CN100378411C - Vapor-compression refrigerant cycle system with ejector - Google Patents
Vapor-compression refrigerant cycle system with ejector Download PDFInfo
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- CN100378411C CN100378411C CNB2005101041902A CN200510104190A CN100378411C CN 100378411 C CN100378411 C CN 100378411C CN B2005101041902 A CNB2005101041902 A CN B2005101041902A CN 200510104190 A CN200510104190 A CN 200510104190A CN 100378411 C CN100378411 C CN 100378411C
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Abstract
A vapor-compression refrigerant cycle system having an ejector includes a first evaporator for evaporating refrigerant from a pressure-increasing portion of the ejector, and a second evaporator for evaporating refrigerant to be drawn into a refrigerant suction port of the ejector. Furthermore, a valve member for opening and closing a refrigerant passage of the second evaporator is arranged in serious with the second evaporator in a refrigerant flow, and refrigerant flowing out of the second evaporator flows into the refrigerant suction port through a refrigerant suction pipe. The system is provided to restrict lubrication oil contained in refrigerant from being introduced from the ejector into and staying in the refrigerant suction pipe when the valve member is closed. For example, the refrigerant suction port is provided at an upper side of the ejector.
Description
Technical field
The present invention relates to have steam compression refrigerant circulating system as the injector of cold-producing medium decompressing unit and cold-producing medium cycling element.Described steam compression refrigerant circulating system is suitable as car air-conditioner for instance.
Background technology
With injector as the steam compression refrigerant circulating system (circulation system of injector) of cold-producing medium decompressing unit and cold-producing medium cycling element for instance at JP-B1-3322263 (corresponding to U.S. Patent No. 6,574,987 and U.S. Patent No. 6,477,857) in be described.For example, in this steam compression refrigerant circulating system, first evaporimeter is arranged on injector and between the gas-liquid separator in injector downstream, and second evaporimeter is arranged between the refrigerant suction port of the liquid refrigerant outlet side of gas-liquid separator and injector.
The present inventor has studied the example of the refrigerating function of switching (switching) second evaporimeter.In this example, be arranged on second vaporizer upstream as the magnetic valve of automatically controlled valve member (certainly, also can use the automatically controlled valve member of other type), and magnetic valve when stopping, the refrigerating function of second evaporimeter cuts out as motor-driven motor-driven valve.In this case, when closed electromagnetic valve, there is not to produce the cold-producing medium stream that sucks the refrigerant suction port of injector from second evaporimeter.In this example, if refrigerant suction port, then is included in the lubricating oil (that is refrigerating machine oil) in the cold-producing medium that flows through injector interior in the lower openings of injector because the gravity effect of lubricating oil falls into refrigerant suction port.Therefore, when closed electromagnetic valve, lubricating oil is stayed in the cold-producing medium suction pipe of the refrigerant suction port that is connected to injector and second injector.In this case, the amount of returning of returning the lubricating oil of compressor reduces, thereby causes the lubricating oil shortage in the compressor.
Summary of the invention
In view of the above problems, an object of the present invention is to provide a kind of steam compression refrigerant circulation with injector, the amount of returning that it can prevent to return the lubricating oil of compressor reduces when the refrigerating function of the evaporimeter of the refrigerant suction port that is connected to injector stops.
According to an aspect of the present invention, a kind of steam compression refrigerant circulating system comprises: compressor is used for compressed refrigerant; Refrigerant cooler is used to cool off the high-pressure refrigerant from compressor discharge; Injector comprises: nozzle is used to make cold-producing medium decompression and expansion from refrigerant cooler; Refrigerant suction port sucks gas refrigerant from the cold-producing medium of nozzle ejection stream from described refrigerant suction port; And supercharging portion, wherein mix from the cold-producing medium of nozzle ejection with from the gas refrigerant that refrigerant suction port sucks, and by speed being converted to the pressure that pressure energy improves cold-producing medium; First evaporimeter is used to make the cold-producing medium evaporation of the supercharging portion of outflow jet, and described first evaporimeter is positioned at the injector downstream, and has the refrigerant outlet that is connected to the compressor suction side; Second evaporimeter is used to make the cold-producing medium evaporation of waiting to suck refrigerant suction port; Automatically controlled valve member is used to open and close the coolant channel of second evaporimeter, described automatically controlled valve member in cold-producing medium stream with the second evaporator series setting; The cold-producing medium suction pipe has first end of the refrigerant outlet that is connected to second evaporimeter and is connected to second end of refrigerant suction port; And restraint device, the lubricating oil that is used for preventing being included in cold-producing medium when automatically controlled valve member is closed is directed in the system cryogen suction pipe and stays in the cold-producing medium suction pipe by refrigerant suction port.
In steam compression refrigerant circulating system, be used to make first evaporimeter of cold-producing medium evaporation of the supercharging portion of outflow jet to be positioned at the injector downstream, be provided with second evaporimeter of the cold-producing medium evaporation that is used to make the refrigerant suction port of waiting to suck injector, the automatically controlled valve member of coolant channel that is used for opening and closing second evaporimeter is in the cold-producing medium stream and the second evaporator series setting, and be provided with the cold-producing medium suction pipe, described cold-producing medium suction pipe has first end of the refrigerant outlet that is connected to second evaporimeter and is connected to second end of the refrigerant suction port of injector.And described system is provided with restraint device, is used for limiting the lubricating oil that is included in cold-producing medium and imports the cold-producing medium suction pipe by refrigerant suction port and stay wherein when automatically controlled valve member is closed.Like this, the lubricating oil that can prevent to return compressor is insufficient when automatically controlled valve member is closed, thereby can improve the greasy property of compressor.
For example, refrigerant suction port is arranged on the injector upside.In this case, utilize this simple structure, can prevent that lubricating oil from falling into the refrigerant suction port of injector.
Alternatively, the cold-producing medium suction pipe can be provided with erection part at the downstream position near refrigerant suction port, and described erection part extends up to the position that is higher than refrigerant suction port.In this case, even when refrigerant suction port is arranged on the bottom of injector, also the lubricants capacity of staying in the cold-producing medium suction pipe can be controlled to be in a small amount.
Alternatively, check-valves can be arranged on the inlet portion of refrigerant suction port, only allows cold-producing medium to flow to the refrigerant suction port from the cold-producing medium suction pipe.Therefore, even when refrigerant suction port is arranged on the injector bottom, check-valves can prevent that also lubricating oil from flowing into the cold-producing medium suction pipe from refrigerant suction port.
In steam compression refrigerant circulating system, auxiliary automatically controlled valve member can be arranged in the coolant channel, wherein imports the refrigerant suction port of compressor by described coolant channel from the cold-producing medium of second evaporimeter.In this case, described automatically controlled valve member is arranged on the inlet portion of the refrigerant suction port of injector, and assists automatically controlled valve member to open when described automatically controlled valve member is closed, thereby flows out the suction side of the cold-producing medium inflow compressor of second evaporimeter.Therefore, even when refrigerant suction port is arranged on the bottom of injector, also may prevent that lubricating oil from staying in the cold-producing medium suction pipe by described automatically controlled valve member and auxiliary automatically controlled valve member.
