EP2620724A1 - Expansion valve - Google Patents
Expansion valve Download PDFInfo
- Publication number
- EP2620724A1 EP2620724A1 EP11826895.2A EP11826895A EP2620724A1 EP 2620724 A1 EP2620724 A1 EP 2620724A1 EP 11826895 A EP11826895 A EP 11826895A EP 2620724 A1 EP2620724 A1 EP 2620724A1
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- EP
- European Patent Office
- Prior art keywords
- orifice
- refrigerant
- outflow
- expansion valve
- middle section
- 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.)
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- 239000003507 refrigerant Substances 0.000 claims abstract description 179
- 239000007788 liquid Substances 0.000 claims description 25
- 238000005057 refrigeration Methods 0.000 claims description 7
- 230000000052 comparative effect Effects 0.000 description 9
- 238000000926 separation method Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 7
- 238000011084 recovery Methods 0.000 description 6
- 230000015572 biosynthetic process Effects 0.000 description 4
- 238000005259 measurement Methods 0.000 description 4
- 238000002474 experimental method Methods 0.000 description 3
- 230000001154 acute effect Effects 0.000 description 2
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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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
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
Definitions
- the present invention relates to an expansion valve, and particularly relates to an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant.
- expansion valves such as the one disclosed in Patent Literature 1 (Japanese Laid-open Patent Application No. 2009-228689 ).
- This expansion valve is provided to a refrigerant circuit of a refrigeration apparatus and is used to depressurize a liquid refrigerant, and as shown in FIG. 5 , the expansion valve has primarily a valve main body 10, a valve body 20, and a drive mechanism 30.
- the valve main body 10 is a member in which a valve seat 12 opening into a valve chest 11 is formed.
- Formed in the valve main body 10 are a refrigerant inlet 13 where refrigerant flows in from the side of the valve chest 11, and a refrigerant outlet 14 where refrigerant flows out underneath the valve chest 11.
- a refrigerant inflow tube 40 is connected to the refrigerant inlet 13, and a refrigerant outflow tube 50 is connected to the refrigerant outlet 14.
- the valve body 20 is a member that is caused to reciprocate relative to the valve seat 12 by the drive mechanism 30.
- the drive mechanism 30 is composed of a motor, a solenoid, or the like. With such a configuration, the flow rate of liquid refrigerant passing between the refrigerant inflow tube 40 and the refrigerant outflow tube 50 is adjusted while the refrigerant is depressurized.
- an orifice 80 is formed in the valve seat 12 as shown in FIG. 6 .
- This orifice 80 is composed only of a portion 81 which has the same diameter (a diameter D0) along the direction of refrigerant outflow (specifically, downward along the reciprocating direction axis line X of the valve body 20).
- An object of the present invention is to minimize the noise that occurs under conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase, in an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant.
- An expansion valve is an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant, the expansion valve comprising a valve main body in which a valve seat opening into a valve chest is formed, and a valve body which reciprocates relative to the valve chest.
- An orifice formed in the valve seat has an orifice entrance having the smallest diameter, an orifice middle section which widens in diameter along the direction of refrigerant outflow from the orifice entrance so as to form a first taper angle, and an orifice exit which either widens in diameter or does not change in diameter along the direction of refrigerant outflow from the orifice middle section so as to form a second taper angle smaller than the first taper angle.
- the inventors of the present application have discovered that when the expansion valve is used under conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase, noise is caused by sounds from cavitation when the refrigerant passes through the orifice and resonance sounds in the refrigerant outflow tube after the refrigerant passes through the orifice.
- the conventional expansion valve when the refrigerant passes through the orifice, separation of the refrigerant flow occurs immediately after the refrigerant has flowed from the valve chest, which has a large flow passage cross section, to the orifice, which has a small flow passage cross section.
- the inventors of the present application have conducted thoroughgoing experiments towards designing a shape of the orifice that would address such noise.
- the inventors of the present application have discovered that the noise described above can be minimized if the orifice has an orifice entrance having the smallest diameter, an orifice middle section which widens in diameter along the direction of refrigerant outflow from the orifice entrance so as to form a first taper angle, and an orifice exit which either widens in diameter or does not change in diameter along the direction of refrigerant outflow from the orifice middle section so as to form a second taper angle smaller than the first taper angle.
- the refrigerant flowing into the orifice from the valve chest first flows into the orifice entrance of the orifice, similar to the conventional example, immediately after which flow separation occurs, and local drops in pressure are likely to occur due to this separation.
- the pressure of the refrigerant can be recovered immediately after it has flowed into the orifice entrance. Such pressure recovery minimizes the occurrence of cavitation, and as a result minimizes the sounds caused by cavitation when the refrigerant passes through the orifice.
- the separated refrigerant can re-agglutinate because of the formation of the orifice exit wherein the diameter widens or the diameter does not change from the orifice middle section along the direction of refrigerant outflow so as to form a second taper angle which is smaller than the first taper angle.
- Such re-agglutination of the refrigerant minimizes the occurrences of spurting which causes pressure fluctuation, and as a result, resonance sound in the refrigerant outflow tube is minimized.
- the expansion valve employing the shape of the orifice having the orifice entrance, the orifice middle section, and the orifice exit as described above makes it possible to minimize noises occurring when the expansion valve is used in conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase.
- An expansion valve according to a second aspect is the expansion valve according to the first aspect, characterized in that a first outflow direction length of the orifice middle section along the direction of refrigerant outflow is one or more times the minimum diameter of the orifice entrance.
- An expansion valve according to a third aspect is the expansion valve according to the first or second aspect, characterized in that the first taper angle is 10 degrees or greater and 60 degrees or less.
