WO2018030364A1 - Détendeur - Google Patents

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Publication number
WO2018030364A1
WO2018030364A1 PCT/JP2017/028675 JP2017028675W WO2018030364A1 WO 2018030364 A1 WO2018030364 A1 WO 2018030364A1 JP 2017028675 W JP2017028675 W JP 2017028675W WO 2018030364 A1 WO2018030364 A1 WO 2018030364A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant passage
shaft
refrigerant
expansion valve
central portion
Prior art date
Application number
PCT/JP2017/028675
Other languages
English (en)
Japanese (ja)
Inventor
松井　賢司
正浩 森下
Original Assignee
カルソニックカンセイ株式会社
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by カルソニックカンセイ株式会社 filed Critical カルソニックカンセイ株式会社
Priority to CN201780047193.8A priority Critical patent/CN109564040A/zh
Publication of WO2018030364A1 publication Critical patent/WO2018030364A1/fr

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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

Definitions

  • the present invention relates to an expansion valve and, for example, relates to an apparatus that adjusts the amount of refrigerant flowing to the evaporator in accordance with the temperature and pressure of the refrigerant flowing from the evaporator.
  • the side of the main body block 103 of the expansion valve 101 is decompressed and expanded by the expansion valve 101 and a port T1 to which a high-pressure refrigerant pipe is connected so as to receive a high-temperature and high-pressure refrigerant from a receiver / dryer (not shown).
  • a port T2 to which a low-pressure refrigerant pipe for supplying a low-temperature and low-pressure refrigerant to an evaporator (not shown) is connected, to a port T3 to which a refrigerant pipe from the evaporator outlet is connected, and to a compressor (not shown)
  • a port T4 to which the leading refrigerant pipe is connected.
  • the port T1 and the port T2 are connected to each other by a refrigerant passage 105 provided in the main body block 103, and the port T3 and the port T4 are connected to each other by a refrigerant passage 107 provided in the main body block 103.
  • a valve portion 109 for adjusting the opening of the refrigerant passage 105 (adjusting the flow rate of the refrigerant flowing through the refrigerant passage 105) is provided.
  • the valve unit 109 includes a valve seat 111 formed on the main body block 103 and a ball-shaped (spherical) valve body 113.
  • the valve body 113 is disposed upstream of the valve seat 111 in the flow direction of the refrigerant flowing through the refrigerant passage 105.
  • valve body 113 moves upward from the state shown in FIG. 10, and the valve body 113 is in close contact with the valve seat 111.
  • a gap 115 is formed between the valve seat 111 and the valve body 113 as shown in FIG.
  • the gap 115 constitutes a variable orifice that throttles the high-pressure refrigerant.
  • a compression coil spring 117 that urges the valve body 113 so that the valve body 113 is seated on the valve seat 111 is disposed.
  • a power element 119 is provided at the upper end of the main body block 103.
  • the power element 119 has a diaphragm 121 made of a flexible metal thin plate arranged so as to partition a space surrounded by a thick metal housing, and the lower surface thereof receives the displacement of the diaphragm 121.
  • a diaphragm receiving plate 123 is disposed.
  • the upper space of the diaphragm 121 constitutes a greenhouse, and is filled with two or more kinds of refrigerant gas and inert gas.
  • a rod 125 that transmits the displacement of the diaphragm 121 to the valve body 113 is disposed below the diaphragm receiving plate 123.
  • the rod 125 is supported by the main body block 103 and can move by a predetermined stroke in the vertical direction of FIG. 10, and also hangs down across the refrigerant passage 107 communicating with the ports T3 and T4. .
  • reference numeral 127 in FIG. 10 is a cover of the rod 125.
  • the rod 125 has an upper end in contact with the lower surface of the diaphragm receiving plate 123 and a lower end in contact with the valve body 113. Thereby, the movement of the diaphragm 121 is transmitted to the valve body 113 through the diaphragm receiving plate 123 and the rod 125.
