JP2019039526A - Contraction device and refrigerating-cycle system - Google Patents

Abstract

To more securely avoid the needle member hunting and fine oscillation of the tapered part of the needle member without increasing the size of the contraction device in a contraction device.SOLUTION: By setting the center axis of a continuous hole 18C to be offset to one side by a predetermined amount with respect to the center axis CS of a needle member 20, the pressure of coolant outflowing to a divergent part 18d of a stationary portion 18A through the circumference of a valve port 18P of a valve seat 18V corresponding to a first inner peripheral surface is smaller than the pressure of coolant outflowing to the divergent part 18d of the stationary portion 18A through the circumference of the valve port 18P of the valve seat 18V corresponding to a second inner peripheral surface. As a result, by the energization force acting in the direction of the X-coordinate axis, since a predetermined moment acts clockwise around the rotation center of a guide shaft part 20P2 of the needle member 20, the slide resistance acts between the periphery of the guide shaft part 20P2 and the inner peripheral edge of the hole 18b of a guide part 18B as a reaction.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a throttle device and a refrigeration cycle system.

  The differential pressure type throttling device can optimally control the refrigerant pressure between the condenser outlet and the evaporator inlet in order to efficiently operate the compressor according to the outside air temperature, and can change the rotation speed of the compressor. Also in the refrigeration cycle system, the refrigerant pressure is optimally controlled in accordance with the rotational speed of the compressor from the viewpoint of labor saving. Such a throttling device is, for example, joined to a primary side pipe connected to a condenser at one end where refrigerant is introduced, and a secondary side pipe connected to an evaporator at the other end where refrigerant flows out. It is joined to. For example, as shown in Patent Document 1, a differential pressure type throttling device includes a cylindrical main body case disposed between a primary side pipe and a secondary side pipe, and a cylindrical body fixed in the main body case. A guide member, a valve seat member, a needle valve that controls opening and closing of the valve port of the valve seat member, a stopper member that is fixed in a conduction chamber that communicates with the primary chamber of the valve seat member and that contacts the end face of the needle valve, and a guide A coil spring arranged in the member and biasing the needle valve in a direction close to the valve port of the valve seat member, and a blade member pressed against the boss portion of the needle valve at one end of the coil spring Has been.

  The guide member has a plurality of open holes communicating with the secondary chamber at a position downstream of the valve port of the valve seat member and extends into the secondary chamber toward the downstream side along the central axis of the main body case. Yes. The valve seat member has a valve port into which the conical needle portion of the needle valve is inserted in the central portion. The valve port communicates with the guide hole of the guide member and between the outer peripheral portion of the guide member and the inner peripheral portion of the main body case through an open hole, and also communicates with a conduction chamber extending toward the primary chamber. The guide portion of the insertion portion of the needle valve that is inserted into the guide hole of the guide member is slidable along the cylindrical guide surface of the guide hole of the guide member. The hemispherical contact portion formed on the blade of the blade member is in sliding contact with the cylindrical guide surface of the guide hole of the guide member by the elastic force of the blade itself. Thereby, when the blade | wing of a blade member and a needle valve receive the pressure of a refrigerant | coolant, since sliding resistance arises between a cylindrical guide surface and the blade | wing of a blade member, the hunting of a needle valve is suppressed.

  In order to suppress hunting of the needle valve in this way, instead of the configuration in which the blade member is provided at the boss portion of the needle valve guided by the guide hole of the guide member, for example, as shown in Patent Document 2, There has been proposed a configuration in which the needle member has a flat surface at a position separated from the central axis by a predetermined distance in the main body portion without the necessity. With such a configuration, during the movement of the needle member, the operating pressure of the refrigerant between the inner peripheral surface of the guide tube and the flat surface of the main body portion of the needle member acts in the radial direction of the main body portion, and the flatness in the main body portion is achieved. A part of the outer peripheral surface facing the surface is pressed against the inner peripheral surface of the guide tube. Therefore, since sliding resistance is generated between a part of the outer peripheral surface of the main body portion of the needle member and the inner peripheral surface of the guide tube, occurrence of hunting of the needle member is suppressed.

  Further, in order to suppress the slight vibration of the valve seat on the valve port due to the turbulent flow of the refrigerant, for example, as shown in Patent Document 3, the needle member is disposed in the secondary side pressure chamber portion of the guide tube. A configuration has been proposed in which an overhanging portion projecting toward the periphery is provided adjacent to the tapered portion. The overhanging portion has a flat surface at a position separated from the central axis by a predetermined distance. The flat surface faces the inner peripheral surface of the secondary pressure chamber and is formed from end to end along the central axis of the overhanging portion. With such a configuration, after the needle member starts moving due to the operating pressure of the refrigerant, a pressure difference is generated around the protruding portion of the needle member due to the flat surface. Along one direction along the periphery of the valve seat valve port. As a result, the fine vibration and rotation of the needle member due to the turbulent flow of the refrigerant are suppressed in the valve port.

