CN102444626A - Jet pump and air conditioner - Google Patents
Jet pump and air conditioner Download PDFInfo
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- CN102444626A CN102444626A CN2011102942009A CN201110294200A CN102444626A CN 102444626 A CN102444626 A CN 102444626A CN 2011102942009 A CN2011102942009 A CN 2011102942009A CN 201110294200 A CN201110294200 A CN 201110294200A CN 102444626 A CN102444626 A CN 102444626A
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Abstract
A jet pump includes a discharge outlet (51a) configured to discharge refrigerant in which relatively high pressure refrigerant and relatively low pressure refrigerant are mixed, a diffuser (55) disposed coaxially with the discharge outlet in an upstream side of the discharge outlet, the diffuser including an inside diameter which gradually reduces in size away from the discharge outlet (51a), a suction hole (52e) following from a minimum diameter portion of the diffuser (55) and to which the lower pressure refrigerant is guided, a high pressure refrigerant path (53) configured to guide the high pressure refrigerant to the diffuser (55), and a nozzle portion (59); configured to eject the high pressure refrigerant from the high pressure refrigerant path (53) into the diffuser (55) in a downstream side of the minimum diameter portion. Through the high pressure refrigerant which is sprayed from the nozzle portion (59), a driving flow which sucks the low pressure refrigerant from the suction hole (52e) is sucked into the diffuser (55), and the low pressure refrigerant is sucked into the diffuser (55).
Description
Technical field
The present invention relates to jet pump and used the aircondition of jet pump.
Background technique
In the past; In air conditioner for vehicles, known have between the radiator of refrigeration cycle and vaporizer, replace expansion valve and sparger be set, improve compressor the suction side pressure and seek to improve the efficient of compressor; And the refrigeration in the raising vaporizer (for example, with reference to patent documentation 1).
This sparger has the injector body spray nozzle part inboard with being arranged on injector body of tubulose.In this injector body; Be provided with successively along the flow direction of refrigeration agent gradually the shape of undergauge restriction, with the mixer of the continuous thin tube-like of the minimum path portion of this restriction, towards the downstream direction diffuser of hole enlargement (diffuser) gradually; The upper reaches in restriction dispose spray nozzle part, between the periphery of the front end of spray nozzle part and restriction, are formed with suction section.In addition, the vapor phase refrigerant of having passed through expansion valve and the 1st vaporizer is directed to suction section from pump port, and on the other hand, liquid phase refrigerant is directed to spray nozzle part from compressor via radiator.
Thereby; The liquid phase refrigerant that constitutes from compressor ejects and puffing from spray nozzle part; Thereby from the vapor phase refrigerant that the suction section of the periphery of spray nozzle part aspirates from evaporator drier, two refrigeration agents mix in mixer, further; After refrigeration agent slows down based on the hole enlargement shape of diffuser and boosts, passed out to the 2nd vaporizer.
Patent documentation 1: TOHKEMY 2005-308384 communique
But, in above-mentioned technology in the past and since sparger be in the downstream of spray nozzle part vertically arranged in series the structure of restriction, mixer, diffuser, therefore become the long shape of axial dimension, cause maximizing.Therefore, the restriction that when as patent documentation 1, being installed in this sparger and two vaporizer one on the aircondition, cause in two vaporizers, the installation direction of sparger is restricted etc. is installed painstakingly.
Summary of the invention
The present invention be conceived to above-mentioned in the past problem and make, its purpose is to provide a kind of small-sized jet pump that is installed on the aircondition that is beneficial to.
In order to achieve the above object; Technological scheme 1 described invention is a kind of jet pump; It is characterized in that; This jet pump has the pump main body that is formed with ejiction opening, diffuser, suction bole coaxially, and this ejiction opening is used to spray the refrigeration agent after the refrigerant mixed of refrigeration agent and relatively low pressure of relatively high pressure; This diffuser is configured in the upper reaches of this ejiction opening, and its internal diameter is along with dwindling gradually away from above-mentioned ejiction opening; This suction bole and the upper reaches of the minimum path portion of this diffuser dispose and are used to guide the refrigeration agent of above-mentioned low pressure mutually continuously; This pump main body has the spray nozzle part that is used for spraying in above-mentioned diffuser from the high-pressure refrigerant path of the refrigeration agent that is used to guide above-mentioned high pressure the refrigeration agent of above-mentioned high pressure on the inner peripheral surface of above-mentioned diffuser; Through spray the refrigeration agent of above-mentioned high pressure from said nozzle portion; Be formed for the refrigeration agent of above-mentioned low pressure is drawn into the driving stream in the above-mentioned diffuser from above-mentioned suction bole, so that the refrigeration agent of above-mentioned low pressure is sucked in the above-mentioned diffuser.
In addition, according to technological scheme 1 described jet pump, technological scheme 2 described inventions are characterised in that, the said pump main body in above-mentioned diffuser and the above-mentioned ejiction opening side position of said nozzle portion have vertically internal diameter constant help stream portion.