- the first taper angle is 10 degrees or greater, the effect of pressure recovery immediately after the refrigerant has flowed into the orifice entrance can be reliably achieved. Moreover, because the first taper angle is 60 degrees or less, it is also possible for the refrigerant in the orifice middle section to re-agglutinate. Specifically, in this expansion valve, having the first taper angle in the angle range described above makes both pressure recovery and refrigerant re-agglutination possible.
- An expansion valve according to a fourth aspect is the expansion valve according to any of the first through third aspects, characterized in that a second inclination angle formed by the orifice exit with a plane orthogonal to the direction of refrigerant outflow is greater than a first inclination angle formed by the orifice middle section with a plane orthogonal to the direction of refrigerant outflow, and is 90 degrees or less.
- the diameter can be prevented from narrowing along the direction of refrigerant outflow.
- the refrigerant flow can thereby be prevented from contracting in the orifice exit, and the effect of minimizing pressure fluctuation in the orifice exit can be improved.
- An expansion valve according to a fifth aspect is the expansion valve according to any of the first through fourth aspects, characterized in that a second outflow direction length of the orifice exit along the direction of refrigerant outflow is equal to or less than the first outflow direction length of the orifice middle section along the direction of refrigerant outflow.
- the orifice exit can be prevented from becoming too long, and increases in pressure loss in the orifice exit can be prevented.
- FIG. 1 is a schematic cross-sectional view of an expansion valve 1 according to an embodiment of the present invention.
- FIG 2 is a cross-sectional view showing a valve seat of an expansion valve according to an embodiment of the present invention.
- Components in FIGS. 1 and 2 that are similar to those of FIGS. 5 and 6 showing a conventional example (specifically, components other than the orifice 80) are denoted by the same symbols.
- the expansion valve 1 is an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant, and the expansion valve has primarily a valve main body 10, a valve body 20, and a drive mechanism 30.
- the valve main body 10 is a member in which a valve seat 12 opening into a valve chest 11 is formed.
- Formed in the valve main body 10 are a refrigerant inlet 13 where refrigerant flows in from the side of the valve chest 11, and a refrigerant outlet 14 where refrigerant flows out underneath the valve chest 11.
- a refrigerant inflow tube 40 is connected to the refrigerant inlet 13, and a refrigerant outflow tube 50 is connected to the refrigerant outlet 14.
- the valve body 20 is a member that is reciprocated relative to the valve seat 12 by the drive mechanism 30.
- the drive mechanism 30 is composed of a motor, a solenoid, or the like. Such a configuration is designed so that the flow rate of liquid refrigerant passing between the refrigerant inflow tube 40 and the refrigerant outflow tube 50 is adjusted while the refrigerant is depressurized.
- the expansion valve 1 is used in conditions such that the refrigerant passes through the refrigerant inlet 13 in a liquid single phase and through the refrigerant outlet 14 also in a liquid single phase.
- an orifice 60 is formed in the valve seat 12.
- the orifice 60 has an orifice entrance 61, an orifice middle section 62, and an orifice exit 63.
- the orifice entrance 61 which faces the valve chest 11, is the portion having the smallest diameter.
- the orifice entrance 61 is a cylindrical portion having the same diameter (a minimum diameter D0) along the direction of refrigerant outflow (specifically, downward along a reciprocating direction axis line X of the valve body 20). Denoting the length of the orifice entrance 61 in the refrigerant outflow direction as the entrance length L0, the entrance length L0 is much smaller than the minimum diameter D0, and in this case is 0.3 times or less the length of the minimum diameter D0.
- valve body 20 By coming in contact with the orifice entrance 61, the valve body 20 blocks the flow of refrigerant between the refrigerant inlet 13 and the refrigerant outlet 14, and by separating from the orifice entrance 61, the valve body 20 allows refrigerant to flow between the refrigerant inlet 13 and the refrigerant outlet 14.
- the orifice middle section 62 is a cylindrical portion which widens in diameter from the orifice entrance 61 toward the direction of refrigerant outflow so that a first taper angle ⁇ is created. Denoting the length of the orifice middle section 62 along the direction of refrigerant outflow as the first outflow direction length L1, the first outflow direction length L1 is one or more times the minimum diameter D0.
- the first taper angle ⁇ is an angle 10 degrees or greater and 60 degrees or less.
- the inclination angle formed by the orifice middle section 62 with a plane orthogonal to the direction of refrigerant outflow (the angle on the side forming an acute angle in this case) is a first inclination angle ⁇ .
- the orifice exit 63 is a cylindrical portion wherein the diameter widens or the diameter does not change from the orifice middle section 62 along the direction of refirigerant outflow, so as to form a second taper angle ⁇ which is smaller than the first taper angle ⁇ .
- the second outflow direction length L2 Denoting the length of the orifice exit 63 along the direction of refrigerant outflow as the second outflow direction length L2, the second outflow direction length L2 is equal to or less than the first outflow direction length L1.
- the second outflow direction length L2 is also equal to or greater than 0.3 times the minimum diameter D0.
- the second inclination angle ⁇ is greater than the first inclination angle ⁇ and is equal to or less than 90 degrees.
- the separated refrigerant can re-agglutinate because of the formation of the orifice exit 63 wherein the diameter widens or the diameter does not change from the orifice middle section 62 along the direction of refrigerant outflow so as to form a second taper angle ⁇ which is smaller than the first taper angle ⁇ .
- Such re-agglutination of the refrigerant minimizes the occurrences of spurting which causes pressure fluctuation, and as a result, resonance sound in the refrigerant outflow tube 50 is minimized.
