CN101737987A - refrigerating cycle - Google Patents
refrigerating cycle Download PDFInfo
- Publication number
- CN101737987A CN101737987A CN200910226504A CN200910226504A CN101737987A CN 101737987 A CN101737987 A CN 101737987A CN 200910226504 A CN200910226504 A CN 200910226504A CN 200910226504 A CN200910226504 A CN 200910226504A CN 101737987 A CN101737987 A CN 101737987A
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- Prior art keywords
- temperature
- expansion valve
- refrigeration cycle
- heat exchange
- low
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
- F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/068—Expansion valves combined with a sensor
- F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Temperature-Responsive Valves (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
A refrigerating cycle capable of certainly and effectively suppressing an excessive increase of refrigerant temperature at a suction side of a compressor without complicating a piping system and a structure of an expansion valve is provided. A refrigerant cycle includes a compressor 101, a condenser 102, an evaporator 103, an internal heat exchanger 104, and an expansion valve 111. In the internal heat exchanger 104, a heat exchange is carried out between a high-temperature refrigerant introduced from the condenser 102 to the expansion valve 111 and a low-temperature refrigerant introduced from the evaporator 103 to the suction side of the compressor 101. In order to detect temperature and/or pressure of a low-temperature refrigerant introduced toward the suction side of the compressor 101 after carrying out the heat exchange in the internal heat exchanger 104, a temperature-sensitive cylinder 70 and/or an external pressure introduction pipe 50 are additionally provided at the expansion valve 111. In the expansion valve 111, a flowing rate of a refrigerant introduced to the evaporator 103 is adjusted responding to temperature and/or pressure of a low-temperature refrigerant after the heat exchange.
Description
Technical field
The present invention relates to a kind of kind of refrigeration cycle that is used for air conditioning for automobiles etc., relate in particular to a kind of kind of refrigeration cycle, it has compressor, condenser, evaporimeter, inner heat exchanger and expansion valve, in inner heat exchanger, carrying out heat exchange from the cold-producing medium of the high temperature of condenser guiding expansion valve with between the refrigerant of low temperature of the suction side of evaporimeter guiding compressor.
Background technology
Being used for the kind of refrigeration cycle of air conditioning for automobiles etc.,, propose and practical application has structure for example shown in Figure 9 in order to improve refrigerating capacity etc. in the past.Promptly, kind of refrigeration cycle 10 in the illustrated embodiment, have compressor 101, condenser 102, evaporimeter 103, inner heat exchanger 104 and expansion valve 110 (aftermentioned), in inner heat exchanger 104, carrying out heat exchange (for example with reference to following patent documentation 1,2) from the cold-producing medium (liquid state) of the HTHP of condenser 102 guiding expansion valves 110 with between the cold-producing medium (gaseous state) of the low-temp low-pressure of the suction side of evaporimeter 103 guiding compressors 101.
An example of this kind of refrigeration cycle 10 employed expansion valves 110 of expression in Figure 10.The expansion valve 110 of illustrated embodiment, be provided with valve chamber 24 with inflow entrance 21 and seat portion 25 (valve port 26), this inflow entrance 21 is used for the high temperature refrigerant from inner heat exchanger 104 is imported to the bottom of valve body 20, and the central portion at expansion valve 110 is provided with flow export 22, and, about the top of valve body 20, be provided with temperature-sensitive inflow entrance 31 and flow export 32, topmost at valve body 20, be equipped with as the diaphragm apparatus 40 of temperature-sensitive pressure-sensitive with moving cell, it changes along with the variations in temperature of the cold-producing medium that flows to flow export 32 from temperature-sensitive with inflow entrance 31 and pressure and moves.
On described valve chamber 24, dispose the spherical valve core 30 that opens and closes described valve port 26 and with this spherical valve core 30 to the helical spring 27 that closes the backup of valve direction.
