US20220146160A1 - Expansion valve - Google Patents
Expansion valve Download PDFInfo
- Publication number
- US20220146160A1 US20220146160A1 US17/435,965 US202017435965A US2022146160A1 US 20220146160 A1 US20220146160 A1 US 20220146160A1 US 202017435965 A US202017435965 A US 202017435965A US 2022146160 A1 US2022146160 A1 US 2022146160A1
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- United States
- Prior art keywords
- valve
- wall
- valve seat
- body portion
- valve body
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- Pending
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- 239000012530 fluid Substances 0.000 claims abstract description 13
- 239000003507 refrigerant Substances 0.000 description 53
- 230000004323 axial length Effects 0.000 description 10
- 238000005057 refrigeration Methods 0.000 description 6
- 239000003990 capacitor Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000003466 welding Methods 0.000 description 5
- 230000009172 bursting Effects 0.000 description 4
- 238000001514 detection method Methods 0.000 description 4
- 239000013256 coordination polymer Substances 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- 210000000078 claw Anatomy 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Images
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
- F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
- F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/068—Expansion valves combined with a sensor
- F25B2341/0683—Expansion valves combined with a sensor the sensor is disposed in the suction line and influenced by the temperature or the pressure of the suction gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/03—Cavitations
-
- 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
- F25B2500/12—Sound
Definitions
- the present invention relates to an expansion valve.
- a temperature-sensitive expansion valve that adjusts an amount of a refrigerant passing therethrough according to temperature, with the aim to cut down installation space and piping.
- a spherical valve body arranged in a valve chamber is positioned to face a valve seat formed as an opening on the valve chamber.
- the valve body is supported by a valve body support arranged in the valve chamber and urged toward the valve seat by a coil spring arranged between a spring holding member attached to the valve main body and the valve body support. Then, the valve body is pressed by an actuation rod driven by a power element and moves away from the valve seat to allow passage of a refrigerant.
- the refrigerant that has passed through a throttle flow channel between the valve seat and the valve body is sent through an outlet port toward an evaporator.
- Patent Literature 1 discloses an expansion valve that defines a refrigerant inlet of the valve chamber and a gap between the valve body support and the valve chamber so as to realize a good balance between reduction of friction noise of the refrigerant when starting the refrigeration cycle system and ensuring a necessary flow rate of the refrigerant passing through the throttle flow channel.
- noise caused by the refrigerant other than the friction noise is also generated in the expansion valve.
- bubbles in the refrigerant may reach the valve seat without being collapsed and may burst simultaneously when the refrigerant passes through the valve seat, which may be recognized as noise.
- the present invention aims at providing an improved expansion valve having a simple configuration and with which noise can be reduced.
- the expansion valve according to the present invention includes:
- valve main body including a valve chamber and a valve seat
- valve body configured to prevent passage of a fluid by being seated on the valve seat and allow passage of the fluid by separating from the valve seat;
- a coil spring configured to urge the valve body toward the valve seat
- an actuation rod configured to press the valve body toward a direction separating from the valve seat against an urging force applied from the coil spring
- valve chamber includes a cylindrical inner wall being connected to the valve seat
- valve body includes a contact portion configured to be seated on the valve seat and a body portion having a tubular shape facing the inner wall, and
- a shape of an inner circumference of the inner wall differs from a shape of an outer circumference of the body portion, so that a space through which the fluid passes is formed between the inner wall and the body portion, and the inner circumference of the inner wall and the outer circumference of the body portion are partially slidably in contact with each other.
- the present invention provides an improved expansion valve having a simple configuration and with which noise can be reduced.
- FIG. 1 is a schematic cross-sectional view illustrating an example where an expansion valve according to a first embodiment is applied to a refrigerant cycle system.
- FIG. 2 is a top view of a cross section taken at line A-A of FIG. 1 .
- FIG. 3 is a perspective view of a valve body according to the present embodiment.
- FIG. 4 is a cross-sectional view illustrating a vicinity of a valve body of an expansion valve according to a second embodiment in enlarged view.
- FIG. 5 is a top view of a cross section taken at line B-B of FIG. 4 .
- FIG. 6 is a perspective view of the valve body according to the present embodiment.
- FIG. 7 is a cross-sectional view illustrating a vicinity of a valve body of an expansion valve according to a third embodiment in enlarged view.
- FIG. 8 is a top view of a cross section taken at line C-C of FIG. 7 .
- FIG. 9 is a perspective view of the valve body according to the present embodiment.
- FIG. 10 is a cross-sectional view of a body portion according to a modified example.
- a direction from a valve body 3 toward an actuation rod 5 is defined as an “upper direction”, and a direction from the actuation rod 5 toward the valve body 3 is defined as a “lower direction”. Therefore, according to the present specification, the direction from the valve body 3 toward the actuation rod 5 is referred to as the “upper direction” regardless of the orientation of an expansion valve 10 .
- a “polygonal tubular shape” refers to a tubular shape having a outer circumference that surrounds an axis with four or more plane surfaces. However, if there are connecting surfaces that connect the plane surfaces, such connecting surfaces are not included in the plane surfaces. Further, “the shape of the inner circumference being different from the shape of the outer circumference in cross section” means that the shape of the inner circumference is neither the same as nor similar to the shape of the outer circumference.
- FIG. 1 is a schematic cross-sectional view illustrating an example where the expansion valve 10 according to the present embodiment is applied to a refrigerant cycle system 100 .
- the expansion valve 10 is connected to a compressor 101 , a capacitor 102 and an evaporator 104 that constitute the refrigerant cycle system 100 .
- the expansion valve 10 includes a valve main body 2 equipped with a cylindrical valve chamber VS, the valve body 3 , an urging device 4 , the actuation rod 5 , and a ring spring 6 .
- the valve main body 2 includes a first flow channel 21 and a second flow channel 22 in addition to a valve chamber VS.
- the first flow channel 21 is a supply-side flow channel, for example, and a refrigerant, also referred to as a fluid, is supplied to the valve chamber VS via a supply-side flow channel.