According to technological scheme 1 or technological scheme 2 described jet pumps; Technological scheme 3 described inventions are characterised in that; The said pump main body has the nozzle outer member and the nozzle inner member that is configured in the radially inner side of said nozzle portion of the radial outside that is configured in said nozzle portion; The said nozzle outer member is formed with the 1st diffusing stream portion of leaning on the part of above-mentioned ejection oral-lateral than said nozzle portion that is used to form in above-mentioned diffuser; And be formed with the pipe patchhole continuously vertically with the minimum path portion of the above-mentioned the 1st diffusing stream portion; The said nozzle inner member has nozzle pipe portion; This nozzle pipe portion forms the tubulose that has above-mentioned suction bole in the axle center; This nozzle pipe portion insert in aforementioned tube patchhole and and interior week of aforementioned tube patchhole between form said nozzle portion, at the interior perimembranous place of the front end that leans on above-mentioned ejiction opening one side of this nozzle pipe portion, be formed with internal diameter from the opening of front end towards above-mentioned suction bole dwindle gradually and be used to form above-mentioned diffuser lean on the 2nd of the above-mentioned suction bole side sections stream portion that looses than said nozzle portion.
In addition; Technological scheme 4 described inventions are a kind of aircondition; It disposes each described jet pump in technological scheme 1～technological scheme 3 in the refrigeration cycle that has compressor, condenser, expansion valve, vaporizer successively, in the downstream of above-mentioned expansion valve; It is characterized in that; Have the 1st vaporizer and the 2nd vaporizer as above-mentioned vaporizer, the refrigeration agent that has passed through above-mentioned expansion valve is branched into the 1st fen branch road and the 2nd fen branch road, and branch road was connected via the inlet side of capillary tube with above-mentioned the 1st vaporizer in above-mentioned the 1st minute; The outlet side of above-mentioned the 1st vaporizer is connected with the above-mentioned suction bole of above-mentioned jet pump; Branch road was connected with the above-mentioned high-pressure refrigerant path of above-mentioned jet pump in above-mentioned the 2nd minute, and above-mentioned ejiction opening is connected with the inlet side of above-mentioned the 2nd vaporizer, and the outlet side of above-mentioned the 2nd vaporizer is connected with the inlet side of above-mentioned compressor; The refrigeration agent that has passed through above-mentioned expansion valve is ejected the driving stream that forms from said nozzle portion in above-mentioned diffuser, thereby the refrigeration agent that has passed through above-mentioned the 1st vaporizer is drawn in the above-mentioned diffuser from above-mentioned suction bole.
In jet pump of the present invention, in diffuser, spray the refrigeration agent of relatively high pressure and in diffuser, produce from the spray nozzle part of the inner peripheral surface of diffuser and drive stream, thus, from the refrigeration agent of the consecutive suction bole suction of diffuser relatively low pressure.
Therefore, needn't correspondingly can provide a kind of axial dimension short jet pump at the downstream tandem configuration restriction, mixer, the diffuser that are used to produce the spray nozzle part that drives stream as in the past.
In addition, technological scheme 2 described jet pumps owing to form the stream portion that helps vertically in the downstream of spray nozzle part, therefore help the situation of stream portion to compare with not being provided with, and can improve suction force.
In technological scheme 3 described jet pumps; By nozzle outer member and nozzle inner member; Between forms spray nozzle part, and forms diffuser by being formed on the diffusing stream portion of the 1st on the nozzle outer member and being formed on the diffusing stream portion of the 2nd on the nozzle inner member.Thereby the inner peripheral surface place that can easily be implemented in the centre of diffuser forms spray nozzle part.
In technological scheme 4 described airconditions; Jet pump looses in diffuser, to spray the refrigeration agent that has passed through expansion valve and form to drive between stream portion and the main diffusing stream portion via nozzle side from spray nozzle part and flows, and the refrigeration agent that will pass through the 1st vaporizer is drawn in the diffuser from pump port.
Therefore, the flow of the 1st vaporizer increases, and can obtain higher cooling performance.
Description of drawings
Fig. 1 is the sectional drawing of expression embodiment's 1 jet pump ZP.
Fig. 2 is the stereogram of major component of expression embodiment's 1 jet pump ZP.
Fig. 3 is the skeleton diagram of air conditioner for vehicles AC that expression has embodiment 1 jet pump ZP.
Fig. 4 is the Mollier line chart of relation of enthalpy and pressure of the refrigeration cycle of the above-mentioned air conditioner for vehicles AC of expression.
Fig. 5 is that expression is used for the Mollier line chart of an example of technology in the past that compares with above-mentioned air conditioner for vehicles AC.
Fig. 6 is the performance plot that helps stream distance L 1 and the relation of suction force among expression embodiment's 1 the jet pump ZP.
Fig. 7 is the sectional drawing of expression embodiment's 2 jet pump ZP2.
Fig. 8 is the sectional drawing of expression embodiment's 3 jet pump ZP3.
Embodiment
Below, based on description of drawings mode of execution of the present invention.
The jet pump of mode of execution of the present invention is characterised in that; It has the pump main body 5 that is formed with ejiction opening 51a, diffuser 55, suction bole 52e coaxially, and this ejiction opening 51a is used to spray the refrigeration agent of the refrigeration agent of the refrigeration agent that is mixed with relatively high pressure and relatively low pressure; This diffuser 55 is configured in the upper reaches of this ejiction opening 51a, and its internal diameter is along with dwindling gradually away from above-mentioned ejiction opening 51a; The upper reaches of the minimum path portion of this suction bole 52e and this diffuser 55 dispose and are used to guide the refrigeration agent of above-mentioned low pressure continuously; This pump main body 5 has the spray nozzle part 59 that is used for spraying in above-mentioned diffuser 55 from the high-pressure refrigerant path 53 of the refrigeration agent that is used to guide above-mentioned high pressure the refrigeration agent of above-mentioned high pressure on the inner peripheral surface of above-mentioned diffuser 55; Through refrigeration agent from the above-mentioned high pressure of said nozzle portion 59 ejections; Formation is drawn into the driving stream in the above-mentioned diffuser 55 with the refrigeration agent of above-mentioned low pressure from above-mentioned suction bole 52e, thereby the refrigeration agent of above-mentioned low pressure is sucked in the above-mentioned diffuser 55.