Described diaphragm apparatus 40 has barrier film 42, this barrier film 42 is used for upward described spherical valve core 30 being driven in the switching direction (above-below direction) of described spherical valve core 30 by drive rod 35 and union body 36, with this barrier film 42 as the next door, descend direction thereon, zoning forms upside balancing gate pit 43 and downside balancing gate pit 44.Enclose the gas that authorized pressure is arranged and pass through to cover 46 sealings upside balancing gate pit 43.Downside balancing gate pit 44 is communicated with inflow entrance 31 and flow export 32 with described temperature-sensitive by open communication portion 45, acts on the lower face side of described barrier film 42 from the pressure of the low-temperature refrigerant of evaporimeter 103 guiding inner heat exchangers 104.
In addition, for described downside balancing gate pit 44, temperature-sensitive are cut off with the circulation that is communicated with of described cold-producing medium flow export 22 with inflow entrance 31, flow export 32, near the central interior that the drive rod 35 of valve body 20 is connected, be provided with hole 38, and between the outer peripheral face of the inner peripheral surface in this hole 38 and drive rod 35, the O shape circle 39 as seal be installed.And, in the bottom of valve chamber 24, having screwed togather spring pressure and regulated with nut 28, the non-O shape that screws togather partly and be equipped with between the inner peripheral surface of valve chamber 24 as seal of regulating with nut 28 at this spring pressure encloses 29.
Therefore, in the expansion valve 110 that constitutes like this, the flow (pressure decline degree and temperature decline degree) of the cold-producing medium of deriving to described evaporimeter 103 from flow export 22 is adjusted according to the temperature and pressure that carries out the low-temperature refrigerant before the heat exchange by described inner heat exchanger 104.
Patent documentation 1: TOHKEMY 2000-346466 communique
Patent documentation 2: TOHKEMY 2007-240041 communique
The problem that invention will solve
Yet, in kind of refrigeration cycle 10 with described inner heat exchanger 104 and expansion valve 110, owing in inner heat exchanger 104, carry out heat exchange, the temperature that is drawn into the cold-producing medium in the compressor 101 is risen, compressor inside (discharge) temperature becomes too high thereupon, the oily deterioration that may take place in the cold-producing medium in this case to be contained and produce unfavorable conditions such as sintering.
In order to prevent the generation of this bad phenomenon, in above-mentioned patent documentation 1, proposition is carried out perception to the refrigerant temperature of compressor suction side, and the countermeasure of the flow of the cold-producing medium that flows through inner heat exchanger being adjusted with triple valve, but in this countermeasure, therefore need triple valve, have piping system is become trend that number of packages complicated, parts also increases.
And, in above-mentioned patent documentation 2, the countermeasure that bypass is arranged at expansion valve and cold-producing medium is cooled off is proposed, but in this countermeasure, when load change, can not control the refrigerant temperature of compressor suction side, and it is complicated that the structure of expansion valve becomes, and causes cost to increase.
Summary of the invention
The present invention In view of the foregoing makes, and its purpose is, a kind of kind of refrigeration cycle is provided, and it can not make the complex structure of piping system and expansion valve, and the refrigerant temperature that reliably and effectively suppresses the compressor suction side excessively rises.
In order to achieve the above object, kind of refrigeration cycle of the present invention, basically has compressor, condenser, evaporimeter, inner heat exchanger and expansion valve, in described inner heat exchanger, carry out heat exchange between the refrigerant of low temperature of suction side of described compressor of leading at the cold-producing medium of the high temperature of the described expansion valve that leads from described condenser with from described evaporimeter, it is characterized in that, for the suction side of the described compressor of sensing directional, carry out the temperature and/or the pressure of the low-temperature refrigerant after the heat exchange by described inner heat exchanger, described expansion valve is set up temperature sensing tube and/or external pressure ingress pipe, in described expansion valve, according to the temperature and/or the pressure of the low-temperature refrigerant after the described heat exchange, the flow of the cold-producing medium that the described evaporimeter of subtend is derived is adjusted.
In preferable form, described expansion valve has driver elements such as diaphragm apparatus, this diaphragm apparatus moves along with changing by described external pressure ingress pipe pressure that import, that carried out the low-temperature refrigerant after the heat exchange, on the switching direction of spool spool is driven.