Described second evaporimeter can be configured to carry out the cooling down operation that is used to cool off air, and can be provided for air is blown to the air blast of second evaporimeter.In this case, open automatically controlled valve member, make that cold-producing medium always flows into second evaporimeter when compressor operating, and air blast stops when the refrigerating function of second evaporimeter stops.Because cold-producing medium always flows into second evaporimeter, thus the refrigerant vapour of refrigerant suction port can always be formed from second evaporimeter to injector, thus prevent that lubricating oil from staying in the cold-producing medium suction pipe.
Alternatively, during compressor operating, after closing described automatically controlled valve member during through the scheduled time, but the described automatically controlled valve member of positive opening.Therefore, may prevent lubricating oil shortage in the compressor.
And, when when compressor starts is worked, stopping the cooling down operation of second evaporimeter, make described automatically controlled valve member open the scheduled time once.Therefore, even in the time started of compressor, the lubricating oil of staying in second evaporimeter and the cold-producing medium suction pipe also can return compressor, thereby prevents the lubricating oil shortage in the compressor.
In steam compression refrigerant circulating system, bypass channel can be set, wherein the cold-producing medium from refrigerant cooler flows into refrigerant suction port by described bypass channel, walks around second evaporimeter and described automatically controlled valve member simultaneously.In this case, auxiliary automatically controlled valve member is arranged in the bypass channel, is used to open and close bypass channel, and during compressor operating, auxiliary automatically controlled valve member is opened when described automatically controlled valve member is closed.Therefore, when the cold-producing medium vaporization function that stops second evaporimeter (for example, refrigerating function), can prevent that the lubricating oil in the compressor is insufficient, thereby can effectively improve the greasy property of compressor.
Description of drawings
Referring to the accompanying drawing detailed description of the preferred embodiment, it is more apparent that above and other objects of the present invention, characteristic and advantage will become according to following, wherein in the accompanying drawings:
Fig. 1 is the schematic diagram that illustrates according to the steam compression refrigerant circulating system with injector of the first embodiment of the present invention;
Fig. 2 is the sectional view that obtains along the line II-II among Fig. 1;
Fig. 3 illustrates the sectional view of the steam compression refrigerant circulating system that has injector in the comparative example;
Fig. 4 is the schematic diagram that the steam compression refrigerant IA055035 circulatory system with injector according to a second embodiment of the present invention is shown;
Fig. 5 is the schematic diagram that the steam compression refrigerant circulating system with injector of a third embodiment in accordance with the invention is shown;
Fig. 6 is the schematic diagram that the steam compression refrigerant circulating system with injector of a fourth embodiment in accordance with the invention is shown;
Fig. 7 is the schematic diagram that the steam compression refrigerant circulating system with injector according to a fifth embodiment of the invention is shown;
Fig. 8 is the schematic diagram that the steam compression refrigerant circulating system with injector according to a sixth embodiment of the invention is shown;
Fig. 9 is the curve map that the operation of the steam compression refrigerant circulating system among the 6th embodiment is shown;
Figure 10 is the curve map of closing that illustrates between the circulation rate of elapsed time behind the closed electromagnetic valve and lubricating oil;
Figure 11 is the flow chart of the control operation of the control device among the 7th embodiment;
Figure 12 is the schematic diagram that illustrates according to the steam compression refrigerant circulating system with injector of the eighth embodiment of the present invention;
Figure 13 is the schematic diagram that illustrates according to the steam compression refrigerant circulating system with injector of the ninth embodiment of the present invention;
Figure 14 is the schematic diagram that illustrates according to the steam compression refrigerant circulating system with injector of modification of the present invention.
The specific embodiment
To the preferred embodiments of the present invention be described referring to accompanying drawing below.
(first embodiment)
In first embodiment, the steam compression refrigerant circulating system with injector shown in Fig. 1 is generally used for car air-conditioner for instance.Steam compression refrigerant circulating system comprises main refrigerant path 15, and wherein cold-producing medium flows with the order of the suction side of waste side, refrigerant cooler 11, flow regulating valve 12, injector 13, first evaporimeter 14 and the compressor 10 of compressor 10.
In the present embodiment, automobile-used engine drives and rotates compressor 10 by belt and electromagnetic clutch 10a etc.The operation of compressor 10 is by electromagnetic clutch 10a switch and control.In this case, by the on/off operation ratio of control compressor 10, the cold-producing medium discharge capacity of controlled system compressor 10.
By carry out heat exchange between high-pressure refrigerant and the extraneous air (that is, the passenger accommodation air outside) that is blown into by the cooling fan (not shown), refrigerant cooler 11 coolings are from the high-pressure refrigerant of compressor 10 dischargings.In the present embodiment, for example, refrigerant cooler 11 is the condensers that are integrated with gas-liquid separator 11a.The condenser (11) that is integrated with separator be configured be used for cooling off with condensation from the condensation part of the high-pressure refrigerant of compressor 10 dischargings, wherein be divided into the supercooled sub-cooled of the liquid refrigerant portion that the gas-liquid separator 11a of gas refrigerant and liquid refrigerant separates with carrier gas liquid/gas separator 11a wherein from the cold-producing medium of condensation part.
Particularly, injector 13 comprises spray nozzle part 13a and the 13b of diffuser portion.Make the cold-producing medium decompression of constant entropy ground and the expansion substantially of flowing out by reducing cold-producing medium spray nozzle part 13a from flow regulating valve 12.Convert the speed energy of cold-producing medium to by pressure energy, in spray nozzle part 13a, improve the cold-producing medium flow velocity cold-producing medium.
In the 13b of diffuser portion,, the speed energy (dynamic pressure) of cold-producing medium is converted to the pressure energy (static pressure) of cold-producing medium by increasing the cross sectional area of the 13b of diffuser portion gradually.Therefore, refrigerant pressure increases in the 13b of diffuser portion.
The cold-producing medium that flows out the diffuser 13b of portion flows into first evaporimeter 14.For example, first evaporimeter 14 is arranged in the air duct of anterior air-conditioning unit, is used for cooling off the air in the front side of waiting to blast passenger accommodation.
In this case, first air blast 16 (for example, electric blower) is arranged in the anterior air-conditioning unit, and the air in the feasible front side of waiting to blast in the passenger accommodation is sent to first evaporimeter 14.Therefore, by from the absorption of air heat through first evaporimeter 14, the low pressure refrigerant of decompression evaporates in first evaporimeter 14 in injector 13, thereby makes air dehumidification and cooling in the front side of waiting to blast passenger accommodation.The vaporized gas cold-producing medium is inhaled into compressor 10 in first evaporimeter 14, and circulation in main refrigerant circulating path 15.
Be arranged on the refrigerant outlet portion of refrigerant cooler 11 from first and second branched bottoms 17,18 of main refrigerant circulating path 15 bifurcateds.First branched bottom 17 is the coolant channels from the refrigerant outlet portion of refrigerant cooler 11 to the refrigerant suction port 13c of injector 13.In first branched bottom 17, be provided with magnetic valve 19, throttle mechanism 20 and second evaporimeter 21 continuously with order from the cold-producing medium upstream side to the cold-producing medium downstream.
For example, second evaporimeter 21 is arranged in the cold-producing medium that is installed on the vehicle, and cools off the air that blasts by second air blast 22 (for example, electric blower) that is arranged in refrigeration machine.Generally speaking, the variation of the thermic load in the refrigeration machine is very little, so can be with the fixed restriction device as throttle mechanism 20.Yet, also the adjustable choke that is fit to can be used as throttle mechanism 20, and magnetic valve 19 and throttle mechanism 20 can be configured to single component.
