 from component A.The vapor phase refrigerant of heat exchanger 26 outflows internally is by compressor 11 inspirations and compression once more.On the other hand, the cold-producing medium in component A flows to suction inlet side pipe road 14 flow into the inner heat exchanger 26, and is brought into supercooled state with the cold-producing medium heat-shift of compressor 11 suction sides, with distribute heat (the some D from Fig. 6 is to an O).In addition, the cold-producing medium in supercooled state is reached the refrigerant condition (the some O from Fig. 6 is to a P) of gas-liquid two-phase by second fixed restriction device 26b decompression.
Cold-producing medium in the gas-liquid two-phase state flow among the first fixed restriction device 22a to be depressurized and to expand, simultaneously with at the cold-producing medium heat-shift of compressor 11 suction sides, with distribute heat (with this order: the some P from Fig. 6 to a K ' to putting a K).Here, because the cold-producing medium of locating in the suction side of the second fixed restriction device 26b in the gas-liquid two-phase state flow among the first fixed restriction device 26a, therefore, the cold-producing medium first fixed restriction device 26a that can be set in the inner heat exchanger 26 suitably reduces pressure.
The cold-producing medium by the first fixed restriction device 26a shown in the straight line from a K ' to some K among Fig. 6 with the reason that the mode of constant entropy expands is, when the cold-producing medium by the first fixed restriction device 26a reached a some K ', cold-producing medium was cooled to the corresponding temperature of temperature with the cold-producing medium at place, compressor 11 suction sides basically.Like this, in Fig. 6 from operation point K ' to operation point K, can not cause the transfer of heat basically.
In addition, similar with first embodiment, flowing into cold-producing medium in second evaporimeter 21 absorbs from the heat of air blast 17a blow out air and evaporates, wherein said cold-producing medium is by the cooling of first evaporimeter 17, is sucked into then among the refrigerant suction port 16b of injector 16, mixes in mixing portion 16c with the liquid phase refrigerant by nozzle segment 16a (among Fig. 6 sequentially from a K, put L to a F).
As mentioned above, in the 3rd embodiment, the cold-producing medium in the gas-liquid two-phase state in second fixed restriction device 26b downstream flow among the first fixed restriction device 26a, thereby cold-producing medium can suitably be reduced pressure by the first fixed restriction device 26a.As a result, the cold-producing medium evaporating temperature of first evaporimeter 17 and second evaporimeter 21 can be set in the different temperature ranges definitely, and second evaporimeter 21 can apply sufficient refrigerating capacity.
In addition, as among Fig. 6 with a D, the some O, the some P and the some K many straight lines that are linked in sequence shown, the enthalpy of cold-producing medium can be lowered at inner heat exchanger 26 places, can be increased in the enthalpy difference (refrigerating capacity) of the refrigerant inlet and the cold-producing medium between the outlet of second evaporimeter 21 simultaneously.This result can improve cycle efficieny.
In addition, similar with second embodiment, because the cold-producing medium in supercooled state is changed at the second fixed restriction device 26b place and is the gas-liquid two-phase state, therefore, even the cold-producing medium in the exit of radiator 12 is in cold excessively state, still can access the effect of first above-mentioned embodiment.
(the 4th embodiment)
In the 4th embodiment, as shown in Figure 7, the second fixed restriction device 20 of first embodiment is not set, and the second fixed restriction device 27 is set at the upstream side of inner heat exchanger 19 with respect to the circulation of first embodiment.The second fixed restriction device 27 is as decompressor, be used for making the cold-producing medium decompression that comes from component A and expand, go it is brought into the gas-liquid two-phase state, and more specifically, this second fixed restriction device 27 is made of throttle orifice or throttling passage.
Therefore, in this embodiment, the first fixed restriction device 19a (capillary) of inner heat exchanger 19 is used to make the cold-producing medium decompression and the expansion of being shunted at component A place and reduced pressure by the second fixed restriction device 27 as decompressor.Be set at the upstream side of the first fixed restriction device 19a and be suitable for making in the cold-producing medium decompression at place, component A downstream and expand and it is brought into the gas-liquid two-phase state as the second fixed restriction device 27 of decompressor.Other parts of this embodiment can have same structure with those parts among first embodiment.
Next, the running of this embodiment will be described below.Be illustrated in the Mollier diagram of operating condition at Fig. 8 of the cold-producing medium in this circulation.In Fig. 8, used same drawing reference numeral to represent the operating condition of the same cold-producing medium that goes out as shown in Figure 2.
At first, similar with first embodiment, when compressor 11 was turned round, cold-producing medium was compressed and cools off (the some C from Fig. 8 is to a D ') by radiator 12.Here it is also noted that in this embodiment, as Fig. 8 mid point D ' was shown, the cold-producing medium that is cooled off by radiator 12 became supercooled state.The cold-producing medium the gas-liquid two-phase state that flows out from radiator 12 is branched part A and is divided into two streams, one of them sequentially flow into nozzle segment side pipe road 13, arrive then injector 16 nozzle segment 16a, mixing portion 16c, diffusion part 16d, first evaporimeter 17 and reservoir 18 (just in Fig. 8 sequentially from a C to a D ', the some E, the some F, the some G and the some H).
The low-pressure vapor phase cold-producing medium that flows out from reservoir 18 flow in the inner heat exchanger 26, and and flows out to the high-pressure refrigerant heat-shift (the some H from Fig. 8 is to an I) in suction inlet side pipe road 14 from component A.The vapor phase refrigerant of heat exchanger 26 outflows internally is by compressor 11 inspirations and compression once more.On the other hand, the cold-producing medium that flows into suction inlet side pipe road 14 from component A flow into the second fixed restriction device 27, to be depressurized to gas-liquid two-phase state (the some D ' from Fig. 8 is to putting a Q).In addition, cold-producing medium in the gas-liquid two-phase state flow among the first fixed restriction device 19a of inner heat exchanger 19, to be depressurized and to expand, simultaneously with at the cold-producing medium heat-shift at place, compressor 11 suction sides, with distribute heat (promptly with this order: the some Q from Fig. 8 to a K ' to putting a K).
The cold-producing medium in the gas-liquid two-phase state at the second fixed restriction device, 27 upstream sides flow among the first fixed restriction device 19a, thereby cold-producing medium can suitably be reduced pressure by the first fixed restriction device 19a.Equally, as among Fig. 8 by shown like that to the straight line of some K from a K ', the cold-producing medium by the first fixed restriction device 19a because of and in the 3rd embodiment, describe same former thereby expand in the mode of constant entropy.
In addition, similar with first embodiment, flowing into cold-producing medium in second evaporimeter 21 absorbs the heat of the air that blows out from air blast 17a and evaporates, wherein said cold-producing medium is by the cooling of first evaporimeter 17, is sucked into then among the refrigerant suction port 16b of injector 16, mixes in mixing portion 16c with the liquid phase refrigerant by nozzle segment 16a (among Fig. 8 sequentially from a K to a L with put F).