Embodiment 1
Below, have the air conditioner for vehicles AC of embodiment 1 jet pump ZP based on Fig. 1～Fig. 5 explanation.
Fig. 3 is the whole skeleton diagram of the schematic configuration of expression air conditioner for vehicles AC; This air conditioner for vehicles AC has refrigeration cycle S, and this refrigeration cycle S has compressor 1, condenser 2, expansion valve 3, capillary tube (capillary) 4, jet pump ZP, the 1st vaporizer the 10, the 2nd vaporizer 20.In addition,, for example use hydrogen chlorine fluorine substitute (134a, 1234yf), but also can use other materials such as hydrocarbon, carbon dioxide, ammonia as the refrigeration agent of this refrigeration cycle S.
Compressor 1 sucks and compressed refrigerant, and driving source rotations such as motor that it is used by vehicle driving or motor drive aspirates and compressed refrigerant, and outlet side is connected with condenser 2.
The outlet side of this expansion valve 3 branches into the 1st fen branch road 11 that is connected with the inlet side of the 1st vaporizer 10 via capillary tube 4 and the 2nd fen branch road 12 that is connected with jet pump ZP at point of branching 31 places.In addition, assembled integratedly by the 1st vaporizer the 10, the 2nd vaporizer 20, jet pump ZP and the capillary tube 4 of dotted line in Fig. 3.
On the 1st fen branch road 11, refrigeration agent expands in capillary tube 4 and reduces pressure, and thus, in the 1st vaporizer 10, carries out the cooling of air through from air, absorbing heat.
Be arranged on the 2nd fen jet pump ZP on the branch road 12 make the intermediate pressure refrigerant of having passed through expansion valve 3 from after spray nozzle part 59 ejections stated and expand to produce to drive and flow; Play a role as the pump that is used to aspirate from the low pressure refrigerant of the 1st vaporizer 10 by its suction force, with this low pressure refrigerant with mix from the intermediate pressure refrigerant of expansion valve 3 and see off to the 2nd vaporizer 20.In addition, the structure of jet pump ZP is detailed in the back.
The inlet side of the 2nd vaporizer 20 is connected with the ejiction opening 51a of jet pump ZP; And outlet side is connected with the inlet side of compressor 1; The gas-liquid two-phase refrigeration agent absorbs heat and becomes the refrigeration agent of the gas phase of low-temp low-pressure in the 2nd vaporizer 20, and this refrigeration agent is sent in the compressor 1 under the pumping action of compressor 1.
The 1st vaporizer 10 is connected with the 2nd vaporizer 20 and is arranged among the unit housings HU; Make with respect to air-supply W; The 1st vaporizer 10 is positioned at downstream; The 2nd vaporizer 20 is positioned at the upper reaches, and this unit housings HU accommodates in air conditioner for vehicles AC the structure (two vaporizers 10,20 and omitted illustrated heater) of carrying out heat exchange with the air-supply W that is formed by fan 6.In addition, the 1st vaporizer 10 is identical structures with the 2nd vaporizer 20, and the gas-liquid two-phase refrigeration agent of low pressure absorbs heat and evaporation, utilizes the refrigeration agent heat of vaporization to cool off air-supply.Two vaporizers the 10, the 20th like this, known structure is omitted diagram, the pipe that its casing, connection casing and confession refrigeration agent with setting up and down passes through, the radiating fin that is arranged on the pipe periphery.
Then, specify the structure of jet pump ZP.
Jet pump ZP is contained in the case portion (omitting diagram) on the side plate that is formed at the skeleton that becomes the 1st vaporizer 10 and the 2nd vaporizer 20 etc., has the pump main body 5 that is made up of nozzle outer member 51 and nozzle inner member 52.
Nozzle outer member 51 forms tubulose; And; Axial right-hand to (being arrow R direction in Fig. 1 towards left and right directions in the drawings; This direction is called the 1st direction) the end, offer ejiction opening 51a, and in as axial figure left to the 2nd direction and this ejiction opening 51a coaxial continuously be formed with the 1st loose the 51b of stream portion, help discharge orifice (pipe patchhole) 51c, pipe patchhole 51d.
The 1st 51b of stream portion that looses forms the shape that towards the 2nd direction internal diameter is dwindled from ejiction opening 51a, in present embodiment 1, as forming the angle in 11 °～17 ° the scope with expansion angle θ a along axial direction angulation.
Help discharge orifice 51c to form with constant inner diameter towards the 2nd direction end vertically with the diameter identical with this minimum path portion from the minimum path portion of the 1st diffusing 51b of stream portion.
The 52a of nozzle pipe portion that nozzle inner member 52 has insertion tube patchhole 51d and helps the tubulose in the discharge orifice 51c and diameter greater than the diameter of the 52a of this nozzle pipe portion, and the base part 52b that connects of the end of the 2nd direction of nozzle outer member 51.In addition, pipe patchhole 51d and help discharge orifice 51c to be equivalent to supply the pipe patchhole of the technological scheme 3 that the 52a of nozzle pipe portion inserts.