In other preferable form, described expansion valve has driver elements such as diaphragm apparatus, this diaphragm apparatus drives spool on the switching direction of spool along with moving by variations in temperature described temperature sensing tube perception, that carried out the low-temperature refrigerant after the heat exchange.
The effect of invention
In kind of refrigeration cycle of the present invention, the temperature and pressure of considering the low-temperature refrigerant after the heat exchange is high before than heat exchange, have temperature sensing tube and/or external pressure ingress pipe, this temperature sensing tube and/or external pressure ingress pipe are used for the suction side of sensing directional compressor, carry out the temperature and/or the pressure of the low-temperature refrigerant after the heat exchange by inner heat exchanger, in expansion valve, temperature and/or pressure according to the low-temperature refrigerant after the described heat exchange, the flow (pressure decline degree and temperature decline degree) of the cold-producing medium that the subtend evaporimeter is derived is adjusted, therefore can not make the complex structure of piping system and expansion valve, and the refrigerant temperature that reliably and effectively suppresses the compressor suction side rises excessively.Therefore, can prevent in advance that compressor inside (discharge) excessive temperature from rising, the oily deterioration that can prevent in the cold-producing medium reliably to be contained and produce unfavorable condition such as sintering.
And kind of refrigeration cycle of the present invention is only transformed a little to existing kind of refrigeration cycle and its employed expansion valve, just can obtain above-mentioned effect, therefore also has the advantage that can not bring bigger cost to increase.
Description of drawings
Fig. 1 is the 1st embodiment (A), the 2nd embodiment (B) that roughly represents kind of refrigeration cycle of the present invention, the structure chart of the 3rd embodiment (C).
Fig. 2 is the profilograph of the employed expansion valve of kind of refrigeration cycle of expression the 1st embodiment.
Fig. 3 is the profilograph of the employed expansion valve of kind of refrigeration cycle of expression the 2nd embodiment.
Fig. 4 is the profilograph of the employed expansion valve of kind of refrigeration cycle of expression the 3rd embodiment.
Fig. 5 is the 4th embodiment (A), the 5th embodiment (B) that roughly represents kind of refrigeration cycle of the present invention, the structure chart of the 6th embodiment (C).
Fig. 6 is the profilograph of partly cut-away of the employed expansion valve of kind of refrigeration cycle of expression the 4th embodiment.
Fig. 7 is the profilograph of partly cut-away of the employed expansion valve of kind of refrigeration cycle of expression the 5th embodiment.
Fig. 8 is the profilograph of partly cut-away of the employed expansion valve of kind of refrigeration cycle of expression the 6th embodiment.
Fig. 9 is a structure chart of roughly representing an example of kind of refrigeration cycle in the past.
Figure 10 is a profilograph of representing the employed expansion valve of kind of refrigeration cycle in the past.
Symbol description
11～16 kind of refrigeration cycle
101 compressors
102 condensers
103 evaporimeters
104 inner heat exchangers
111～116 expansion valves
20 valve bodies
21 inflow entrances
22 flow exports
24 valve chambers
30 spherical valve cores
40 diaphragm apparatus
43 upside balancing gate pits
44 downside balancing gate pits
50 external pressure ingress pipes
54 pressure import path
70 temperature sensing tubes
72 capillaries
The specific embodiment
Below, the example to kind of refrigeration cycle of the present invention describes with reference to the accompanying drawings.
The 1st embodiment, the 2nd embodiment, the 3rd embodiment of Fig. 1 (A), (B), (C) expression kind of refrigeration cycle of the present invention.And Fig. 2, Fig. 3, Fig. 4 represent the employed expansion valve 111,112,113 of the 1st, the 2nd, the 3rd embodiment respectively.About the kind of refrigeration cycle 11,12,13 shown in Fig. 1 (A), (B), (C) and Fig. 2～expansion valve 111,112,113 shown in Figure 4, with the kind of refrigeration cycle 10 of described Fig. 9, example in the past shown in Figure 10 and the identical symbol of the corresponding part mark of each several part of expansion valve 110, stress difference below with in the past example.