JP 2006-142335 A Japanese Patent Application Laid-Open No. 2006-161178 JP 2017-58081 A

  In the throttling device as shown in Patent Document 2 and Patent Document 3, the throttling device is further reduced in size, and the hunting of the needle member and the fine vibration of the tip of the needle member as described above are more reliably performed. It is desired to avoid it.

  However, in order to more surely avoid the fine vibration of the tip of the needle member, the needle member may be enlarged in order to increase the pressing force by increasing the area of the flat surface of the needle member as described above. There is a limit.

  In view of the above-described problems, the present invention is a throttling device and a refrigeration cycle system, and more reliably hunting the needle member and fine vibration of the tip of the needle member without increasing the size of the throttling device. An object is to provide a throttling device and a refrigeration cycle system that can be avoided.

  In order to achieve the above-described object, a throttling device according to the present invention is arranged in a pipe that supplies a refrigerant, and has a tube main body that has open end portions that communicate with the pipe at both ends, and an inner peripheral portion of the tube main body. A valve seat having a valve port, a base having a base at a position spaced from the valve port, and arranged to be close to or away from the valve port of the valve seat to control an opening area of the valve port; A needle member having a guide shaft portion connected to the end of the detail and extending toward the upstream side of the flow of the refrigerant, and a needle disposed on the upstream side of the flow of the refrigerant from the position of the valve seat in the inner peripheral portion of the tube body The guide shaft portion of the member is slidably disposed, and is disposed between the guide portion and one open end of the tube body, and the needle member is attached in a direction close to the valve port of the valve seat. Biasing member, guide portion and valve seat Flow rate control for controlling the flow rate difference of the refrigerant flowing between the tapered portion of the needle member and the inner peripheral edge portion of the valve port through the gap between the guide portion arranged on the primary side and the valve seat And means.

  Further, the enlarged portion communicating with the valve port may be formed at a position downstream of the valve seat so as to face the tapered portion of the needle member.

  The flow rate control means is formed between the guide portion and the valve seat, and the position of the central axis of the communication hole communicating with the valve port and opening at both ends is biased to one with respect to the position of the central axis of the needle member May be included. The enlarged portion may be formed at a position that is substantially in the same direction as the direction in which the position of the central axis of the communication hole deviates to one with respect to the position of the central axis of the needle member and is downstream of the valve seat.

  The flow rate control means is formed between the guide portion and the valve seat, and has a configuration in which the central axis of the communication hole communicating with the valve port intersects the central axis of the needle member, and one end of the communication hole is opened, and the communication hole The other end may be closed. The other end of the communication hole may be closed by a flow rate adjusting piece.

  The flow rate control means is formed between the guide portion and the valve seat, and has a configuration in which the central axis of the communication hole communicating with the valve port intersects the central axis of the needle member, and one end of the communication hole is an open end that opens The other end of the communication hole may have an opening end portion having an inner diameter smaller than the inner diameter of the opening end portion. The flow rate control means is formed between the guide portion and the valve seat, and has a configuration in which the central axis of the communication hole opened at both ends communicating with the valve port intersects the central axis of the needle member, and the inner diameter of the open end of the communication hole It may further include a pore having a smaller inner diameter and communicating with the communicating hole and facing the needle member.

  The throttling device according to the present invention further includes a stopper member provided at an end portion of the guide portion so as to surround the guide shaft portion and the biasing member of the needle member, and having a hollow portion into which the refrigerant enters, and the flow rate control The means is formed between the guide portion and the valve seat, and has a configuration in which the central axis of the communication hole that opens at both ends communicating with the valve port intersects the central axis of the needle member. Formed in the circumferential direction of the stopper member between the tube portion and the inner peripheral portion of the tube body, and the flow rate of the refrigerant flowing into the communication hole from one opening end flows into the communication hole from the other opening end. It may also include a flow rate adjusting projection that limits the flow rate to be lower than the flow rate of the refrigerant to be reduced.

  Furthermore, the refrigeration cycle system according to the present invention includes an evaporator, a compressor, and a condenser, and the above-described throttling device is provided in a pipe arranged between the outlet of the condenser and the inlet of the evaporator. It is provided.

  According to the throttling device and the refrigeration cycle system according to the present invention, the flow rate control means has a flow rate difference between the refrigerant flowing between the guide member and the valve seat between the taper of the needle member and the inner peripheral edge of the valve port. The urging force acts on the needle member's taper in one direction by controlling it so as to be generated around the taper, and as a reaction thereof, sliding between the guide shaft portion and the guide portion of the needle member occurs. Since dynamic resistance is reliably generated, hunting of the needle member and fine vibration of the tip of the needle member can be avoided more reliably without increasing the size of the throttle device.