- the second flow channel 22 is a discharge-side flow channel, for example, and the fluid in the valve chamber VS is discharged via an orifice portion 27 and the second flow channel 22 to the exterior of the expansion valve.
- the first flow channel 21 and the valve chamber VS are connected via a connection path 21 a having a smaller diameter than the first flow channel 21 .
- the valve chamber VS includes a valve seat 20 which is an inner circumference of a lower edge of the orifice portion 27 having a cylindrical shape, and a cylindrical inner wall 24 connected to the valve seat 20 and having a greater diameter than the valve seat 20 .
- FIG. 2 is a top view of a cross section taken at line A-A of FIG. 1 , and it illustrates a cross section of the valve body 3 in a direction orthogonal to the axis.
- FIG. 3 is a perspective view of the valve body 3 .
- the valve body 3 is formed by consecutively connecting a conical contact portion 31 , a body portion 32 having a hexagonal tubular shape, a flange portion 33 having a disk shape, and an end portion 34 having a cylindrical shape.
- a tapered surface 31 b of the contact portion 31 is abutted against the valve seat 20 .
- An upper surface 31 a of the contact portion 31 is a plane surface that is orthogonal to an axis L.
- An outer circumference of the body portion 32 is composed of six plane surfaces 32 a and connecting surfaces 32 b that are formed between adjacent plane surfaces 32 a .
- Each connecting surface 32 b can either be a plane surface or a curved surface, and the peripheral length is preferably 1 ⁇ 4 or less of the peripheral length of the plane surface 32 a .
- the axial-direction length of the body portion 32 is preferably the same size as an inner diameter of an inner wall 24 of the valve chamber VS (or a maximum diagonal length of the body portion 32 ) or greater.
- the valve body 3 is arranged in the valve chamber VS.
- a shape of an inner circumference of the inner wall 24 of the valve chamber VS and a shape of an outer circumference of the body portion 32 differ, and according to an eccentricity of the valve chamber VS and the valve body 3 , one of the connecting surfaces 32 b abut and slide against the inner wall 24 of the valve chamber VS.
- the inner wall 24 of the valve chamber VS does not abut against the plane surfaces 32 a . Therefore, the refrigerant will pass through the space formed between the inner wall 24 and the plane surfaces 32 a.
- FIG. 1 in a state where the valve body 3 is seated on the valve seat 20 having an annular shape arranged in the valve main body 2 , the first flow channel 21 and the second flow channel 22 are in a non-communicated state. Meanwhile, in a state where the valve body 3 is separated from the valve seat 20 , the first flow channel 21 and the second flow channel 22 are in a communicated state. However, there may be a case where a limited amount of refrigerant is allowed to pass through even when the valve body 3 is seated on the valve seat 20 .
- a lower end of the actuation rod 5 inserted to an actuation rod inserting hole 28 of the valve main body 2 and also inserted to the orifice portion 27 with a gap therebetween is in contact with the upper surface 31 a of the valve body 3 in a manner relatively displaceable in a direction intersecting the axis L. Further, the actuation rod 5 can press the valve body 3 toward a valve opening direction against an urging force applied from the urging device 4 . In a state where the actuation rod 5 moves in the lower direction, the valve body 3 separates from the valve seat 20 and the expansion valve 10 will be in an opened state.
- the power element 8 for driving the actuation rod 5 will be described.
- the power element 8 is attached to a recessed portion 2 a provided on a top portion of the valve main body 2 .
- the recessed portion 2 a is communicated via a communication path 2 b with a return flow channel 23 within the valve main body 2 through which the refrigerant from the evaporator 104 passes.
- the actuation rod 5 is passed through the communication path 2 b .
- a female screw is formed on an inner circumference of the recessed portion 2 a.
- the power element 8 includes a plug 81 , an upper lid member 82 , a diaphragm 83 , a stopper member 84 , and a receiver member 86 .
- the upper lid member 82 includes a conical portion 82 a arranged at a center and a flange portion 82 b having an annular shape and extending from a lower end of the conical portion 82 a toward the outer circumference.
- An opening 82 c is formed at a top portion of the conical portion 82 a , which can be sealed by the plug 81 .
- the diaphragm 83 is formed of a thin plate material on which a plurality of corrugated shapes of concentric circles are formed, and it has an outer diameter that is approximately the same as an outer diameter of the flange portion 82 b.
- the stopper member 84 includes a fitting hole 84 a formed at a center of a lower end thereof.
- the receiver member 86 includes a flange portion 86 a having an outer diameter that is approximately the same as the outer diameter of the flange portion 82 b of the upper lid member 82 , a stepped portion 86 c having an annular support surface 86 b that is substantially orthogonal to the axis L, and a hollow cylindrical portion 86 b .
- a male screw is formed on an outer circumference of the hollow cylindrical portion 86 b.
- the upper lid member 82 , the diaphragm 83 , the stopper member 84 and the receiver member 86 are arranged so that they are in a positional relationship as illustrated in FIG. 1 .
- the outer circumference portions of the flange portion 82 b of the upper lid member 82 , the diaphragm 83 and the flange portion 86 a of the receiver member 86 are superposed, the outer circumference portions are subjected to girth welding by TIG welding, laser welding or plasma welding, for example, and integrated.
- the opening 82 c is sealed by the plug 81 , and thereafter, the plug 81 is fixed to the upper lid member 82 by projection welding, for example.
- the diaphragm 83 receives pressure from the operative gas filled in the pressure operation chamber PO in a direction pressing the diaphragm 83 toward the receiver member 86 , so that the diaphragm 83 abuts against and is supported by an upper surface of the stopper member 84 arranged in a space (pressure detection chamber PD) surrounded by the diaphragm 83 and the receiver member 86 .
- the male screw on the hollow cylindrical portion 86 b of the receiver member 86 is screwed to the female screw on the recessed portion 2 a of the valve main body 2 that is communicated with the return flow channel 23 , and the power element 8 is thereby fixed to the valve main body 2 .
- a packing PK is interposed between the power element 8 and the valve main body 2 so as to prevent leakage of the refrigerant from the recessed portion 2 a when the power element 8 is attached to the valve main body 2 .