The 52a of nozzle pipe portion is configured to and helps discharge orifice 51c and pipe patchhole 51d roughly coaxial, and its front end is inserted into the intermediate portion that helps discharge orifice 51c.In addition; The 52a of this nozzle pipe portion form its external diameter than help discharge orifice 51c and the internal diameter of pipe patchhole 51d little; Between the interior week of itself and pipe patchhole 51d, be formed with periphery refrigerant passage (high-pressure refrigerant path) 53, and at the 52a of nozzle pipe portion and help and be formed with the spray nozzle part 59 that is used for spraying in diffuser 55 from the inner peripheral surface of diffuser 55 low pressure refrigerant between the discharge orifice 51c.In addition; Periphery refrigerant passage 53 can form with the diameter difference of pipe patchhole 51d by the 52a of nozzle pipe portion; But when being identically formed pipe patchhole 51d with the diameter that helps discharge orifice 51c, periphery refrigerant passage 53 also can through vertically in the periphery of the interior week of pipe patchhole 51d and the 52a of nozzle pipe portion any one or both on groove be set form.
In addition, periphery refrigerant passage 53 via the access 52d of the base part 52b that runs through nozzle inner member 52 and the 2nd fen branch road 12, be that the outlet side of expansion valve 3 is connected.
In addition, the 52a of nozzle pipe portion has the identical suction bole 52e of diameter of the minimum diameter pump port 57 partly of the 2nd diffusing 52c of stream portion, diameter and the 2nd diffusing 52c of stream portion that dwindle internal diameter towards the opening 54 of the front end of the 1st diffusing 51b of stream portion opening, from this opening 54 gradually.And the end of the 2nd direction of suction bole 52e is connected with the outlet side of the 1st vaporizer 10 via the cross-drilled hole 52f that runs through along the axle orthogonal direction.
The expansion angle θ a that the 2nd diffusing 52c of stream portion forms its expansion angle and the 1st diffusing 51b of stream portion is identical, and this expansion angle forms 11 °～17 ° the interior angle of scope.The 2nd diffusing 52c of stream portion and the 1st diffusing 51b of stream portion together form diffuser 55.
Be formed on the front end of the said nozzle pipe 52a of portion and help the spray nozzle part 59 between the discharge orifice 51c to form by a plurality of nozzle bore 52h.That is, as shown in Figure 2, in the periphery of the 52a of nozzle pipe portion, be spline-like and alternately be formed with and help the protuberance 52g that connects in interior week of discharge orifice 51c and the nozzle bore 52h that self-service discharge orifice 51c leaves to internal diameter direction.Thus; In the front end periphery of the 52a of nozzle pipe portion and help between the interior week of discharge orifice 51c; Periphery along opening 54 is provided with a plurality of nozzle bore 52h, is formed with the spray nozzle part 59 that periphery refrigerant passage 53 is connected by these a plurality of nozzle bore 52h with the axial intermediate portion of diffuser 55.In addition, the opening area of this spray nozzle part 59, be the size below 1/4 that the gross area of the opening of nozzle bore 52h forms the sectional area of suction bole 52e.
Return Fig. 1, in helping discharge orifice 51c, loose between the 51b of stream portion at the front end of the 52a of nozzle pipe portion and the 1st vertically, be provided be used to make from the low pressure refrigerant of the outlet side of the 1st vaporizer 10 with mix mutually from the intermediate pressure refrigerant of expansion valve 3 help stream portion 56.When the diameter with suction bole 52e was made as D, preferably this helped the axial dimension (below, be called help stream distance L 1 with it) of stream portion 56 to form the size that helps stream distance L 1≤3D, in present embodiment 1, forms the size slightly shorter than D.
Then, based on the effect of the air conditioner for vehicles AC of the Mollier line chart illustrative embodiment 1 of the skeleton diagram of Fig. 3 and Fig. 4.
In compressor 1, the vapor phase refrigerant of the low pressure shown in the some a of the Mollier line chart of Fig. 4 is aspirated, and shown in a b, becomes HTHP and is sent to condenser 2.In condenser 2, refrigerant loses heat and condensation become the liquid phase refrigerant of the normal temperature and pressure shown in the c.In expansion valve 3, the liquid phase refrigerant decompression of the high pressure shown in the some c is also controlled flow, becomes the gas-liquid two-phase refrigeration agent of low-temp low-pressure, is sent to the 1st fen branch road 11 and the 2nd fen branch road 12 at a d place by shunting.
At this, the refrigeration agent of delivering to the 1st fen branch road 11 expands in capillary tube 4, reduces pressure, and in the 1st vaporizer 10, carries out the heat of heat exchange and absorption air-supply W afterwards, becomes the many refrigeration agents of gas phase of low-temp low-pressure.In this case, in the Mollier line chart of Fig. 4, the variation between some d and the some e 1 in the expression capillary tube 4, the enthalpy change between some e1 and the some f1 in expression the 1st vaporizer 10.On the other hand; The refrigeration agent that has passed through the 2nd fen branch road 12 is sent to nozzle bore 52h from periphery refrigerant passage 53 and by throttling in jet pump ZP; Thereby the spray nozzle part 59 that looses between 52c of stream portion and the 1st diffusing 51b of stream portion from the 2nd of diffuser 55 sprays at a high speed, and reduces pressure, expands through hole enlargement.
Like this; In jet pump ZP; Because the pressure difference that produces from the speed difference of the refrigeration agent of spray nozzle part 59 ejection and the refrigeration agent the suction bole 52e and by these two pressure difference factors of pressure difference from the puffing effect generation of nozzle bore 52h when diffuser 55 sprays; Be used to carry pressure P 1 and the pressure P 3 of diffuser 55 of the suction bole 52e of the refrigeration agent that has passed through the 1st vaporizer 10 to become the relation of P1＞P3; And, under the effect of the suction force of compressor 1, the refrigeration agent of suction bole 52e by efficiently from pump port 57 suctions to diffuser 55.