It is a front view which shows an example of the needle subassembly used for 1st Example of the aperture_diaphragm | restriction apparatus which concerns on this invention. It is sectional drawing shown along the II-II line in FIG. It is sectional drawing which shows the schematic structure of 1st Example of the aperture_diaphragm | restriction apparatus which concerns on this invention. It is a figure which shows roughly the structure of an example of the refrigerating cycle system to which the 1st Example thru | or 5th Example of the aperture_diaphragm | restriction apparatus which concerns on this invention is applied. It is sectional drawing with which it uses for operation | movement description of the needle subassembly shown by FIG. (A) is sectional drawing which shows another example of the needle subassembly used in the example shown by FIG. 3, (B) is the arrow line view seen from the direction which the arrow B in (A) shows. . (A) is sectional drawing which shows another example of the needle subassembly used in the example shown by FIG. 3, (B) is the arrow line view seen from the direction which the arrow B in (A) shows. is there. (A) is sectional drawing which shows schematic structure of 2nd Example of the aperture_diaphragm | restriction apparatus which concerns on this invention, (B) is sectional drawing shown along a VIIIB-VIIIB line | wire in (A). is there. It is a fragmentary sectional view of the guide tube which comprises a part of other example of the needle subassembly used for the example shown by FIG. 8 (A). It is a fragmentary sectional view of the guide tube which comprises a part of further another example of the needle subassembly used for the example shown by FIG. 8 (A). (A) is sectional drawing which shows schematic structure of 3rd Example of the aperture_diaphragm | restriction apparatus based on this invention, (B) is sectional drawing shown along the XIB-XIB line | wire in (A). is there. (A) is sectional drawing which shows schematic structure of 4th Example of the aperture_diaphragm | restriction apparatus which concerns on this invention, (B) is sectional drawing shown along the XIIB-XIIB line | wire in (A). is there. (A) is sectional drawing which shows schematic structure of 5th Example of the aperture_diaphragm | restriction apparatus based on this invention, (B) is a fragmentary sectional view which expands and shows the XIIIB part in (A). .

  FIG. 3 schematically shows a first embodiment of a diaphragm device according to the invention.

  For example, as shown in FIG. 4, the expansion device is disposed between the outlet of the condenser 6 and the inlet of the evaporator 2 in the piping of the refrigeration cycle system. The throttle device is joined to the primary side pipe Du1 at one end 10E1 of the tube body 10 to be described later, and joined to the secondary side pipe Du2 at the other end 10E2 of the tube body 10 from which the refrigerant flows out. The primary side pipe Du1 connects the outlet of the condenser 6 and the throttle device, and the secondary side pipe Du2 connects the inlet of the evaporator 2 and the throttle device. The compressor 4 is connected between the outlet of the evaporator 2 and the inlet of the condenser 6 by a pipe Du3 joined to the outlet of the evaporator 2 and a pipe Du4 joined to the inlet of the condenser 6. ing. The compressor 4 is driven and controlled by a control unit (not shown). Thereby, the refrigerant | coolant in a refrigerating-cycle system will be circulated along the arrow shown by FIG. 4, for example.

  In FIG. 3, the expansion device includes a tube body 10 joined to the piping of the above-described refrigeration cycle system, a guide tube 18 fixed to the inner peripheral portion 10 a of the tube body 10, and a refrigerant integrally formed with the guide tube 18. One of the valve seat 18V, the needle member 20, the coil spring 16 that urges the needle member 20 in the direction approaching the valve seat 18V, and the coil spring 16 A spring receiving member 22 that supports the end portion and a cylindrical stopper member 12 that receives one end of the needle member 20 are included as main elements.

  An outer peripheral portion of the fixing portion 18A of the guide tube 18 having an outer diameter smaller than the inner diameter of the tube main body 10 is fixed to an intermediate portion that is separated from the one end 10E2 in the inner peripheral portion 10a of the tube main body 10 by a predetermined distance. .

  The guide tube 18 is made by machining with any material of, for example, copper, brass, aluminum, or stainless steel. The guide tube 18 includes a fixed portion 18A that is fixed to the inner peripheral portion 10a of the tube body 10 and a guide portion 18B that slidably guides a guide shaft portion 20P2 of a needle member 20 described later.

  The guide tube 18 is fixed by the protrusions formed by the depressions 10CA1 and 10CA2 of the tube main body 10 by caulking process biting into the grooves 18CA1 and 18CA2 on the outer peripheral portion of the fixing portion 18A. The guide tube 18 has a metal stopper member 12 on the outer peripheral portion of the end portion of the guide portion 18B closest to the one end 10E1 of the tube main body 10.

  The stopper member 12 is formed with a uniform thickness, for example, by press working with a copper alloy thin plate material. Since the stopper member 12 is formed by press molding, it is manufactured at a relatively low cost.

