CN101033805A - Expansion valve - Google Patents

Expansion valve Download PDF

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Publication number
CN101033805A
CN101033805A CNA2007100860243A CN200710086024A CN101033805A CN 101033805 A CN101033805 A CN 101033805A CN A2007100860243 A CNA2007100860243 A CN A2007100860243A CN 200710086024 A CN200710086024 A CN 200710086024A CN 101033805 A CN101033805 A CN 101033805A
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CN
China
Prior art keywords
expansion valve
refrigerant
refrigeration agent
pressure
temperature
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CNA2007100860243A
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Chinese (zh)
Inventor
広田久寿
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TGK Co Ltd
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TGK Co Ltd
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Publication of CN101033805A publication Critical patent/CN101033805A/en
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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
    • 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
    • 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
    • F25B41/32—Expansion valves having flow rate limiting means other than the valve member, e.g. having bypass orifices in the valve body
    • 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
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/06—Damage
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/08—Exceeding a certain temperature value in a refrigeration component or cycle

Abstract

A thermostatic expansion valve 3 is applied to a refrigeration cycle having an internal heat exchanger 5 for heat exchange between high-temperature refrigerant flowing from a condenser 2 to the expansion valve 3 and low-temperature refrigerant flowing from an evaporator 4 2 via the expansion valve 3 to a compressor. The expansion valve 3 comprises a bypass passage 3a or 3b for guiding refrigerant either from a high-pressure refrigerant inlet or a low-pressure refrigerant outlet to the downstream side of a temperature-sensing section, such that moist refrigerant is mixed with refrigerant whose degree of superheat is controlled by the expansion valve 3. This lowers the temperature of refrigerant that is drawn into the compressor 1.To provide an expansion valve which is capable of preventing the temperature of refrigerant compressed by a compressor from becoming too high, when a refrigeration load on a refrigeration cycle using an internal heat exchanger is high. A thermostatic expansion valve is applied to a refrigeration cycle provided with an internal heat exchanger that performs heat exchange between high-temperature refrigerant flowing from a condenser to the expansion valve and low-temperature refrigerant flowing from an evaporator to a compressor via the expansion valve. The expansion valve comprises a bypass passage or for causing refrigerant in a high-pressure refrigerant inlet or a low-pressure refrigerant outlet to flow to the downstream side of a temperature-sensing section, such that moist refrigerant is mixed with refrigerant whose degree of superheat is controlled by the expansion valve. This lowers the temperature of refrigerant that is drawn into the compressor when refrigeration load is high is lowered, to thereby prevent the temperature of refrigerant compressed by the compressor from becoming too high.

Description

Expansion valve
Technical field
The present invention relates to a kind of expansion valve, relate more specifically to a kind of thermostatic expansion valve, this thermostatic expansion valve is according to the temperature and pressure in the outlet port of the vaporizer in the refrigeration cycle of air conditioner for automobile, controls the flow velocity of the refrigeration agent of waiting to be supplied to vaporizer.
Background technique
From angle, proposed to use carbon dioxide substitute CFC substitute (HFC-134a) to be used as being used for the refrigeration agent of the refrigeration cycle of air conditioner for automobile about the environmental problem of global warming.In the cooling cycle system that utilizes carbon dioxide as refrigeration agent,, use internal exchanger (for example seeing TOHKEMY 2001-108308 communique) usually in order to raise the efficiency.
Internal exchanger is configured to like this, that is, carry out heat exchange at the refrigeration agent in the path that extends to expansion valve from gas cooler (its cooling compressed high-temperature high-pressure refrigerant) of flowing through and between the refrigeration agent in the path that extends to compressor from trap of flowing through by compressor.By this structure, overheated from the vapor phase refrigerant that trap is extracted out by the refrigeration agent in the path on the high pressure side of the internal exchanger of flowing through, be transported to compressor then.This makes compressor can suck drying cryogen, therefore operation effectively.
By contrast, in using the refrigeration cycle of HFC-134a, attempt to adopt the system that is combined with internal exchanger equally as refrigeration agent.Expect that the efficient of this system also is improved.