As mentioned above, in this embodiment, because the cold-producing medium in the gas-liquid two-phase state at place, the second fixed restriction device, 27 downstreams flow among the first fixed restriction device 19a, therefore, cold-producing medium can suitably be reduced pressure by the first fixed restriction device 19a.As a result, the cold-producing medium evaporating temperature of first evaporimeter 17 and second evaporimeter 21 can be set in the different temperature ranges definitely, and second evaporimeter 21 can apply sufficient refrigerating capacity.
Like this, as among Fig. 8 from a Q to the straight line of a K shown, the enthalpy of cold-producing medium can be lowered in inner heat exchanger 19, and can be increased in the refrigerant inlet of second evaporimeter 21 and the enthalpy difference (refrigerating capacity) of cold-producing medium between the outlet.As a result, the efficient of circulation can be enhanced.
In addition, in the 4th embodiment, because the cold-producing medium in the gas-liquid two-phase state can flow into the first fixed restriction device 19a, therefore, even in the cold-producing medium in the exit of radiator 12 was state at gas-liquid two-phase, the first fixed restriction device 19a still can suitably make the cold-producing medium decompression.
(the 5th embodiment)
In the 5th embodiment, as shown in Figure 9, in the loop structure of first embodiment, the place, downstream at radiator 12a has increased gas/liquid separative element 30, and the cold-producing medium that is used for coming from radiator 12 is separated into vapor phase refrigerant and liquid phase refrigerant.Gas/liquid separative element 30 has the shape of jar shape, and by the difference on the density between vapor phase refrigerant and the liquid phase refrigerant, cold-producing medium is separated into gas phase and liquid phase.Like this, liquid phase refrigerant is stored in the bottom of gas/liquid separative element 30 in vertical direction.
In addition, in this embodiment, nozzle segment side pipe road 13 and suction inlet side pipe road 14 are connected on the liquid phase refrigerant container of gas/liquid separative element 30, and liquid phase refrigerant flow into from this container in nozzle segment side pipe road 13 and the suction inlet side pipe road 14 and shunted simultaneously.Therefore, in this embodiment, in the liquid phase refrigerant container of gas/liquid separative element 30, be provided with component A.Other parts of this embodiment can have same structure with those parts of first embodiment.
Next, below with reference to the Mollier diagram among Figure 10 the running of cold-producing medium circulation of this embodiment and the operating condition of the cold-producing medium in this cold-producing medium circulation are described.In Figure 10, used same drawing reference numeral to represent the same refrigerant condition that goes out as shown in Figure 2.
At first, when the circulation of the 5th embodiment was turned round, the cold-producing medium that is discharged out from compressor 11 was cooled off by radiator 12, and is separated into vapor phase refrigerant and liquid phase refrigerant by gas/liquid separative element 30.Like this, the liquid phase refrigerant at gas/liquid separative element 30 places is by a D in Figure 10 " cold-producing medium on the saturated solution phase line that illustrates.
Be branched nozzle segment 16a, mixing portion 16c, diffusion part 16d, first evaporimeter 17, reservoir 18 and the heat exchanger 19 that liquid phase refrigerant that part A flow into nozzle segment side pipe road 13 after separately sequentially flows to injector 16 (just in Figure 10 sequentially from a C to a D ", some E, some F, some G, some H and some I).In addition, the vapor phase refrigerant that flows out in the heat exchanger 19 internally is by compressor 11 inspirations and be compressed once more.
On the other hand, the liquid phase refrigerant that flows to suction inlet side pipe road 14 from component A flow into the first throttle device 19a of inner heat exchanger 19 being compressed and expanding, and simultaneously with the cold-producing medium heat-shift at place, compressor 11 suction sides, with distribute heat (the some D from Figure 10 " to putting a J).
Because the liquid phase refrigerant that is separated by gas/liquid separative element 30 is the cold-producing medium on the saturated solution phase line, therefore, because the little pressure that cold-producing medium just takes place after flowing into the first fixed restriction device 19a reduces, makes cold-producing medium be brought into the gas-liquid two-phase state.This causes that basically cold-producing medium flow into the first fixed restriction device 19a in the state of gas-liquid two-phase.As a result, the first fixed restriction device 19a can make the cold-producing medium decompression fully.
In addition, the cold-producing medium that flows out in the heat exchanger 19 sequentially flows to the mixing portion 16c of the second fixed restriction device 20, second evaporimeter 21 and injector 16 internally, be similar to first embodiment (just in Figure 10 sequentially from a J to a K, some L and some F).
As mentioned above, in the 5th embodiment, the first fixed restriction device 19a can make cold-producing medium suitably reduce pressure, and the enthalpy that flow into the cold-producing medium of second evaporimeter 21 thus can be lowered, thereby obtains and the same effect of first embodiment.
In addition, even the operating condition of cold-producing medium circulation is owing to the change of cooling load or similar load is fluctuateed, and the mass dryness fraction at the cold-producing medium in radiator 12 downstreams is changed, and the saturated liquid cold-producing medium on the saturated solution phase line also can flow to the first fixed restriction device 19a definitely.As a result, cold-producing medium can suitably and unchangeably be reduced pressure by the first fixed restriction device 19a, and the influence of the operating condition of the kind of refrigeration cycle in the not injected device refrigerant cycle device.
(the 6th embodiment)
In the 6th embodiment, as shown in figure 11, in the circulation of the cold-producing medium of second embodiment, increase the identical gas/liquid separative element 30 of structure of gas/liquid separative element 30 among its structure and the 5th embodiment, and in the liquid phase refrigerant container of gas/liquid separative element 30, be provided with component A.Those parts among other parts of this embodiment and second embodiment have same structure.The state of the cold-producing medium in the circulation of this embodiment is illustrated in the Mollier diagram of Figure 12.In Figure 12, use identical Reference numeral to represent and refrigerant condition identical shown in Fig. 4.
When the cold-producing medium of this embodiment circulation during, at the cold-producing medium at the component A place saturated liquid cold-producing medium of (in by a D " illustrate) on the saturated solution phase line as Figure 12 by running.In second embodiment, even become supercooled state or gas-liquid two-phase state at the cold-producing medium in the exit of radiator 12, the second fixed restriction device 20 also can suitably make the cold-producing medium decompression.
Like this, even when being branched cold-producing medium that part A separates is saturated liquid cold-producing medium on the saturated solution phase line, the second fixed restriction device 20 that is used as first decompressor also can suitably make the cold-producing medium decompression, obtains and second effect that embodiment is identical like this.
In addition, similar with the 5th embodiment, even the operating condition of cold-producing medium circulation is owing to the change of cooling load or similar load is fluctuateed, and the mass dryness fraction of the cold-producing medium of locating in the downstream of radiator 12 is changed, and the saturated liquid cold-producing medium on the saturated solution phase line also can flow to the first fixed restriction device 25 infalliblely.As a result, cold-producing medium can suitably and unchangeably be reduced pressure by the second fixed restriction device 20, and the operating condition of the circulation of the cold-producing medium in the not injected device refrigerant cycle device influences.