The kind of refrigeration cycle 11 of the 1st example, for the suction side of sensing directional compressor 101, carry out the pressure of the low-temperature refrigerant after the heat exchange by inner heat exchanger 104, one end of external pressure ingress pipe 50 is attached at conduit 125 that the suction side to inner heat exchanger 104 and compressor 101 is connected midway, and near the pressure the bottom of the other end of external pressure ingress pipe 50 and the downside balancing gate pit 44 that is located at expansion valve 111 is imported path 54 to be connected, in expansion valve 111, according to the pressure of the low-temperature refrigerant after the described heat exchange, the flow (pressure decline degree and temperature decline degree) of the cold-producing medium that subtend evaporimeter 103 is derived is adjusted.
More particularly, the kind of refrigeration cycle 11 employed expansion valves 111 of the 1st embodiment, as shown in Figure 2, in order to cut off downside balancing gate pit 44 and temperature-sensitive inflow entrance 31, connection between the flow export 32, the open communication portion 45 of in the past example is changed to the less bar inserting hole 62 of diameter, between this bar inserting hole 62 and drive rod 35, O shape circle 63 as seal is installed, and import path 54 by described external pressure ingress pipe 50 and pressure, will import described downside balancing gate pit 44 by the pressure that inner heat exchanger 104 carries out the low-temperature refrigerant after the heat exchange.
Like this, in the kind of refrigeration cycle 11 of present embodiment, the temperature and pressure of considering the low-temperature refrigerant after the heat exchange is high before than heat exchange, has external pressure ingress pipe 50, it is used for the suction side of sensing directional compressor 101, carry out the pressure of the low-temperature refrigerant after the heat exchange by inner heat exchanger 104, in expansion valve 111, the flow of the cold-producing medium of deriving according to the pressure subtend evaporimeter 103 of the low-temperature refrigerant after the described heat exchange is adjusted, therefore can not make the complex structure of piping system and expansion valve, and the refrigerant temperature that reliably and effectively suppresses the suction side of compressor 101 rises excessively.Therefore, can prevent in advance that compressor inside (discharge) excessive temperature from rising, and the oily deterioration that can prevent in the cold-producing medium reliably to be contained and produce unfavorable condition such as sintering.
And the kind of refrigeration cycle of present embodiment is only transformed a little to existing kind of refrigeration cycle and its employed expansion valve, just can obtain above-mentioned effect, therefore also has the advantage that can not bring bigger cost to increase.
The kind of refrigeration cycle 12 of the 2nd embodiment, for the temperature suction side of sensing directional compressor 101, carry out the low-temperature refrigerant after the heat exchange by inner heat exchanger 104, with conduit 125 disposed adjacent of temperature sensing tube 70 with the suction side that is connected inner heat exchanger 104 and compressor 101, and as shown in Figure 3, upside balancing gate pit 43 with temperature sensing tube 70 and expansion valve 112 is connected with capillary 72, in expansion valve 112, according to the temperature of the low-temperature refrigerant after the described heat exchange, the flow of the cold-producing medium that subtend evaporimeter 103 is derived is adjusted.
In the kind of refrigeration cycle 12 that constitutes like this, has temperature sensing tube 70, it is used for the temperature suction side, carried out the low-temperature refrigerant after the heat exchange by inner heat exchanger 104 of sensing directional compressor 101, in expansion valve 112, the flow of the cold-producing medium of deriving according to the temperature subtend evaporimeter 103 of the low-temperature refrigerant after the described heat exchange is adjusted, therefore identical with the 1st embodiment, can not make the complex structure of piping system and expansion valve, and the refrigerant temperature that reliably and effectively suppresses the suction side of compressor 101 rises excessively.Therefore, can prevent in advance that compressor inside (discharge) excessive temperature from rising, and the oily deterioration that can prevent in the cold-producing medium reliably to be contained and produce unfavorable condition such as sintering.