  • the expansion valve 101 when the temperature of the refrigerant returned from the evaporator to the port T3 is lowered, the temperature of the temperature sensing chamber of the power element 119 is lowered, and the refrigerant gas in the temperature sensing chamber is condensed on the inner surface of the diaphragm 121. As a result, the pressure in the power element 119 is reduced and the diaphragm 121 is displaced upward, and the rod 125 is pushed by the compression coil spring 117 and moved upward. As a result, the valve body 113 moves to the valve seat 111 side, the passage area of the high-pressure refrigerant (passage area in the gap 115) is reduced, and the flow rate of the refrigerant sent to the evaporator is reduced. This also works in the same way when the pressure of the refrigerant returning from the evaporator to the port T3 increases.
  • Patent Document 1 the one described in Patent Document 1 is known as the one in which the cover 127 is removed from the above-described conventional expansion valve.
  • the conventional expansion valve shown in FIG. 10 has a problem that the number of components increases and the structure becomes complicated by providing a cover.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide an expansion valve that can prevent the generation of noise with a simple configuration.
  • a shaft for operating the valve portion to adjust the amount of the refrigerant flowing through the valve portion is disposed in the refrigerant passage through which the refrigerant flows.
  • the eigenvalue of the arranged refrigerant passage is set larger than the frequency of Karman vortex generated by the outer diameter of the shaft.
  • the outer shape of the shaft is formed in a cylindrical shape.
  • the shaft is an expansion valve disposed in the refrigerant passage in an exposed state.
  • the expansion valve according to one aspect of the present invention can prevent noise from being generated with a simple configuration.
  • FIG. 1 is a diagram showing a schematic configuration of an expansion valve according to an embodiment of the present invention.
  • FIG. 2 is a diagram schematically showing the expansion valve according to the embodiment of the present invention.
  • FIG. 3 is a diagram showing a relationship between the diameter of the refrigerant passage and the eigenvalue of the refrigerant passage in the expansion valve according to the embodiment of the present invention.
  • FIG. 4A is a diagram showing a cross section of the refrigerant passage provided with the shaft
  • FIG. 4B is a diagram showing the relationship between the reduced area ratio of the refrigerant passage and the passage resistance.
  • FIG. 5A is a diagram showing a cross-section (permeation circle diameter) of the refrigerant passage provided with the shaft, and FIG.
  • FIG. 5B is a diagram showing the relationship between the reduced area ratio of the refrigerant passage and the passage resistance.
  • C is a figure which shows the cross section (permeation
  • FIG. 6 is a diagram showing a noise generation state when the shaft diameter and the diameter of the central portion of the refrigerant passage are changed.
  • FIG. 7 is a diagram showing the ratio of the projected area of the shaft to the projected area of the refrigerant passage center when the shaft diameter and the diameter of the refrigerant passage center are changed.
  • FIG. 8 is a diagram showing the ratio of the projected area of the shaft to the projected area of the refrigerant passage center when the shaft diameter and the diameter of the refrigerant passage center are changed.
  • FIG. 9 is a diagram showing a reduction rate of the equivalent circular diameter when the shaft diameter and the diameter of the central portion of the refrigerant passage are changed.
  • FIG. 10 is a view showing a conventional expansion valve
  • the expansion valve 1 according to the embodiment of the present invention is used for a cooling cycle (for example, a refrigeration cycle of an air conditioner for an automobile) in the same manner as the conventional expansion valve 101 and the expansion valve described in Patent Document 1.
  • a cooling cycle for example, a refrigeration cycle of an air conditioner for an automobile
  • the expansion valve 1 corresponds to a first refrigerant passage (a refrigerant passage corresponding to the refrigerant passage 105 shown in FIG. 10) and a second refrigerant passage 3 (a refrigerant passage 107 shown in FIG. 10). Refrigerant path).
  • the expansion valve 1 is different from the conventional expansion valve 101 in the configuration of the second refrigerant passage (second refrigerant flow path) 3 and the shaft 5, but other portions are the same as those of the conventional expansion valve 101.
  • the configuration is almost the same.
  • a shaft 5 is disposed in a second refrigerant passage (hereinafter simply referred to as “refrigerant passage”) 3 of the expansion valve 1.