- the pressure detection chamber PD of the power element 8 is communicated with the return flow channel 23 .
- the ring spring 6 is a vibration absorption member that suppresses the vibration of the actuation rod 5 .
- the ring spring 6 is arranged in an annular portion 26 adjacent to the actuation rod inserting hole 28 of the valve main body 2 and applies a predetermined elastic force to an outer circumference surface of the actuation rod 5 by a claw portion protruded to an inner circumference direction.
- the urging device 4 includes a coil spring 41 formed by winding a round wire helically, and a spring holding member 43 .
- the spring holding member 43 has a function to seal the opening of the valve chamber VS of the valve main body 2 and also has a function to support a lower end of the coil spring 41 .
- An O-ring 44 is arranged between the spring holding member 43 and the inner wall of the valve chamber VS to prevent leakage of the refrigerant.
- valve body 3 illustrated in FIG. 3 is retained by having an upper end of the coil spring 41 abut against a lower side of the flange portion 33 and also having the end portion 34 fit to an inner side of the upper end of the coil spring 41
- the refrigerant pressurized by the compressor 101 is liquefied in the capacitor 102 and sent to the expansion valve 10 . Further, the refrigerant subjected to adiabatic expansion in the expansion valve 10 is sent to the evaporator 104 , and in the evaporator 104 , the refrigerant is subjected to heat exchange with the air flowing in a circumference of the evaporator. The refrigerant returning from the evaporator 104 is returned through the expansion valve 10 (more specifically, the return flow channel 23 ) toward the compressor 101 .
- a high-pressure refrigerant is supplied to the expansion valve 10 from the capacitor 102 . More specifically, the high-pressure refrigerant from the capacitor 102 is supplied via the first flow channel 21 to the valve chamber VS.
- the refrigerant containing bubbles in the valve chamber VS is guided along the axial length of the body portion 32 through a relatively narrow gap between the plane surfaces 32 a of the body portion 32 of the valve body 3 and the inner wall 24 , during which time the bubbles are gradually collapsed. Therefore, the bubbles will not collapse simultaneously when the refrigerant passes through the valve seat 20 , so that the energy generated by the bursting of the bubbles is reduced and the noise generated during passage of the refrigerant is cut down. Further, by having the refrigerant flow along the plane surfaces 32 a along the axial length of the body portion 32 , a flow straightening effect of the refrigerant is achieved.
- the pressure operation chamber PO and the pressure detection chamber PD that are separated by the diaphragm 83 are provided inside the power element 8 . Therefore, when the operative gas within the pressure operation chamber PO is liquefied, the actuation rod 5 moves to the upper direction, and when the liquefied operative gas is gasified, the actuation rod 5 moves to the lower direction. Thus, the switching between the valve-opened state and the valve-closed state of the expansion valve 10 is carried out.
- the pressure detection chamber PD of the power element 8 is communicated with the return flow channel 23 . Therefore, the pressure of the refrigerant flowing through the return flow channel 23 is transmitted via the stopper member 84 and the diaphragm 83 to the operative gas inside the pressure operation chamber PO. Thereby, the volume of the operative gas inside the pressure operation chamber PO is changed, and the actuation rod 5 is driven.
- the expansion valve 10 illustrated in FIG. 1 the amount of the refrigerant supplied from the expansion valve 10 to the evaporator 104 is automatically adjusted according to the pressure of the refrigerant returning from the evaporator 104 to the expansion valve 10 .
- FIG. 4 is a cross-sectional view illustrating a vicinity of a valve body of an expansion valve 10 A in enlarged view.
- FIG. 5 is a top view of a cross section taken at line B-B of FIG. 4 .
- FIG. 6 is a perspective view of the valve body 3 A.
- the valve body 3 A is formed by consecutively connecting a conical contact portion 31 A, a body portion 32 A having a hexagonal tubular shape, and an end portion 34 A having a cylindrical shape.
- a tapered surface 31 Ab of the contact portion 31 A is abutted against the valve seat 20 .
- an upper surface 31 Aa of the contact portion 31 A is a plane surface that is orthogonal to the axis L.
- An outer circumference of the body portion 32 A is composed of six plane surfaces 32 Aa and connecting surfaces 32 Ab that are formed between adjacent plane surfaces 32 a .
- Each connecting surface 32 b can either be a plane surface or a curved surface.
- the peripheral length of the body portion 32 A is preferably the same size as a diameter of an inner wall 24 A of the valve chamber VS (or a maximum diagonal length of the body portion 32 ) or greater.
- the connecting surfaces 32 Ab constitute a sliding contact portion, and the plane surfaces 32 Aa constitute a flow channel portion.
- An inner wall 24 A of the valve chamber VS is formed greater than an outer diameter of the coil spring 41 .
- the refrigerant containing bubbles in the valve chamber VS is guided along the axial length of the body portion 32 A through a relatively narrow gap between the plane surfaces 32 Aa of the body portion 32 A of the valve body 3 A and the inner wall 24 A, during which time the bubbles are gradually collapsed. Therefore, the bubbles will not collapse simultaneously when the refrigerant passes through the valve seat 20 , so that the energy generated by the bursting of the bubbles is reduced and the noise generated during passage of the refrigerant is cut down. Further, by having the refrigerant flow along the plane surfaces 32 Aa along the axial length of the body portion 32 A, a flow straightening effect of the refrigerant is achieved.
- FIG. 7 is a cross-sectional view illustrating a vicinity of a valve body of an expansion valve 10 B in enlarged view.
- FIG. 8 is a top view of the cross section taken at line C-C of FIG. 7 .
- FIG. 9 is a perspective view of a valve body 3 B.
- the valve body 3 B is formed by consecutively connecting a conical contact portion 31 B, a body portion 32 B having a cylindrical shape, a flange portion 33 B having a disk shape, and an end portion 34 B having a cylindrical shape.
- a tapered surface 31 Bb of the contact portion 31 B is abutted against the valve seat 20 .
- an upper surface 31 Ba of the contact portion 31 B is a plane surface that is orthogonal to the axis L.