Yet, in using the refrigeration cycle of HFC-134a, use thermostatic expansion valve usually as expansion valve as refrigeration agent.The refrigeration agent at thermostatic expansion valve control evaporator outlet place makes it have predetermined degree of superheat.The result, the refrigeration cycle that is provided with internal exchanger (carrying out heat exchange between the refrigeration agent in the refrigeration agent in making is flowing through extends to expansion valve from condenser path and the path that extends to compressor from vaporizer of flowing through), the refrigeration agent overheated in the outlet port of vaporizer is further overheated by internal exchanger, be delivered to compressor then, thereby occur by become Tai Gao so that of the temperature of compressor refrigerant compressed owing to high temperature makes the problem of the deterioration of lubricant in the compressor, especially all the more so when refrigeration cycle is moved under the higher state of cooling load.
Summary of the invention
The present invention considers that above problem makes, and its purpose is to provide a kind of expansion valve, and this expansion valve can prevent from by the cooling load of the temperature of compressor refrigerant compressed on the refrigeration cycle of using internal exchanger to become too high when higher.
In order to address the above problem, according to the present invention, a kind of thermostatic expansion valve is provided, this thermostatic expansion valve is configured to by making temperature sensing portion sensing control the flow velocity of the refrigeration agent that is delivered to vaporizer from the temperature and pressure of the refrigeration agent of vaporizer outflow, this thermostatic expansion valve comprises bypass channel, this bypass channel is formed between high-pressure refrigerant inlet or low pressure refrigerant outlet and the coolant channel, be used to make high pressure liquid refrigerant or low-pressure gas-liquid mix refrigerant to flow to the downstream side of described temperature sensing portion, wherein high-pressure refrigerant is supplied to described high-pressure refrigerant inlet, low pressure refrigerant is delivered to described vaporizer from described low pressure refrigerant outlet, and described coolant channel passes through the described refrigeration agent that flows out from described vaporizer.
When combination illustrates the accompanying drawing of the preferred embodiments of the present invention with exemplary forms, will know above and other purpose of the present invention, feature and advantage from following explanation.
Description of drawings
Fig. 1 is the system diagram of using according to the refrigeration cycle of expansion valve of the present invention.
Fig. 2 is the central longitudinal sectional view according to the structure of first embodiment's expansion valve.
Fig. 3 is the central longitudinal sectional view according to the structure of second embodiment's expansion valve.
Fig. 4 is the central longitudinal sectional view according to the structure of the 3rd embodiment's expansion valve.
Fig. 5 is the central longitudinal sectional view according to the structure of the 4th embodiment's expansion valve.
Fig. 6 is the central longitudinal sectional view according to the structure of the 5th embodiment's expansion valve.
Fig. 7 is the central longitudinal sectional view according to the structure of the 6th embodiment's expansion valve.
Fig. 8 is the central longitudinal sectional view according to the structure of the 7th embodiment's expansion valve.
Embodiment
Hereinafter will be based on being applied to use HFC-134a as refrigeration agent and comprise that the example of the refrigeration cycle of internal exchanger describes embodiments of the invention in detail.
Fig. 1 is that the system diagram according to the refrigeration cycle of expansion valve of the present invention is used in expression.
This refrigeration cycle comprises the condenser 2 of the refrigeration agent that compressor 1, the condensation of compressed refrigerant is compressed, the refrigeration agent throttling that makes cooling and the expansion valve 3 that expands and the vaporizer 4 that makes the refrigeration agent evaporation of expansion.In addition, this refrigeration cycle is included in from condenser 2 and flow to the refrigeration agent of expansion valve 3 and flow to the internal exchanger 5 that carries out heat exchange between the refrigeration agent of compressor 1 from vaporizer 4 via expansion valve 3.
Expansion valve 3 is so-called thermostatic expansion valves, this thermostatic expansion valve has the temperature sensing portion of the temperature and pressure that is used for the refrigeration agent that sensing flows out from vaporizer 4, and is configured for according to the flow velocity of being controlled the refrigeration agent that is delivered to vaporizer 4 by the temperature and pressure of the refrigeration agent of temperature sensing portion sensing.Expansion valve 3 according to the present invention comprises that in inside the high pressure liquid refrigerant that is used to make heat exchanger 5 conveyings internally flow to the bypass channel 3a (being represented by solid arrow) in the downstream side of temperature sensing portion, perhaps is used to make the low-pressure gas-liquid mix refrigerant that is delivered to vaporizer 4 to flow to the bypass channel 3b (being represented by dotted arrow) in the downstream of temperature sensing portion.The details of the structure of expansion valve 3 will be described below.