(the 7th embodiment)
In this embodiment, as shown in figure 13, in the circulation of the cold-producing medium of the 3rd embodiment, increase the identical gas/liquid separative element 30 of structure of gas/liquid separative element 30 among its structure and the 5th embodiment, and in the liquid phase refrigerant container of gas/liquid separative element 30, be provided with component A.Other parts of this embodiment can have same structure with those parts among the 3rd embodiment.The state of the cold-producing medium in the cold-producing medium circulation of this embodiment is shown in the Mollier diagram of Figure 14.In Figure 14, used same drawing reference numeral to represent the same refrigerant condition that goes out as shown in Figure 6.
When the cold-producing medium of this embodiment circulation during, at the cold-producing medium at the component A place saturated liquid cold-producing medium of (in by a D " illustrate) on the saturated solution phase line as Figure 14 by running.In the 3rd embodiment, even become supercooled state or gas-liquid two-phase state at the cold-producing medium in the exit of radiator 12, the first fixed restriction device 26a that is arranged in the inner heat exchanger 26 still can suitably make the cold-producing medium decompression.Like this, even when being branched cold-producing medium that part A separates and becoming saturated liquid cold-producing medium on the saturated solution phase line, can obtain equally and the 3rd the identical effect of embodiment.
In addition and the 5th embodiment similar, cold-producing medium can be set at suitably and the unchangeably decompression of the first fixed restriction device 26a in the inner heat exchanger 26, and the operating condition of not cooled dose circulation influences.
(the 8th embodiment)
In the 8th embodiment, as shown in figure 15, in the circulation of the cold-producing medium of the 4th embodiment, increase the identical gas/liquid separative element 30 of structure of gas/liquid separative element 30 among its structure and the 5th embodiment, and in the liquid phase refrigerant container of gas/liquid separative element 30, be provided with component A.Other parts of this embodiment can have same structure with those parts among the 4th embodiment.The operating condition of the cold-producing medium in the circulation of the 8th embodiment is shown in the Mollier diagram of Figure 16.In Figure 16, used same drawing reference numeral to represent the same refrigerant condition that goes out as shown in Figure 8.
When the cold-producing medium of this embodiment circulation during, at the cold-producing medium at the component A place cold-producing medium of (in by a D " illustrate) on the saturated solution phase line as Figure 14 by running.In the 8th embodiment, even become supercooled state or gas-liquid two-phase state at the cold-producing medium in the exit of radiator 12, the first fixed restriction device 19a of inner heat exchanger 19 still can suitably make the cold-producing medium decompression.Like this, even when being branched cold-producing medium that part A separates and becoming cold-producing medium on the saturated solution phase line, can obtain equally and above-mentioned the 4th the identical effect of embodiment.
In addition and the 5th embodiment similar, cold-producing medium can be by suitably and unchangeably decompression of the first fixed restriction device 19a of inner heat exchanger 19, and the operating condition of the cold-producing medium of not injected device refrigerant cycle device circulation influences.
(the 9th embodiment)
In second above-mentioned embodiment, the first fixed restriction device 25 is along the upstream that is set at the second fixed restriction device 20 from the cold-producing medium stream in the suction inlet side pipe road 14 that component A is shunted.In the 9th embodiment, as shown in figure 17, used a kind of variable restrictor mechanism 31 to substitute the first fixed restriction device 25 of second embodiment.Along with the increase in the degree of supercooling of the cold-producing medium at place, the downstream of radiator 12, this variable restrictor mechanism 31 is configured to reduce the coolant channel area.
For example, variable restrictor mechanism 31 is variable restrictor mechanisms of a kind of machinery, and adjust the extent of opening of valve body (not shown) according to temperature and pressure, thereby adjust flow by the cold-producing medium of variable restrictor mechanism 31 at the cold-producing medium in the exit of variable restrictor mechanism 31.Therefore, can adjust to predetermined gas-liquid two-phase state in the refrigerant condition in the exit of variable restrictor mechanism 31 with being determined.
More specifically, the valve body of variable restrictor mechanism 31 is connected on the diaphragm element 31a as pressure-responsive device.In addition, diaphragm element 31a comes the dislocation valve body according to the pressure that is filled gaseous mediums of responsive to temperature cylinder 31b (just according to the pressure in the temperature of the cold-producing medium in the exit of variable restrictor mechanism 31) with at the stress level of the cold-producing medium in the exit of variable restrictor mechanism 31, thereby adjust the extent of opening of valve body, wherein the stress level at the cold-producing medium in the exit of variable restrictor mechanism 31 is introduced in the balance pipe 31c.Other parts except variable restrictor mechanism 31 of this embodiment can have same structure with those parts among second embodiment.
Therefore, the state of the cold-producing medium in the running of the cold-producing medium of this embodiment circulation is shown as the identical Mollier diagram of Mollier diagram with second embodiment shown in Fig. 4 basically.In addition, in this embodiment, by variable restrictor mechanism 31, the cold-producing medium that flow into the second fixed restriction device 20 can be brought into the gas-liquid two-phase state with being determined, thereby obtains the effect identical with the effect of second embodiment definitely.
(the tenth embodiment)
In the 3rd above-mentioned embodiment, the second fixed restriction device 26b is arranged in the upstream of the first fixed restriction device 26a that is arranged on inner heat exchanger 26.Yet, in the tenth embodiment, as shown in figure 18, used variable restrictor mechanism 31 identical among a kind of and above-mentioned the 9th embodiment to substitute the second fixed restriction device 26 of the 3rd embodiment.In the cold-producing medium circulation of as shown in figure 18 the tenth embodiment, other part is similar to those parts of above-mentioned the 3rd embodiment.
Therefore, the state of the cold-producing medium in the running of the circulation of the tenth embodiment is shown as the identical Mollier diagram of Mollier diagram with the 3rd embodiment shown in Fig. 6 basically.In addition, in the tenth embodiment, by variable restrictor mechanism 31, the cold-producing medium that flow among the first fixed restriction device 26a of downstream part of variable restrictor mechanism 31 can be brought into the gas-liquid two-phase state with being determined, thereby obtains definitely and the identical effect of effect of the 3rd embodiment.
(the 11 embodiment)
In the 4th above-mentioned embodiment, the second fixed restriction device 27 is arranged in the upstream of the first fixed restriction device 19a that is arranged on inner heat exchanger 19.Yet, in the 11 embodiment, as shown in figure 19, used variable restrictor mechanism 31 identical among a kind of and above-mentioned the 9th embodiment to substitute the second fixed restriction device 27 of the 4th embodiment.In the cold-producing medium circulation of as shown in figure 19 the 11 embodiment, other part can be similar to those parts of above-mentioned the 4th embodiment.
Therefore, the state of the cold-producing medium in the running of the circulation of the 11 embodiment is shown as the identical Mollier diagram of Mollier diagram with the 4th embodiment shown in Fig. 8 basically.In addition, in the 11 embodiment, by variable restrictor mechanism 31, the cold-producing medium that flow among the first fixed restriction device 19a can be brought into the gas-liquid two-phase state with being determined, thereby obtains definitely and the identical effect of effect of the 4th embodiment.