- the length of the body portion 32 B should preferably be the same as a maximum diagonal length of an inner wall 24 B of the valve chamber VS (or a diameter of the body portion 32 B) or greater.
- the inner wall 24 B of the valve chamber VS has a hexagonal tubular shape formed of six plane surfaces 24 Bb.
- the outer circumference of the body portion 32 B of the valve body 3 B is in contact with the plane surfaces 24 Bb at any of the six contact points CP illustrated in FIG. 8 . Therefore, the contact point CP at the outer circumference surface of the body portion 32 B constitutes a sliding contact portion, and the outer circumference surface between adjacent contact points CP constitutes a flow channel portion.
- the other configurations are similar to the embodiment described above, so they are denoted with the same reference numbers and detailed descriptions thereof are omitted.
- the refrigerant containing bubbles in the valve chamber VS is guided along the axial length of the body portion 32 B through a relatively narrow gap between the outer circumference surface of the body portion 32 B of the valve body 3 B and the inner wall 24 B, during which time the bubbles are gradually collapsed. Therefore, the bubbles will not collapse simultaneously when the refrigerant passes through the valve seat 20 , so that the energy generated by the bursting of the bubbles is reduced and the noise generated during passage of the refrigerant is cut down. Further, by having the refrigerant flow along the plane surfaces 24 Bb along the axial length of the body portion 32 B, a flow straightening effect of the refrigerant is achieved.
- FIG. 10 is a view similar to FIG. 2 illustrating a cross section of a valve body and an inner wall of a valve chamber according to a modified example.
- an inner wall 24 D of a valve chamber at a valve main body 2 D is a cylindrical surface
- a body portion 32 D of the valve body has a non-round cross section.
- the body portion 32 D is formed of a partially cylindrical surface 32 Da and a plane surface 32 Db.
- the width of the plane surface 32 Db is shorter than a diameter of the partially cylindrical surface 32 Da.
- a cross-sectional shape of the body portion 32 D is the same throughout the whole length of the body portion 32 D.
- the partially cylindrical surface 32 Da constitutes the sliding contact portion
- the plane surface 32 Db constitutes the flow channel portion.
- the other configurations are similar to the embodiments described earlier, so they are denoted with the same reference numbers, and detailed descriptions thereof are omitted.
- the refrigerant containing bubbles in the valve chamber is guided along the axial length of the body portion 32 D through a relatively narrow gap between the plane surface 32 Db of the body portion 32 D of the valve body and the inner wall 24 D, during which time the bubbles are gradually collapsed. Therefore, the bubbles will not collapse simultaneously when the refrigerant passes through the valve seat, so that the energy generated by the bursting of the bubbles is reduced and the noise generated during passage of the refrigerant is cut down. Further, by having the refrigerant flow along the plane surface 32 Db along the axial length of the body portion 32 D, a flow straightening effect of the refrigerant is achieved.
- the present invention is not limited to the above-described embodiments.
- Arbitrary components of the above-described embodiments can be modified within the scope of the present invention. Further, arbitrary components can be added to or omitted from the above-described embodiments.
- the flow channel portion is not limited to being a plane surface, and it can be a protruded curved surface or a recessed curved surface.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Fluid Mechanics (AREA)
- Temperature-Responsive Valves (AREA)
- Lift Valve (AREA)
- Details Of Valves (AREA)
Abstract
Description
- The present invention relates to an expansion valve.
- Hitherto, in a refrigeration cycle system adopted in an air conditioner mounted on an automobile, for example, a temperature-sensitive expansion valve that adjusts an amount of a refrigerant passing therethrough according to temperature, with the aim to cut down installation space and piping.
- In a general expansion valve, a spherical valve body arranged in a valve chamber is positioned to face a valve seat formed as an opening on the valve chamber. The valve body is supported by a valve body support arranged in the valve chamber and urged toward the valve seat by a coil spring arranged between a spring holding member attached to the valve main body and the valve body support. Then, the valve body is pressed by an actuation rod driven by a power element and moves away from the valve seat to allow passage of a refrigerant. The refrigerant that has passed through a throttle flow channel between the valve seat and the valve body is sent through an outlet port toward an evaporator.
- At an initial timing when the refrigeration cycle system is started, a liquid density of the refrigerant passing through the throttle flow channel between the valve seat and the valve body is low, and a flow speed of the refrigerant increases as the flow resistance reduces. Therefore, a large friction noise tends to occur at a valve portion at the start of the refrigeration cycle system, and therefore, limiting of flow rate of the refrigerant is required as a countermeasure. Meanwhile, during a stable period in which a certain time has elapsed from the activation of the refrigeration cycle, friction noise becomes small since the liquid density becomes higher compared to when the refrigeration cycle is started. The flow rate during the stable period should not be limited excessively, and rather, there is a contradictory request of a need to ensure a sufficient refrigerant flow rate.
- Patent Literature 1 discloses an expansion valve that defines a refrigerant inlet of the valve chamber and a gap between the valve body support and the valve chamber so as to realize a good balance between reduction of friction noise of the refrigerant when starting the refrigeration cycle system and ensuring a necessary flow rate of the refrigerant passing through the throttle flow channel.
-
- [PTL 1] Publication of Japanese Patent No. 5369259
- Meanwhile, noise caused by the refrigerant other than the friction noise is also generated in the expansion valve. For example, according to the expansion valve disclosed in Patent Literature 1, bubbles in the refrigerant may reach the valve seat without being collapsed and may burst simultaneously when the refrigerant passes through the valve seat, which may be recognized as noise.
- Therefore, the present invention aims at providing an improved expansion valve having a simple configuration and with which noise can be reduced.
- In order to achieve the above object, the expansion valve according to the present invention includes:
- a valve main body including a valve chamber and a valve seat;
- a valve body configured to prevent passage of a fluid by being seated on the valve seat and allow passage of the fluid by separating from the valve seat;
- a coil spring configured to urge the valve body toward the valve seat; and
- an actuation rod configured to press the valve body toward a direction separating from the valve seat against an urging force applied from the coil spring,
- wherein the valve chamber includes a cylindrical inner wall being connected to the valve seat,
- the valve body includes a contact portion configured to be seated on the valve seat and a body portion having a tubular shape facing the inner wall, and
- in a cross section taken in a direction orthogonal to an axis of the valve body, a shape of an inner circumference of the inner wall differs from a shape of an outer circumference of the body portion, so that a space through which the fluid passes is formed between the inner wall and the body portion, and the inner circumference of the inner wall and the outer circumference of the body portion are partially slidably in contact with each other.