Fig. 2 is the central longitudinal sectional view according to the structure of first embodiment's expansion valve.
Expansion valve 10 according to first embodiment has main body 11, and the side of this main body 11 is formed with: high-pressure refrigerant inlet 12, high-temperature high-pressure liquid cryogen heat exchanger 5 internally are delivered in this high-pressure refrigerant inlet 12; Low pressure refrigerant outlet 13 is delivered to vaporizer 4 through the low-temp low-pressure liquid of expansion valve 10 throttlings and expansion from this low pressure refrigerant outlet 13; Coolant channel inlet 14, this coolant channel inlet 14 is used to receive the refrigeration agent through evaporation of from evaporator drier 4; And coolant channel outlet 15, the refrigeration agent that this coolant channel outlet 15 is used for passing through expansion valve 10 is delivered to internal exchanger 5.
Valve seat 16 is integrally formed at high-pressure refrigerant inlet 12 with main body 11 and exports in the passage that is communicated with between 13 with low pressure refrigerant, and arranges spherical valve member 17 on the upstream side of valve seat 16.Be provided for the valve element receiving element 18 and the compression helical spring 19 of receiving valve element 17 in the space that holds valve element 17, this compression helical spring 19 promotes valve element 17 via valve element receiving element 18 along the direction that valve element 17 is placed on the valve seat 16.As shown in Figure 1, the lower end of compression helical spring 19 is received by the spring receiving element 20 that is assemblied in the adjusting screw 21, and adjusting screw 21 is screwed into the lower end of main body 11.Adjusting screw 21 has by regulating the amount that itself is screwed in the main body 11 regulates the function of the load of compression helical spring 19.
In addition, expansion valve 10 has the temperature sensing portion in the upper end of main body of being arranged on 11.Temperature sensing portion comprises upper shell 22, lower shell body 23, with barrier film of separately arranging by the mode in the space of described housings close 24 and the dish 25 that is arranged in barrier film 24 belows.
In dish 25 arranged beneath axle 26 is arranged, be used for the displacement of barrier film 24 is delivered to valve element 17.The top of axle 26 is kept by holder 28, and holder 28 is arranged to cross over the coolant channel 27 that is communicated with between coolant channel inlet 14 and coolant channel outlet 15 and extends.In holder 28, be furnished with the compression helical spring 29 that applies lateral load to the upper end of axle 26, thereby the axle that suppresses to be caused by the pressure surge of high-pressure refrigerant 26 vibrates longitudinally along it.
Main body 11 is formed with bypass channel 30, and the high-pressure refrigerant that is delivered in the main body 11 is walked around expansion valve 10 by this bypass channel 30.Bypass channel 30 is formed between high-pressure refrigerant inlet 12 and the coolant channel 27, and has the differential pressure control valve in the middle part of inserting it, and wherein high pressure liquid refrigerant is delivered in the high-pressure refrigerant inlet 12.Differential pressure control valve comprises: valve seat 31; Valve element 32, this valve element 32 according to the relation relative with valve seat 31 with can be towards being arranged on the downstream side of this valve seat 31 with mode away from valve seat 31 motions; Compression helical spring 33, this compression helical spring 33 promotes valve element 32 along the valve closing direction; And spring receiving element 34, this spring receiving element 34 is force-fitted in the bypass channel 30, is used to receive compression helical spring 33.Rod valve element 32 has a plurality of connectivity slots, and these connectivity slots are formed in the periphery of this valve element 32, makes these connectivity slots extend longitudinally, and when differential pressure control valve is opened, the high pressure liquid refrigerant connectivity slot of flowing through.
Expansion valve 10 sensings of Gou Chenging return the pressure and temperature of the refrigeration agent of coolant channel inlet 14 from vaporizer 4 as mentioned above.When higher or its pressure is low when the temperature of this refrigeration agent, barrier film 24 is shifted downwards, as shown in Figure 2, and this displacement is passed to valve element 17 via axle 26, thereby making valve element 17 open direction along valve moves, and when lower or its pressure is higher, cause valve element 17 to move along the valve closing direction when the temperature of this refrigeration agent, thereby the opening degree of control expansion valve 10 waits to be delivered to the flow velocity of the refrigeration agent of vaporizer 4 with control.Expansion valve 10 is by the refrigerant temperature in the outlet of sensing vaporizer 4, and control waits to be delivered to the flow velocity of the refrigeration agent of vaporizer 4, thereby control flows into the refrigeration agent of coolant channels inlet 14 from vaporizer 4, makes this refrigeration agent have predetermined degree of superheat.