And the kind of refrigeration cycle of present embodiment is only transformed a little to existing kind of refrigeration cycle and its employed expansion valve, just can obtain above-mentioned effect, therefore also has the advantage that can not bring bigger cost to increase.
The kind of refrigeration cycle 13 of the 3rd embodiment, it is the combination of the kind of refrigeration cycle 12 of the kind of refrigeration cycle 11 of the 1st embodiment and the 2nd embodiment, have external pressure ingress pipe 50 and temperature sensing tube 70 the two, and it is roughly the same near the downside balancing gate pit 44 of its employed expansion valve 113 with the 1st embodiment, roughly the same near the upside balancing gate pit 43 with the 2nd embodiment, in expansion valve 113, according to the pressure and temperature of the low-temperature refrigerant after the described heat exchange, the flow of the cold-producing medium that subtend evaporimeter 103 is derived is adjusted.
In the kind of refrigeration cycle 13 that constitutes like this, identical with the 1st embodiment with the 2nd embodiment, can prevent in advance that compressor inside (discharge) excessive temperature from rising, and the oily deterioration that can prevent in the cold-producing medium reliably to be contained and produce unfavorable condition such as sintering.
The 4th embodiment, the 5th embodiment, the 6th embodiment of Fig. 5 (A), (B), (C) expression kind of refrigeration cycle of the present invention.And Fig. 6 represents the employed expansion valve 114 of the 4th embodiment, and Fig. 7 represents the employed expansion valve 115 of the 5th embodiment, and Fig. 8 represents the employed expansion valve 116 of the 6th embodiment.About the kind of refrigeration cycle 14,15,16 shown in Fig. 5 (A), (B), (C) and Fig. 6, Fig. 7, expansion valve 114,115,116 shown in Figure 8, with the kind of refrigeration cycle 11,12,13 of described the 1st, the 2nd, the 3rd embodiment and the identical symbol of the corresponding part mark of each several part of expansion valve 111,112,113, stress difference below with them.
4th, kind of refrigeration cycle 14,15, the 16 employed expansion valves 114,115,116 of the 5th, the 6th embodiment, be not provided with the temperature-sensitive that is provided with in kind of refrigeration cycle 11,12, the 13 employed expansion valves 111,112,113 of above-mentioned the 1st, the 2nd, the 3rd embodiment with inflow entrance 31 and flow export 32, come in the obstructed overexpansion valve 114,115 (116) of refrigerant of low temperature of flash-pot 103 and by directly to inner heat exchanger 104 guiding.
The kind of refrigeration cycle 14 of the 4th embodiment, the kind of refrigeration cycle 12 of the 2nd embodiment is identical as described, for the suction side of sensing directional compressor 101, carry out the temperature of the low-temperature refrigerant after the heat exchange by inner heat exchanger 104, with conduit 125 disposed adjacent of temperature sensing tube 70 with the suction side that is connected inner heat exchanger 104 and compressor 101, and as shown in Figure 6, the upside balancing gate pit 43 that connects temperature sensing tube 70 and expansion valve 112 with capillary 72, in expansion valve 114, according to the temperature of the low-temperature refrigerant after the described heat exchange, the flow of the cold-producing medium that subtend evaporimeter 103 is derived is adjusted.And, on the valve body 20 of the employed expansion valve 114 of this example, be provided with the internal pressure path 66 that downside balancing gate pit 44 and flow export 22 are communicated with.
In addition, in such expansion valve, usually, with temperature sensing tube near the refrigerant temperature the outlet of evaporimeter 103 is carried out perception (with reference to figure 5 (B)), but present embodiment is characterised in that, carry out perception with 70 pairs of temperature sensing tubes by the refrigerant temperature that inner heat exchanger 104 carries out after the heat exchange, promptly changed the allocation position of temperature sensing tube 70.
In the kind of refrigeration cycle 14 that constitutes like this, also can obtain the action effect roughly the same with the kind of refrigeration cycle 12 of the 2nd embodiment.