  • the shaft 5 operates the valve portion in order to adjust the amount of refrigerant flowing through the valve portion (not shown in FIGS. 1 and 2).
  • the refrigerant for example, R134a
  • evaporator not shown
  • the value of the eigenvalue F0 of the refrigerant passage 3 in which the shaft 5 is disposed is the frequency of Karman vortex generated according to the outer diameter D4 of the shaft 5 (the frequency of refrigerant due to Karman vortex in the refrigerant passage). It is set larger than the value of F1. Details of the refrigerant passage central portion 7 will be described later.
  • the eigenvalue F0 is a natural frequency of the refrigerant when the refrigerant is flowing through the refrigerant passage 3 including the refrigerant passage central portion 7.
  • the eigenvalue F0 the value in the refrigerant passage 3 from which the shaft 5 is removed is listed, but the value in the refrigerant path 3 in which the shaft 5 is arranged may be listed.
  • the outer shape of the shaft 5 is formed in a cylindrical shape, and is disposed in the refrigerant passage 3 in a state where the shaft 5 is exposed.
  • the expansion valve 1 includes a body (main body block) 9 made of, for example, aluminum or resin.
  • One opening of the first refrigerant passage (refrigerant inlet; corresponding to port T1 in FIG. 10) is connected to a receiver / dryer (not shown) via a pipe, and the other of the first refrigerant passage
  • the opening (refrigerant outlet; corresponding to port T2 in FIG. 10) is connected to the evaporator via a pipe.
  • One opening (refrigerant inlet; corresponding to port T3 in FIG. 10) of the refrigerant passage 3 is connected to the evaporator via a pipe, and the other opening (refrigerant outlet; port T4 in FIG. 10) of the refrigerant passage 3 is connected. Is connected to the compressor via a pipe.
  • a valve portion (not shown) for adjusting the amount of refrigerant flowing through the first refrigerant passage is provided in the middle of the first refrigerant passage.
  • the shaft 5 is supported by the body 9, extends in the vertical direction in the refrigerant passage 3, and crosses the refrigerant passage 3.
  • the shaft 5 moves in the vertical direction of FIGS. 1 and 2 with respect to the body 9 according to the temperature and pressure of the refrigerant in the refrigerant passage 3.
  • the opening degree of the valve part provided in the 1st refrigerant path is changed, and the quantity of the refrigerant
  • the refrigerant passage 3 is set larger than the frequency F1 of Karman vortex generated by the outer diameter of the shaft 5 and the flow of the refrigerant.
  • the refrigerant passage 3 is formed in a columnar shape, and the refrigerant flows through the columnar space substantially parallel to the extending direction of the axis of the column (from the right to the left in FIGS. 1 and 2). .
  • the outer diameter D4 of the cylindrical shaft 5 is sufficiently smaller than the inner diameter D2 of the cylindrical refrigerant passage 3.
  • the central axis of the shaft 5, that is, the central axis extending in the vertical direction in FIGS. 1 and 2, and the central axis of the refrigerant passage 3 intersect each other at a single point. Further, the shaft 5 extends the columnar refrigerant passage 3 over the entire length in the radial direction, that is, the vertical direction in FIGS. 1 and 2.
  • a power element 11 is provided at a location slightly entering upward from the refrigerant passage 3, as in the conventional case, and is in the direction of extension of the central axis that is the longitudinal direction of the shaft 5.
  • One end, that is, the upper end is engaged with the power element 11, and the other end in the longitudinal direction of the shaft 5 is engaged with the valve portion.
  • the shaft 5 is appropriately moved in the extending direction of the central axis to adjust the opening degree of the valve portion. It is supposed to be.
  • the opening degree of the valve portion increases as the shaft 5 moves downward, and the opening degree of the valve portion increases as the shaft 5 moves upward. Becomes smaller.
  • D2 is the inner diameter of the refrigerant passage central portion 7 shown in FIG. 1 and FIG.
  • the unit of F0 is Hz, and the unit of D2 is mm.