(the 12 embodiment)
In the 12 embodiment, as shown in figure 20,, be used for separating the oil eliminator 11b of lubricating oil waste side being provided with of compressor 11 from cold-producing medium with respect to the structure of the cold-producing medium of first embodiment circulation.Oil eliminator 11b is arranged for the lubricating oil that is used for lubricate compressors 11 that is dissolved in the cold-producing medium is separated from cold-producing medium, and oil is turned back to the cold-producing medium suction side of compressor 11 via mechanism of decompressor 11c.
In addition, in this embodiment, gas/liquid separative element 30 is placed on the downstream of radiator 12.Gas/liquid separative element 30 and the gas/liquid separative element 30 that uses in the 5th to the 8th embodiment have same basic system.What should be noted that is that the liquid phase refrigerant container of the gas/liquid separative element 30 of this embodiment only is connected on first inner heat exchanger 24.Like this, in the liquid phase refrigerant container of the gas/liquid separative element 30 of the 12 embodiment, component A is not set.
First inner heat exchanger 24 of this embodiment has the structure same with the inner heat exchanger 24 of second embodiment, and the function that only has between the cold-producing medium at the liquid phase refrigerant at place, exchange gas/liquid separative element 30 downstreams and place, compressor 11 suction sides the heat of (more specifically, the cold-producing medium that passes through coolant channel) from the outlet side of first evaporimeter 17 to the suction inlet of compressor 11.In addition, the outlet of locating in the high-pressure side of first inner heat exchanger 24 that is used for liquid phase refrigerant is connected to variable restrictor mechanism 32.
Similar with first embodiment, be branched cold-producing medium stream that part A shunts and be fit to flow into nozzle segment side pipe road 13 and flow in the suction inlet side pipe road 14.Second inner heat exchanger 19 is set at the downstream of component A in the suction inlet side pipe road 14, and at the upstream side of second evaporimeter 21.
Therefore, in this embodiment, the fixed restriction device 19a (more specifically, being capillary) of second inner heat exchanger 19 has constituted to be used to make and has been branched cold-producing medium decompression that part A shunts and the decompressor that expands.
Similarly, variable restrictor mechanism 32 is set at the downstream of radiator 12 and the upstream side of component A, and has constituted and be used to make cold-producing medium decompression that flow into component A and the decompressor that expands.That is to say that variable restrictor mechanism 32 makes cold-producing medium decompression, with among the fixed restriction device 19a that flow into second inner heat exchanger 19 in ejector type refrigerating cycle device.
In addition, second inner heat exchanger 19 has constituted the refrigerant loses heat device of the heat that is used for dispersing cold-producing medium in the decompression and the expansion process of cold-producing medium together with fixed restriction device 19a.
In addition, in the 12 embodiment, as shown in figure 20, flow from first evaporimeter 17 at the compressor suction side cold-producing medium at place, the suction side of compressor 11 (the cold-producing medium that passes through coolant channel just), at first inner heat exchanger, 24 places and liquid phase refrigerant heat-shift at the place, downstream of gas/liquid separative element 30 from the outlet side of first evaporimeter 17 to the suction inlet of compressor 11.In addition, the compressor suction side cold-producing medium that flows out from first inner heat exchanger 24 is at second inner heat exchanger 19 and the cold-producing medium heat-shift of locating in the downstream of component A.Thereafter, compressor suction side cold-producing medium flows in the reservoir 18, being separated into gas phase and liquid phase, and vapor phase refrigerant is sucked in the compressor 11.
Can understand, the coolant channel that makes cold-producing medium be sucked into compressor 11 is not limited to the structure that is made of the element of being placed with the order among above-mentioned Figure 20, and can have any component structure of placing in proper order with any other.For example, to be sucked into the cold-producing medium of compressor 11 can be at first at second inner heat exchanger, 19 places from first evaporimeter 17 flow, with cold-producing medium heat-shift in the downstream of component A, the liquid phase refrigerant heat-shift that can locate in first inner heat exchanger, 24 places and gas/liquid separative element 30 downstreams then.Thereafter, cold-producing medium can flow in the reservoir 18.Other parts of the 12 embodiment can have same structure with those parts among first embodiment.
Next, below with reference to the Mollier diagram among Figure 21 the running of cold-producing medium circulation of the 12 embodiment and the operating condition of the cold-producing medium in this circulation are described.In Figure 21, used same drawing reference numeral to represent and the identical cold-producing medium operating condition of operating condition described in the foregoing description.
At first, when the cold-producing medium circulation of this embodiment was turned round, the cold-producing medium that is discharged out from compressor 11 (as being illustrated by a C among Figure 21) was cooled off by radiator 12, and is separated into vapor phase refrigerant and liquid phase refrigerant by gas/liquid separative element 30.Like this, the liquid phase refrigerant at gas/liquid separative element 30 places is by a D in Figure 21 " saturated liquid cold-producing medium on the saturated solution phase line that illustrates.
The liquid phase refrigerant that flows out from gas/liquid separative element 30 flow in first inner heat exchanger 24, with the cold-producing medium heat-shift at compressor 11 suction sides places, with distribute heat, cold-producing medium is brought into supercooled state (the some D from Figure 21 " to putting an O) thus.In addition, the liquid phase refrigerant that flows out from first inner heat exchanger 24 in supercooled state is become gas-liquid two-phase state (the some O from Figure 21 is to a Q) by 32 decompressions of variable restrictor mechanism.
Be branched part A by the gas-liquid two-phase cold-producing medium of variable restrictor mechanism 32 decompressions and be divided into two streams, one of them sequentially flow into nozzle segment side pipe road 13, then from the nozzle segment 16a of injector 16 to mixing portion 16c, diffusion part 16d and first evaporimeter 17 (among Figure 21 sequentially from a Q to an E, some F, some G and some H).
The cold-producing medium that flows out from first evaporimeter 17 at first flow in first inner heat exchanger 24, with the liquid phase refrigerant heat-shift (the some H from Figure 21 is to an I) that flows out from gas/liquid separative element 30.Then, the cold-producing medium that is inhaled into compressor 11 is flow in second inner heat exchanger 19, with the high-pressure refrigerant heat-shift that flows to suction inlet side pipe road 14 from component A, to flow into (the some I from Figure 21 is to a R) in the reservoir 18.And the vapor phase refrigerant that comes from reservoir 18 is by compressor 11 inspirations and by compression once more (the some R among Figure 21 is to some C).
On the other hand, the cold-producing medium the gas-liquid two-phase state that flows to suction inlet side pipe road 14 from component A flow in second inner heat exchanger 19.And be depressurized during the fixed restriction device 19a of the cold-producing medium in flowing into second inner heat exchanger 19 by second inner heat exchanger 19 and expand, simultaneously and the cold-producing medium heat-shift at place, compressor 11 suction sides, with distribute heat (in Figure 21 sequentially from a Q to a S ' and put S).
Here, because cold-producing medium in the gas-liquid two-phase state flow among the fixed restriction device 19a, therefore, the cold-producing medium throttling arrangement 19a that can be fixed suitably reduces pressure.Even be noted that the line from a S ' to a S of Figure 21, because identical with the 3rd embodiment, the cold-producing medium by fixed restriction device 19a expands in the mode of constant entropy basically.