- The present invention provides an improved expansion valve having a simple configuration and with which noise can be reduced.
-
FIG. 1 is a schematic cross-sectional view illustrating an example where an expansion valve according to a first embodiment is applied to a refrigerant cycle system. -
FIG. 2 is a top view of a cross section taken at line A-A ofFIG. 1 . -
FIG. 3 is a perspective view of a valve body according to the present embodiment. -
FIG. 4 is a cross-sectional view illustrating a vicinity of a valve body of an expansion valve according to a second embodiment in enlarged view. -
FIG. 5 is a top view of a cross section taken at line B-B ofFIG. 4 . -
FIG. 6 is a perspective view of the valve body according to the present embodiment. -
FIG. 7 is a cross-sectional view illustrating a vicinity of a valve body of an expansion valve according to a third embodiment in enlarged view. -
FIG. 8 is a top view of a cross section taken at line C-C ofFIG. 7 . -
FIG. 9 is a perspective view of the valve body according to the present embodiment. -
FIG. 10 is a cross-sectional view of a body portion according to a modified example. - In the present specification, a direction from a
valve body 3 toward anactuation rod 5 is defined as an “upper direction”, and a direction from theactuation rod 5 toward thevalve body 3 is defined as a “lower direction”. Therefore, according to the present specification, the direction from thevalve body 3 toward theactuation rod 5 is referred to as the “upper direction” regardless of the orientation of anexpansion valve 10. - In the present specification, a “polygonal tubular shape” refers to a tubular shape having a outer circumference that surrounds an axis with four or more plane surfaces. However, if there are connecting surfaces that connect the plane surfaces, such connecting surfaces are not included in the plane surfaces. Further, “the shape of the inner circumference being different from the shape of the outer circumference in cross section” means that the shape of the inner circumference is neither the same as nor similar to the shape of the outer circumference.
- A general configuration of the
expansion valve 10 according to a first embodiment will be described with reference toFIG. 1 .FIG. 1 is a schematic cross-sectional view illustrating an example where theexpansion valve 10 according to the present embodiment is applied to arefrigerant cycle system 100. In the present embodiment, theexpansion valve 10 is connected to acompressor 101, acapacitor 102 and anevaporator 104 that constitute therefrigerant cycle system 100. - The
expansion valve 10 includes a valve main body 2 equipped with a cylindrical valve chamber VS, thevalve body 3, an urging device 4, theactuation rod 5, and a ring spring 6. - The valve main body 2 includes a
first flow channel 21 and asecond flow channel 22 in addition to a valve chamber VS. Thefirst flow channel 21 is a supply-side flow channel, for example, and a refrigerant, also referred to as a fluid, is supplied to the valve chamber VS via a supply-side flow channel. Thesecond flow channel 22 is a discharge-side flow channel, for example, and the fluid in the valve chamber VS is discharged via anorifice portion 27 and thesecond flow channel 22 to the exterior of the expansion valve. Thefirst flow channel 21 and the valve chamber VS are connected via a connection path 21 a having a smaller diameter than thefirst flow channel 21. - The valve chamber VS includes a
valve seat 20 which is an inner circumference of a lower edge of theorifice portion 27 having a cylindrical shape, and a cylindricalinner wall 24 connected to thevalve seat 20 and having a greater diameter than thevalve seat 20. -
FIG. 2 is a top view of a cross section taken at line A-A ofFIG. 1 , and it illustrates a cross section of thevalve body 3 in a direction orthogonal to the axis.FIG. 3 is a perspective view of thevalve body 3. InFIG. 3 , thevalve body 3 is formed by consecutively connecting aconical contact portion 31, abody portion 32 having a hexagonal tubular shape, aflange portion 33 having a disk shape, and anend portion 34 having a cylindrical shape. - A
tapered surface 31 b of thecontact portion 31 is abutted against thevalve seat 20. Anupper surface 31 a of thecontact portion 31 is a plane surface that is orthogonal to an axis L. An outer circumference of thebody portion 32 is composed of sixplane surfaces 32 a and connectingsurfaces 32 b that are formed betweenadjacent plane surfaces 32 a. Each connectingsurface 32 b can either be a plane surface or a curved surface, and the peripheral length is preferably ¼ or less of the peripheral length of theplane surface 32 a. Further, the axial-direction length of thebody portion 32 is preferably the same size as an inner diameter of aninner wall 24 of the valve chamber VS (or a maximum diagonal length of the body portion 32) or greater. - The
valve body 3 is arranged in the valve chamber VS. In the cross section ofFIG. 2 , a shape of an inner circumference of theinner wall 24 of the valve chamber VS and a shape of an outer circumference of thebody portion 32 differ, and according to an eccentricity of the valve chamber VS and thevalve body 3, one of the connectingsurfaces 32 b abut and slide against theinner wall 24 of the valve chamber VS. Meanwhile, regardless of the eccentricity of the valve chamber VS and thevalve body 3, theinner wall 24 of the valve chamber VS does not abut against the plane surfaces 32 a. Therefore, the refrigerant will pass through the space formed between theinner wall 24 and the plane surfaces 32 a. - In
FIG. 1 , in a state where thevalve body 3 is seated on thevalve seat 20 having an annular shape arranged in the valve main body 2, thefirst flow channel 21 and thesecond flow channel 22 are in a non-communicated state. Meanwhile, in a state where thevalve body 3 is separated from thevalve seat 20, thefirst flow channel 21 and thesecond flow channel 22 are in a communicated state. However, there may be a case where a limited amount of refrigerant is allowed to pass through even when thevalve body 3 is seated on thevalve seat 20. - A lower end of the