  • the eigenvalue F0 of the refrigerant passage 3 is not only the inner diameter D2 of the refrigerant passage central portion 7, but also the flow rate (flow velocity) of the refrigerant flowing through the refrigerant passage 3, the inner diameters D1 and D3 of the passages of the insertion joints 13 and 15 (FIG. 2), and also varies depending on the distance between the insertion joints 13 and 15, that is, the length L of the refrigerant passage central portion 7 and the outer diameter D4 of the shaft 5.
  • V is the flow velocity of the refrigerant flowing through the refrigerant passage central portion 7, and its unit is m / sec.
  • the unit of D4 is mm, and the unit of F1 is kHz.
  • the characteristic value F0 of the refrigerant passage 3 (refrigerant passage central portion 7) in which the shaft 5 is disposed is set to be larger than the Karman vortex frequency F1 generated by the outer diameter D4 of the shaft 5.
  • FIG. Will be described with reference to FIG.
  • the inner diameter D2 may be set to the inner diameter D2 on the left side of the diagram G2.
  • the inner diameter D2 of the refrigerant passage central portion 7 is set within the range A1 in the diagram G3, the eigenvalue F0> the Karman vortex frequency F1.
  • the inner diameter D2 of the refrigerant passage central portion 7 is preferably about 11 mm, more preferably about 13 mm, and further preferably about 14 mm.
  • the inner diameter D2 of the refrigerant passage central portion 7 traversed by the shaft 5 is about 17 mm.
  • the inner diameter D2 of the refrigerant passage central portion 7 is set within the range A2 in the diagram G4, the eigenvalue F0> the Karman vortex frequency F1.
  • the inner diameter D2 of the refrigerant passage central portion 7 is preferably about 10 mm, more preferably about 12 mm, and further preferably about 13 mm.
  • the inner diameter D2 of the refrigerant passage central portion 7 traversed by the shaft 5 is about 16 mm.
  • the inner diameter D2 of the refrigerant passage central portion 7 is set within the range A3 in the diagram G5, the eigenvalue F0> the Karman vortex frequency F1.
  • the inner diameter D2 of the refrigerant passage central portion 7 is preferably about 13 mm, more preferably about 16 mm, and further preferably about 17 mm.
  • the inner diameter D2 of the refrigerant passage central portion 7 traversed by the shaft 5 is about 18 mm.
  • the expansion valve 1 will be further described.
  • the projected area S1 of the shaft 5 is 25% or less of the projected area S2 of the refrigerant passage 3, that is, the refrigerant passage central portion 7.
  • the projected area S1 of the shaft 5 may be less than 25% of the projected area S2 of the refrigerant passage 3.
  • the projected area S1 of the shaft 5 is an area of the shaft 5 when the cylindrical refrigerant passage central portion 7 is viewed from the extending direction of the central axis. That is, it is the area of the part shown by the oblique line in FIG.
  • S1 / S2 ⁇ 0.25. That is, the ratio of the projection area S1 to the projection area S2, that is, S1 / S2 is within the range A4 shown in FIG. It is desirable that S1 / S2 be within the range of 0.10 to 0.25. It is more desirable that S1 / S2 is within the range of 0.12 to 0.25. Note that S1 / S2 ⁇ 0.30 may be satisfied.
  • the outer diameter D4 of the shaft 5 is, for example, 2.0 mm or more and 3 mm or less.
  • the outer diameter D4 of the shaft 5 is more preferably 2.2 mm or more and 3 mm or less.
  • the outer diameter D4 of the shaft 5 is 2.9 mm or less.
  • the inner diameter D2 of the refrigerant passage central portion 7 refrigerant is preferably 14 mm or more and 19 mm or less.
  • the outer diameter D4 of the shaft 5 is desirably 2.0 mm or more so that the Karman vortex frequency F1 is not too high.
  • the outer diameter D4 of the shaft 5 is more preferably 2.2 mm or more. If the generation of noise can be suppressed by other conditions, the above value of 25% may be exceeded. In this case, for example, 30% or less is desirable.
  • the reduction rate of the equivalent circular diameter is 16% or less.