- the expansion valve 1 employing the shape of the orifice 60 having the orifice entrance 61, the orifice middle section 62, and the orifice exit 63 as described above makes it possible to minimize noises occurring when the expansion valve is used in conditions such that the refrigerant passes through the refrigerant inlet 13 in a liquid single phase and through the refrigerant outlet 14 also in a liquid single phase.
- the first outflow direction length L1 of the orifice middle section 62 along the direction of refrigerant outflow is one or more times the minimum diameter D0 of the orifice entrance 61
- refrigerant can re-agglutinate not only in the orifice exit 63 but in the orifice middle section 62 as well, whereby the effect of minimizing resonance sounds in the refrigerant outflow tube 50 can be improved.
- the second outflow direction length L2 of the orifice exit 63 along the direction of refrigerant outflow is equal to or greater than 0.3 times the minimum diameter D0 of the orifice entrance 61, the effect of minimizing resonance sounds in the refrigerant outflow tube 50 can be reliably achieved.
- the expansion valve 1 because the first taper angle ⁇ is 10 degrees or greater, the effect of pressure recovery immediately after the refrigerant has flowed into the orifice entrance 61 can be reliably achieved. Moreover, because the first taper angle ⁇ is 60 degrees or less, it is also possible for the refrigerant in the orifice middle section 62 to re-agglutinate. Specifically, in the expansion valve 1, having the first taper angle ⁇ in the angle range described above makes both pressure recovery and refrigerant re-agglutination possible.
- the second inclination angle ⁇ formed by the orifice exit 63 with a plane orthogonal to the direction of refrigerant outflow is 90 degrees or less, the diameter can be prevented from narrowing along the direction of refrigerant outflow.
- the refrigerant flow can thereby be prevented from contracting in the orifice exit 63, and the effect of minimizing pressure fluctuation in the orifice exit 63 can be improved.
- the orifice exit 63 can be prevented from becoming too long, and increases in pressure loss in the orifice exit 63 can be prevented.
- FIG. 3 is a graph showing the relationship between cavitation number and noise value according to differences in the shape of the orifice formed in the valve seat 12.
- FIG 4 is a cross-sectional view showing the valve seat 12 of an expansion valve according to a comparative example.
- the minimum diameter D0 was set to 1.6 mm, the entrance length L0 to 0.5 mm, the first taper angle ⁇ to 20 degrees (the first inclination angle ⁇ to 80 degrees), the first outflow direction length L1 to 3.8 mm, the second taper angle ⁇ to 0 degrees (the second inclination angle ⁇ to 90 degrees), and the second outflow direction length L2 to 0.7 mm.
- R410A was used as the refrigerant
- the depressurization width between the refrigerant inlet 13 and the refrigerant outlet 14 was 0.8 MPa
- the refrigerant flow rate was 75 to 85 kg/h
- the cavitation number ⁇ (based on the refrigerant outlet 14) was varied between approximately -0.1 to approximately 0.9 by varying the refrigerant temperature between 5°C to 25°C
- the noise value (the noise value caused by cavitation) in the expansion valve 1 alone at a distance of 0.3 m was measured (refer to the value of the working example in FIG. 3 ). Measurement of resonance sounds was also taken separately while the refrigerant outflow tube 50 was connected.
- the noise value caused by cavitation is minimized to 55 dBA or less in conditions such that the refrigerant passes through the refrigerant inlet 13 in a liquid single phase and through the refrigerant outlet 14 also in a liquid single phase (in other words, conditions such that the cavitation number ⁇ is 0 or greater).
- the working example of the orifice 60 there was no resonance in the refrigerant outflow tube 50, and noise from resonance sounds was at a level that could be ignored.
- the noise level caused by cavitation increased to a maximum of 65 dBA under the same measurement conditions as the working example, and the noise level caused by cavitation had increased by about 10 dBA above that of the working example of the orifice 60 described above (refer to the value of the conventional example in FIG 3 ).
- the orifice 80 of the conventional example similar to the working example of the orifice 60, there was no resonance in the refrigerant outflow tube 50, and noise from resonance sounds was at a level that could be disregarded.
- the noise level caused by cavitation was at the same level as that of the working example of the orifice 60 described above under the same measurement conditions as the working example (refer to the value of the comparative example in FIG 3 ).
- noise caused by resonance sounds can be brought down to an insignificant level by forming the orifice exit 63 wherein the diameter widens or the diameter does not change so as to form the second taper angle ⁇ smaller than the first taper angle ⁇ along the direction of refrigerant outflow from the orifice middle section 61.
- the orifice middle section 72 is formed but an orifice exit is not as in the comparative example ( FIG. 4 )
- resonance occurs in the refrigerant outflow tube 50, and the noise caused by resonance sounds reaches an extremely high level.
- the present invention has a wide range of application in expansion valves which are provided to refrigerant circuits of refrigeration apparatuses and which depressurize liquid refrigerant.
Abstract
Description
- The present invention relates to an expansion valve, and particularly relates to an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant.
- In the past, there have been expansion valves such as the one disclosed in Patent Literature 1 (Japanese Laid-open Patent Application No.