Similar with above-mentioned first embodiment, the cold-producing medium that flows to second evaporimeter 21 absorbs the heat of the air that blows out from air blast 17a and evaporates, wherein said cold-producing medium is by 17 coolings of first evaporimeter, being evaporated among the refrigerant suction port 16b that cold-producing medium is sucked into injector 16 in second evaporimeter 21 then, indrawn thus cold-producing medium are mixed (from Figure 21 mid point S to a L and some F) in mixing portion 16c with the liquid phase refrigerant by nozzle segment 16a.
As mentioned above, in this embodiment, variable restrictor mechanism 32 allows the cold-producing medium in the gas-liquid two-phase state at place, downstream to flow among the fixed restriction device 19a, thereby suitably makes the cold-producing medium decompression at fixed restriction device 19a place.The cold-producing medium evaporating temperature of first evaporimeter 17 and second evaporimeter 21 can be set in the different temperature ranges with being determined, and second evaporimeter 21 can apply sufficient refrigerating capacity.
In addition, in fixed restriction device 19a, shown in many straight lines from a Q to a S of the Mollier diagram of Figure 21, because the cold-producing medium of locating in the downstream of component A is depressurized and expands, and while distribute heat, therefore, the pressure of cold-producing medium can be lowered, and the enthalpy of cold-producing medium can be lowered simultaneously.The enthalpy difference (refrigerating capacity) that this can increase the refrigerant inlet and the cold-producing medium between the outlet of second evaporimeter 21 makes cycle efficieny be enhanced.
In addition, because the cold-producing medium circulation is provided with variable restrictor mechanism 32, be used for coming from the cold-producing medium stream of radiator 12, make cold-producing medium decompression and expansion at the upstream side place of component A, therefore, the operating state that flow into the cold-producing medium of component A can be stabilized at an easy rate.Therefore, according to present embodiment, the cold-producing medium that flow into component A is stabilized to the gas-liquid two-phase state, and this can suitably make the cold-producing medium decompression by fixed restriction device 19a, and is not influenced by the operating condition of the circulation of the cold-producing medium in ejector type refrigerating cycle device.
(the 13 embodiment)
In the 12 above-mentioned embodiment, used second inner heat exchanger 19, be used to exchange the heat between the cold-producing medium at the cold-producing medium at place, component A downstream and place, compressor 11 suction sides.In this embodiment, as shown in figure 22, use second inner heat exchanger 33, be used to exchange the heat between the cold-producing medium that flow into cold-producing medium before second evaporimeter 21 and place, second evaporimeter, 21 downstreams at place, component A downstream.
Second inner heat exchanger 33 have with the 12 embodiment in the similar structure of basic structure of second inner heat exchanger 19.Like this, the coolant channel of second inner heat exchanger 33 at place, component A downstream is formed (particularly by fixed restriction device 33a, be capillary), second inner heat exchanger 33 has constituted the refrigerant loses heat device in ejector type refrigerating cycle device simultaneously.
In addition, second inner heat exchanger 33 be used for exchanging component A the place, downstream the place, downstream that flow into the cold-producing medium before second evaporimeter 21 and second evaporimeter 21 pass through heat between second evaporimeter 21 cold-producing medium afterwards.Like this, in this embodiment, as shown in figure 22, the cold-producing medium that flows out from first evaporimeter 17 is at the liquid phase refrigerant heat-shift of first inner heat exchanger 24 with the place, downstream of gas/liquid separative element 30, then, flow in the reservoir 18 and be sucked into compressor 11 to be separated into gas phase and liquid phase refrigerant, this has constituted coolant channel.Those parts among other parts of the 13 embodiment and the 12 embodiment have same structure.
Next, below with reference to the Mollier diagram among Figure 23 the running of cold-producing medium circulation of the 13 embodiment and the operating condition of the cold-producing medium in this circulation are described.In Figure 23, used same drawing reference numeral to represent the refrigerant condition substantially the same with the refrigerant condition shown in the foregoing description.
At first, similar with the 12 embodiment, when the cold-producing medium circulation of the 13 embodiment is turned round, the cold-producing medium that is discharged out from compressor 11 is cooled off by radiator 12, sequentially flow to then first coolant channel of gas/liquid separative element 30, first inner heat exchanger 24 and variable restrictor mechanism 32, be brought into the gas-liquid two-phase state (in Figure 23 sequentially from a C to a D ", some O and some Q).
Be branched part A by the gas-liquid two-phase cold-producing medium of variable restrictor mechanism 32 decompressions and be divided into two streams, one of them sequentially flows to nozzle segment side pipe road 13, then from the nozzle segment 16a of injector 16 to mixing portion 16c, diffusion part 16d and first evaporimeter 17 (among Figure 21 sequentially from a Q to an E, some F, some G and some H).
The cold-producing medium that flows out from first evaporimeter 17 flow in second coolant channel of first inner heat exchanger 24, with the liquid phase refrigerant heat-shift that from gas/liquid separative element 30, flows out, so that be introduced in (the some H from Figure 23 is to an I) in the reservoir 18.And vapor phase refrigerant is sucked into and is compressed (the some I Figure 23 to some a C) by compressor 11 once more from reservoir 18.
On the other hand, the cold-producing medium the gas-liquid two-phase state that flows to suction inlet side pipe road 14 from component A flows in second inner heat exchanger 33.Flow into cold-producing medium second inner heat exchanger 33 from component A and be depressurized and expand, simultaneously when the fixed restriction device 33a by second inner heat exchanger 33 and the cold-producing medium heat-shift at the place, downstream of second evaporimeter 21 come distribute heat (in Figure 23 sequentially from a Q to a T ' and put T).At this moment, the enthalpy of the cold-producing medium of locating in the downstream of second evaporimeter 21 has increased (the some L from Figure 23 is to a L ').
Here, because cold-producing medium in the gas-liquid two-phase state flow into the fixed restriction device 33a from component A, therefore, fixed restriction device 33a can make the cold-producing medium that flow into before second evaporimeter 21 suitably reduce pressure.Be noted that because identical with above-mentioned the 3rd embodiment, the cold-producing medium by fixed restriction device 33a expands in the mode of constant entropy basically shown in the straight line from a T ' to some T of Figure 23.
In addition, be similar to the 12 embodiment, the cold-producing medium that flow into second evaporimeter 21 is sucked among the refrigerant suction port 16b of injector 16, and mixes (in Figure 21 sequentially from a T to a L ' and some F) in mixing portion 16c with the liquid phase refrigerant by nozzle segment 16a.In addition, in the 13 embodiment, the cold-producing medium that flows out from second evaporimeter 21 by second inner heat exchanger 33 and with the gas-liquid two-phase cold-producing medium heat-shift of fixed restriction device 33a by second inner heat exchanger 21 after, be sucked among the suction inlet 16b of injector 16.Therefore, can be reduced at the enthalpy of the cold-producing medium at the outlet side place of second evaporimeter 21, thereby increase the refrigerant outlet side of second evaporimeter 21 and the difference of the enthalpy between the refrigerant inlet side.