  • the “D” -shaped refrigerant passage section 17 is a portion of one refrigerant passage of two refrigerant passages divided into two equal parts by the shaft 5.
  • FIG. 5A is a view of the portion 7 of the refrigerant passage 3 in which the shaft 5 is provided as viewed from the flow direction of the refrigerant.
  • the semicircle 19 in the portion 7 of the refrigerant passage 3 where the shaft 5 is not present is the two refrigerant passages formed by dividing the circular refrigerant passage central portion 7 into two equal parts with a predetermined diameter. It is a part of one of the refrigerant passages.
  • FIG. 5C is a view of the refrigerant passage when the shaft 5 is removed as seen from the refrigerant flow direction.
  • Af1 is the area of the “D” -shaped portion 17 and Wp1 is the wet length, that is, the entire circumference of the outer periphery of the “D” -shaped portion 17 or the wall surface of the “D” -shaped portion. Length.
  • the recessed portion 2 (see FIGS. 1 and 2) around the shaft 5 that is countersunk may be ignored.
  • Af2 is the area of the semicircular portion, and Wp2 is the wet length, that is, the length of the wall surface of the semicircular portion.
  • (De2-De1) /De2 ⁇ 0.16 the reduction rate (De2-De1) / De2 of the equivalent circular diameter is within the range A5 shown in FIG. Note that (De2-De1) / De2 may fall within the range of 0.125 to 0.16. It is more desirable that (De2-De1) / De2 be within the range of 0.13 to 0.16.
  • insertion joints 13 and 15 are inserted into the refrigerant passage 3 of the expansion valve 1, and the value of the inner diameter D ⁇ b> 2 of the refrigerant passage 3, that is, the refrigerant passage central portion 7, is , 15 is larger than the values of the inner diameters D1, D3.
  • the joints (insertion joints) 13 and 15 are provided by being inserted into both ends of one end of the refrigerant passage 3 and the other end of the refrigerant passage 3, respectively.
  • an inlet side joint (upstream side joint) 13 that is inserted into the refrigerant path 3 from the refrigerant passage inlet and provided at the refrigerant inlet as a joint and the inlet flow side joint 13 are separate from each other, and the refrigerant path
  • An outlet side joint 15 that is inserted into the refrigerant passage 3 from the outlet and provided at the refrigerant outlet is provided.
  • the value of the length L in the axial direction of the central portion 7 of the refrigerant passage 3 is divided by the value of the depth D in the radial direction of the central portion 7 of the refrigerant passage 3.
  • the value of the parameter a obtained by multiplying the value of the inner diameter dimension (D1 or D3) is set to be less than 40.
  • a cylindrical portion of the upstream joint 13, that is, a portion 21 whose outer diameter is equal to the inner diameter D 2 of the refrigerant passage 3 and whose inner diameter is D 1 enters the refrigerant passage 3.
  • a cylindrical portion of the downstream side joint 15, that is, a portion 23 having an outer diameter equal to the inner diameter D ⁇ b> 2 of the refrigerant passage 3 and an inner diameter D ⁇ b> 3 enters the refrigerant passage 3.
  • the tip of the cylindrical portion 21 of the upstream joint 13 inserted in the refrigerant passage 3 (the right end in FIG. 1) and the tip of the cylindrical portion 23 of the downstream joint 15 inserted in the refrigerant passage 3 (The left end in FIG. 1) are separated from each other by a distance L.
  • a central portion (refrigerant passage central portion) 7 where the joints 13 and 15 are not present is formed at the central portion of the refrigerant passage 3.
  • the shaft 5 is provided in the center of the refrigerant passage central portion 7 and is separated from the upstream side joint 13 and the downstream side joint 15.
  • the dimension L of the axial length of the refrigerant passage central portion 7 is a dimension of the refrigerant passage central portion 7 in the extending direction of the central axis of the central portion 7 of the refrigerant passage, as already understood. That is, it is a dimension between the upstream joint 13 and the downstream joint 15.
  • the radial depth D of the refrigerant passage central portion 7 is “2” obtained by subtracting the value of the inner diameter D3 of the cylindrical portion of the downstream joint 15 from the value of the diameter D2 of the refrigerant passage central portion 7.