Second branched bottom 18 is the coolant channels from the refrigerant outlet portion of refrigerant cooler 11 to the suction side of compressor 10.In second branched bottom 18, throttle mechanism 23 and the 3rd evaporimeter 24 are set continuously successively.For example, the 3rd evaporimeter 24 is arranged in the air duct of rear portion air-conditioning unit (not shown), is used for cooling off the air of the back seat side that blasts passenger accommodation.
For example, air sends to the 3rd evaporimeter 24 by the 3rd air blast (for example, electric blower) that is arranged in the rear portion air-conditioning unit, and from the cooling air of the 3rd evaporimeter 24 by the back seat side of drum in passenger accommodation.By from waiting to blast the absorption of air heat of passenger accommodation back seat side, the low pressure refrigerant of decompression reduces pressure in the 3rd evaporimeter 24 in throttle mechanism 23, thus the air of the back seat side of drum cooler in passenger accommodation, and can obtain refrigerating function.In the example shown in Fig. 1, thermal expansion valve is used as throttle mechanism 23, and regulates the flow of the cold-producing medium that flows into the 3rd evaporimeter 24 by throttle mechanism 23.In this case, the adjustable valve opening degree that flows mechanism 23 successively makes the degree of superheat of cold-producing medium in exit of evaporimeter 24 become predetermined value.
Fig. 2 is the sectional view of the injector 13 that obtains along the line II-II among Fig. 1.Top-bottom direction among Fig. 2 is mounted to the top-bottom direction of vehicle corresponding to injector 13.As shown in Figure 2, injector 13 has cylindrical shell 13d, and the open top of refrigerant suction port 13c in housing 13d.
Cold-producing medium suction pipe 25 has the vertical stretch that is connected to refrigerant suction port 13c, and has height H 1.As shown in fig. 1, cold-producing medium suction pipe 25 is the refrigerant pipes from second evaporimeter 21 to the refrigerant suction port 13c of injector 13.In Fig. 2, cylindrical portion 13e is arranged on the access road of the cylindrical portion 13e formation spray nozzle part 13 of housing 13d inside with shrinking away from theshell body 13d predetermined gap.
The electromagnetic clutch 10a of compressor 10, first to the 3rd air blast 16,22,24a and magnetic valve 19 etc. are by the control signal electric control from control device 26.Control device 26 is configured with micro computer and centers on the circuit of micro computer.The operation signal of the operating parts of the detection signal of sensor groups (not shown) and air conditioning guidance panel is imported into control device 26.
Then, with the operation of describing according to the steam compression circulating system cold-producing medium of present embodiment.When cooling down operation (refrigerating function) is the refrigeration machine institute that is mounted to vehicle when essential, the passenger opens the refrigeration machine switch (not shown) of air conditioning guidance panel.In the cooling down operation of refrigeration machine, the operation of magnetic valve 19 is by control device 26 controls, so that open magnetic valve 19.Under this state, when handling compressor 10 by car engine, compressor 10 is compressed into the high pressure-temperature state with cold-producing medium.The high pressure, high temperature refrigerant of discharging from compressor 10 flows into refrigerant cooler 11, then by extraneous air cooling and condensation.
The cooling refrigeration agent of flowing out refrigerant cooler 11 is branched into the cold-producing medium stream of the cold-producing medium stream of the cold-producing medium stream of the main refrigerant circulating path 15 of flowing through, first branched bottom 17 of flowing through and second branched bottom 18 of flowing through.
Flow through the cold-producing medium of main refrigerant circulating path 15 through flow regulating valve 12, flow into injector 13.The cold-producing medium that flows into injectors 13 from flow regulating valve 12 reduces pressure among spray nozzle part 13a and expands.That is, the pressure energy of cold-producing medium is transformed into the speed energy of cold-producing medium in spray nozzle part 13a, and the high speed cold-producing medium is from the spout ejection of spray nozzle part 13a.Simultaneously, because the high speed jet of cold-producing medium, refrigerant pressure reduces around the outlet of spray nozzle part 13a, thereby vaporized gas cold-producing medium in second evaporimeter 21 is sucked from refrigerant suction port 13c.
Mix in the downstream of spray nozzle part 13a from the cold-producing medium of spray nozzle part 13 ejections with from the cold-producing medium that refrigerant suction port 13c sucks, and flow into the diffuser 13b of portion.Because cross sectional area enlarges in the 13b of diffuser portion, so the speed of cold-producing medium can change into pressure energy in the 13b of diffuser portion, thereby refrigerant pressure increases in the 13b of diffuser portion.The cold-producing medium that flows out the outlet of the diffuser 13b of portion flows into first evaporimeter 14.
In first evaporimeter 14, by from absorption of air heat, make evaporator evaporation, thereby cooling waits to rouse the air of the front stall side in the passenger accommodation through first evaporimeter 14.Gas refrigerant from first evaporimeter 14 is inhaled into compressor 10, and compression in compressor 10, with circulation in main refrigerant circulating path 15.The cold air of cooling is by the front stall side of first air blast, 16 drums in passenger accommodation in evaporimeter 14.Therefore, can carry out the cooling down operation in the front stall zone that is used to cool off passenger accommodation.
If flow regulating valve 12 is thermal expansion valves, then can regulate the valve opening degree of flow regulating valve 12, make the degree of superheat of cold-producing medium of the export department of the evaporimeter 14 of winning become predetermined value, and can be adjusted in the cold-producing medium stream that flows in first evaporimeter 14.
The cold-producing medium that is diverted to second branched bottom 18 from main refrigerant circulating path 15 is depressurized throttle mechanism 23.The low pressure refrigerant that is depressurized in throttle mechanism 23 flows into the 3rd evaporimeter 24, and by from treating that drum is evaporated to the absorption of air heat of passenger accommodation back seat side.The boil-off gas cold-producing medium that is inhaled into from the 3rd evaporimeter 24 is inhaled in the suction volume of compressor 10, and is compressed in compressor 10.Cold air by 24 coolings of the 3rd evaporimeter passes through the back seat district of the 3rd air blast 24a drum in passenger accommodation, so that the back seat district in the cooling passenger accommodation.
From the cold-producing medium of first evaporimeter 14 with from the downstream refrigerant side combination before cold-producing medium flows into compressor 10 of the cold-producing medium of the 3rd evaporimeter 24 at first evaporimeter 14 and the 3rd evaporimeter 24.Therefore, the cold-producing medium evaporating pressure of first evaporimeter 14 is identical with the cold-producing medium evaporating pressure of the 3rd evaporimeter 24.As a result, the cold-producing medium evaporation rate is first identical with 24 places with the 3rd evaporimeter 10, thereby can obtain to have the cooling capacity of uniform temp grade in the first and the 3rd evaporimeter 14 and 24.
The magnetic valve 19 of cold-producing medium through opening from main refrigerant circulating path 15 inflows first branched bottom 17 then is depressurized in throttle mechanism 20.The low pressure refrigerant of decompression flows into second evaporimeter 21 in throttle mechanism 20, and by evaporating second evaporimeter 21 from utilizing second air blast 22 to blast the absorption of air heat of refrigeration machine.Therefore, utilize second evaporimeter 21 can obtain the refrigerating function of cold-producing medium.The gas refrigerant that is evaporated in second evaporimeter 21 sucks the refrigerant suction port 13c of injector 13.