On the other hand, the liquid refrigerant that is delivered to the coolant channel inlet 14 from vaporizer 4 mixes with the superheated refrigerant of passing through coolant channels 27 via bypass channel 30.The bypass amount of coming the controlling liquid refrigeration agent according to the pressure in the high-pressure refrigerant inlet 12 and the pressure reduction between the pressure in the coolant channel 27.When the refrigeration agent load is low, head pressure and the pressure reduction between the suction pressure in the compressor 1 are lower, so pressure and the pressure reduction between the pressure in the coolant channel 27 that high-pressure refrigerant is gone in 12 are also lower, thereby close the differential pressure control valve that is inserted in the bypass channel 30.In this case, stop liquid refrigerant to flow directly in the downstream side of temperature sensing portion.This is because when the refrigeration agent load is low, be not very high by the temperature of compressor 1 refrigerant compressed.
When refrigeration agent is loaded when higher, head pressure in the compressor 1 and the pressure reduction between the suction pressure increase, and pressure in the high-pressure refrigerant inlet 12 and the pressure reduction between the pressure in the coolant channel 27 also increase, thereby the pressure reduction at the differential pressure control valve two ends becomes when being equal to or higher than predetermined value (for example 1.3MPa), the Driving force of differential pressure control valve opposing compression helical spring 33 and opening is so that liquid refrigerant flows into the downstream side of temperature sensing portion and mixes with liquid refrigerant under the superheat state.Thereby this temperature that has reduced the refrigeration agent under the superheat state makes mixture become wet refrigeration agent.Internal exchanger 5 makes this refrigeration agent and the refrigeration agent heat exchange that reduces from the temperature of condenser 2, thereby this refrigeration agent is evaporated and overheated, and makes overheated refrigeration agent be inhaled into compressor 1.Therefore, prevented that the temperature that sucks the refrigeration agent of compressor 1 from becoming too high, this has prevented to be become too high by the temperature of compressor 1 refrigerant compressed.This prevented in the compressor 1 with the thermal metamorphism of refrigeration agent through the lubricant oil of refrigeration cycle circulation.
Fig. 3 is the central longitudinal sectional view according to the structure of second embodiment's expansion valve.In Fig. 3, the composed component identical with composed component shown in Figure 2 represented by identical reference character, and omitted detailed description.
With different is according to first embodiment's expansion valve 10 (wherein inserting differential pressure control valve in bypass channel 30), be characterised in that according to second embodiment's expansion valve 40 bypass channel 30 is provided with and opens wide the very little hole 35 of degree.According to the expansion valve 40 that constitutes as mentioned above, the liquid refrigerant bypass channel 30 of always flowing through.Therefore, may be too low though when the refrigeration agent load is low, be delivered to the temperature of the refrigeration agent of internal exchanger 5, compare with expansion valve 10 according to first embodiment, can reduce cost.
Fig. 4 is the central longitudinal sectional view according to the structure of the 3rd embodiment's expansion valve.In Fig. 4, the composed component identical with composed component shown in Figure 2 represented by identical reference character, and omitted detailed description.
With different is according to first embodiment's expansion valve 10 (wherein bypass channel 30 is formed between high-pressure refrigerant inlet 12 and the coolant channel 27), expansion valve 50 according to the 3rd embodiment is characterised in that bypass channel 30 passes main body 11 and is formed between low pressure refrigerant outlet 13 and the coolant channel 27.