2009-228689 FIG. 5 , the expansion valve has primarily a valvemain body 10, avalve body 20, and adrive mechanism 30. The valvemain body 10 is a member in which avalve seat 12 opening into avalve chest 11 is formed. Formed in the valvemain body 10 are arefrigerant inlet 13 where refrigerant flows in from the side of thevalve chest 11, and arefrigerant outlet 14 where refrigerant flows out underneath thevalve chest 11. Arefrigerant inflow tube 40 is connected to therefrigerant inlet 13, and arefrigerant outflow tube 50 is connected to therefrigerant outlet 14. Thevalve body 20 is a member that is caused to reciprocate relative to thevalve seat 12 by thedrive mechanism 30. Thedrive mechanism 30 is composed of a motor, a solenoid, or the like. With such a configuration, the flow rate of liquid refrigerant passing between therefrigerant inflow tube 40 and therefrigerant outflow tube 50 is adjusted while the refrigerant is depressurized. - In the conventional expansion valve described above, an
orifice 80 is formed in thevalve seat 12 as shown inFIG. 6 . Thisorifice 80 is composed only of aportion 81 which has the same diameter (a diameter D0) along the direction of refrigerant outflow (specifically, downward along the reciprocating direction axis line X of the valve body 20). There are cases in which such an expansion valve is used under conditions such that the refrigerant passes through the refrigerant inlet 13 in a liquid single phase and through therefrigerant outlet 14 also in a liquid single phase, and the noise generated in such usage conditions becomes a problem. - An object of the present invention is to minimize the noise that occurs under conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase, in an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant.
- An expansion valve according to a first aspect is an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant, the expansion valve comprising a valve main body in which a valve seat opening into a valve chest is formed, and a valve body which reciprocates relative to the valve chest. An orifice formed in the valve seat has an orifice entrance having the smallest diameter, an orifice middle section which widens in diameter along the direction of refrigerant outflow from the orifice entrance so as to form a first taper angle, and an orifice exit which either widens in diameter or does not change in diameter along the direction of refrigerant outflow from the orifice middle section so as to form a second taper angle smaller than the first taper angle.
- The inventors of the present application have discovered that when the expansion valve is used under conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase, noise is caused by sounds from cavitation when the refrigerant passes through the orifice and resonance sounds in the refrigerant outflow tube after the refrigerant passes through the orifice. Specifically, in the conventional expansion valve, when the refrigerant passes through the orifice, separation of the refrigerant flow occurs immediately after the refrigerant has flowed from the valve chest, which has a large flow passage cross section, to the orifice, which has a small flow passage cross section. Localized drops in pressure are caused by this separation, and cavitation occurs in the portions where these localized drops in pressure occur. Such cavitation is one cause of the noise. When separation in the refrigerant flow occurs while the refrigerant is passing through the orifice, the refrigerant will spurt, causing the pressure to fluctuate, and the refrigerant will flow into the refrigerant outflow tube through the refrigerant outlet. Resonance sounds occur in the refrigerant outflow tube due to the pressure fluctuation reaching the refrigerant outflow tube. Such resonance sounds are one cause of the noise.
- In view of this, the inventors of the present application have conducted thoroughgoing experiments towards designing a shape of the orifice that would address such noise. The inventors of the present application have discovered that the noise described above can be minimized if the orifice has an orifice entrance having the smallest diameter, an orifice middle section which widens in diameter along the direction of refrigerant outflow from the orifice entrance so as to form a first taper angle, and an orifice exit which either widens in diameter or does not change in diameter along the direction of refrigerant outflow from the orifice middle section so as to form a second taper angle smaller than the first taper angle.
- With such a shape of the orifice, the refrigerant flowing into the orifice from the valve chest first flows into the orifice entrance of the orifice, similar to the conventional example, immediately after which flow separation occurs, and local drops in pressure are likely to occur due to this separation. However, because of the formation of the orifice middle section which widens in diameter along the direction of refrigerant outflow from the orifice entrance, the pressure of the refrigerant can be recovered immediately after it has flowed into the orifice entrance. Such pressure recovery minimizes the occurrence of cavitation, and as a result minimizes the sounds caused by cavitation when the refrigerant passes through the orifice. With the mere intention to recover refrigerant pressure through the orifice middle section, there is a risk that the separation of refrigerant flow will remain, the refrigerant will spurt, causing the pressure to fluctuate, and the refrigerant will flow into the refrigerant outflow tube through the refrigerant outlet. However, the separated refrigerant can re-agglutinate because of the formation of the orifice exit wherein the diameter widens or the diameter does not change from the orifice middle section along the direction of refrigerant outflow so as to form a second taper angle which is smaller than the first taper angle. Such re-agglutination of the refrigerant minimizes the occurrences of spurting which causes pressure fluctuation, and as a result, resonance sound in the refrigerant outflow tube is minimized.
- As described above, in the expansion valve, employing the shape of the orifice having the orifice entrance, the orifice middle section, and the orifice exit as described above makes it possible to minimize noises occurring when the expansion valve is used in conditions such that the refrigerant passes through the refrigerant inlet in a liquid single phase and through the refrigerant outlet also in a liquid single phase.
- An expansion valve according to a second aspect is the expansion valve according to the first aspect, characterized in that a first outflow direction length of the orifice middle section along the direction of refrigerant outflow is one or more times the minimum diameter of the orifice entrance.
- In this expansion valve, because the first outflow direction length of the orifice middle section along the direction of refrigerant outflow is one or more times the minimum diameter of the orifice entrance, refrigerant can re-agglutinate not only in the orifice exit but in the orifice middle section as well, whereby the effect of minimizing resonance sounds in the refrigerant outflow tube can be improved.
- An expansion valve according to a third aspect is the expansion valve according to the first or second aspect, characterized in that the first taper angle is 10 degrees or greater and 60 degrees or less.
- In this expansion valve, because the first taper angle is 10 degrees or greater, the effect of pressure recovery immediately after the refrigerant has flowed into the orifice entrance can be reliably achieved. Moreover, because the first taper angle is 60 degrees or less, it is also possible for the refrigerant in the orifice middle section to re-agglutinate. Specifically, in this expansion valve, having the first taper angle in the angle range described above makes both pressure recovery and refrigerant re-agglutination possible.