  One end of the stopper member 12 is fixed to the guide portion 18B by the protrusion formed by the depression 12CA1 of the stopper member 12 by caulking process biting into the groove 18CB1 at the end portion of the guide portion 18B. The caulking recesses 12CA1 are formed at a plurality of locations, for example, three locations with a predetermined interval along the circumferential direction of the stopper member 12. The cylindrical stopper member 12 has a closed end at the other end, and is structured to cover the coil spring 16 and the spring receiving member 22. The other end of the stopper member 12 extends from the guide portion 18B toward the one end 10E1 side of the tube body 10. In addition, the closed end portion has a flat inner surface. The inner surface of the closed end portion receives an end surface 20P5 of an adjusting screw 20P4 described later. The adjustment screw 20P4 is formed integrally with one end of the guide shaft portion 20P2 of the needle member 20, and is screwed into the female screw 22A at one end of the spring receiving member 22. A hollow portion 14 into which a liquid refrigerant enters is formed inside the stopper member 12. A predetermined gap is formed between the inner peripheral surface of the stopper member 12 other than the recess 12CA1 and the outer peripheral surface of the end portion of the guide portion 18B other than the groove 18CB1. Therefore, the refrigerant supplied from the one end 10E1 side of the tube main body 10 along the arrow shown in FIG. 3 passes through the gap and the gap between the hole 18b of the guide portion 18B and the outer peripheral portion of the guide shaft portion 20P2. 12 into the hollow portion 14.

  A guide portion 18B is formed in a portion of the guide tube 18 upstream of a communication hole 18C described later. The guide shaft portion 20P2 of the needle member 20 is slidably fitted in the hole portion 18b of the guide portion 18B.

  The valve port 18P and the hole 18b of the valve seat 18V of the fixed portion 18A in the guide tube 18 are formed on a common central axis. At that time, since the guide portion 18B and the fixed portion 18A of the guide tube 18 are integrally formed, the valve port 18P and the hole portion 18b of the valve seat 18V have a common central axis so that the centers thereof coincide with each other. It becomes easy to process on the line with high accuracy.

  A substantially circular communication hole 18C is formed immediately below the valve seat 18V between the valve seat 18V and the guide portion 18B in the fixed portion 18A. The communication hole 18C functioning as the refrigerant introduction hole penetrates the guide tube 18 along the Y coordinate axis, as shown in an enlarged manner in FIGS. The communication hole 18C allows the valve port 18P to communicate between the outer peripheral portion of the guide tube 18 and the stopper member 12 and the inner peripheral portion 10a of the tube main body 10.

  1 and 2, the Y coordinate axis is set to intersect the central axis CS of the needle member 20, and the Z coordinate axis is set parallel to the central axis CS of the needle member 20. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis. The center axis CO of the communication hole 18C is set so as to deviate to the left by a predetermined amount ΔD with respect to the center axis CS of the needle member 20 in FIG. The predetermined amount ΔD (offset amount) is set in a range of 0.1 mm to 0.6 mm, for example. As a result, as shown in FIG. 2, one inner peripheral surface (hereinafter also referred to as a first inner peripheral surface 18ISa) along the Y coordinate axis forming the communication hole 18C faces the tapered portion 20P1 of the needle member 20. The mutual distance between the outer peripheral surface and the other inner peripheral surface (hereinafter also referred to as the second inner peripheral surface 18ISb) along the Y coordinate axis that forms the communication hole 18C faces the tapered portion 20P1 of the needle member 20. Smaller than the distance between the outer peripheral surfaces. Accordingly, the cross-sectional area between the first inner peripheral surface 18ISa through which the refrigerant passes and the outer peripheral surface of the tapered portion 20P1 of the needle member 20 is the tip of the second inner peripheral surface 18ISb through which the refrigerant passes and the needle member 20. Since the cross-sectional area between the outer peripheral surface of 20P1 is small and the flow of the refrigerant flowing from both ends of the communication hole 18C is a steady flow, the first inner peripheral surface 18ISa and the needle member 20 The flow rate of the refrigerant passing between the outer peripheral surface of the tapered portion 20P1 is higher than the flow rate of the refrigerant passing between the second inner peripheral surface 18ISb and the outer peripheral surface of the tapered portion 20P1 of the needle member 20. . Thereby, as shown in FIG. 5, the flow rate of the refrigerant flowing out to the divergent portion 18d of the fixed portion 18A through the peripheral edge of the valve port 18P of the valve seat 18V corresponding to the first inner peripheral surface 18ISa is the second inner surface. It becomes larger than the flow velocity of the refrigerant flowing out to the divergent portion 18d of the fixed portion 18A through the peripheral edge of the valve port 18P of the valve seat 18V corresponding to the peripheral surface 18ISb. The pressure of the refrigerant flowing out to the divergent portion 18d of the fixed portion 18A through the peripheral edge of the valve port 18P of the valve seat 18V corresponding to the first inner peripheral surface 18ISa is determined based on the continuous inner equation and Bernoulli's theorem. It becomes smaller than the pressure of the refrigerant flowing out to the divergent portion 18d of the fixed portion 18A through the peripheral edge of the valve port 18P of the valve seat 18V corresponding to the surface 18ISb. As a result, in FIG. 5, the urging force is applied to the action point AP of the taper 20P1 as a typical action point that can be assumed for convenience of explanation, for example, in the direction indicated by the arrow, that is, approximately the X coordinate axis in FIG. By acting in the direction, a predetermined moment acts in the clockwise direction around the rotation center RP of the guide shaft portion 20P2 of the needle member 20 as a typical rotation center that can be assumed, so that the outer peripheral portion of the guide shaft portion 20P2 A sliding resistance is generated as a reaction between the inner peripheral edge of the hole 18b of the guide portion 18B. At that time, since the distance L between the action point AP of the tapered portion 20P1 and the rotation center RP of the guide shaft portion 20P2 of the needle member 20 can be set relatively long, the above-described urging force is further increased.