  • the depth dimension D may be obtained by dividing the value obtained by subtracting the value of the inner diameter D1 of the cylindrical portion of the upstream joint 13 from the value of the diameter D2 of the refrigerant passage central portion 7 by “2”. .
  • the parameter is “a”, the dimension of the axial length of the refrigerant passage central portion 7 is “L”, the depth of the refrigerant passage central portion 7 in the radial direction is “D”, and the cylinder of the downstream joint 15
  • the inner diameter D2 of the refrigerant passage central portion 7 is made smaller than before in order to increase the eigenvalue F0.
  • the inner diameter D2 of the refrigerant passage central portion 7 is reduced from the conventional inner diameter of 18 mm to 15 mm.
  • D1 is 12 mm
  • D2 is 15 mm
  • D3 is 13.7 mm
  • D4 is 2.4 mm
  • L is 12 mm.
  • the expansion valve 1 operates in the same manner as the conventional expansion valve 101 or the like. That is, the flow rate of the refrigerant flowing through the evaporator is appropriately adjusted according to the temperature and pressure of the refrigerant flowing through the refrigerant passage 3.
  • the dimension L of the axial length of the refrigerant passage central portion 7 is fixed to 18 mm, and the inner diameter D2 of the refrigerant passage central portion 7 and the outer diameter D4 of the shaft 5 are changed. .
  • the noise is within the allowable range at the circle mark.
  • the inner diameter D2 is in the range of 12 mm to 19 mm and the outer diameter D4 of the shaft 5 is in the range of 2.8 mm to 5.0 mm
  • the inner diameter D2 is in the range of 12 mm to 18 mm
  • the outer diameter D4 of the shaft 5 is in the range of 2.6 mm to 2.8 mm
  • the inner diameter D2 is in the range of 12 mm to 17 mm
  • the outer diameter D4 of the shaft 5 is in the range of 2.4 mm to 2.6 mm.
  • the inner diameter D2 is in the range of 12 mm to 15 mm and the outer diameter D4 of the shaft 5 is in the range of 2.2 mm to 2.4 mm, the inner diameter D2 is in the range of 12 mm to 14 mm. Further, when the outer diameter D4 of the shaft 5 is within the range of 2.0 mm to 2.2 mm, the noise is within the allowable range.
  • the inner diameter D2 of the refrigerant passage center 7 and the shaft 5 such that the range indicated by the thick frame shown in FIG. If the outer diameter D4 is adopted, generation of noise can be suppressed.
  • the inner diameter of the refrigerant passage central portion 7 capable of suppressing noise by using the range indicated by the thick frame shown in FIG. 8 instead of FIG. 7, that is, the range in which the number in the frame is 0.18 to 0.25. You may employ
  • the dimension L of the axial length of the refrigerant passage central portion 7 is fixed to 18 mm, and the inner diameter D2 of the refrigerant passage central portion 7 and the outer diameter D4 of the shaft 5 are changed. .
  • noise can be suppressed within a range indicated by a thick frame.
  • the numbers such as “0.847” shown in FIG. 9 assume that the outer diameter of the shaft 5 is “0” and the fluid diameter ratio when the fluid diameter obtained by equally dividing the refrigerant passage central portion 7 is “1”. Is shown.
  • a value obtained by subtracting “0.847” from “1” is the reduction rate of the equivalent circular diameter. If the reduction rate of the equivalent circular diameter is 0.13 to 0.16, that is, 13% to 16%, noise can be suppressed.
  • the outer shape of the shaft 5 is formed in a cylindrical shape, and the shaft 5 is exposed in the refrigerant passage 3 (the refrigerant passage central portion 7). For this reason, the expansion valve 1 does not require a cover surrounding the shaft 5, and it is not necessary to form dimples or the like on the outer surface of the shaft 5 to form a large number of irregularities on the outer surface of the shaft 5. ing. That is, the configuration of the expansion valve 1 is simplified. Further, the outer surface of the shaft 5 has a smooth shape with no irregularities. For this reason, the flow path resistance of the refrigerant passage 3 can be reduced.