As mentioned above, in the 13 embodiment, variable restrictor mechanism 32 makes the cold-producing medium gas-liquid two-phase state that reduces pressure, and the cold-producing medium that is depressurized of variable restrictor mechanism 32 is introduced among the 33a of fixed restriction mechanism after being branched the part A shunting.Therefore, the cold-producing medium of locating in the downstream of component A is by the 33a of fixed restriction mechanism of second inner heat exchanger 33 decompression and expand while distribute heat in second inner heat exchanger 33, thereby acquisition and the 12 effect that embodiment is identical.
(other embodiment)
The invention is not restricted to the embodiments described, and can do following different modification to embodiment:
(1) in each embodiment except second, the 6th and the 9th above-mentioned embodiment, capillary 19a, 26a, 33a are used as the fixed restriction device, and capillary 19a, 26a, 33a are by hard solder to the refrigerant tubing in inner heat exchanger (just, to carry out the heat exchange refrigerant pipeline of heat exchange with capillary 19a, 26a, 33a) on, thereby constitute the refrigerant loses heat device, be used for distributing the heat of the cold-producing medium of inner heat exchanger in decompression and expansion process.Particularly, capillary 19a, 26a, 33a and being connected of heat exchange refrigerant pipeline in inner heat exchanger can realize in the following manner.
For example, each capillary 19a, 26a, 33a can be arranged on the peripheral surface of heat exchange refrigerant pipeline as the crow flies along the axis direction of the heat exchange refrigerant pipeline in inner heat exchanger, and capillary 19a, 26a, 33a and heat exchange refrigerant pipeline can be had an excellent heat conductivity in inner heat exchanger metal bond material is connected integratedly.As the metal bond material, can use soft soldering or hard solder to fill metal.In addition, the peripheral surface that may be arranged to around the heat exchange refrigerant pipeline in each inner heat exchanger of capillary 19a, 26a, 33a twines in the mode of spiral.
The Zone Full of each capillary 19a, 26a, 33a does not need to be connected on the heat exchange refrigerant pipeline in inner heat exchanger, and the part of each capillary 19a, 26a, 33a can be connected on the heat exchange refrigerant pipeline in inner heat exchanger.In other words, though each capillary 19a, 26a, 33a are not connected to zone on the heat exchange refrigerant pipeline in the inner heat exchanger and can only be used to make the cold-producing medium decompression and expand, the zone on the heat exchange refrigerant pipeline that is connected to inner heat exchanger of each capillary 19a, 26a, 33a can be used for distributing in decompression and expansion process the heat of cold-producing medium.
In addition, shown in the whole allocation plan of above-mentioned embodiment, as inner heat exchanger, used a kind of reverse-flow heat exchange structure, wherein the flow direction of the cold-producing medium by capillary 19a, 26a, 33a is opposite with the flow direction of the cold-producing medium of the heat exchange refrigerant pipeline of locating by compressor 11 suction sides, has improved the efficient of heat exchange thus.
(2) in each embodiment except second, the 6th and the 9th above-mentioned embodiment, used inner heat exchanger 19,26 and 33 as the refrigerant loses heat device, but the refrigerant loses heat device is not limited to these.
For example, can be provided for being blown into the air blast of cooling air towards fixed restriction device (capillary) 19a, 26a, the 33a of inner heat exchanger 19,26,33, air that is blown into by air blast and cold-producing medium heat-shift thus by fixed restriction device 19a, 26a, 33a, thus make cold-producing medium distribute heat by fixed restriction device 19a, 26a, 33a.
(3) in the 6th to the 8th above-mentioned embodiment, be provided with gas/liquid separative element 30.Yet, in the circulation of cold-producing medium in the 6th to the 8th embodiment and the 9th to the 11 embodiment similar, can use variable restrictor mechanism 31.
Thus, the saturated liquid cold-producing medium on the saturated solution phase line flow in the variable restrictor mechanism 31, can improve when making cold-producing medium reduce pressure the gas-liquid two-phase state controllability to cold-producing medium like this.This can guarantee easily to allow cold-producing medium to enter into the gas-liquid two-phase state before flowing into next decompressor.
(4) in the 9th to the 11 above-mentioned embodiment, used the variable restrictor mechanism 31 that is configured with mechanical variable restrictor mechanism, and the extent of opening of valve is adjusted by the temperature and pressure that detects at the cold-producing medium in the exit of variable restrictor mechanism 31.Yet, can be detected at the temperature and pressure of the cold-producing medium in the exit of radiator 21, so that be adjusted at the extent of opening of the valve in the variable restrictor mechanism 31.Alternatively, can use the electronic variable throttle mechanism as variable restrictor mechanism 31.
(5) though the above-mentioned the 12 and the 13 embodiment in, as an example, be provided with the oil eliminator 11b that is used for isolating lubricating oil from cold-producing medium in the suction side of compressor 11, but be appreciated that oil eliminator 11b and mechanism of decompressor 11c can be applied in the cold-producing medium circulation of the first to the 11 each embodiment among the embodiment.
(6) in the above-described embodiment, variable restrictor mechanism 15 is placed on the upstream side of the nozzle segment 16a of injector 16, and adjusts the refrigerant flow Ge flow into suction side pipeline 14 for the flow rate ratio η that flow into the refrigerant flow Gnoz in nozzle segment side pipe road 13 from component A (η=Ge/Gnoz).Yet, can use a kind of changeable flow formula injector, wherein variable restrictor mechanism 15 is cancelled, and can be electronically and/or mechanically change the area of the coolant channel of nozzle segment 16a.
In this case, for example, structure by first embodiment, can detect degree of superheat at the cold-producing medium in the exit of second evaporimeter 21, and can control the extent of opening in the coolant channel zone of nozzle segment 16a, make degree of superheat at the cold-producing medium in the exit of second evaporimeter 21 in preset range.
(7) in the above-described embodiment, first evaporimeter 17 is positioned for cooling off identical space with second evaporimeter 21.Yet, will by the space of first evaporimeter 17 cooling can with will be different by the space of second evaporimeter, 21 coolings.For example, can use first evaporimeter 17, be used for the air conditioning in vehicle chamber, and can use second evaporimeter 21, be used to be arranged on the refrigerator in the vehicle chamber.Similarly, the present invention can be applied to a kind of cold-producing medium circulation, and this cold-producing medium circulation only applies the cooling action by second evaporimeter 21, and has cancelled first evaporimeter 17 therefrom.That is to say that in each cold-producing medium circulation of ejector type refrigerating cycle device, first evaporimeter 17 of Miao Shuing can be omitted in the above-described embodiments.In addition, in each cold-producing medium circulation of ejector type refrigerating cycle device, the reservoir 18 of Miao Shuing can be omitted in the above-described embodiments.
(8) in the above-described embodiment, first evaporimeter 17 and second evaporimeter 21 be used to cool off the space that will be cooled, and radiator 12 are used for heat is dispersed into air as outdoor heat exchanger as indoor heat exchanger.On the contrary, the present invention can be applied to heat pump cycle, wherein first evaporimeter 17 and second evaporimeter 21 are as outdoor heat converter, be used for absorbing heat from thermal source, for example outdoor air, and radiator 12 is used for heating and wants heated fluid, air that for example is supplied or water as indoor heat converter.