  In addition, the cross-sectional shape along the X coordinate axis shown in FIG. 1 in the communication hole 18C described above is not limited to a substantially circular shape, and may be another shape such as an ellipse, for example. In such a case, the tapered portion 20P1 of the needle member 20 has a cross-sectional area between the first inner peripheral surface 18ISa through which the refrigerant passes and the outer peripheral surface of the tapered portion 20P1 of the needle member 20 so that the refrigerant passes. The cross-sectional area between the second inner peripheral surface 18ISb and the outer peripheral surface of the tapered portion 20P1 of the needle member 20 may be different. Further, the center axis CO of the communication hole 18C is not limited to such an example. For example, in FIG. 1, the center axis CO may be set so as to be deviated to the right by a predetermined amount ΔD with respect to the center axis CS of the needle member 20. .

  The valve seat 18V in the guide tube 18 has a valve port 18P into which the tapered portion 20P1 in the needle member 20 is inserted at the inner central portion. The valve port 18P has a circular opening that penetrates along the central axis of the valve seat 18V with a predetermined uniform diameter. The valve port 18P is not limited to such an example. For example, the valve port 18P may pierce toward the one end 10E1 along the central axis of the valve seat 18V.

  At the downstream side of the valve seat 18V in the guide tube 18, a divergent portion 18d whose inner diameter gradually increases toward the downstream side than the diameter of the valve port 18P is formed inside the fixed portion 18A. The divergent portion 18d is continuous with the inner peripheral portion 18e of the cylindrical fixing portion 18A.

  As shown in FIG. 3, the needle member 20 is made of a material such as brass or stainless steel by machining, and has a tapered portion 20P1 formed facing the valve seat 18V, and a hole in the guide portion 18B. The guide shaft portion 20P2 slidably fitted to the portion 18b, the spring receiving member connecting portion 20P3 formed at the tip of the guide shaft portion 20P2, and the adjustment screw 20P4 are configured as main elements. .

  The minimum diameter portion of the truncated conical tapered portion 20P1 having a predetermined taper angle is set to be slightly smaller than the diameter of the guide shaft portion 20P2. When the end face 20P5 of the adjusting screw 20P4 of the needle member 20 is brought into contact with the inner surface of the closed end of the stopper member 12, the tapered portion 20P1 serves as a base portion, that is, a connecting portion with an end portion 20F, which will be described later. The valve port 18P is spaced from the valve port 18P by a predetermined distance in the direction of the divergent portion 18d. The above-mentioned base portion may preferably have a tapered portion having a diameter larger than the diameter of the valve port 18P or a straight portion. Further, the tapered portion 20P1 is not limited to such an example, and for example, the tapered portion 20P1 may not have the protruding portion 20F at the extreme end.

  A spring receiving member 22 is fixed to the spring receiving member connecting portion 20P3 of the needle member 20 by caulking. The spring receiving member connecting portion 20P3 is formed by, for example, an annular groove. The spring receiving member 22 is fixed by the protrusion formed by the depression 22CA1 of the spring receiving member 22 by caulking process biting into the groove of the spring receiving member connecting portion 20P3. One end of the coil spring 16 is supported by the spring support portion 22F of the spring receiving member 22 facing the above-described guide portion 18B. The spring support portion 22F protruding to the side is integrally formed at a position separated by a predetermined distance in the direction of approaching the guide portion 18B from the above-described depression 22CA1. The other end of the coil spring 16 is supported by the spring receiving portion 18f of the guide portion 18B described above. The end face 18g of the abutting portion connected to the spring receiving portion 18f of the guide portion 18B and the end portion 22G of the cylindrical portion of the spring supporting portion 22F of the spring receiving member 22 are separated from each other by a predetermined distance. A coil spring 16 is wound around the cylindrical portion of the spring support portion 22F of the spring receiving member 22. Accordingly, if the needle member 20 is moved toward the other end 10E2 by a predetermined value or more, the end surface 18g of the contact portion of the guide portion 18B and the end portion 22G of the cylindrical portion of the spring support portion 22F Is in contact, the movement of the needle member 20 is restricted. Therefore, it is avoided that the coil spring 16 is excessively compressed to a predetermined value or more.