The pressure of the cold-producing medium evaporating pressure of first evaporimeter 14 after corresponding to supercharging in the 13b of diffuser portion.In contrast, because the refrigerant outlet side of second evaporimeter 21 is connected to the refrigerant suction port 13c of injector 13, so the pressure of putting up with in the post-decompression minimizing of spray nozzle part 13a imposes on second evaporimeter 21.
Therefore, can make the cold-producing medium evaporating pressure of second evaporimeter 21 be lower than the cold-producing medium evaporating pressure of first evaporimeter 14 and the 3rd evaporimeter 24.Therefore, can make the cold-producing medium evaporating temperature of second evaporimeter 21 be lower than the cold-producing medium evaporating temperature of first evaporimeter 14 and the 3rd evaporimeter 24.Like this, the refrigerating function in the lower temperature range of the cooling down operation in being suitable for refrigeration machine can be obtained, refrigerating function in the higher temperature scope of the cooling down operation that is suitable for passenger accommodation can be obtained by first evaporimeter 14 and the 3rd evaporimeter 24 simultaneously.
When not needing to be used for the cooling down operation of cooling refrigeration machine, turn off the refrigeration machine switch of air conditioning guidance panel by the passenger.In this case, control device 26 stops power supply to magnetic valve 19, thereby magnetic valve 19 cuts out.Utilize this operation, stop the operation of second air blast 22 by control device 26.
Because magnetic valve 19 cuts out, block the cold-producing medium that flows into first branched bottom 17.In this case, cold-producing medium flow through the main refrigerant circulating path 15 and second branched bottom 18, and obtain to be used to cool off the refrigerating function of passenger accommodation by first evaporimeter 14 and second evaporimeter 24.
When blocking the cold-producing medium stream of first branched bottom 17, cold-producing medium is not inhaled into the refrigerant suction port 13c of injector 13.In this case, the bigger because density that is included in the lubricating oil in the cold-producing medium becomes in the downstream space of the spray nozzle part 13a injector 13 in is so lubricating oil often accumulates in the interior bottom of spray nozzle part 13a downstream injector 13.
Fig. 3 is that the refrigerant suction port 13c that wherein is connected to second evaporimeter 21 is positioned at the comparative example that the bottom side of injector 13 and cold-producing medium suction pipe 25 are connected to the refrigerant suction port 13c below the injector 13.In this case, lubricating oil is because himself gravity falls into refrigeration machine suction inlet 13c, and stays in the cold-producing medium suction pipe 25.
In contrast, in first embodiment, the refrigerant suction port 13c of injector 13 is positioned at the top (for example, the top among Fig. 2) of the housing 13d of injector 13, and the extension that vertically extends predetermined altitude H is arranged in the cold-producing medium suction pipe 25.Therefore, may prevent to be included in the refrigerant suction port 13c that lubricating oil in the cold-producing medium falls within the catchment of the spray nozzle part 13a in the injector 13.
Therefore, prevent that lubricating oil from staying in the cold-producing medium suction pipe 25 when magnetic valve 19 cuts out.As a result, can prevent lubricating oil shortage in the compressor 10.
In the above-described embodiments, refrigerant suction port 13c is arranged on the top of the housing 13d of injector 13.Yet the refrigerant suction port 13c of injector 13 can be arranged on by position " a " and " b " shown in the chain-dotted line among Fig. 2 and locate, and is lower than the top but is higher than the center.In this case, cold-producing medium suction pipe 25 can heeling condition as shown in Figure 2 be connected to refrigerant suction port 13c.Even in this case, can prevent that also lubricating oil from falling into refrigeration machine suction inlet 13c, thereby prevent that lubricating oil from staying in the cold-producing medium suction pipe 25.
And refrigerant suction port 13c can be arranged in the scope " c " (180 ° upper side range) shown in the upper diagram 2 of housing 13d of injector 13.
(second embodiment)
In above-mentioned first embodiment, the refrigerant suction port 13c of injector 13 is arranged on the top of housing 13d.Yet in a second embodiment, as shown in Figure 4, refrigerant suction port 13c is arranged on the bottom of housing 13d, and the erection part 25a that extends in vertical direction is formed on the downstream portion in the cold-producing medium suction pipe 25.Erection part 25a can upwards vertically extend predetermined altitude from the foot of injector 13.In Fig. 4, H2 represents the height of vertically extending erection part 25a.
In the present embodiment, can make the following of downstream of the erection part 25a in the cold-producing medium suction pipe 25 have pipe portion shorter.Therefore, even when the cold-producing medium suction 13c of portion is arranged on the bottom (for example, the bottom) of housing 13d, also the lubricated amount in the cold-producing medium suction pipe 25 stayed can be controlled to be amount seldom.
In Fig. 4, the upstream portion vertical curve of erection part 25a and erection part 25a upstream, however they are also flexible in the arc-shaped.And, the height of change erection part 25a in the time of can only being higher than the cold-producing medium suction 13c of portion at the top of erection part 25a.And, when the top of erection part 25a is set to be higher than the central portion of injector 13, can effectively reduce the lubricated amount of staying in the cold-producing medium suction pipe 25.
In a second embodiment, can be similar to above-mentioned first embodiment and form other parts.
(the 3rd embodiment)
Fig. 5 illustrates the steam compression refrigerant circulating system of the 3rd embodiment.In the 3rd embodiment, magnetic valve 19 is not arranged in first branched bottom 17, and is passing through throttle mechanism 20 back second evaporimeters 21 that flow into first branching portion 17 from the cold-producing medium that main refrigerant circulating path 15 flows out.Therefore, when compressor 10 work, cold-producing medium always flows into second evaporimeter 21 in first branched bottom 17.
Therefore, in the present embodiment,, also stop the operation of second air blast 22 when refrigeration machine function (refrigeration machine cooling down operation) when stopping.When stopping second air blast 22, the caloric receptivity of the cold-producing medium in second evaporimeter 2 is very little, and sucks the refrigerant suction port of injector 13 through a large amount of liquid refrigerants of throttle mechanism 20, and can not be evaporated in second evaporimeter 21.
In the 3rd embodiment, when compressor 10 work, always form cold-producing medium inlet flow from cold-producing medium suction pipe 25 to refrigerant suction port 13c.Therefore, even when refrigerant suction port 13c is arranged on bottom (for example, the bottom), lubricating oil can not fall into refrigerant suction port 13c owing to himself gravity.
In the 3rd embodiment, can be similar to above-mentioned first embodiment other parts are set.And, even in the 3rd embodiment, refrigerant suction port 13c can be arranged on the top of the housing 13d of injector 13.
(the 4th embodiment)
Fig. 6 illustrates the steam compression refrigerant circulating system of the 4th embodiment.In described steam compression refrigerant circulating system, refrigerant suction port 13c is arranged on the bottom (for example bottom) of injector 13, and check-valves 27 is arranged on the inlet portion of refrigerant suction port 13c.That is, only allow the check-valves 27 of unidirectional cold-producing medium stream to be positioned at the downstream end of cold-producing medium suction pipe 25 from cold-producing medium suction pipe 25 to refrigerant suction port 13c.Therefore, check-valves 27 prevents cold-producing medium and the lubricating oil reverse flow from refrigerant suction port 13c to cold-producing medium suction pipe 25.