In expansion valve 50, though differential pressure control valve is inserted in the bypass channel 30, the spring-load of compression helical spring 33 is arranged so that when the pressure reduction of differential pressure control valve at its two ends is not less than the predetermined value of 0.03MPa for example and opens.By this structure, when the refrigeration agent load is low, the flow velocity of refrigeration agent of vaporizer 4 of flowing through is lower, therefore pressure and the pressure reduction between the pressure in its outlet in the inlet of vaporizer 4 is also lower, and this pressure reduction is approximately equal to the pressure reduction at the differential pressure control valve two ends in inserting bypass channel 30, thereby differential pressure control valve is closed.As a result, when high pressure liquid refrigerant is flowed through gap between valve element 17 and the valve seat 16, export all gas-liquid mixed refrigerants that expand at 13 places at low pressure refrigerant and all be transported to vaporizer 4, and be prevented from flowing directly in the downstream side of temperature sensing portion.
Load when higher when refrigeration agent, the flow velocity of the refrigeration agent of the vaporizer 4 of flowing through is higher, so the pressure reduction between the pressure in the pressure in the inlet of vaporizer 4 and its outlet becomes higher, that is, the pressure reduction at the differential pressure control valve two ends increases.When this pressure reduction becomes when being equal to or higher than predetermined value, the Driving force of differential pressure control valve opposing compression helical spring 33 and opening so that liquid refrigerant flow into temperature sensing portion the downstream side and with superheat state under refrigerant mixed.Therefore, prevent that the temperature that sucks the refrigeration agent in the compressor 1 from becoming too high, this has also prevented to be become too high by the temperature of compressor 1 refrigerant compressed.This has also prevented the thermal metamorphism of the lubricant oil in the compressor 1.
Fig. 5 is the central longitudinal sectional view according to the structure of the 4th embodiment's expansion valve.In Fig. 5, the composed component identical with composed component shown in Figure 3 represented by identical reference character, and omitted detailed description.
Similar with expansion valve 40 according to second embodiment, in bypass channel 30, form porose 35 according to the 4th embodiment's expansion valve 60.According to the expansion valve 60 of structure as mentioned above, the gas-liquid mixed refrigerant bypass channel 30 of always can flowing through.As mentioned above, the refrigerant mixed of the gas-liquid mixed refrigerant and the coolant channel of flowing through, thus reduction is delivered to the temperature of the refrigeration agent of internal exchanger 5, and this has prevented to be become too high by the temperature of compressor 1 refrigerant compressed.
Fig. 6 is the central longitudinal sectional view according to the structure of the 5th embodiment's expansion valve.In Fig. 6, the composed component identical with composed component shown in Figure 2 represented by identical reference character, and omitted detailed description.
In the expansion valve 70 according to the 5th embodiment, bypass channel 30 forms by passing the through hole that main body 11 forms, and makes axle 26 insertions that are arranged between temperature sensing portion and the valve element 17 pass this through hole.In bypass channel 30, the valve element 32 of differential pressure control valve can be arranged to be used for the guide of axle 26 with axial motion, and compression helical spring 33 is arranged between valve element 32 and the holder 28, and the direction on the valve seat 31 that is used for forming along the stepped part that valve element 32 is placed in by bypass channel 30 promotes valve element 32.
When comparing according to the expansion valve 50 of Fig. 4 of the 3rd embodiment, the difference of expansion valve 70 and expansion valve 50 only is the position of bypass channel 30, and this expansion valve 70 has the differential pressure control valve that is arranged in the bypass channel 30, and the pressure reduction of this differential pressure control valve at its two ends becomes when being equal to or higher than predetermined value to be opened.Therefore, expansion valve 70 is operated in identical mode.
In addition, though the position arrange openings relative with temperature sensing portion at coolant channel 27, refrigeration agent is supplied to coolant channel 27 by this opening from bypass channel 30, but passing the low temperature gas-liquid mixed refrigerant that differential pressure control valve is supplied to coolant channel 27 from bypass channel 30 is come the refrigeration agent of from evaporator drier 4 to transport towards coolant channel outlet 15 immediately, thereby gas-liquid mixed refrigerant is mixed in the downstream side of temperature sensing portion with the refrigeration agent that returns from vaporizer 4, and its temperature is not sensed by temperature sensing portion.
Fig. 7 is the central longitudinal sectional view according to the structure of the 6th embodiment's expansion valve.In Fig. 7, the composed component identical with composed component shown in Figure 3 represented by identical reference character, and omitted detailed description.