actuation rod 5 inserted to an actuationrod inserting hole 28 of the valve main body 2 and also inserted to theorifice portion 27 with a gap therebetween is in contact with theupper surface 31 a of thevalve body 3 in a manner relatively displaceable in a direction intersecting the axis L. Further, theactuation rod 5 can press thevalve body 3 toward a valve opening direction against an urging force applied from the urging device 4. In a state where theactuation rod 5 moves in the lower direction, thevalve body 3 separates from thevalve seat 20 and theexpansion valve 10 will be in an opened state. - Next, a
power element 8 for driving theactuation rod 5 will be described. InFIG. 1 , thepower element 8 is attached to a recessedportion 2 a provided on a top portion of the valve main body 2. The recessedportion 2 a is communicated via acommunication path 2 b with areturn flow channel 23 within the valve main body 2 through which the refrigerant from the evaporator 104 passes. Theactuation rod 5 is passed through thecommunication path 2 b. A female screw is formed on an inner circumference of the recessedportion 2 a. - The
power element 8 includes aplug 81, anupper lid member 82, adiaphragm 83, astopper member 84, and areceiver member 86. - The
upper lid member 82 includes aconical portion 82 a arranged at a center and aflange portion 82 b having an annular shape and extending from a lower end of theconical portion 82 a toward the outer circumference. Anopening 82 c is formed at a top portion of theconical portion 82 a, which can be sealed by theplug 81. - The
diaphragm 83 is formed of a thin plate material on which a plurality of corrugated shapes of concentric circles are formed, and it has an outer diameter that is approximately the same as an outer diameter of theflange portion 82 b. - The
stopper member 84 includes a fitting hole 84 a formed at a center of a lower end thereof. - The
receiver member 86 includes a flange portion 86 a having an outer diameter that is approximately the same as the outer diameter of theflange portion 82 b of theupper lid member 82, a steppedportion 86 c having anannular support surface 86 b that is substantially orthogonal to the axis L, and a hollowcylindrical portion 86 b. A male screw is formed on an outer circumference of the hollowcylindrical portion 86 b. - A process for assembling the
power element 8 will be described. Theupper lid member 82, thediaphragm 83, thestopper member 84 and thereceiver member 86 are arranged so that they are in a positional relationship as illustrated inFIG. 1 . - Further, in a state where the outer circumference portions of the
flange portion 82 b of theupper lid member 82, thediaphragm 83 and the flange portion 86 a of thereceiver member 86 are superposed, the outer circumference portions are subjected to girth welding by TIG welding, laser welding or plasma welding, for example, and integrated. - Next, after filling a space (pressure operation chamber PO) surrounded by the
upper lid member 82 and thediaphragm 83 with operative gas through theopening 82 c formed on theupper lid member 82, theopening 82 c is sealed by theplug 81, and thereafter, theplug 81 is fixed to theupper lid member 82 by projection welding, for example. - In this state, the
diaphragm 83 receives pressure from the operative gas filled in the pressure operation chamber PO in a direction pressing thediaphragm 83 toward thereceiver member 86, so that thediaphragm 83 abuts against and is supported by an upper surface of thestopper member 84 arranged in a space (pressure detection chamber PD) surrounded by thediaphragm 83 and thereceiver member 86. - During assembly of the
power element 8, in a state where an upper end of theactuation rod 5 is fit to the fitting hole 84 a of thestopper member 84, the male screw on the hollowcylindrical portion 86 b of thereceiver member 86 is screwed to the female screw on the recessedportion 2 a of the valve main body 2 that is communicated with thereturn flow channel 23, and thepower element 8 is thereby fixed to the valve main body 2. - In this state, a packing PK is interposed between the
power element 8 and the valve main body 2 so as to prevent leakage of the refrigerant from the recessedportion 2 a when thepower element 8 is attached to the valve main body 2. In this state, the pressure detection chamber PD of thepower element 8 is communicated with thereturn flow channel 23. - The ring spring 6 is a vibration absorption member that suppresses the vibration of the
actuation rod 5. The ring spring 6 is arranged in anannular portion 26 adjacent to the actuationrod inserting hole 28 of the valve main body 2 and applies a predetermined elastic force to an outer circumference surface of theactuation rod 5 by a claw portion protruded to an inner circumference direction. - The urging device 4 includes a
coil spring 41 formed by winding a round wire helically, and aspring holding member 43. Thespring holding member 43 has a function to seal the opening of the valve chamber VS of the valve main body 2 and also has a function to support a lower end of thecoil spring 41. An O-ring 44 is arranged between thespring holding member 43 and the inner wall of the valve chamber VS to prevent leakage of the refrigerant. - The
valve body 3 illustrated inFIG. 3 is retained by having an upper end of thecoil spring 41 abut against a lower side of theflange portion 33 and also having theend portion 34 fit to an inner side of the upper end of thecoil spring 41 - An operation example of the
expansion valve 10 will be described with reference toFIG. 1 . The refrigerant pressurized by thecompressor 101 is liquefied in thecapacitor 102 and sent to theexpansion valve 10. Further, the refrigerant subjected to adiabatic expansion in theexpansion valve 10 is sent to theevaporator 104, and in theevaporator 104, the refrigerant is subjected to heat exchange with the air flowing in a circumference of the evaporator. The refrigerant returning from theevaporator 104 is returned through the expansion valve 10 (more specifically, the return flow channel 23) toward thecompressor 101. - A high-pressure refrigerant is supplied to the
expansion valve 10 from thecapacitor 102. More specifically, the high-pressure refrigerant from thecapacitor 102 is supplied via thefirst flow channel 21 to the valve chamber VS. - In a state where the