The kind of refrigeration cycle 15 of the 5th embodiment, identical with the kind of refrigeration cycle 11 of above-mentioned the 1st embodiment, for the suction side of sensing directional compressor 101, carry out the pressure of the low-temperature refrigerant after the heat exchange by inner heat exchanger 104, one end of external pressure ingress pipe 50 is attached at conduit 125 that the suction side to inner heat exchanger 104 and compressor 101 is connected midway, and the other end of external pressure ingress pipe 50 and L shaped pressure are imported path 54 to be connected, this pressure imports downside balancing gate pit 44 and the external communications of path 54 with expansion valve 115, in expansion valve 115, according to the pressure of the low-temperature refrigerant after the described heat exchange, the flow of the cold-producing medium that subtend evaporimeter 103 is derived is adjusted.In addition, here, with temperature sensing tube 70 and near the conduit 124 that is connected evaporimeter 103 and inner heat exchanger 104 (outlet of evaporimeter 103) disposed adjacent, the upside balancing gate pit 43 with temperature sensing tube 70 and expansion valve 112 is connected with capillary 72.
In the kind of refrigeration cycle 15 that constitutes like this, also can obtain the action effect roughly the same with the kind of refrigeration cycle 11 of the 1st embodiment.
The kind of refrigeration cycle 16 of the 6th embodiment, it is the combination of the kind of refrigeration cycle 15 of the kind of refrigeration cycle 14 of the 4th embodiment and the 5th embodiment, therefore have external pressure ingress pipe 50 and temperature sensing tube 70 the two, and it is roughly the same near the downside balancing gate pit 44 of its employed expansion valve 116 with the 5th embodiment, roughly the same near the upside balancing gate pit 43 with the 4th embodiment, in expansion valve 116, according to the pressure and temperature of the low-temperature refrigerant after the described heat exchange, the flow of the cold-producing medium that subtend evaporimeter 103 is derived is adjusted.
In the kind of refrigeration cycle 16 that constitutes like this, identical with the 1st embodiment with the 2nd embodiment, can prevent in advance that compressor inside (discharge) excessive temperature from rising, and the oily deterioration that can prevent in the cold-producing medium reliably to be contained and produce unfavorable condition such as sintering.
Claims (3)
1. kind of refrigeration cycle, have compressor, condenser, evaporimeter, inner heat exchanger and expansion valve, in described inner heat exchanger, carry out heat exchange between the refrigerant of low temperature of suction side of described compressor of leading at the cold-producing medium of the high temperature of the described expansion valve that leads from described condenser with from described evaporimeter, it is characterized in that
For temperature and/or the pressure suction side of the described compressor of sensing directional, carry out the low-temperature refrigerant after the heat exchange by described inner heat exchanger, described expansion valve is set up temperature sensing tube and/or external pressure ingress pipe, in described expansion valve, according to the temperature and/or the pressure of the low-temperature refrigerant after the described heat exchange, the flow of the cold-producing medium that the described evaporimeter of subtend is derived is adjusted.
2. kind of refrigeration cycle as claimed in claim 1, it is characterized in that, described expansion valve has driver elements such as diaphragm apparatus, this diaphragm apparatus moves along with changing by described external pressure ingress pipe pressure that import, that carried out the low-temperature refrigerant after the heat exchange, on the switching direction of spool spool is driven.