- An expansion valve according to a fourth aspect is the expansion valve according to any of the first through third aspects, characterized in that a second inclination angle formed by the orifice exit with a plane orthogonal to the direction of refrigerant outflow is greater than a first inclination angle formed by the orifice middle section with a plane orthogonal to the direction of refrigerant outflow, and is 90 degrees or less.
- In this expansion valve, because the second inclination angle formed by the orifice exit with a plane orthogonal to the direction of refrigerant outflow is 90 degrees or less, the diameter can be prevented from narrowing along the direction of refrigerant outflow. The refrigerant flow can thereby be prevented from contracting in the orifice exit, and the effect of minimizing pressure fluctuation in the orifice exit can be improved.
- An expansion valve according to a fifth aspect is the expansion valve according to any of the first through fourth aspects, characterized in that a second outflow direction length of the orifice exit along the direction of refrigerant outflow is equal to or less than the first outflow direction length of the orifice middle section along the direction of refrigerant outflow.
- In this expansion valve, because the second outflow direction length of the orifice exit along the direction of refrigerant outflow is equal to or less than the first outflow direction length of the orifice middle section along the direction of refrigerant outflow, the orifice exit can be prevented from becoming too long, and increases in pressure loss in the orifice exit can be prevented.
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FIG. 1 is a schematic cross-sectional view of an expansion valve according to an embodiment of the present invention. -
FIG. 2 is a cross-sectional view showing a valve seat of an expansion valve according to an embodiment of the present invention. -
FIG. 3 is a graph showing the relationship between cavitation number and noise value depending on differences in the shape of an orifice formed in the valve seat. -
FIG. 4 is a cross-sectional view showing the valve seat of an expansion valve according to a comparative example. -
FIG. 5 is a schematic cross-sectional view of an expansion valve according to a conventional example. -
FIG. 6 is a cross-sectional view showing the valve seat of the expansion valve according to the conventional example. - An embodiment of the expansion valve according to the present invention is described hereinbelow based on the drawings. The specific configuration of the embodiment of the expansion valve according to the present invention is not limited to the following embodiment, and can be modified within a range that does not deviate from the scope of the invention.
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FIG. 1 is a schematic cross-sectional view of anexpansion valve 1 according to an embodiment of the present invention.FIG 2 is a cross-sectional view showing a valve seat of an expansion valve according to an embodiment of the present invention. Components inFIGS. 1 and2 that are similar to those ofFIGS. 5 and6 showing a conventional example (specifically, components other than the orifice 80) are denoted by the same symbols. - Similar to the conventional example (
FIGS. 5 and6 ), theexpansion valve 1 is an expansion valve which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant, and the expansion valve has primarily a valvemain body 10, avalve body 20, and adrive mechanism 30. The valvemain body 10 is a member in which avalve seat 12 opening into avalve chest 11 is formed. Formed in the valvemain body 10 are arefrigerant inlet 13 where refrigerant flows in from the side of thevalve chest 11, and arefrigerant outlet 14 where refrigerant flows out underneath thevalve chest 11. Arefrigerant inflow tube 40 is connected to therefrigerant inlet 13, and arefrigerant outflow tube 50 is connected to therefrigerant outlet 14. Thevalve body 20 is a member that is reciprocated relative to thevalve seat 12 by thedrive mechanism 30. Thedrive mechanism 30 is composed of a motor, a solenoid, or the like. Such a configuration is designed so that the flow rate of liquid refrigerant passing between therefrigerant inflow tube 40 and therefrigerant outflow tube 50 is adjusted while the refrigerant is depressurized. There are also cases in which theexpansion valve 1 is used in conditions such that the refrigerant passes through therefrigerant inlet 13 in a liquid single phase and through therefrigerant outlet 14 also in a liquid single phase. - In the
valve seat 12, similar to the conventional example (FIG. 6 ), anorifice 60 is formed in thevalve seat 12. Theorifice 60 has anorifice entrance 61, an orificemiddle section 62, and anorifice exit 63. - The
orifice entrance 61, which faces thevalve chest 11, is the portion having the smallest diameter. Theorifice entrance 61 is a cylindrical portion having the same diameter (a minimum diameter D0) along the direction of refrigerant outflow (specifically, downward along a reciprocating direction axis line X of the valve body 20). Denoting the length of theorifice entrance 61 in the refrigerant outflow direction as the entrance length L0, the entrance length L0 is much smaller than the minimum diameter D0, and in this case is 0.3 times or less the length of the minimum diameter D0. By coming in contact with theorifice entrance 61, thevalve body 20 blocks the flow of refrigerant between therefrigerant inlet 13 and therefrigerant outlet 14, and by separating from theorifice entrance 61, thevalve body 20 allows refrigerant to flow between therefrigerant inlet 13 and therefrigerant outlet 14. - The orifice
middle section 62 is a cylindrical portion which widens in diameter from theorifice entrance 61 toward the direction of refrigerant outflow so that a first taper angle α is created. Denoting the length of the orificemiddle section 62 along the direction of refrigerant outflow as the first outflow direction length L1, the first outflow direction length L1 is one or more times the minimum diameter D0. The first taper angle α is anangle 10 degrees or greater and 60 degrees or less. The inclination angle formed by the orificemiddle section 62 with a plane orthogonal to the direction of refrigerant outflow (the angle on the side forming an acute angle in this case) is a first inclination angle θ. - The