In the expansion valve 80 according to the 6th embodiment, bypass channel 30 forms by passing the through hole that main body 11 forms, and makes that being arranged in axle 26 between temperature sensing portion and the valve element 17 inserts and pass this through hole, and formation porose 35 in its intermediate portion.Expansion valve 80 is in the configuration aspects that wet refrigeration agent is always mixed with the superheated refrigerant of carrying from vaporizer 4 and basic identical according to the expansion valve 60 of Fig. 5 of the 4th embodiment, so expansion valve 80 is operated in the mode identical with expansion valve 60.
Fig. 8 is the central longitudinal sectional view according to the structure of the 7th embodiment's expansion valve.In Fig. 8, the composed component identical with composed component shown in Figure 4 represented by identical reference character, and omitted detailed description.
Expansion valve 90 according to the 7th embodiment is applied to a refrigeration cycle, and this refrigeration cycle adopts bimetallic tube 36 conducts at the pipe on the side of compressor 1 and condenser 2.Bimetallic tube 36 forms by arranging outer tube 36a and interior pipe 36b coaxially, and because the refrigeration agent of the refrigeration agent of the outer tube 36a that flows through and the interior pipe 36b that flows through is separated by interior pipe 36b, so bimetallic tube 36 has the function of internal exchanger 5.
Expansion valve 90 has the high-pressure refrigerant inlet 12 that is arranged on the side that valve element 17 opens wide, and being arranged in compression helical spring 19 and spring receiving element 20 on the downstream side of valve element 7, the high-temperature high-pressure liquid cryogen is delivered to high-pressure refrigerant inlet 12 from condenser 2.Bypass channel 30 is formed between the low-temp low-pressure chamber and coolant channel 27 of arrangement of valves element 17, and the refrigeration agent that returns from vaporizer 4 passes through coolant channel 27.The open end of leading to coolant channel 27 at bypass channel 30 is furnished with valve element 32, and valve element 32 is remaining on along the mode that the direction that opens and closes bypass channel 30 is moved on the axle 26.Valve element 32 is compressed helical spring 33 and promotes along the direction that valve element 32 is placed on the valve seat 31, thereby forms differential pressure control valve.
From the outer tube 36a of bimetallic tube 36 be delivered to high-temperature high-pressure liquid cryogen the high-pressure refrigerant inlet 12 through the gap between valve element 17 and the valve seat 16 time by throttling and expand into low-temperature low-pressure refrigerant, and export 13 from low pressure refrigerant and be delivered to vaporizer 4.The refrigeration agent that returns from vaporizer 4 is received by coolant channel inlet 14, and is delivered to the interior pipe 36b of bimetallic tube 36 from coolant channel outlet 15 through coolant channel 27.At this moment, temperature sensing portion sensing is through the temperature and pressure of the refrigeration agent of coolant channel 27, thereby control waits to be delivered to the flow velocity of the refrigeration agent of vaporizer 4.
In addition, pressure reduction between the pressure that is arranged in the refrigeration agent in the differential pressure control valve sensing low pressure refrigerant outlet 13 in the bypass channel 30 and the pressure of the refrigeration agent in the coolant channel 27, thus control exports 13 flow velocitys that flow to the refrigeration agent of coolant channel 27 from low pressure refrigerant.Though the position relative with temperature sensing portion at coolant channel 27 forms opening, refrigeration agent is supplied to coolant channel 27 by this opening from bypass channel 30, but the low temperature gas-liquid mixed refrigerant that is supplied to coolant channel 27 through differential pressure control valves from bypass channel 30 is transported towards coolant channel outlet 15 by the refrigeration agent of vaporizer 4 evaporations, thereby the temperature of gas-liquid mixed refrigerant is not by temperature sensing portion sensing.
Though in the above-described embodiments, described being applied to have internal exchanger and using the example of HFC-134a, but the present invention also can be applicable to use the refrigeration cycle of less and other refrigeration agent that physical property is similar of global warming coefficient as the refrigeration cycle of refrigeration agent.
Expansion valve according to the present invention is constructed such that wet refrigeration agent flows to the downstream side of temperature sensing portion through bypass channel.Therefore, when the present invention is applied to adopt the refrigeration cycle of internal exchanger, can reduce the temperature for the treatment of to be delivered to the refrigeration agent of compressor via heat exchanger.This makes and can prevent to be become too high by the temperature of compressor refrigerant compressed under high cooling load situation, thereby prevents the thermal metamorphism of the lubricant oil in the compressor.