It should be understood that such change and modification drop on by in the defined protection domain of the present invention of appended claim.
Claims (24)
1. ejector type refrigerating cycle device comprises:
Compressor (11), this compressor are used for compression and refrigerant emission;
Radiator (12), this radiator are used for distributing the heat of the high-temperature high-pressure refrigerant of discharging from compressor;
The cold-producing medium diverting flow that component (A), this component are used for the radiator downstream is first a fluid stream and second a fluid stream;
Injector (16), the high velocity stream inspiration of the cold-producing medium that suction part (16a) and refrigerant suction port (16b) that this injector comprises the cold-producing medium decompression that is used to make first a fluid stream that comes from component and expands, cold-producing medium are ejected from nozzle segment by described refrigerant suction port (16b);
(33a), this decompressor is used to make the cold-producing medium decompression of second a fluid stream that comes from component and expands decompressor for 19a, 26a;
Evaporimeter (21), this evaporimeter are used to evaporate the cold-producing medium in the decompressor downstream, and described evaporimeter has the refrigerant outlet of the refrigerant suction port that is coupled to injector; And
Refrigerant loses heat device (19,26,33), when decompressor made the cold-producing medium decompression and expands, this refrigerant loses heat device was used to distribute the heat of cold-producing medium.
2. ejector type refrigerating cycle device according to claim 1, wherein, the refrigerant loses heat device is the inner heat exchanger (19,26,33) that is used to exchange the cold-producing medium by decompressor and will be drawn to the heat between the cold-producing medium of compressor.
3. ejector type refrigerating cycle device according to claim 2, wherein, described decompressor comprises the capillary that is arranged in the inner heat exchanger.
4. ejector type refrigerating cycle device according to claim 1 also comprises:
Gas/liquid separative element (30), this gas/liquid separative element is used for the cold-producing medium in the radiator downstream is separated into vapor phase refrigerant and liquid phase refrigerant,
Wherein, component will be divided into first a fluid stream and second a fluid stream by the liquid phase refrigerant that the gas/liquid separative element separates.
5. according to the described ejector type refrigerating cycle device of each claim among the claim 1-4, wherein, described decompressor as the first decompression part (33a), described ejector type refrigerating cycle device also comprises for 19a, 23a:
The second decompression part (26b, 27,31), this second decompression part is used to make the cold-producing medium decompression of second a fluid stream that comes from component,
Wherein, the second decompression part is positioned at the downstream of component and the position of the first decompression upstream partly, and, make the cold-producing medium decompression of second a fluid stream in the gas-liquid two-phase state, that distribute from component along the upstream side place of the cold-producing medium of second a fluid stream stream in the first decompression part.
6. according to the described ejector type refrigerating cycle device of each claim in the claim 14, wherein, described decompressor as the first decompression part (33a), described ejector type refrigerating cycle device also comprises for 19a, 23a:
The second decompression part (32), this second decompression part is used to make the cold-producing medium decompression that comes from radiator,
Wherein, the second decompression part is positioned at the upstream of component and the location downstream of radiator along cold-producing medium stream, and makes the cold-producing medium decompression in the gas-liquid two-phase state.
7. ejector type refrigerating cycle device according to claim 6, wherein, the second decompression part is variable restrictor mechanism (32), when the degree of supercooling of the cold-producing medium at place, radiator downstream increased, this variable restrictor mechanism reduced its throttling passage area.
8. according to the described ejector type refrigerating cycle device of each claim among the claim 1-4, wherein, described decompressor as the first decompression part (33a), described ejector type refrigerating cycle device also comprises for 19a, 23a:
The second decompression part (20), this second decompression part is used to make the cold-producing medium decompression of having been reduced pressure by the first decompression part,
Wherein, the position of the downstream that described second reduces pressure partly is positioned at the first decompression part and the upstream of radiator, and
Wherein, the first decompression part at the upstream side place of the second decompression part, makes the cold-producing medium decompression of second a fluid stream in the gas-liquid two-phase state, that distribute from component along the cold-producing medium stream of second a fluid stream.
9. according to the described ejector type refrigerating cycle device of each claim among the claim 1-4, also comprise:
Another evaporimeter (17), this evaporimeter are positioned at the refrigerant outlet side of injector, are used to evaporate the cold-producing medium that flows out from injector; And
Reservoir (18), this reservoir are positioned the refrigerant outlet side of another evaporimeter,
Wherein, reservoir has the vapor phase refrigerant outlet of the cold-producing medium suction side that is connected to compressor.
10. ejector type refrigerating cycle device according to claim 9,
Wherein, heat abstractor is an inner heat exchanger (19,26,33), the cold-producing medium that the cold-producing medium that this inner heat exchanger has second a fluid stream that comes from component flows through the first coolant channel part wherein and comes from the vapor phase refrigerant outlet of reservoir flows through the second coolant channel part wherein towards the cold-producing medium suction side of compressor.
11. an ejector type refrigerating cycle device comprises:
Compressor (11), this compressor are used for compression and refrigerant emission;
Radiator (12), this radiator are used for distributing the heat of the high-temperature high-pressure refrigerant of discharging from compressor;
The cold-producing medium diverting flow that component (A), this component are used for the radiator downstream is first a fluid stream and second a fluid stream;
Injector (16), this injector comprises cold-producing medium decompression that is used to make first a fluid stream that comes from component and nozzle segment (16a) and the refrigerant suction port (16b) that expands, the high velocity stream inspiration of the cold-producing medium that cold-producing medium is ejected from nozzle segment from described refrigerant suction port;
First decompressor (32), this first decompressor are used to make cold-producing medium decompression and the expansion from second a fluid stream of component shunting;
Evaporimeter (21), this evaporimeter are used to evaporate the cold-producing medium in the downstream of first decompressor, and described evaporimeter has the refrigerant outlet of the refrigerant suction port that is coupled to injector; And
Second decompressor, this second decompressor is positioned at the downstream of component and the upstream of first decompressor along the cold-producing medium stream of second a fluid stream, is used for making the cold-producing medium decompression at second a fluid stream of gas-liquid two-phase state.
12. ejector type refrigerating cycle device according to claim 11 also comprises:
Inner heat exchanger (19,26), this inner heat exchanger have be provided with first decompressor (19a, first coolant channel part 26a) and the cold-producing medium that will be drawn to compressor flow through the second coolant channel part wherein,
Wherein, first coolant channel part and the second coolant channel part of inner heat exchanger is set, flows through the cold-producing medium of first coolant channel part and flow through heat exchange between second coolant channel cold-producing medium partly with execution.
13. ejector type refrigerating cycle device according to claim 11, wherein, described first decompressor comprises capillary.
14. ejector type refrigerating cycle device according to claim 12, wherein, first decompressor is arranged on the capillary in first coolant channel of inner heat exchanger.
15. ejector type refrigerating cycle device according to claim 11,
Wherein, second decompressor is a variable restrictor mechanism, and when the degree of supercooling of the cold-producing medium at radiator downstream place increased, this variable restrictor mechanism reduced its throttling passage area.