In the Mollier line chart of Fig. 4, the part that some e2 is illustrated in that the intermediate pressure refrigerant of having passed through the 2nd fen branch road 12 in the diffuser 55 expands and mixes with low pressure refrigerant from the 1st vaporizer 10 is put the state that f2 representes the outlet of the 2nd vaporizer 20.
Thereby in Fig. 4, the scope of A1 is represented the enthalpy change in the 1st vaporizer 10, and the scope of A2 is represented the enthalpy change in the 2nd vaporizer 20.
At this, the cooling performance in two vaporizers 10,20 can multiply by refrigerant flow with the difference of evaporator inlet enthalpy and evaporator outlet enthalpy to be confirmed.
Therefore; Under the situation of present embodiment 1, the cooling performance of two vaporizers 10,20 becomes the value of gained after the value that the difference that adds the 1st evaporator inlet enthalpy (e1) and the 1st evaporator outlet enthalpy (f1) on the basis of value that difference at the 2nd evaporator inlet enthalpy (e2) and the 2nd evaporator outlet enthalpy (f2) multiply by refrigerant flow multiply by refrigerant flow.Thereby in present embodiment 1, the increase of the refrigerant flow of the 1st vaporizer 10 that causes through the suction force by jet pump ZP can obtain the raising of cooling performance.
Mollier line chart when Fig. 5 representes in the past technology in order to compare with present embodiment.Under the situation of patent documentation 1 described technology in the past; Its purpose is through obtaining to be suppressed by the effect of boosting that sparger brings the work done amount of compressor; As shown in the figure; The refrigeration agent that has passed through the 1st vaporizer boosts by sparger and is sent to the 2nd vaporizer, thereby the increased pressure of the outlet of the 2nd vaporizer correspondingly can suppress the amount of boost in the compressor.
Relative therewith, the jet pump ZP of present embodiment 1 seeks to improve the air-cooling system performance in the 1st vaporizer 10 through increasing by means of the refrigerant flow of pumping function as stated, correspondingly can seek to reduce the work done amount of compressor 1 grade.Therefore, as shown in Figure 4, the pressure of the outlet of the 2nd vaporizer 20 is lower than the pressure of the outlet of the 1st vaporizer 10.
Below, enumerate embodiment 1 jet pump ZP and have the effect of the air conditioner for vehicles AC of this jet pump ZP.
A) in jet pump ZP; Axial intermediate portion on the inner peripheral surface that is formed at diffuser 55; From the 2nd loose the 52c of stream portion and the 1st loose spray nozzle part 59 between the 51b of stream portion in diffuser 55, gush out self-expanding valve 3 refrigeration agent and produce and drive stream, from pump port 57 suctions of the radially central authorities that are configured in diffuser 55 refrigeration agent by 10 conveyings of the 1st vaporizer.
Therefore, needn't correspondingly axial dimension can be shortened, the miniaturization of jet pump ZP can be sought in the downstream tandem configuration restriction and the mixer of spray nozzle part as in the past.In fact, can be made as in the past about 1/3 axial dimension.
And, owing to can make jet pump ZP miniaturization, therefore also can improve the degrees of freedom that is provided with of two vaporizers 10,20 o'clock that are wholely set air conditioner for vehicles AC.
B) because jet pump ZP is used for decompression member that refrigeration agent is reduced pressure; Therefore by the pressure difference that produces to the speed difference of the refrigeration agent of the intermediate portion high velocity jet of diffuser 55 and the refrigeration agent the suction bole 52e from spray nozzle part 59 and by under the action of pressure of the puffing effect generation of nozzle bore 52h when diffuser 55 sprays; By the suction of the pressure P of having utilized suction bole 52e 1, can obtain higher suction force, be pump performance with the pressure difference of the pressure P 3 of diffuser 55.
C) in diffuser 55, between the 2nd diffusing 52c of stream portion and the 1st diffusing 51b of stream portion, be provided with the stream portion 56 that helps.
Fig. 6 is the suction force performance plot of jet pump ZP, as shown in the drawingly knows, when the axial length of having guaranteed to help stream portion 56 (=help stream distance L 1), helps the situation of stream distance L 1 to compare with fully being provided with, and suction force increases.In addition; The D of transverse axis is the diameter of suction bole 52e, shown in this suction force performance plot, in the time will helping stream distance L 1 to form the value about 3D; Can obtain maximum suction force; But in present embodiment 1, pay the utmost attention to the miniaturization of jet pump ZP, help stream distance L 1 to be set at the size shorter a little than the diameter D of suction bole 52e.
D) owing to below 1/4 of sectional area that the gross area of nozzle bore 52h is made as suction bole 52e; Therefore can the refrigeration agent flow velocity that eject from spray nozzle part 59 be made as the speed of the refrigeration agent flow velocity that fully is higher than suction bole 52e side, can guarantee the pressure difference that produces by both speed difference and obtain higher suction force.
E) when the front end periphery at the 52a of nozzle pipe portion forms spray nozzle part 59; Be the contacted a plurality of protuberance 52g of inner peripheral surface that all shapes were provided with and helped discharge orifice 51c, therefore can suppress the 52a of nozzle pipe portion in the state lower edge radial displacement of in helping discharge orifice 51c, inserting its front end.Thus, can and help the dimensionally stable that makes spray nozzle part 59 between the discharge orifice 51c, can obtain stable suction force, i.e. stable pumping function at the 52a of nozzle pipe portion.