contact portion 31 of thevalve body 3 is seated on the valve seat 20 (in other words, when theexpansion valve 10 is in the closed state), thefirst flow channel 21 upstream of the valve chamber VS and thesecond flow channel 22 downstream of the valve chamber VS are in a non-communicated state. Meanwhile, in a state where thecontact portion 31 of thevalve body 3 is separated from the valve seat 20 (in other words, when theexpansion valve 10 is in the opened state), the refrigerant supplied to the valve chamber VS is sent through theorifice portion 27 and thesecond flow channel 22 toward theevaporator 104. - According to the present embodiment, in a state where the
contact portion 31 of thevalve body 3 is separated from thevalve seat 20, the refrigerant containing bubbles in the valve chamber VS is guided along the axial length of thebody portion 32 through a relatively narrow gap between the plane surfaces 32 a of thebody portion 32 of thevalve body 3 and theinner wall 24, during which time the bubbles are gradually collapsed. Therefore, the bubbles will not collapse simultaneously when the refrigerant passes through thevalve seat 20, so that the energy generated by the bursting of the bubbles is reduced and the noise generated during passage of the refrigerant is cut down. Further, by having the refrigerant flow along the plane surfaces 32 a along the axial length of thebody portion 32, a flow straightening effect of the refrigerant is achieved. - Switching of the closed state and the opened state of the
expansion valve 10 is carried out by theactuation rod 5 connected to thepower element 8. In this state, the connectingsurfaces 32 b of thebody portion 32 sliding against theinner wall 24 has a long length corresponding to the axial length of thebody portion 32, so that tilting that may be caused when thecontact portion 31 of thevalve body 3 separates from thevalve seat 20 can be suppressed. Thus, further to theupper surface 31 a being relatively displaceable with respect to theactuation rod 5, smooth movement of thevalve body 3 can be ensured. - In
FIG. 1 , the pressure operation chamber PO and the pressure detection chamber PD that are separated by thediaphragm 83 are provided inside thepower element 8. Therefore, when the operative gas within the pressure operation chamber PO is liquefied, theactuation rod 5 moves to the upper direction, and when the liquefied operative gas is gasified, theactuation rod 5 moves to the lower direction. Thus, the switching between the valve-opened state and the valve-closed state of theexpansion valve 10 is carried out. - Further, the pressure detection chamber PD of the
power element 8 is communicated with thereturn flow channel 23. Therefore, the pressure of the refrigerant flowing through thereturn flow channel 23 is transmitted via thestopper member 84 and thediaphragm 83 to the operative gas inside the pressure operation chamber PO. Thereby, the volume of the operative gas inside the pressure operation chamber PO is changed, and theactuation rod 5 is driven. In other words, according to theexpansion valve 10 illustrated inFIG. 1 , the amount of the refrigerant supplied from theexpansion valve 10 to theevaporator 104 is automatically adjusted according to the pressure of the refrigerant returning from theevaporator 104 to theexpansion valve 10. - Next, an expansion valve according to a second embodiment will be described.
FIG. 4 is a cross-sectional view illustrating a vicinity of a valve body of an expansion valve 10A in enlarged view.FIG. 5 is a top view of a cross section taken at line B-B ofFIG. 4 .FIG. 6 is a perspective view of thevalve body 3A. - In
FIG. 6 , thevalve body 3A is formed by consecutively connecting a conical contact portion 31A, abody portion 32A having a hexagonal tubular shape, and an end portion 34A having a cylindrical shape. - A tapered surface 31Ab of the contact portion 31A is abutted against the
valve seat 20. Further, an upper surface 31Aa of the contact portion 31A is a plane surface that is orthogonal to the axis L. An outer circumference of thebody portion 32A is composed of six plane surfaces 32Aa and connecting surfaces 32Ab that are formed between adjacent plane surfaces 32 a. Each connectingsurface 32 b can either be a plane surface or a curved surface. The peripheral length of thebody portion 32A is preferably the same size as a diameter of aninner wall 24A of the valve chamber VS (or a maximum diagonal length of the body portion 32) or greater. The connecting surfaces 32Ab constitute a sliding contact portion, and the plane surfaces 32Aa constitute a flow channel portion. - An
inner wall 24A of the valve chamber VS is formed greater than an outer diameter of thecoil spring 41. The other configurations are similar to the above-described embodiment, so the similar components are denoted with the same reference numbers and detailed descriptions thereof are omitted. - According to the present embodiment, in a state where the contact portion 31A of the
valve body 3A is separated from thevalve seat 20, the refrigerant containing bubbles in the valve chamber VS is guided along the axial length of thebody portion 32A through a relatively narrow gap between the plane surfaces 32Aa of thebody portion 32A of thevalve body 3A and theinner wall 24A, during which time the bubbles are gradually collapsed. Therefore, the bubbles will not collapse simultaneously when the refrigerant passes through thevalve seat 20, so that the energy generated by the bursting of the bubbles is reduced and the noise generated during passage of the refrigerant is cut down. Further, by having the refrigerant flow along the plane surfaces 32Aa along the axial length of thebody portion 32A, a flow straightening effect of the refrigerant is achieved. - Since the connecting surfaces 32Ab of the
body portion 32A that abut against theinner wall 24A during opening and closing of the valve have a long length corresponding to the axial length of thebody portion 32A, tilting caused when the contact portion 31A of thevalve body 3A separates from thevalve seat 20 can be suppressed. Thus, further to the upper surface 31Aa being relatively displaceable with respect to theactuation rod 5, smooth movement of thevalve body 3 can be ensured. - Especially since the position in which the connecting surfaces 32Ab abut against the
inner wall 24A is relatively distant from the axis L, tilting of thevalve body 3A can be suppressed effectively. - Next, an expansion valve according to a third embodiment will be described.