  The male screw of the adjusting screw 20P4 formed integrally with the spring receiving member connecting portion 20P3 of the needle member 20 is screwed into the hole of the female screw 22A on the inner peripheral portion of the spring receiving member 22. The hole of the female screw 22A extends in a direction away from the recess 22CA1 with respect to the guide portion 18B. The adjusting screw 20P4 adjusts the urging force of the coil spring 16.

  In the throttling device, the outer peripheral portion of the tapered portion 20P1 of the needle member 20 has an opening end portion of the valve port 18P due to a differential pressure (a difference between the refrigerant inlet pressure on the one end 10E1 side and the refrigerant outlet pressure on the other end 10E2 side). The separation start timing at which the separation starts from the peripheral edge of the coil spring 16 is set based on the biasing force of the coil spring 16. The spring constant of the coil spring 16 is set to a predetermined value. After the biasing force of the coil spring 16 is adjusted by the adjusting screw 20P4, the protrusion formed by the depression 22CA1 of the spring receiving member 22 by caulking process bites into the groove of the spring receiving member connecting portion 20P3, thereby adjusting the screw 20P4. The position with respect to the spring receiving member 22 is fixed.

  When the end surface 20P5 of the adjusting screw 20P4 is brought into contact with the flat inner surface of the closed end of the stopper member 12, the taper is formed at a position corresponding to the open end of the valve port 18P on the outer periphery of the taper 20P1 of the needle member 20. The outer peripheral part of 20P1 is arrange | positioned so that a predetermined clearance may be formed with respect to the periphery of the opening end part of the valve port 18P. As a result, a pressure difference can always be generated from the minute valve opening (the end face 20P5 of the adjustment screw 20P4 is in contact with the stopper member 12) to the full opening, and the needle member 20 can be prevented from vibrating. . At that time, a throttle portion is formed between the tapered portion 20P1 of the needle member 20 and the open end portion of the valve port 18P. The throttle portion refers to a portion (narrowest portion) where the intersection of the perpendicular line from the peripheral edge of the valve port 18P to the bus bar of the tapered detail 20P1 and the bus bar of the tapered detail 20P1 is closest to the edge of the valve port 18P. The area of the conical surface drawn by the perpendicular is the opening area of the diaphragm.

  When the pressure of the refrigerant in the tube main body 10 is equal to or less than a predetermined value, the end surface 20P5 of the adjustment screw 20P4 is in contact with the inner surface of the closed end of the stopper member 12 by the urging force of the coil spring 16.

  The predetermined amount of bleed that passes through the throttle portion is set by the amount of the predetermined gap formed with respect to the peripheral edge of the opening end of the valve port 18P. Further, since the end face 20P5 of the adjusting screw 20P4 in the spring receiving member 22 of the needle member 20 is in contact with the inner surface of the closed end of the stopper member 12, the secondary side acting on the urging force of the coil spring 16 and the needle member 20 is applied. Undesirable pressure from the needle member 20 prevents the tapered portion 20P1 from biting into the open end of the valve port 18P of the valve seat 18V.

  The above-described guide tube 18, the needle member 20 inserted into the valve port 18P and the hole 18b of the guide tube 18, the spring receiving member 22 into which the adjusting screw 20P4 of the needle member 20 is screwed in a predetermined amount, and the spring receiving member 22 A needle subassembly is formed by the coil spring 16 and the stopper member 12 disposed between the guide tube 18 and the end of the guide portion 18B of the guide tube 18. The flow rate control means for controlling the flow rate of the refrigerant flowing out to the divergent portion 18d of the fixed portion 18A through the peripheral edge of the valve port 18P of the valve seat 18V includes the communication hole 18C of the guide tube 18 and the tapered portion 20P1 of the needle member 20. It will be formed by.

  In such a configuration, when the force acting on the needle member 20 due to the refrigerant pressure does not exceed the urging force of the coil spring 16, as described above, when the refrigerant is supplied through the primary side pipe Du1, the refrigerant pressure is The pressure is reduced by passing through the one end 10E1 of the tube main body 10, the inner peripheral portion 10a of the tube main body 10 and the outer peripheral portion of the stopper member 12 through the communication path 18C and the above-described throttle portion, and then the refrigerant is guided to the guide tube. 18 is discharged from the other end 10E2 through the inner peripheral portion 18e of the fixed portion 18A with a predetermined bleed amount.