F) in air conditioner for vehicles AC, in the downstream of expansion valve 3 jet pump ZP is set, by the suction force of this jet pump ZP the refrigerant flow of the 1st vaporizer 10 is increased, cooling capacity can be improved, and the work done amount of compressor 1 can be reduced.And the suction force of jet pump ZP need not be used special-purpose power and be to use the driving force by the mobile generation of refrigeration agent, therefore not only efficiently but also economical.
Other embodiments
Below, other embodiments are described, these other embodiments are variation of embodiment 1; Therefore its difference only is described; Through the structure tag identical symbol identical with embodiment or other embodiments omitted explanation, and about action effect, also omit the explanation identical with embodiment 1.
Embodiment's 2 shown in Figure 7 jet pump ZP2 is embodiment 1 a variation, is to compare with embodiment 1 to have formed the axial dimension that helps discharge orifice 251c longways, will be made as the example of about 3 times value of the diameter D of suction bole 52e as the stream distance L 1 that helps of the length that helps stream portion 256.
Thereby, in embodiment 2 jet pump ZP2, like above-mentioned c) said, through being made as the value that helps about stream distance L 1=3D, can the suction force of jet pump ZP2 be made as maximum.Even as embodiment 2, be made as under the situation that helps stream distance L 1=3D, the axial dimension of jet pump ZP also can be made as the size below 1/2 of sparger in the past.
In addition; As shown in Figure 6 and since help stream distance L 1 the diameter D with respect to suction bole 52e be made as 3D apart from the time reach maximum, therefore shown in embodiment 1 and embodiment 2; Through helping stream distance L 1 to be made as the size below the 3D; Can seek miniaturization, can obtain essential pump performance simultaneously, be preferred.
As shown in Figure 8, embodiment 3 jet pump ZP3 is provided with the moving member 300 that is used to make nozzle inner member 352 to move vertically, forms the example that the length that helps stream portion 356 can change.In addition, the jet pump ZP3 of expansion valve 3 is applied to the air conditioner for vehicles AC identical with embodiment 1.
Moving member 300 becomes following structure: the temperature that detects the refrigeration agent that comes out from the 1st vaporizer 10; Refrigerant temperature is relatively high more more from helping stream portion 356 the shortest original states to increase to help stream distance L 1 (promptly, near 3D size); And; According to the pressure difference of the refrigerant pressure of the outlet of the refrigerant pressure of the outlet of expansion valve 3 and the 1st vaporizer 10, pressure difference is more little to be increased more and helps stream distance L 1 (promptly, near the size of 3D), back detailed description.
Below, based on the jet pump ZP3 of Fig. 8 illustrative embodiment 3.
As shown in Figure 8,351 form tubulose, have coaxially successively from the end of a side the 1st loose the 51b of stream portion, help discharge orifice (pipe patchhole) 351c, nozzle receiving bore (pipe patchhole) 351d.
Nozzle inner member 352 forms tubulose, has 352a of nozzle pipe portion and compression zone 352p, and runs through vertically in its axle center and to be formed with suction bole 352e.
The 352a of nozzle pipe portion is configured to nozzle receiving bore 351d and helps discharge orifice 351c coaxial; Its front end inserts and helps in the discharge orifice 351c; Periphery at its fore-end; Have protuberance 52g and the nozzle bore 52h identical with embodiment 1, thereby at the 352a of nozzle pipe portion and help and be formed with spray nozzle part 59 between the discharge orifice 351c.
Moving member 300 has along the 2nd direction (direction in the opposite direction with arrow R) to the 1st spring 301 of the compression zone 352p application of force of nozzle inner member 352 with along 2nd spring 302 of the 1st direction (arrow R direction) to the compression zone 352p application of force.The 2nd spring 302 is springs of shape memory metal system, and more than predefined temperature, the 2nd spring 302 has the low more characteristic of the high more spring constant of this refrigerant temperature with the refrigerant temperature of the outlet side of the 1st vaporizer 10 with being directly proportional.
The 1st spring 301 uses the spring of following spring force: when the spring constant of the 2nd spring 302 becomes low relatively state; To the 2nd direction pushing nozzle inner member 352; Nozzle inner member 352 is configured in to make helps stream distance L 1 to become the position of the size about above-mentioned 3D; Under the high relatively state of the spring constant of the 2nd spring 302, can nozzle inner member 352 be configured in and help stream distance L 1 to become near the position 0.
In addition; A spring-loaded member 303 that the 2nd spring 302 is arranged falls; The outside thread that is formed on its periphery is meshed with the internal thread in the interior week that is formed on nozzle receiving bore 351d; Can be center rotation and mobile vertically with the axle center through making it, set initial characteristic based on the balance of two springs 301,302.
Thereby; In jet pump ZP3; The refrigerant pressure of the outlet side of the 1st vaporizer 10 increases and is little with the pressure difference of the refrigerant pressure of the outlet side of expansion valve 3; The reaction force to the active force of the 1st spring 301 is little, makes nozzle inner member 352 to the direction that helps stream distance L 1 to increase, promptly the 2nd direction moves.
In addition, the refrigerant temperature that gets into Room 312 the 2nd through the 1st vaporizer 10 is high more, and the spring constant of the 2nd spring 302 is low more, and the tendency that helps stream distance L 1 to increase is big more.