orifice exit 63 is a cylindrical portion wherein the diameter widens or the diameter does not change from the orificemiddle section 62 along the direction of refirigerant outflow, so as to form a second taper angle β which is smaller than the first taper angle α. Denoting the length of theorifice exit 63 along the direction of refrigerant outflow as the second outflow direction length L2, the second outflow direction length L2 is equal to or less than the first outflow direction length L1. The second outflow direction length L2 is also equal to or greater than 0.3 times the minimum diameter D0. Denoting the inclination angle formed by theorifice exit 63 with a plane orthogonal to the direction of refrigerant outflow (the angle on the side forming an acute angle in this case) as the second inclination angle ζ, the second inclination angle ζ is greater than the first inclination angle θ and is equal to or less than 90 degrees. - When the
expansion valve 1 described above is actuated, similar to the conventional example, refrigerant flowing into theorifice 60 from thevalve chest 11 first flows into theorifice entrance 61 of theorifice 60, immediately after which flow separation occurs, and local drops in pressure are likely to occur due to this separation. However, because of the formation of the orificemiddle section 62 which widens in diameter along the direction of refrigerant outflow from theorifice entrance 61, the pressure of the refrigerant can be recovered immediately after it has flowed into theorifice entrance 61. Such pressure recovery minimizes the occurrence of cavitation, and as a result minimizes the sounds caused by cavitation when the refrigerant passes through theorifice 60. With the mere intention to recover refrigerant pressure through the orificemiddle section 62, there is a risk that the separation of refrigerant flow will remain, the refrigerant will spurt, causing the pressure to fluctuate, and the refrigerant will flow into therefrigerant outflow tube 50 through therefrigerant outlet 14. However, the separated refrigerant can re-agglutinate because of the formation of theorifice exit 63 wherein the diameter widens or the diameter does not change from the orificemiddle section 62 along the direction of refrigerant outflow so as to form a second taper angle β which is smaller than the first taper angle α. Such re-agglutination of the refrigerant minimizes the occurrences of spurting which causes pressure fluctuation, and as a result, resonance sound in therefrigerant outflow tube 50 is minimized. - As described above, in the
expansion valve 1, employing the shape of theorifice 60 having theorifice entrance 61, the orificemiddle section 62, and theorifice exit 63 as described above makes it possible to minimize noises occurring when the expansion valve is used in conditions such that the refrigerant passes through therefrigerant inlet 13 in a liquid single phase and through therefrigerant outlet 14 also in a liquid single phase. - In the
expansion valve 1, because the first outflow direction length L1 of the orificemiddle section 62 along the direction of refrigerant outflow is one or more times the minimum diameter D0 of theorifice entrance 61, refrigerant can re-agglutinate not only in theorifice exit 63 but in the orificemiddle section 62 as well, whereby the effect of minimizing resonance sounds in therefrigerant outflow tube 50 can be improved. Because the second outflow direction length L2 of theorifice exit 63 along the direction of refrigerant outflow is equal to or greater than 0.3 times the minimum diameter D0 of theorifice entrance 61, the effect of minimizing resonance sounds in therefrigerant outflow tube 50 can be reliably achieved. - In this
expansion valve 1, because the first taper angle α is 10 degrees or greater, the effect of pressure recovery immediately after the refrigerant has flowed into theorifice entrance 61 can be reliably achieved. Moreover, because the first taper angle α is 60 degrees or less, it is also possible for the refrigerant in the orificemiddle section 62 to re-agglutinate. Specifically, in theexpansion valve 1, having the first taper angle α in the angle range described above makes both pressure recovery and refrigerant re-agglutination possible. - In this
expansion valve 1, because the second inclination angle β formed by theorifice exit 63 with a plane orthogonal to the direction of refrigerant outflow is 90 degrees or less, the diameter can be prevented from narrowing along the direction of refrigerant outflow. The refrigerant flow can thereby be prevented from contracting in theorifice exit 63, and the effect of minimizing pressure fluctuation in theorifice exit 63 can be improved. In order to allow refrigerant to re-agglutinate while preventing the refrigerant flow from contracting in theorifice exit 63, it is preferable to employ a configuration for theorifice exit 63 in which the diameter does not change due to the second inclination angle β being 90 degrees. - Furthermore, in this
expansion valve 1, because the second outflow direction length L2 of theorifice exit 63 along the direction of refrigerant outflow is equal to or less than the first outflow direction length L1 of the orificemiddle section 62 along the direction of refrigerant outflow, theorifice exit 63 can be prevented from becoming too long, and increases in pressure loss in theorifice exit 63 can be prevented. - Next, an experimental example of the
orifice 60 described above is shown inFIG. 3 , together with a comparative example (FIG 4 ) and a conventional example (FIG. 6 ).FIG 3 is a graph showing the relationship between cavitation number and noise value according to differences in the shape of the orifice formed in thevalve seat 12.FIG 4 is a cross-sectional view showing thevalve seat 12 of an expansion valve according to a comparative example. - First is a description of an experiment relating to the working example (