  Furthermore, when the force acting on the needle member 20 due to the pressure of the refrigerant exceeds the urging force of the coil spring 16, the refrigerant flowing through the above-described throttle portion presses the needle member 20 in a direction further away from the peripheral edge of the valve port 18P. It will be. At that time, the pressure of the refrigerant flowing out to the divergent portion 18d of the fixed portion 18A through the peripheral edge of the valve port 18P of the valve seat 18V corresponding to the first inner peripheral surface 18ISa is determined based on the continuous equation and Bernoulli's theorem. It becomes smaller than the pressure of the refrigerant flowing out to the divergent portion 18d of the fixed portion 18A through the peripheral edge of the valve port 18P of the valve seat 18V corresponding to the inner peripheral surface 18ISb. As a result, in FIG. 5, the urging force acts on the action point AP of the taper 20P1 in the direction indicated by the arrow, that is, the direction of the X coordinate axis in FIG. The minute vibration of the tapered portion 20P1 of the member 20 is more reliably avoided.

  FIGS. 6A and 6B show another example of a needle subassembly used in the throttling device shown in FIG. 6A and 6B, the same components as those in the example shown in FIG. 3 are denoted by the same reference numerals, and redundant description thereof is omitted.

  The needle subassembly includes a guide tube 18 ′ fixed to the inner peripheral portion 10a of the tube body 10 and a valve seat 18′V that forms a refrigerant flow rate adjusting unit that is integrally formed with the guide tube 18 ′ and adjusts the flow rate of the refrigerant. The needle member 20, the coil spring 16 that urges the needle member 20 toward the valve seat 18'V, the spring receiving member 22 that supports one end of the coil spring 16, and the needle member And a cylindrical stopper member 12 for receiving one end of 20.

  The guide tube 18 'is made by machining with any material of copper, brass, aluminum, stainless steel or the like, for example. The guide tube 18 'includes a fixed portion 18'A that is fixed to the inner peripheral portion 10a of the tube body 10 and a guide portion 18'B that slidably guides the guide shaft portion 20P2 of the needle member 20. Yes.

  The guide tube 18 'is fixed by the protrusions formed by the depressions 10CA1 and 10CA2 of the tube main body 10 by caulking process biting into the grooves 18'CA1 and 18'CA2 on the outer peripheral portion of the fixing portion 18'A. The guide tube 18 ′ has a metal stopper member 12 on the outer peripheral portion of the end portion of the guide portion 18 ′ B closest to the one end 10 E 1 of the tube body 10.

  A guide portion 18'B is formed in the guide tube 18 'at a portion upstream of a communication hole 18'C described later. A guide shaft portion 20P2 of the needle member 20 is slidably fitted in the hole portion 18'b of the guide portion 18'B.

  The valve seat 18′V in the guide tube 18 ′ has a valve port 18′P into which the tapered portion 20P1 in the needle member 20 is inserted at the center of the inside. The valve port 18'P has a circular opening that penetrates along the central axis of the valve seat 18'V with a predetermined uniform diameter. In addition, valve port 18'P is not restricted to such an example, For example, you may penetrate in a divergent shape toward the one end 10E1 along the central axis of valve seat 18'V.

  The valve port 18'P and the hole 18'b of the valve seat 18'V of the fixed portion 18'A in the guide tube 18 'are formed on a common central axis. At that time, since the guide portion 18'B and the fixed portion 18'A in the guide tube 18 'are integrally formed, the valve port 18'P and the hole portion 18'b of the valve seat 18'V It becomes easy to process with high accuracy on a common central axis so that the centers coincide with each other.

  Between the valve seat 18′V and the guide portion 18′B in the fixed portion 18′A, a substantially circular communication hole 18′C is formed immediately below the valve seat 18′V. As shown in FIG. 6A, the communication hole 18′C functioning as the refrigerant introduction hole passes through the guide tube 18 ′ along the Y coordinate axis. The communication hole 18 ′ C allows the valve port 18 ′ P to communicate between the outer peripheral portion of the guide tube 18 ′ and the stopper member 12 and the inner peripheral portion 10 a of the tube main body 10.