FIG. 7 is a cross-sectional view illustrating a vicinity of a valve body of an expansion valve 10B in enlarged view.FIG. 8 is a top view of the cross section taken at line C-C ofFIG. 7 .FIG. 9 is a perspective view of avalve body 3B. - In
FIG. 9 , thevalve body 3B is formed by consecutively connecting aconical contact portion 31B, abody portion 32B having a cylindrical shape, a flange portion 33B having a disk shape, and an end portion 34B having a cylindrical shape. - A tapered surface 31Bb of the
contact portion 31B is abutted against thevalve seat 20. Further, an upper surface 31Ba of thecontact portion 31B is a plane surface that is orthogonal to the axis L. The length of thebody portion 32B should preferably be the same as a maximum diagonal length of aninner wall 24B of the valve chamber VS (or a diameter of thebody portion 32B) or greater. - As illustrated in
FIG. 8 , theinner wall 24B of the valve chamber VS has a hexagonal tubular shape formed of six plane surfaces 24Bb. The outer circumference of thebody portion 32B of thevalve body 3B is in contact with the plane surfaces 24Bb at any of the six contact points CP illustrated inFIG. 8 . Therefore, the contact point CP at the outer circumference surface of thebody portion 32B constitutes a sliding contact portion, and the outer circumference surface between adjacent contact points CP constitutes a flow channel portion. The other configurations are similar to the embodiment described above, so they are denoted with the same reference numbers and detailed descriptions thereof are omitted. - According to the present embodiment, in a state where the
contact portion 31B of thevalve body 3B is separated from thevalve seat 20, the refrigerant containing bubbles in the valve chamber VS is guided along the axial length of thebody portion 32B through a relatively narrow gap between the outer circumference surface of thebody portion 32B of thevalve body 3B and theinner wall 24B, during which time the bubbles are gradually collapsed. Therefore, the bubbles will not collapse simultaneously when the refrigerant passes through thevalve seat 20, so that the energy generated by the bursting of the bubbles is reduced and the noise generated during passage of the refrigerant is cut down. Further, by having the refrigerant flow along the plane surfaces 24Bb along the axial length of thebody portion 32B, a flow straightening effect of the refrigerant is achieved. - Since the plane surfaces 24Bb that abut against the
body portion 32B have a long length corresponding to the axial direction of thevalve body 3B, tilting caused when thecontact portion 31B of thevalve body 3B separates from thevalve seat 20 can be suppressed. Thus, further to the upper surface 31Ba being relatively displaceable with respect to theactuation rod 5, smooth movement of thevalve body 3B can be ensured. -
FIG. 10 is a view similar toFIG. 2 illustrating a cross section of a valve body and an inner wall of a valve chamber according to a modified example. In the present modified example, aninner wall 24D of a valve chamber at a valvemain body 2D is a cylindrical surface, whereas a body portion 32D of the valve body has a non-round cross section. Specifically, the body portion 32D is formed of a partially cylindrical surface 32Da and a plane surface 32Db. The width of the plane surface 32Db is shorter than a diameter of the partially cylindrical surface 32Da. A cross-sectional shape of the body portion 32D is the same throughout the whole length of the body portion 32D. The partially cylindrical surface 32Da constitutes the sliding contact portion, and the plane surface 32Db constitutes the flow channel portion. The other configurations are similar to the embodiments described earlier, so they are denoted with the same reference numbers, and detailed descriptions thereof are omitted. - According to the present modified example, in a state where the valve body is separated from the valve seat, the refrigerant containing bubbles in the valve chamber is guided along the axial length of the body portion 32D through a relatively narrow gap between the plane surface 32Db of the body portion 32D of the valve body and the
inner wall 24D, during which time the bubbles are gradually collapsed. Therefore, the bubbles will not collapse simultaneously when the refrigerant passes through the valve seat, so that the energy generated by the bursting of the bubbles is reduced and the noise generated during passage of the refrigerant is cut down. Further, by having the refrigerant flow along the plane surface 32Db along the axial length of the body portion 32D, a flow straightening effect of the refrigerant is achieved. - The present invention is not limited to the above-described embodiments. Arbitrary components of the above-described embodiments can be modified within the scope of the present invention. Further, arbitrary components can be added to or omitted from the above-described embodiments. For example, the flow channel portion is not limited to being a plane surface, and it can be a protruded curved surface or a recessed curved surface.
-
- 10, 10A, 10B: expansion valve
- 2, 2A,
2 B 2D: valve main body - 3, 3A, 3B: valve body
- 4: urging device
- 5: actuation rod
- 6: ring spring
- 8: power element
- 20: valve seat
- 21: first flow channel
- 22: second flow channel
- 23: return flow channel
- 26: annular portion
- 27: orifice portion
- 41: coil spring
- 42: valve body support
- 43: spring holding member
- 100: refrigerant cycle system
- 101: compressor
- 102: capacitor
- 104: evaporator
- VS: valve chamber
Claims (5)
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JP2019-048420 | 2019-03-15 | ||
JP2019048420A JP7089769B2 (en) | 2019-03-15 | 2019-03-15 | Expansion valve |
PCT/JP2020/005113 WO2020189092A1 (en) | 2019-03-15 | 2020-02-10 | Expansion valve |
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US20220146160A1 true US20220146160A1 (en) | 2022-05-12 |
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US17/435,965 Pending US20220146160A1 (en) | 2019-03-15 | 2020-02-10 | Expansion valve |
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EP (1) | EP3940279A4 (en) |
JP (1) | JP7089769B2 (en) |
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JP2012052693A (en) * | 2010-08-31 | 2012-03-15 | Fuji Koki Corp | Solenoid valve-integrated expansion valve |
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JPS4922047Y1 (en) * | 1972-07-31 | 1974-06-13 | ||
JPS60121172U (en) * | 1984-01-23 | 1985-08-15 | 太平洋工業株式会社 | Temperature automatic expansion valve |
JP2571357Y2 (en) * | 1991-05-24 | 1998-05-18 | 株式会社鷺宮製作所 | Injection valve for refrigeration cycle |
JP3782896B2 (en) * | 1998-08-05 | 2006-06-07 | 株式会社テージーケー | Supercooling control type expansion valve |
JP2005351605A (en) * | 2004-06-14 | 2005-12-22 | Daikin Ind Ltd | Expansion valve and refrigeration device |
CN100504253C (en) * | 2005-02-28 | 2009-06-24 | 大金工业株式会社 | Expansion valve and refrigeration device |
JP5369259B2 (en) | 2008-08-25 | 2013-12-18 | 株式会社テージーケー | Expansion valve |
JP5804784B2 (en) * | 2011-06-08 | 2015-11-04 | 株式会社不二工機 | Check valve |
JP5906372B2 (en) * | 2011-09-30 | 2016-04-20 | 株式会社テージーケー | Control valve |
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2020
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