Below only as explanation of the principles of the present invention.In addition, because those skilled in the art carry out many modifications and changes easily, so shown in not wishing the present invention is defined in and described precise structure and application, so all suitable modifications and equivalent can be thought to drop in the scope of the present invention in claims and the equivalent thereof.

Claims (8)

1. thermostatic expansion valve, this thermostatic expansion valve are configured to control by the temperature and pressure that makes the refrigeration agent that temperature sensing portion sensing flows out from vaporizer the flow velocity of the refrigeration agent of waiting to be delivered to vaporizer, and this thermostatic expansion valve comprises:
Bypass channel, this bypass channel is formed between high-pressure refrigerant inlet or low pressure refrigerant outlet and the coolant channel, be used to make high pressure liquid refrigerant or low-pressure gas-liquid mix refrigerant to flow to the downstream side of described temperature sensing portion, wherein high-pressure refrigerant is supplied to described high-pressure refrigerant inlet, low pressure refrigerant is delivered to described vaporizer from described low pressure refrigerant outlet, and described coolant channel passes through the described refrigeration agent that flows out from described vaporizer.
2. expansion valve according to claim 1 is characterized in that, described bypass channel is to pass main body to be formed on hole between described high-pressure refrigerant inlet and the described coolant channel.
3. expansion valve according to claim 1, it is characterized in that, described bypass channel is formed in the passage between described high-pressure refrigerant inlet and the described coolant channel and has differential pressure control valve passing main body, and the pressure reduction of this differential pressure control valve at its two ends becomes and opens when being not less than predetermined value.
4. expansion valve according to claim 1 is characterized in that, described bypass channel is to pass main body to be formed on hole between outlet of described low pressure refrigerant and the described coolant channel.
5. expansion valve according to claim 1, it is characterized in that, described bypass channel is formed in the passage between outlet of described low pressure refrigerant and the described coolant channel and has differential pressure control valve passing main body, and the pressure reduction of this differential pressure control valve at its two ends becomes and opens when being not less than predetermined value.
6. expansion valve according to claim 1, it is characterized in that described bypass channel is to pass the through hole that main body forms, and makes an insertion pass this through hole, described axle is arranged between described temperature sensing portion and the valve element, and this valve element control is delivered to the flow velocity of the refrigeration agent of described vaporizer.
7. expansion valve according to claim 1, it is characterized in that, described bypass channel has differential pressure control valve in through hole, the pressure reduction of this differential pressure control valve at its two ends becomes and opens when being not less than predetermined value, described through hole passes main body and forms, make an insertion pass this through hole, described axle is arranged between described temperature sensing portion and the valve element, and this valve element control is delivered to the flow velocity of the refrigeration agent of described vaporizer.
8. expansion valve according to claim 1 is characterized in that this expansion valve is applied to be provided with the refrigeration cycle of internal exchanger, and described heat exchanger carries out heat exchange between the refrigeration agent of refrigeration agent that flows out from condenser and suction compressor.
CNA2007100860243A 2006-03-07 2007-03-07 Expansion valve Pending CN101033805A (en)

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Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4212367C2 (en) * 1991-04-15 2000-08-03 Denso Corp Device for removing water in a cooling system
JPH05196324A (en) * 1992-01-20 1993-08-06 Nippondenso Co Ltd Expansion valve for refrigerating cycle
JPH0914495A (en) * 1995-06-28 1997-01-14 Mitsubishi Heavy Ind Ltd Block type expansion valve and air conditioner
JP3924935B2 (en) * 1998-07-09 2007-06-06 株式会社デンソー Thermal expansion valve
US6615599B1 (en) * 2002-06-26 2003-09-09 Delphi Technologies Inc. Thermostatic expansion valve and air conditioning system for low refrigerant charge
US6758052B2 (en) * 2002-07-02 2004-07-06 Delphi Technologies, Inc. HVAC system with post-shut down isolation and venting of evaporator using H-shaped valve

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EP1832822B1 (en) 2009-01-21
DE602007000497D1 (en) 2009-03-12
JP2007240041A (en) 2007-09-20
EP1832822A2 (en) 2007-09-12
KR20070092118A (en) 2007-09-12
US20070209387A1 (en) 2007-09-13

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