  • the eigenvalue F0 of the refrigerant passage central portion 7 where the shaft 5 is disposed is set to be larger than the frequency F1 of Karman vortex generated by the shaft 5. For this reason, when the refrigerant flows through the refrigerant passage 3 in which the shaft 5 is disposed, resonance between the Karman vortex generated by the shaft 5 and the refrigerant in the refrigerant passage 3 is avoided, and generation of noise is prevented. Can do.
  • the diameter of the shaft 5 may be increased.
  • the projected area S1 in the refrigerant passage 3 is increased and the passage resistance of the refrigerant flow is increased. Will go up.
  • the projected area S 1 of the shaft 5 is 25% or less of the projected area S 2 of the refrigerant passage central portion 7, so that the refrigerant due to an increase in the projected area S 1 of the shaft 5 in the refrigerant passage 3. An increase in the flow path resistance can be suppressed, and the Karman vortex frequency F1 can be lowered appropriately.
  • the expansion valve 1 is not provided with a cover surrounding the shaft 5 as in the prior art. That is, the substantial outer diameter of the shaft 5 in the refrigerant passage 2 is small. For this reason, even if the Karman vortex frequency F1 is increased, the inner diameter D2 of the refrigerant passage central portion 7 is smaller than that of the conventional one, so that the generation of noise can be prevented.
  • the reduction rate of the equivalent circular diameter is 16% or less in the “D” -shaped refrigerant passage section 17 in the portion 7 of the refrigerant passage 3 where the shaft 5 is provided.
  • the friction loss on the wall surface through which the refrigerant flows, that is, the refrigerant passage and the wall surface of the shaft can be reduced, and the passage resistance of the refrigerant flow in the portion 7 of the refrigerant passage 3 provided with the shaft 5 can be suppressed. .
  • the value of the inner diameter D2 of the refrigerant passage central portion 7 is larger than the values of the inner diameters D1 and D3 of the joints 13 and 15, so that the passage resistance in the refrigerant passage 2 increases. Is suppressed.
  • the expansion valve 1 even if the value of the parameter a is set to less than 40, the eigenvalue F0 of the refrigerant passage 3 in which the shaft 5 is disposed is the Karman vortex generated by the outer diameter D4 of the shaft 5. Since it is set to be larger than the frequency F1, it is possible to prevent the generation of noise due to the flow of the refrigerant.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un détendeur (1) pour laquelle un arbre (5) actionnant une partie de soupape afin de régler la quantité de réfrigérant qui s'y s'écoule est disposée dans un passage de réfrigérant (3) à travers lequel s'écoule le réfrigérant. La valeur caractéristique (F0) du passage de réfrigérant (3) dans lequel l'arbre (5) est configurée, est réglée de manière à être supérieure à la fréquence (F1) d'un tourbillon de Karman généré par l'arbre (5). La forme extérieure de l'arbre (5) est cylindrique. L'arbre (5) est disposé de manière ouverte dans le passage de réfrigérant (3).
PCT/JP2017/028675 2016-08-10 2017-08-08 Détendeur WO2018030364A1 (fr)

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CN201780047193.8A CN109564040A (zh) 2016-08-10 2017-08-08 膨胀阀

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JP2016157838A JP2018025364A (ja) 2016-08-10 2016-08-10 膨張弁
JP2016-157838 2016-08-10

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Publication number Priority date Publication date Assignee Title
JP2016145656A (ja) * 2015-02-06 2016-08-12 株式会社テージーケー 膨張弁およびその配管取付構造

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JPH10288424A (ja) * 1997-04-11 1998-10-27 Fuji Koki Corp 温度式膨張弁
JPH11173705A (ja) * 1997-12-09 1999-07-02 Tgk Co Ltd バイパス管路付冷凍サイクル用膨張弁
JP2004053181A (ja) * 2002-07-23 2004-02-19 Fuji Koki Corp 膨張弁
JP2016044861A (ja) * 2014-08-21 2016-04-04 株式会社テージーケー 膨張弁

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