3. kind of refrigeration cycle as claimed in claim 1 or 2, it is characterized in that, described expansion valve has driver elements such as diaphragm apparatus, this diaphragm apparatus drives spool on the switching direction of spool along with moving by variations in temperature described temperature sensing tube perception, that carried out the low-temperature refrigerant after the heat exchange.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008-294844 | 2008-11-18 | ||
| JP2008294844A JP2010121831A (en) | 2008-11-18 | 2008-11-18 | Refrigerating cycle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101737987A true CN101737987A (en) | 2010-06-16 |
Family
ID=41818427
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910226504A Pending CN101737987A (en) | 2008-11-18 | 2009-11-18 | refrigerating cycle |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP2187150A3 (en) |
| JP (1) | JP2010121831A (en) |
| CN (1) | CN101737987A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102530803A (en) * | 2012-01-12 | 2012-07-04 | 苏权兴 | Refrigerant subpackage equipment |
| CN105299972A (en) * | 2014-07-24 | 2016-02-03 | C.R.F.阿西安尼顾问公司 | Air conditioning system for motor-vehicles |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8931305B2 (en) | 2010-03-31 | 2015-01-13 | Denso International America, Inc. | Evaporator unit |
| CN103017409B (en) * | 2013-01-15 | 2015-12-02 | 吴秀华 | Efficient energy-saving freezes, heats all-in-one |
| FR3028015A1 (en) * | 2014-10-30 | 2016-05-06 | Valeo Systemes Thermiques | THERMAL MANAGEMENT DEVICE FOR A MOTOR VEHICLE |
| FR3028016A1 (en) * | 2014-10-30 | 2016-05-06 | Valeo Systemes Thermiques | THERMAL MANAGEMENT DEVICE FOR A MOTOR VEHICLE |
| CN113654284B (en) * | 2020-05-12 | 2024-06-25 | 浙江三花商用制冷有限公司 | Temperature sensing part and refrigerating system with same |
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| CN101033805A (en) * | 2006-03-07 | 2007-09-12 | 株式会社Tgk | Expansion valve |
| JP2008122034A (en) * | 2006-11-15 | 2008-05-29 | Sanden Corp | Air conditioner for vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JPH06241580A (en) * | 1993-02-18 | 1994-08-30 | Nippondenso Co Ltd | Freezing cycle device |
| JP2000346466A (en) | 1999-06-02 | 2000-12-15 | Sanden Corp | Vapor compression type refrigerating cycle |
| JP4323619B2 (en) * | 1999-06-17 | 2009-09-02 | 株式会社日本クライメイトシステムズ | Air conditioner for vehicles |
| US6460358B1 (en) * | 2000-11-13 | 2002-10-08 | Thomas H. Hebert | Flash gas and superheat eliminator for evaporators and method therefor |
| JP4246189B2 (en) * | 2005-09-07 | 2009-04-02 | 株式会社デンソー | Refrigeration cycle equipment |
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2008
- 2008-11-18 JP JP2008294844A patent/JP2010121831A/en active Pending
-
2009
- 2009-11-09 EP EP09175357.4A patent/EP2187150A3/en not_active Withdrawn
- 2009-11-18 CN CN200910226504A patent/CN101737987A/en active Pending
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| JPH02561U (en) * | 1988-06-13 | 1990-01-05 | ||
| CN1078035A (en) * | 1992-04-27 | 1993-11-03 | 三洋电机株式会社 | Air conditioner |
| CN1238034A (en) * | 1996-11-19 | 1999-12-08 | 丹福斯有限公司 | Process for control of refrigeration system, as well as refrigeration system and expansion valve |
| CN101033805A (en) * | 2006-03-07 | 2007-09-12 | 株式会社Tgk | Expansion valve |
| JP2008122034A (en) * | 2006-11-15 | 2008-05-29 | Sanden Corp | Air conditioner for vehicle |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102530803A (en) * | 2012-01-12 | 2012-07-04 | 苏权兴 | Refrigerant subpackage equipment |
| CN102530803B (en) * | 2012-01-12 | 2013-06-05 | 苏权兴 | Refrigerant subpackage equipment |
| CN105299972A (en) * | 2014-07-24 | 2016-02-03 | C.R.F.阿西安尼顾问公司 | Air conditioning system for motor-vehicles |
| CN105299972B (en) * | 2014-07-24 | 2019-05-17 | C.R.F.阿西安尼顾问公司 | Air handling system for motor vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2187150A3 (en) | 2014-01-15 |
| EP2187150A2 (en) | 2010-05-19 |
| JP2010121831A (en) | 2010-06-03 |
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Application publication date: 20100616 |