FIG 2 ) of theorifice 60 according to an embodiment of the present invention. The dimensions and measurement conditions of theorifice 60 were set in the following manner. First, the minimum diameter D0 was set to 1.6 mm, the entrance length L0 to 0.5 mm, the first taper angle α to 20 degrees (the first inclination angle θ to 80 degrees), the first outflow direction length L1 to 3.8 mm, the second taper angle β to 0 degrees (the second inclination angle ζ to 90 degrees), and the second outflow direction length L2 to 0.7 mm. R410A was used as the refrigerant, the depressurization width between therefrigerant inlet 13 and therefrigerant outlet 14 was 0.8 MPa, the refrigerant flow rate was 75 to 85 kg/h, and while the cavitation number σ (based on the refrigerant outlet 14) was varied between approximately -0.1 to approximately 0.9 by varying the refrigerant temperature between 5°C to 25°C, the noise value (the noise value caused by cavitation) in theexpansion valve 1 alone at a distance of 0.3 m was measured (refer to the value of the working example inFIG. 3 ). Measurement of resonance sounds was also taken separately while therefrigerant outflow tube 50 was connected. - According to such an experiment, in the working example (
FIG. 2 ) of theorifice 60, it can be seen that the noise value caused by cavitation is minimized to 55 dBA or less in conditions such that the refrigerant passes through therefrigerant inlet 13 in a liquid single phase and through therefrigerant outlet 14 also in a liquid single phase (in other words, conditions such that the cavitation number σ is 0 or greater). In the working example of theorifice 60, there was no resonance in therefrigerant outflow tube 50, and noise from resonance sounds was at a level that could be ignored. - In the
orifice 80 of the conventional example (FIG. 6 ), wherein the minimum diameter D0 was 1.6 mm and the length of theorifice 80 in the direction of refrigerant outflow was 5.0 mm, the noise level caused by cavitation increased to a maximum of 65 dBA under the same measurement conditions as the working example, and the noise level caused by cavitation had increased by about 10 dBA above that of the working example of theorifice 60 described above (refer to the value of the conventional example inFIG 3 ). In theorifice 80 of the conventional example, similar to the working example of theorifice 60, there was no resonance in therefrigerant outflow tube 50, and noise from resonance sounds was at a level that could be disregarded. - In an
orifice 70 of the comparative example (FIG 4 ), wherein theorifice exit 63 is omitted from the working example of theorifice 60, the first taper angle α of an orificemiddle section 72 was 150 degrees, and the first outflow direction length L1 of the orificemiddle section 72 was 1.0 mm, the noise level caused by cavitation was at the same level as that of the working example of theorifice 60 described above under the same measurement conditions as the working example (refer to the value of the comparative example inFIG 3 ). However, in theorifice 70 of the comparative example, unlike the working example of theorifice 60 and/or theorifice 80 of the conventional example, there was resonance in therefrigerant outflow tube 50, and noise caused by resonance sounds was at an extremely high level. - It can be seen from which that the noise level caused by cavitation can be minimized by forming the orifice
middle sections FIG. 2 ) and/or the comparative example (FIG. 4 ). However, as in the orifice 70 (FIG. 4 ) of the comparative example, when the first taper angle α is too large or the first outflow direction length L1 is too short, it is clear that resonance in therefrigerant outflow tube 50 occurs readily. As in the working example (FIG. 2 ), noise caused by resonance sounds can be brought down to an insignificant level by forming theorifice exit 63 wherein the diameter widens or the diameter does not change so as to form the second taper angle β smaller than the first taper angle α along the direction of refrigerant outflow from the orificemiddle section 61. Conversely, it is clear that if the orificemiddle section 72 is formed but an orifice exit is not as in the comparative example (FIG. 4 ), resonance occurs in therefrigerant outflow tube 50, and the noise caused by resonance sounds reaches an extremely high level. - As described above, it is clear that when a shape for the
orifice 60 is employed which has theorifice entrance 61, the orificemiddle section 62, and theorifice exit 63, such as in the working example, it is possible to effectively minimize both noise caused by cavitation and noise caused by resonance occurring under conditions such that the refrigerant passes through therefrigerant inlet 13 in a liquid single phase and through therefrigerant outlet 14 also in a liquid single phase. - The present invention has a wide range of application in expansion valves which are provided to refrigerant circuits of refrigeration apparatuses and which depressurize liquid refrigerant.
-
- 1
- Expansion valve
- 10
- Valve main body
- 11
- Valve chest
- 12
- Valve seat
- 13
- Refrigerant inlet
- 14
- Refrigerant outlet
- 20
- Valve body
- 60
- Orifice
- 61
- Orifice entrance
- 62
- Orifice middle section
- 63
- Orifice exit
-
- [Patent Literature 1]
Japanese Laid-open Patent Application No.2009-228689
Claims (5)
- An expansion valve (1) which is provided to a refrigerant circuit of a refrigeration apparatus and which depressurizes a liquid refrigerant, the expansion valve comprising a valve main body (10) in which a valve seat (12) opening into a valve chest (11) is formed, and a valve body (20) which reciprocates relative to the valve chest;
the expansion valve being characterized in that an orifice (60) formed in the valve seat has an orifice entrance (61) having the smallest diameter, an orifice middle section (62) which widens in diameter along the direction of refrigerant outflow from the orifice entrance so as to form a first taper angle, and an orifice exit (63) which either widens in diameter or does not change in diameter along the direction of refrigerant outflow from the orifice middle section so as to form a second taper angle smaller than the first taper angle. - The expansion valve (1) according to claim 1, characterized in that:a first outflow direction length of the orifice middle section (62) along the direction of refrigerant outflow is one or more times the minimum diameter of the orifice entrance (61).
- The expansion valve (1) according to claim 1 or 2, characterized in that:the first taper angle is 10 degrees or greater and 60 degrees or less.
- The expansion valve (1) according to any of claims 1 through 3, characterized in that:a second inclination angle formed by the orifice exit (63) with a plane orthogonal to the direction of refrigerant outflow is greater than a first inclination angle formed by the orifice middle section (62) with a plane orthogonal to the direction of refrigerant outflow, and is 90 degrees or less.