Therefore, check-valves 27 prevents that lubricating oil from staying in the cold-producing medium suction pipe 25 when magnetic valve 19 cuts out.That is, when refrigeration machine function (refrigeration machine cooling down operation) when stopping, check-valves 27 prevents that lubricating oil from flowing into cold-producing medium suction pipe 25 from refrigerant suction port 13c, even also be like this when refrigerant suction port 13c is arranged on the bottom of housing 13d.
In the 4th embodiment, can with the similar formation other parts of above-mentioned first embodiment.
(the 5th embodiment)
Fig. 7 illustrates the steam compression refrigerant circulating system of the 5th embodiment.In above-mentioned first embodiment, magnetic valve 19 is arranged on the upstream side of the throttle mechanism 20 in first branched bottom 17.In described the 5th embodiment, refrigerant suction port 13c is arranged on the bottom (for example, the bottom) of housing 13d, and magnetic valve 19 is positioned at the inlet portion of refrigerant suction port 13c.That is, magnetic valve 19 is positioned at the downstream end of cold-producing medium suction pipe 25.And the bypass channel 28 that is connected to the suction side of compressor 10 is connected to first branched bottom 17 in the downstream of second evaporimeter 21.The pilot solenoid valve 29 that is operably connected with magnetic valve 19 is arranged in bypass channel 28.
In the 5th embodiment,, close magnetic valve 19 by the control output of control device 26, and pilot solenoid valve 29 is opened when the switch of opening refrigeration machine and when setting the refrigeration machine halted state.And, stop the operation of second air blast 22 by the control output of control device 26.
Close owing to be positioned at the magnetic valve 19 of the inlet portion of refrigerant suction port 13c, stay in the cold-producing medium suction pipe 25 so can prevent lubricating oil, even also be like this when refrigerant suction port 13c is arranged on the bottom of injector 13.And, flow to the suction side of compressor 10 owing to import the cold-producing medium of first branched bottom 17 by bypass channel 28, stay in second evaporimeter 21 when magnetic valve 19 cuts out so can prevent lubricating oil.
In the 5th embodiment, when the switch of opening refrigeration machine and manipulation refrigeration machine, magnetic valve 19 is opened, and pilot solenoid valve 29 is closed, and handles second air blast 22 by the control output of control device 26.
(the 6th embodiment)
Fig. 8 illustrates the steam compression refrigerant circulating system of the 6th embodiment.In the 6th embodiment, similar with the comparative example of Fig. 3, refrigerant suction port 13c is arranged on the bottom of injector 13, and cold-producing medium suction pipe 25 is connected to the cold-producing medium suction portion 13 in the bottom side of injector 13.
In the 6th embodiment, the opening and closing operation of control magnetic valve 19 in the refrigeration machine halted state.Particularly, timer 26 is arranged in the control device 26.At compressor 10 duration of works, when the refrigeration machine switch of air conditioning panel cuts out and sets the refrigeration machine halted state, the function of beginning timer 2 6a.
The function of timer 2 6a will be described referring to Fig. 9.The abscissa of Fig. 9 represents to set the elapsed time after the refrigeration machine halted state.After setting the refrigeration machine halted state during through scheduled time t1, or rather, in the closed condition that continues magnetic valve 19 after the scheduled time, based on signal force switch (opening and closing) magnetic valve 19 pre-determined numbers from the timer 2 6a of control device 26.
That is, the operation of magnetic valve 19 makes the lasting scheduled time " ton " of open mode of magnetic valve 19 and lasting second scheduled time " off " of closed condition of magnetic valve 19 alternately repeat pre-determined number by the timer 2 6a control of control device 26.In this case, cold-producing medium can flow into first branched bottom 17 intermittently, and can will stay the refrigerant suction port 13c that lubricating oil in the cold-producing medium suction pipe 25 sends to injector 13.
Figure 10 illustrates the situation that magnetic valve 19 cuts out during the refrigeration machine halted state.The abscissa of Figure 10 represents to set the elapsed time after the refrigeration machine halted state.When magnetic valve 19 cut out, along with the elapsed time becomes more and more longer, the lubricated amount of staying in the cold-producing medium suction pipe 25 increased.Therefore, the circulation rate R1 (oil recycle ratio) that sucks the lubricating oil of compressor 10 reduces.Oil recycle ratio R1 can calculate according to following formula:
R1＝A1/(A1+A2)×100(％)
Wherein A1 represents to return the lubricants capacity of compressor 10, and A2 represents to return the refrigerant amount of compressor 10.
As shown in Figure 10, after magnetic valve 19 cuts out back elapsed time t1, cause the shortage of the oil of compressor 10.Therefore, the temperature of compressor 10 is brought up to limiting temperature, and compressor 10 becomes maximum heat state (heat limit).
Therefore, as shown in Figure 9, in the 6th embodiment, after magnetic valve 19 cuts out back elapsed time t1, alternately repeat the opening and closing scheduled time of magnetic valve 19.In this case, the necessary grade that oil recycle ratio can be improved, thus can prevent the shortage of the lubricating oil in the compressor 10.
In Fig. 9, positive opening magnetic valve 19 is set at three times repeatedly.Yet, can will be set at repeatedly more than once repeatedly.
(the 7th embodiment)
To the seventh embodiment of the present invention be described referring to Figure 11 now.Figure 11 illustrates the control operation according to the control device 26 of the modification of the 6th embodiment.In the 7th embodiment, in the control operation of the 6th embodiment, add the operation of step S12.That is, can with the similar execution of the control operation of above-mentioned the 6th embodiment other step except step S12.
The control operation of the 7th embodiment will be described now.At first, at step S11, determine whether to carry out the cooling down operation of second evaporimeter 21.When not carrying out the cooling down operation of second evaporimeter 21, the operation of execution in step S12.
At step S12, after handling steam compression refrigerant circulating system (compressor 10), only carry out oil and return control once.Return control period at oil, open 19 scheduled times of magnetic valve as switch valve.After execution oil returns control, close magnetic valve 19, simultaneously, control program moves to step S13.For example, in the steam compression refrigerant circulating system shown in Fig. 8, even when the time that steam compression refrigerant circulating system begins stops the refrigerating function of second evaporimeter 21, the lubricating oil of staying in the refrigerant pipe of second evaporimeter 21 and second evaporimeter, 21 sides can be sucked refrigerant suction port 13c, and can make it return the suction side of compressor 100.
Then, at step S13, handle the timer 2 6a of the control device of describing among the 6th embodiment 26.Then, at step S14, determine whether disappear the scheduled time at setting timer 2 6a head.
After step S14 disappears the scheduled time, carry out oil at step S15 and return the control predetermined time interval.That is, return control period and open magnetic valve 19 predetermined time intervals at oil.After opening magnetic valve 19 predetermined time intervals, close magnetic valve 19, and control program proceeds to step S15.
At step S16, replacement timer 2 6a, thus can repeat the control program shown in Figure 11.