Therefore, in the air conditioner for vehicles AC of the jet pump ZP3 with embodiment 3, move as follows according to air conditioning load.
When air conditioning load was low, in air conditioner for vehicles AC, refrigerant flow reduced.In this case, less through the refrigerant flow of two vaporizers 10,20, in temperature distribution, producing has deviation, and the tendency that is easy to produce local freezing grade is arranged.
On the contrary; In present embodiment 1; Refrigerant flow more in this wise; The pressure difference of the refrigerant pressure of the outlet side of the refrigerant pressure of the outlet side of the 1st vaporizer 10 and expansion valve 3 reduces, and therefore in jet pump ZP3, nozzle inner member 352 is towards the configuration of the 2nd direction and help stream distance L 1 to increase.
Thereby the suction force that is produced by jet pump ZP3 strengthens and the refrigerant flow increase, and the temperature in each vaporizer 10,20 is cooled off respectively well efficiently.
On the other hand, when air conditioning load was higher, in air conditioner for vehicles AC, the refrigerant temperature of the outlet side of the 1st vaporizer 10 increased.
Therefore, in jet pump ZP3, the refrigerant temperature of Room 312 the 2nd rises, and the spring constant of the 2nd spring 302 reduces.Thereby in jet pump ZP, nozzle inner member 352 moves and helps 1 growth of stream distance L to the 2nd direction.
Thus, in jet pump ZP3, suction force strengthens and refrigerant flow increases the cooling capacity in the time of can guaranteeing high load.
As stated, in embodiment 3 jet pump ZP3, can change the suction force characteristic of jet pump ZP3, can cool off efficiently according to the air conditioning load condition of air conditioner for vehicles AC.
And, the moving member 300 that carries out this action based on air conditioning load be do not use electrically driven (operated) temperature transducer, actuator, to the parts of its controller that drives.Particularly; Nozzle inner member 352 has the compression zone 352p of refrigerant pressure of outlet side of refrigerant pressure and the expansion valve 3 of the outlet side that bears the 1st vaporizer 10, and the 2nd spring 302 usagies of nozzle inner member 352 application of forces is answered the shape memory spring of refrigerant temperature of the outlet side of the 1st vaporizer 10 vertically.
Therefore, compare, can form cheap and small-sized with the parts that used electrically driven (operated) temperature transducer, actuator, controller.
And; In embodiment 3,, be provided with and the protuberance 52g that contacts in interior week that helps discharge orifice 351c at the front end of nozzle inner member 352; Even therefore nozzle inner member 352 moves vertically; Also can make the shaft core position of nozzle inner member 352 consistent, can keep the constant area of nozzle bore 52h, can obtain stable pumping action with 351 shaft core position.
More than; Mode of execution of the present invention and embodiment 1～embodiment 3 have been specified with reference to accompanying drawing; But concrete structure is not limited to this mode of execution and embodiment 1～embodiment 3, and the design alteration that does not break away from the degree of purport of the present invention all comprises in the present invention.
For example, in embodiment 1～embodiment 3, show, but so long as aircondition also can be applied to vehicle with device in addition the example of ejector applications in air conditioner for vehicles.
In addition, as spray nozzle part, show and be that spline-like alternately forms protuberance 52g and nozzle bore 52h and the spray nozzle part 59 that forms, but spray nozzle part is not limited thereto, and also can be formed on the whole periphery of front end of nozzle arrangement.In addition, the size of the circumferencial direction of protuberance 52g and nozzle bore 52h is not limited to the size shown in the embodiment.In addition, to the parts that radially move, show the protuberance 52g that extends vertically, but its shape is not limited thereto, and also can use parts such as projection merely as the front end of limits nozzle inner member 52.
In addition; In embodiment 3; Show the moving member 300 that has used the 1st spring 301 and the 2nd spring 302; But as the parts that nozzle arrangement is moved vertically, be not limited to use the parts of this spring, also can come drive actuator according to the output of the self-controller of the checkout value that utilizes temperature transducer or pressure transducer; Thereby when the refrigerant temperature of the outlet side of the 1st vaporizer is high temperature and the pressure difference of the outlet side of the outlet side of the 1st vaporizer and expansion valve hour, help stream distance L 1 to become driving near the length of 3D.
In addition, in an embodiment, show the pump main body, but also can form by a member by nozzle outer member and these two examples that member forms of nozzle inner member.That is, can wear ejiction opening, diffuser, suction bole from axial both ends or one end with respect to the pump main body, further offer spray nozzle part in the centre of diffuser, jet pump of the present invention is made in the processing that this spray nozzle part is connected with the high-pressure refrigerant path.
Claims (13)
1. a jet pump is characterized in that,
This jet pump comprises ejiction opening, diffuser, suction bole, high-pressure refrigerant path, spray nozzle part, and this ejiction opening is used to spray the refrigeration agent after the refrigerant mixed of refrigeration agent and relatively low pressure of relatively high pressure; This diffuser is in the upper reaches and this ejiction opening arranged coaxial of this ejiction opening, and its internal diameter is along with dwindling gradually away from above-mentioned ejiction opening; This suction bole disposes with the upper reaches of the minimum path portion of this diffuser mutually continuously and with above-mentioned ejiction opening coaxially, is used to guide the refrigeration agent of above-mentioned low pressure; This high-pressure refrigerant path is used for the refrigeration agent of above-mentioned high pressure is guided to above-mentioned diffuser; This spray nozzle part is used for more minimum through partly leaning on downstream part in above-mentioned diffuser, to spray the refrigeration agent of above-mentioned high pressure from this high-pressure refrigerant path than above-mentioned.