- The expansion valve (1) according to any of claims 1 through 4, characterized in that:a second outflow direction length of the orifice exit (63) along the direction of refrigerant outflow is equal to or less than the first outflow direction length of the orifice middle section (62) along the direction of refrigerant outflow.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010213239A JP5563940B2 (en) | 2010-09-24 | 2010-09-24 | Expansion valve |
PCT/JP2011/071574 WO2012039450A1 (en) | 2010-09-24 | 2011-09-22 | Expansion valve |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2620724A1 true EP2620724A1 (en) | 2013-07-31 |
EP2620724A4 EP2620724A4 (en) | 2014-03-19 |
EP2620724B1 EP2620724B1 (en) | 2019-07-24 |
Family
ID=45873934
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11826895.2A Active EP2620724B1 (en) | 2010-09-24 | 2011-09-22 | Expansion valve |
Country Status (6)
Country | Link |
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US (1) | US20130175351A1 (en) |
EP (1) | EP2620724B1 (en) |
JP (1) | JP5563940B2 (en) |
CN (1) | CN103097836B (en) |
ES (1) | ES2751362T3 (en) |
WO (1) | WO2012039450A1 (en) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5395775B2 (en) * | 2010-10-12 | 2014-01-22 | 株式会社鷺宮製作所 | Motorized valve |
JP5327351B2 (en) * | 2012-04-09 | 2013-10-30 | ダイキン工業株式会社 | Air conditioner |
JP6280704B2 (en) * | 2013-07-23 | 2018-02-14 | Kyb株式会社 | Control valve |
CN103697177A (en) * | 2013-12-30 | 2014-04-02 | 浙江高中压阀门有限公司 | Aluminum oxide adjusting valve |
CN104930762B (en) * | 2014-03-19 | 2019-04-19 | 浙江三花智能控制股份有限公司 | Electric expansion valve |
WO2016056077A1 (en) * | 2014-10-08 | 2016-04-14 | 三菱電機株式会社 | Expansion valve, and refrigeration cycle device using expansion valve |
CN106711533B (en) * | 2015-07-17 | 2019-08-27 | 浙江三花汽车零部件有限公司 | Heat-exchange device |
JP6633121B2 (en) * | 2018-04-12 | 2020-01-22 | 三菱電機株式会社 | Expansion valve and refrigeration cycle device using expansion valve |
CN108709004A (en) * | 2018-07-23 | 2018-10-26 | 温州大阳科技有限公司 | A kind of waste water solenoid valve preventing blocked primary orifice waste water |
CN111503290A (en) * | 2019-01-31 | 2020-08-07 | 浙江三花智能控制股份有限公司 | Electronic expansion valve |
JP2019070449A (en) * | 2019-02-05 | 2019-05-09 | 株式会社鷺宮製作所 | Motor valve and refrigeration cycle system |
EP4134600A4 (en) * | 2020-04-09 | 2023-05-31 | Mitsubishi Electric Corporation | Refrigeration cycle device and air-conditioning device |
JP7050347B2 (en) * | 2020-07-02 | 2022-04-08 | 株式会社不二工機 | Flow control valve |
CN217736277U (en) * | 2022-01-26 | 2022-11-04 | 浙江盾安人工环境股份有限公司 | Electronic expansion valve |
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JPH0942510A (en) * | 1995-07-27 | 1997-02-14 | Daikin Ind Ltd | Electric expansion valve for refrigerator and refrigerator |
JP2004340260A (en) * | 2003-05-15 | 2004-12-02 | Saginomiya Seisakusho Inc | Flow control valve |
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EP2211077A2 (en) * | 2009-01-22 | 2010-07-28 | Fujikoki Corporation | Motor-driven valve |
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US4718456A (en) * | 1984-04-16 | 1988-01-12 | Steam Systems And Services, Incorporated | Steam conditioning valve |
JPH0650459A (en) * | 1992-07-31 | 1994-02-22 | Taiheiyo Kogyo Kk | Moderate action solenoid valve |
US7210640B2 (en) * | 2001-11-30 | 2007-05-01 | Caterpillar Inc | Fuel injector spray alteration through a moveable tip sleeve |
JP4114457B2 (en) * | 2002-10-11 | 2008-07-09 | ダイキン工業株式会社 | Shut-off valve and air conditioner |
JP4925638B2 (en) * | 2005-10-14 | 2012-05-09 | 株式会社不二工機 | Motorized valve |
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JP2009228689A (en) | 2008-03-19 | 2009-10-08 | Fuji Koki Corp | Electric valve |
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2010
- 2010-09-24 JP JP2010213239A patent/JP5563940B2/en active Active
-
2011
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- 2011-09-22 CN CN201180044279.8A patent/CN103097836B/en active Active
- 2011-09-22 WO PCT/JP2011/071574 patent/WO2012039450A1/en active Application Filing
- 2011-09-22 ES ES11826895T patent/ES2751362T3/en active Active
- 2011-09-22 US US13/822,184 patent/US20130175351A1/en not_active Abandoned
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JPH0942510A (en) * | 1995-07-27 | 1997-02-14 | Daikin Ind Ltd | Electric expansion valve for refrigerator and refrigerator |
JP2004340260A (en) * | 2003-05-15 | 2004-12-02 | Saginomiya Seisakusho Inc | Flow control valve |
JP2007292336A (en) * | 2006-04-21 | 2007-11-08 | Saginomiya Seisakusho Inc | Valve device for ammonia refrigerant refrigerating cycle device, and ammonia refrigerant refrigerating cycle device |
EP2211077A2 (en) * | 2009-01-22 | 2010-07-28 | Fujikoki Corporation | Motor-driven valve |
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Also Published As
Publication number | Publication date |
---|---|
JP2012067964A (en) | 2012-04-05 |
WO2012039450A1 (en) | 2012-03-29 |
JP5563940B2 (en) | 2014-07-30 |
EP2620724B1 (en) | 2019-07-24 |
CN103097836B (en) | 2015-06-17 |
EP2620724A4 (en) | 2014-03-19 |
CN103097836A (en) | 2013-05-08 |
US20130175351A1 (en) | 2013-07-11 |
ES2751362T3 (en) | 2020-03-31 |
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