According to the 7th embodiment, when when steam compression refrigerant circulating system begins, stopping the refrigerating function of second evaporimeter 21, open magnetic valve 19 predetermined time intervals.Therefore, even when not carrying out the refrigerating function of second evaporimeter 21 in the moment that steam compression refrigerant circulating system begins, the lubricating oil of staying in the refrigerant pipe of second evaporimeter 21 and second evaporimeter, 21 1 sides can be inhaled into refrigerant suction port 13c once, and can return the suction side of compressor 10.
Therefore, when the refrigerating function of second evaporimeter 21 stops, can preventing to return the shortage of the oil mass of compressor 10, and compressor 10 can be stablized and works effectively.Similar to the 6th embodiment, carry out oily return once after, at the closed condition certain hour that continues magnetic valve 19 back positive opening magnetic valve 19 at interval.
(the 8th embodiment)
Figure 12 illustrates the steam compression refrigerant circulating system of the 8th embodiment.Compare with the structure of the comparative example of Fig. 3, in the steam compression refrigerant circulating system shown in Figure 12, bypass channel 31 is set in addition and is used to open and close the pilot solenoid valve 32 of bypass channel 31.By bypass channel 31, the cold-producing medium inflow refrigerant suction port 13c from main refrigerant circulating path 15 walks around the magnetic valve 19 and second evaporimeter 21 simultaneously.
In the 8th embodiment, when not carrying out the cooling down operation of second evaporimeter 21, open pilot solenoid valve 32, make cold-producing medium flow through bypass channel 31 scheduled volumes.Magnetic valve 19 and pilot solenoid valve 32 are by control device 26 controls.With the flow set of the cold-producing medium in the bypass channel 31 for only preventing lubricating oil because himself gravity falls into refrigerant suction port 13c.Therefore, can be less with the flow set of the cold-producing medium in the bypass channel 31, and can be with capillary as bypass channel 31.
According to the 8th embodiment, when by closing magnetic valve 19 when stopping the cooling down operation of second evaporimeter 21, cold-producing medium flows through bypass channel 31 predetermined amount of flow.Therefore, cold-producing medium always flows into the refrigerant suction port 13c of injectors 13 from bypass channel 31, thereby prevents lubricating oil because himself gravity falls into refrigerant suction port 13c.
The amount of returning of lubricating oil of returning compressor 1 when as a result, the cooling down operation that can prevent second evaporimeter 21 stops is insufficient.The greasy property that therefore, can keep compressor 10 effectively.
(the 9th embodiment)
In above-mentioned first to the 8th embodiment, be provided with first branched bottom 17, wherein the downstream of refrigerant cooler 11 is connected to the refrigerant suction port 13c of injector 13 by described first branched bottom 17.And magnetic valve 19, throttle mechanism 20 and second evaporimeter 21 are set in sequence in first branched bottom 17.In the 9th embodiment, change the arrangement of first branched bottom 17 as shown in Figure 13.
In the 9th embodiment, gas-liquid separator 30 is arranged on the downstream of first evaporimeter 14, and it is separated in gas-liquid separator 30 to flow out the cold-producing medium of first evaporimeter 14.The liquid refrigerant that separates in gas-liquid separator 30 is stored in the gas-liquid separator 30, and the gas refrigerant in the gas-liquid separator 30 is supplied with the suction side of compressor 10.
And liquid refrigerant outlet 30a is arranged on the bottom of gas-liquid separator 30, and uses first branched bottom 17 to make liquid refrigerant outlet 30a be connected to refrigerant suction port 13c.In first branched bottom 17, on the refrigerant flow direction of first branched bottom 17, set gradually magnetic valve 19, throttle mechanism 20 and second evaporimeter 21.
Similar to above-mentioned first embodiment, refrigerant suction port 13c is arranged on the top of injector 13.And refrigerant suction port 25 has the vertically extending erection part that makes progress from refrigerant suction port 13c.Therefore, can effectively prevent lubricating oil because himself gravity falls into refrigerant suction port 13c.
Identical with above-mentioned first embodiment, in the 9th embodiment, the cold-producing medium evaporating pressure of second evaporimeter 21 (cold-producing medium evaporating temperature) is lower than the cold-producing medium evaporating pressure (cold-producing medium evaporating temperature) of first evaporimeter 14.
And, in the 9th embodiment, omit the gas-liquid separator 11a of stream proximate valves 12 and the refrigerant cooler 11 of above-mentioned first to the 8th embodiment.In described the 9th embodiment, gas-liquid separator 30 is arranged on the downstream of first evaporimeter 14, and the gas separated cold-producing medium is inhaled into compressor 10 in liquid separator 30.
And, when carrying out the cooling down operation of second evaporimeter 21, open magnetic valve 19, so that the liquid refrigerant in the gas-liquid separator 30 imports second branched bottom 17 from liquid refrigerant outlet 30a.Liquid refrigerant from the liquid refrigerant of gas-liquid separator 30 outlet 30a reduce pressure in throttle structure 20, and evaporates in second evaporimeter 21.Cold-producing medium from second evaporimeter 21 sucks injector 13 from refrigerant suction port 13c.
In the 9th embodiment, the structure of the change of first branched bottom 17 and gas-liquid separator 30 is used for the steam compression refrigerant circulating system of first embodiment and combines with it.Yet the structure of this change can be used for the arbitrary steam compression refrigerant circulating system according to second to the 8th embodiment.
(other embodiment)
Although invention has been described in conjunction with preferred embodiments more of the present invention referring to accompanying drawing, should point out that variations and modifications are obvious to those of skill in the art.
For example, in above-mentioned first to the 9th embodiment, the front stall district that first evaporimeter 14 is used to cool off passenger accommodation, the back seat district that the 3rd evaporimeter 24 is used to cool off passenger accommodation, and second evaporimeter 21 is used to carry out the cooling down operation of refrigeration machine.Yet, in the above-described embodiments, can omit the 3rd evaporimeter 24 and the coolant channel structure that is used for the 3rd evaporimeter 24.For example, the present invention can be applicable to not be with the steam compression refrigerant circulating system of the 3rd evaporimeter 24 as shown in Figure 14.
In the example shown in Figure 14, in the system architecture of the 9th embodiment, omitted the 3rd evaporimeter 24.Yet, can in according to one the steam compression refrigerant circulating system of first to the 8th embodiment, omit the 3rd evaporimeter 24.
In above-mentioned first to the 9th embodiment, second evaporimeter 21 is used to be mounted to the cooling down operation of the refrigeration machine of vehicle.Yet first and second evaporimeters 14 and 21 can be used for carrying out the air conditioning operation of the zones of different in the passenger accommodation of vehicle.For example, in the situation that the 3rd evaporimeter 24 is not set, first evaporimeter 14 and second evaporimeter 21 can be used for carrying out the air conditioning in interior front stall district of passenger accommodation and the back seat district.
Alternatively, first evaporimeter 14 and second evaporimeter 21 can be used for carrying out the cooling down operation of refrigeration machine.In this case, wherein the first higher evaporimeter 14 of cold-producing medium evaporating temperature can be used as the cooling chamber of refrigeration machine, and second evaporimeter 21 that wherein the cold-producing medium evaporating temperature is lower can be used as the refrigerating chamber of refrigeration machine.