2. jet pump according to claim 1 is characterized in that,
Comprise the nozzle outer member of tubulose and the nozzle inner member of the tubulose of the radially inner side that is configured in this nozzle outer member,
Above-mentioned ejiction opening is formed on an end of said nozzle outer member,
Above-mentioned suction bole is formed at the said nozzle inner member,
Above-mentioned high-pressure refrigerant path and said nozzle portion are formed on respectively between said nozzle outer member and the said nozzle inner member.
3. jet pump according to claim 2 is characterized in that,
The said nozzle inner member has nozzle pipe portion, and this nozzle pipe portion is used between itself and said nozzle outer member, forming said nozzle portion.
4. jet pump according to claim 3 is characterized in that,
Said nozzle portion has a plurality of nozzle bores along the circumferential configuration of said nozzle inner member.
5. jet pump according to claim 4 is characterized in that,
Above-mentioned a plurality of nozzle bore is circumferential and protuberance alternate configurations in the outer circumferential face upper edge of said nozzle pipe portion; Interior all butts of this protuberance and said nozzle outer member and extend along the length direction of said nozzle pipe portion, and should a plurality of nozzle bores above-mentioned diffusers in edge extending axially.
6. jet pump according to claim 2 is characterized in that,
Above-mentioned diffuser has the 1st diffusing stream portion and the 2nd diffusing stream portion; The 1st diffusing stream portion is formed at the inner peripheral surface of an above-mentioned end of said nozzle outer member; The 2nd diffusing stream portion is formed at the interior perimembranous place of the front end that leans on above-mentioned ejiction opening one side of said nozzle inner member, and its internal diameter dwindles towards above-mentioned suction bole from the opening of front end gradually.
7. jet pump according to claim 6 is characterized in that,
Said nozzle portion is ejected to the refrigeration agent of above-mentioned high pressure in the above-mentioned diffuser between the above-mentioned the 1st diffusing stream portion and the above-mentioned the 2nd diffusing stream portion.
8. jet pump according to claim 6 is characterized in that,
The said nozzle inner member has nozzle pipe portion, and this nozzle pipe portion is used between itself and said nozzle outer member, forming said nozzle portion, and the above-mentioned the 2nd stream portion that looses is formed at the inner peripheral surface of said nozzle pipe portion.
9. jet pump according to claim 6 is characterized in that,
The said nozzle inner member has nozzle pipe portion; This nozzle pipe portion is used between itself and said nozzle outer member, forming said nozzle portion; On the said nozzle outer member, be formed with the pipe patchhole that forms through partial continuous of minimum that looses stream portion with the above-mentioned the 1st; Said nozzle pipe portion inserts in the aforementioned tube patchhole, between the interior week of this nozzle pipe portion and aforementioned tube patchhole, forms said nozzle portion.
10. jet pump according to claim 6 is characterized in that,
The above-mentioned the 2nd the loose axis angulation of internal surface and above-mentioned diffuser of axis angulation and the above-mentioned the 1st diffusing stream portion of internal surface and above-mentioned diffuser of stream portion is identical.
11. jet pump according to claim 1 is characterized in that,
Above-mentioned diffuser the above-mentioned ejiction opening side position of said nozzle portion have vertically internal diameter constant help stream portion.
12. jet pump according to claim 11 is characterized in that,
When the diameter with above-mentioned suction bole was made as D, the above-mentioned axial dimension L1 that helps stream portion satisfied the relation of L1≤3D.
13. an aircondition, it is configured in the downstream of above-mentioned expansion valve in the refrigeration cycle of the compressor that has claim 1 record successively, condenser, expansion valve, vaporizer, it is characterized in that,
Have the 1st vaporizer and the 2nd vaporizer as above-mentioned vaporizer,
The refrigeration agent that has passed through above-mentioned expansion valve is branched into the 1st fen branch road and the 2nd fen branch road,
Branch road was connected via the inlet side of capillary tube with above-mentioned the 1st vaporizer in above-mentioned the 1st minute,
The outlet side of above-mentioned the 1st vaporizer is connected with the above-mentioned suction bole of above-mentioned jet pump,
Branch road was connected with the above-mentioned high-pressure refrigerant path of above-mentioned jet pump in above-mentioned the 2nd minute,
Above-mentioned ejiction opening is connected with the inlet side of above-mentioned the 2nd vaporizer,
The outlet side of above-mentioned the 2nd vaporizer is connected with the inlet side of above-mentioned compressor,
In above-mentioned diffuser, spray from said nozzle portion at the refrigeration agent that has passed through above-mentioned expansion valve under the effect of the driving stream that forms, the refrigeration agent that has passed through above-mentioned the 1st vaporizer is drawn in the above-mentioned diffuser from above-mentioned suction bole.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-228225 | 2010-10-08 | ||
| JP2010228225 | 2010-10-08 |
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| CN102444626A true CN102444626A (en) | 2012-05-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011102942009A Pending CN102444626A (en) | 2010-10-08 | 2011-09-26 | Jet pump and air conditioner |
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| CN104428541A (en) * | 2012-07-09 | 2015-03-18 | 株式会社电装 | Ejector |
| CN104769367A (en) * | 2012-07-24 | 2015-07-08 | 赤木富士雄 | Fluid transportation device and fluid transportation method |
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| CN104769367B (en) * | 2012-07-24 | 2017-10-13 | 赤木富士雄 | Fluid handling device and fluid method for carrying |
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Application publication date: 20120509 |