16., also comprise according to the described ejector type refrigerating cycle device of each claim among the claim 11-15:
Gas/liquid separative element (30), this gas/liquid separative element are used for the cold-producing medium in radiator downstream is separated into vapor phase refrigerant and liquid phase refrigerant,
Wherein, component will be divided into first a fluid stream and second a fluid stream by the liquid phase refrigerant that the gas/liquid separative element separates.
17. an ejector type refrigerating cycle device comprises:
Compressor (11), this compressor are used for compression and refrigerant emission;
Radiator (12), this radiator are used for distributing the heat of the high-temperature high-pressure refrigerant of discharging from compressor;
Component (A), this component are used for the cold-producing medium at place, radiator downstream is split into first a fluid stream and second a fluid stream;
Injector (16), this injector comprises cold-producing medium decompression that is used to make first a fluid stream that comes from component and nozzle segment (16a) and the refrigerant suction port (16b) that expands, the high velocity stream inspiration of the cold-producing medium that cold-producing medium is ejected from nozzle segment from described refrigerant suction port;
First decompressor (19a, 33a), this first decompressor is used to make the cold-producing medium decompression of second a fluid stream that comes from component and expands;
Evaporimeter (21), this evaporimeter are used to evaporate the cold-producing medium at place, decompressor downstream, and described evaporimeter has the refrigerant outlet of the refrigerant suction port that is coupled to injector;
Refrigerant loses heat device (19,33), when first decompressor made the cold-producing medium decompression and expands, this refrigerant loses heat device was used to distribute the heat of cold-producing medium; And
Second decompressor (32), this second decompressor is positioned at the downstream of radiator and the upstream of component along cold-producing medium stream, is used to make the cold-producing medium decompression from radiator.
18. ejector type refrigerating cycle device according to claim 17, wherein, the refrigerant loses heat device is inner heat exchanger (19), the exchange of this inner heat exchanger by first decompressor (19) cold-producing medium and will be sucked into heat between the cold-producing medium of compressor.
19. ejector type refrigerating cycle device according to claim 17, wherein, the refrigerant loses heat device is inner heat exchanger (33), the exchange of this inner heat exchanger by first decompressor (33a) cold-producing medium and the heat between the cold-producing medium that from evaporimeter, flows out.
20. according to the described ejector type refrigerating cycle device of each claim among the claim 17-19, wherein, first decompressor comprise capillary (19a, 33a).
21. an ejector type refrigerating cycle device comprises:
Compressor (11), this compressor are used for compression and refrigerant emission;
Radiator (12), this radiator are used for distributing the heat of the high-temperature high-pressure refrigerant of discharging from compressor;
Component (A), this component are used for the cold-producing medium in radiator downstream is split into first a fluid stream and second a fluid stream;
Injector (16), this injector comprises cold-producing medium decompression that is used to make first a fluid stream that comes from component and nozzle segment (16a) and the refrigerant suction port (16b) that expands, the high velocity stream inspiration of the cold-producing medium that cold-producing medium is ejected from nozzle segment from described refrigerant suction port;
(33a), this first decompressor makes the cold-producing medium decompression of second a fluid stream that comes from component and expands first decompressor for 19a, 26a;
Evaporimeter (21), this evaporimeter are used to evaporate the cold-producing medium at the place, downstream of the first decompression part, and described evaporimeter has the refrigerant outlet of the refrigerant suction port that is coupled to injector;
Inner heat exchanger (19,26,33), the cold-producing medium that this inner heat exchanger has second a fluid stream that comes from component flows through the first coolant channel part wherein, with flow through wherein the second coolant channel part at the cold-producing medium of the downstream part of the refrigerant outlet of injector towards compressor
Wherein, first coolant channel part and the second coolant channel part are set in inner heat exchanger, flow through the cold-producing medium of first coolant channel part and flow through heat exchange between second coolant channel cold-producing medium partly with execution; And
Wherein, first coolant channel of inner heat exchanger partly is provided with the first decompression part.
22. ejector type refrigerating cycle device according to claim 21 also comprises:
The second decompression part (32), this second decompression part is positioned at the downstream of radiator and the upstream portion office of component along cold-producing medium stream, is used to make the cold-producing medium decompression from radiator.
23. ejector type refrigerating cycle device according to claim 21 also comprises:
Second reduces pressure partly (26b, 27,31), and this second decompression part is positioned at the downstream of component and the part place of the first decompression upstream partly, is used to make the cold-producing medium of second a fluid stream that comes from component to reduce pressure.
24. ejector type refrigerating cycle device according to claim 21 also comprises:
The second decompression part (20), this second decompression part are positioned at the part place of the upstream of the downstream of the first decompression part and evaporimeter, the cold-producing medium decompression that is used to make first coolant channel of heat exchanger internally partly to flow out.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006005847 | 2006-01-13 | ||
| JP2006005847 | 2006-01-13 | ||
| JP2006214404 | 2006-08-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101078570A true CN101078570A (en) | 2007-11-28 |
| CN100543381C CN100543381C (en) | 2009-09-23 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2007100023658A Expired - Fee Related CN100543381C (en) | 2006-01-13 | 2007-01-15 | Ejector type refrigerating cycle device |
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| Country | Link |
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| CN (1) | CN100543381C (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102706047A (en) * | 2011-03-28 | 2012-10-03 | 株式会社电装 | Refrigerant distributor and refrigeration cycle device |
| CN104903594A (en) * | 2012-12-27 | 2015-09-09 | 株式会社电装 | Ejector |
| CN110505968A (en) * | 2017-04-18 | 2019-11-26 | 三电汽车空调系统株式会社 | Vehicle air attemperation apparatus |
| CN116538699A (en) * | 2023-04-18 | 2023-08-04 | 西安交通大学 | CO (carbon monoxide) 2 Two-stage compression double-temperature refrigerating system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104807242B (en) * | 2015-05-06 | 2017-03-29 | 西安交通大学 | A kind of steam compressed combined cycle system of household freezer based on the supercool potentiation of quasiconductor |
-
2007
- 2007-01-15 CN CNB2007100023658A patent/CN100543381C/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102706047A (en) * | 2011-03-28 | 2012-10-03 | 株式会社电装 | Refrigerant distributor and refrigeration cycle device |
| CN102706047B (en) * | 2011-03-28 | 2015-01-14 | 株式会社电装 | Refrigerant distributor and refrigeration cycle device |
| US9239178B2 (en) | 2011-03-28 | 2016-01-19 | Denso Corporation | Refrigerant distributor and refrigeration cycle device |
| CN104903594A (en) * | 2012-12-27 | 2015-09-09 | 株式会社电装 | Ejector |
| CN110505968A (en) * | 2017-04-18 | 2019-11-26 | 三电汽车空调系统株式会社 | Vehicle air attemperation apparatus |
| CN110505968B (en) * | 2017-04-18 | 2023-03-28 | 三电有限公司 | Air conditioner for vehicle |
| CN116538699A (en) * | 2023-04-18 | 2023-08-04 | 西安交通大学 | CO (carbon monoxide) 2 Two-stage compression double-temperature refrigerating system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100543381C (en) | 2009-09-23 |
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