In the above-described embodiments, can use any cold-producing medium that is used in usually in the steam compression refrigerant circulating system.For example, can be with freon family cold-producing medium, organic compound cold-producing medium, HC group cold-producing medium and carbon dioxide as cold-producing medium.And, can be with steam compression refrigerant circulating system as having a supercritical refrigerant circulatory system of the high-pressure side refrigerant pressure that is higher than the cold-producing medium critical pressure, or as the refrigerant-cycle systems with the high-pressure side refrigerant pressure that is lower than the cold-producing medium critical pressure.Here, the organic compound cold-producing medium is made up of carbon, fluorine, chlorine and hydrogen, is normally used cold-producing medium.Freon family cold-producing medium is hydrochlorofluorocarazeotropic (HCFC) family's cold-producing medium or hydrogen fluorine carbon (HFC) family cold-producing medium for instance.And, can be with isobutene (R600a), propane (R290) as hydrocarbon (HC) family cold-producing medium.
In the above-described embodiments, can be with fixed volume formula compressor as compressor 10.In this case, use the squeeze operation of clutch 10a control compressor 10, and control the discharge capacity of cold-producing medium from compressor 10 by the operation of opening/manage of control compressor 10.Alternatively, can be with variable displacement compressor as compressor 10.In this case, the volume of compressor is by control device 26 controls, so that can control from the refrigerant amount of compressor 10 dischargings.Alternatively, can be with motor compressor as compressor 10.In this case, by the rotary speed of control motor compressor 10, can control from the refrigerant amount of compressor 10 dischargings.
In the above-described embodiments, can be with adjustable nozzle as spray nozzle part 13a.In this case, can change the cold-producing medium flow area (for example, throttling opening degree) of spray nozzle part 13a.
In above-mentioned first to the 8th embodiment, flow regulating valve 12 is arranged on the upstream portion of injector 13.Yet, when the flow of the cold-producing medium that flows is regulated by the throttle operation of injector 13, can omit flow regulating valve 12 in first evaporimeter 14.
Although invention has been described referring to the preferred embodiments of the present invention, should be understood that to the invention is not restricted to preferred embodiment and structure.The object of the invention is to cover various modifications and equivalent arrangements.In addition, although each parts of preferred embodiment are shown with various preferred compositions and structure, comprise more, still less or only make up also within the spirit and scope of the present invention with other of each parts.
Claims (11)
1. steam compression refrigerant circulating system comprises:
Compressor (10) is used for compressed refrigerant;
Refrigerant cooler (11) is used to cool off the high-pressure refrigerant from compressor discharge;
Injector (13) comprising: nozzle (13a) is used to make cold-producing medium decompression and expansion from refrigerant cooler (11); Refrigerant suction port (13c), the cold-producing medium stream that sprays from nozzle (13a) sucks gas refrigerant from described refrigerant suction port; And supercharging portion (13b), wherein mix from the cold-producing medium of nozzle ejection with from the gas refrigerant that refrigerant suction port sucks, and by speed being converted to the pressure that pressure energy improves cold-producing medium;
First evaporimeter (14) is used to make the cold-producing medium evaporation of the supercharging portion of outflow jet, and described first evaporimeter is positioned at the injector downstream, and has the refrigerant outlet that is connected to the compressor suction side;
Second evaporimeter (21) is used to make the cold-producing medium evaporation of refrigerant suction port to be sucked (13c);
Automatically controlled valve member (19) is used to open and close the coolant channel of second evaporimeter, described automatically controlled valve member in cold-producing medium stream with the second evaporator series setting;
Cold-producing medium suction pipe (25) has first end of the refrigerant outlet that is connected to second evaporimeter and is connected to second end of refrigerant suction port; And
Restraint device is used for preventing being directed in the system cryogen suction pipe (25) by refrigerant suction port (13c) and staying in the cold-producing medium suction pipe (25) when automatically controlled valve member (19) is included in cold-producing medium when closing lubricating oil.
2. steam compression refrigerant circulating system according to claim 1, wherein refrigerant suction port is arranged on the injector upside as described restraint device.
3. steam compression refrigerant circulating system according to claim 1, wherein refrigerant suction port is arranged on the bottom of injector, cold-producing medium suction pipe (25) has the erection part (25a) of the described restraint device of conduct that is positioned at downstream position, and described erection part (25a) extends up to the position that is higher than refrigerant suction port.
4. steam compression refrigerant circulating system according to claim 1, wherein said restraint device are the check-valves (27) that is positioned at the inlet portion place of refrigerant suction port (13c), only allow cold-producing medium to flow to refrigerant suction port from the cold-producing medium suction pipe.
5. steam compression refrigerant circulating system comprises:
Compressor (10) is used for compressed refrigerant;
Refrigerant cooler (11) is used to cool off the high-pressure refrigerant from compressor discharge;
Injector (13) comprising: nozzle (13a) is used to make cold-producing medium decompression and expansion from refrigerant cooler (11); Refrigerant suction port (13c), the cold-producing medium stream that sprays from nozzle (13a) sucks gas refrigerant from described refrigerant suction port; And supercharging portion (13b), wherein mix from the cold-producing medium of nozzle ejection with from the gas refrigerant that refrigerant suction port sucks, and by speed being converted to the pressure that pressure energy improves cold-producing medium;
First evaporimeter (14) is used to make the cold-producing medium evaporation of the supercharging portion of outflow jet, and described first evaporimeter is positioned at the injector downstream, and has the refrigerant outlet that is connected to the compressor suction side;
Second evaporimeter (21) is used to make the cold-producing medium evaporation of refrigerant suction port to be sucked (13c);
Automatically controlled valve member (19) is positioned at the inlet portion of refrigerant suction port (13c);
Auxiliary automatically controlled valve member (29) is arranged in the bypass channel (28), wherein from the cold-producing medium of second evaporimeter (21) refrigerant suction port, wherein by described bypass channel (28) importing compressor:
Auxiliary automatically controlled valve member (29) is opened when closing at described automatically controlled valve member (19), thereby flows out the suction side of the cold-producing medium inflow compressor of second evaporimeter (21).
6. steam compression refrigerant circulating system comprises:
Compressor (10) is used for compressed refrigerant;
Refrigerant cooler (11) is used to cool off the high-pressure refrigerant from compressor discharge;
Injector (13) comprising: nozzle (13a) is used to make cold-producing medium decompression and expansion from refrigerant cooler; Refrigerant suction port (13c), the refrigerant vapour that sprays from nozzle (13a) sucks gas refrigerant from described refrigerant suction port; And supercharging portion (13b), wherein mix from the cold-producing medium of nozzle ejection with from the gas refrigerant that refrigerant suction port sucks, and by speed being converted to the pressure that pressure energy improves cold-producing medium;
First evaporimeter (14) is used to make the cold-producing medium evaporation of the supercharging portion of outflow jet, and described first evaporimeter is positioned at the injector downstream, and has the refrigerant outlet that is connected to the compressor suction side;
Second evaporimeter (21) is used to make the cold-producing medium evaporation of refrigerant suction port to be sucked (13c), and described evaporation apparatus is useful on the refrigerating function of cooling air;
Air blast (22) is used for the air drum to second evaporimeter (21); With
Cold-producing medium suction pipe (25) has first end of the refrigerant outlet that is connected to second evaporimeter and is connected to second end of refrigerant suction port (13c), wherein:
Cold-producing medium always flows into second evaporimeter (21) when compressor operating; And
Described air blast (22) stops when the refrigerating function of second evaporimeter (21) stops.
7. steam compression refrigerant circulating system comprises:
Compressor (10) is used for compressed refrigerant;
Refrigerant cooler (11) is used to cool off the high-pressure refrigerant from compressor discharge;
Injector (13) comprising: nozzle (13a) is used to make cold-producing medium decompression and expansion from refrigerant cooler; Refrigerant suction port (13c), the refrigerant vapour that sprays from nozzle (13a) sucks gas refrigerant from described refrigerant suction port; And supercharging portion (13b), wherein mix from the cold-producing medium of nozzle ejection with from the gas refrigerant that refrigerant suction port sucks, and by speed being converted to the pressure that pressure energy improves cold-producing medium;
First evaporimeter (14) is used to make the cold-producing medium evaporation of the supercharging portion of outflow jet, and described first evaporimeter is positioned at the injector downstream, and has the refrigerant outlet that is connected to the compressor suction side;
Second evaporimeter (21) is used to make the cold-producing medium evaporation of refrigerant suction port to be sucked (13c), so that have refrigerating function;
Automatically controlled valve member (19) is used to open and close the coolant channel of second evaporimeter (21), described automatically controlled valve member in cold-producing medium stream with the second evaporator series setting;
Cold-producing medium suction pipe (25) has first end of the refrigerant outlet that is connected to second evaporimeter and is connected to second end of refrigerant suction port; And
Control device (26) is used to control the operation of automatically controlled valve member,
Wherein at compressor (10) duration of work, after closing automatically controlled valve member (19) during through the scheduled time, the automatically controlled valve member of described control device (26) positive opening (19).
8. steam compression refrigerant circulating system according to claim 7, wherein when the moment that compressor (10) is started working stopped the refrigerating function of second evaporimeter (21), automatically controlled valve member (19) was opened predetermined time interval.
9. steam compression refrigerant circulating system comprises:
Compressor (10) is used for compressed refrigerant;
Refrigerant cooler (11) is used to cool off the high-pressure refrigerant from compressor discharge;
Injector (13) comprising: nozzle (13a) is used to make cold-producing medium decompression and expansion from refrigerant cooler; Refrigerant suction port (13c), the refrigerant vapour that sprays from nozzle (13a) sucks gas refrigerant from described refrigerant suction port; And supercharging portion (13b), wherein mix from the cold-producing medium of nozzle ejection with from the gas refrigerant that refrigerant suction port sucks, and by speed being converted to the pressure that pressure energy improves cold-producing medium;
First evaporimeter (14) is used to make the cold-producing medium evaporation of the supercharging portion of outflow jet, and described first evaporimeter is positioned at the injector downstream, and has the refrigerant outlet that is connected to the compressor suction side;
Second evaporimeter (21) is used to make the cold-producing medium evaporation of refrigerant suction port to be sucked (13c);
The first automatically controlled valve member (19) is used to open and close the coolant channel of second evaporimeter, described automatically controlled valve member in cold-producing medium stream with the second evaporator series setting;
Cold-producing medium suction pipe (25) has first end of the refrigerant outlet that is connected to second evaporimeter and is connected to second end of refrigerant suction port (13c); And
Bypass channel (31), wherein the cold-producing medium from refrigerant cooler (11) flows into refrigerant suction port (13c) by described bypass channel, walks around second evaporimeter (21) and described automatically controlled valve member (19) simultaneously; And
The second automatically controlled valve member (32) is positioned on the described bypass channel (31), is used to open and close described bypass channel (31), wherein
At compressor (10) duration of work, when closing the first automatically controlled valve member (19), open the second automatically controlled valve member (32).
10. according to arbitrary described steam compression refrigerant circulating system among the claim 4-9, wherein refrigerant suction port is arranged on the bottom of injector.
11. a steam compression refrigerant circulating system comprises:
Compressor (10) is used for compressed refrigerant;
Refrigerant cooler (11) is used to cool off the high-pressure refrigerant from compressor discharge;
Injector (13) comprising: nozzle (13a) is used to make cold-producing medium decompression and expansion from refrigerant cooler (11); Refrigerant suction port (13c), the cold-producing medium stream that sprays from nozzle (13a) sucks gas refrigerant from described refrigerant suction port; And supercharging portion (13b), wherein mix from the cold-producing medium of nozzle ejection with from the gas refrigerant that refrigerant suction port sucks, and by speed being converted to the pressure that pressure energy improves cold-producing medium;
First evaporimeter (14) is used to make the cold-producing medium evaporation of the supercharging portion of outflow jet, and described first evaporimeter is positioned at the injector downstream, and has the refrigerant outlet that is connected to the compressor suction side;
Second evaporimeter (21) is used to make the cold-producing medium evaporation of refrigerant suction port to be sucked (13c);
Automatically controlled valve member (19) is used to open and close the coolant channel of second evaporimeter, described automatically controlled valve member in cold-producing medium stream with the second evaporator series setting;
Cold-producing medium suction pipe (25) has first end of the refrigerant outlet that is connected to second evaporimeter and is connected to second end of refrigerant suction port;
Bypass channel (31), wherein the cold-producing medium from refrigerant cooler (11) flows into refrigerant suction port (13c) by described bypass channel, walks around second evaporimeter (21) and described automatically controlled valve member (19) simultaneously; And
Auxiliary automatically controlled valve member (32) is positioned on the described bypass channel, is used to open and close described bypass channel, wherein
At compressor (10) duration of work, when closing described automatically controlled valve member, open described auxiliary automatically controlled valve member.
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| CNB2005101041902A Active CN100378411C (en) | 2004-09-29 | 2005-09-29 | Vapor-compression refrigerant cycle system with ejector |
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| US9453668B2 (en) * | 2010-10-18 | 2016-09-27 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus and refrigerant circulating method |
| CN103032119A (en) * | 2011-12-19 | 2013-04-10 | 摩尔动力(北京)技术股份有限公司 | Cold source power system |
| CN103712277B (en) * | 2012-09-29 | 2017-10-13 | 杭州三花研究院有限公司 | A kind of automotive air-conditioning system |
| CN104633881B (en) * | 2015-02-11 | 2017-11-14 | 山西方洁路路通净化技术有限公司 | A kind of injecting type air-conditioning of heat energy recycling |
| US10323545B2 (en) | 2015-06-02 | 2019-06-18 | Heat Source Energy Corp. | Heat engines, systems for providing pressurized refrigerant, and related methods |
| CN106196678B (en) * | 2016-07-10 | 2018-10-12 | 北京工业大学 | A kind of pump driving double evaporators base station heat radiator with injector |
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| US5444987A (en) * | 1993-07-02 | 1995-08-29 | Alsenz; Richard H. | Refrigeration system utilizing a jet enthalpy compressor for elevating the suction line pressure |
| JPH11139154A (en) * | 1997-11-07 | 1999-05-25 | Tgk Co Ltd | Air conditioner for automobile |
| JP3322263B1 (en) * | 2000-03-15 | 2002-09-09 | 株式会社デンソー | Ejector cycle, gas-liquid separator used therefor, and water heater and heat management system using this ejector cycle |
| US20030131611A1 (en) * | 2002-01-15 | 2003-07-17 | Hiroshi Oshitani | Air conditioner with ejector cycle system |
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| Publication number | Publication date |
|---|---|
| CN1755297A (en) | 2006-04-05 |
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