  6A and 6B, the Y coordinate axis is set so as to intersect the central axis CS of the needle member 20, and the Z coordinate axis is set parallel to the central axis CS of the needle member 20. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis. The center axis CO of the communication hole 18′C is also deviated to the left by a predetermined amount ΔD with respect to the center axis CS of the needle member 20 in FIG. 6A as well as the example shown in FIG. Is set. The predetermined amount ΔD (offset amount) is set in a range of 0.1 mm to 0.6 mm, for example. Thereby, the one inner peripheral surface (hereinafter also referred to as the first inner peripheral surface 18′ISa) along the Y coordinate axis that forms the communication hole 18′C and the outer peripheral surface facing each other in the tapered portion 20P1 of the needle member 20 The distance between the two faces the other inner peripheral surface (hereinafter also referred to as the second inner peripheral surface 18′ISb) along the Y coordinate axis forming the communication hole 18′C and the tapered portion 20P1 of the needle member 20. Smaller than the distance between the outer peripheral surfaces. Accordingly, the cross-sectional area between the first inner peripheral surface 18′ISa through which the refrigerant passes and the outer peripheral surface of the tapered portion 20P1 of the needle member 20 is equal to the second inner peripheral surface 18′ISb through which the refrigerant passes and the needle member. It becomes small compared with the cross-sectional area between the outer peripheral surfaces of the 20 tapered portions 20P1. Therefore, when the flow of the refrigerant flowing in from both ends of the communication hole 18′C is a steady flow, it passes between the first inner peripheral surface 18′ISa and the outer peripheral surface of the tapered portion 20P1 of the needle member 20. The flow rate of the refrigerant is faster than the flow rate of the refrigerant passing between the second inner peripheral surface 18′ISb and the outer peripheral surface of the tapered portion 20P1 of the needle member 20. Thereby, the flow rate of the refrigerant flowing out to the divergent portion 18'd of the fixed portion 18'A through the peripheral edge of the valve port 18'P of the valve seat 18'V corresponding to the first inner peripheral surface 18'ISa is the second It becomes faster than the flow rate of the refrigerant flowing out to the divergent portion 18'd of the fixed portion 18'A through the peripheral edge of the valve port 18'P of the valve seat 18'V corresponding to the inner peripheral surface 18'ISb. The pressure of the refrigerant flowing into the divergent portion 18'd of the fixed portion 18'A through the peripheral edge of the valve port 18'P of the valve seat 18'V corresponding to the first inner peripheral surface 18'ISa is a continuous type and Bernoulli. The pressure of the refrigerant flowing out to the divergent portion 18'd of the fixed portion 18'A through the periphery of the valve port 18'P of the valve seat 18'V corresponding to the second inner peripheral surface 18'ISb based on the theorem of And become small. As a result, in FIG. 5, the urging force resulting from the flow velocity difference (pressure difference) of the refrigerant formed near the periphery of the valve port 18′P of the valve seat 18′V is applied to the action point AP of the tapered portion 20P1. By acting in the direction indicated by the arrow, that is, approximately in the X-coordinate axis direction in FIG. 2, a predetermined moment acts in the clockwise direction around the rotation center RP of the guide shaft portion 20P2 of the needle member 20, so that the guide shaft portion 20P2 A sliding resistance is generated as a reaction between the outer peripheral portion and the inner peripheral edge of the hole 18b of the guide portion 18B. At that time, since the distance L between the action point AP of the tapered portion 20P1 and the rotation center RP of the guide shaft portion 20P2 of the needle member 20 can be set relatively long, the above-described urging force is further increased.

  Furthermore, a divergent portion 18′d whose inner diameter gradually increases toward the downstream side than the diameter of the valve port 18′P is provided at the downstream side of the valve seat 18′V in the guide tube 18 ′. It is formed inside 'A. The divergent portion 18'd is continuous with the inner peripheral portion 18'e of the cylindrical fixing portion 18'A. As shown in FIG. 6 (B), the enlarged portion 18′EN is formed on a part of the inner peripheral portion 18′e connected to the divergent portion 18′d, for example, in a range of a circumferential angle of about 90 degrees or more and less than 180 degrees. The needle member 20 is formed around a tapered portion 20P1. The enlarged portion 18′EN is a cross-sectional area of the refrigerant flow path formed between the outer peripheral portion and the inner peripheral portion 18′e of the tapered portion 20P1 in the needle member 20, and the transverse portion of the portion facing the sandwiched detail 20P1. In particular, the crossing of the flow path through which the refrigerant flowing out through the peripheral edge of the valve port 18′P of the valve seat 18′V corresponding to the above-described second inner peripheral surface 18′ISb flows so as to partially expand than the area. It is formed to enlarge the area. The enlarged portion 18′EN extends along the central axis of the needle member 20 to the end of the inner peripheral portion 18′e of the cylindrical fixing portion 18′A.

  Thereby, since the cross-sectional area of the flow path of the refrigerant | coolant around the taper 20P1 in the needle member 20 becomes larger than the cross-sectional area of the part which pinches | interposes the taper 20P1, the flow rate of the refrigerant | coolant which passes enlarged part 18'EN However, it becomes slower than the flow rate of the refrigerant passing through the portions facing each other across the taper 20P1. Therefore, the action point AP of the tapered portion 20P1 in the needle member 20 based on the difference between the flow rate of the refrigerant passing through the enlarged portion 18'EN and the flow rate of the refrigerant passing through the portion facing the enlarged portion 18'EN across the tapered portion 20P1. The direction of the urging force acting on the valve seat 18′V is the same as the direction of the urging force caused by the flow velocity difference (pressure difference) of the refrigerant formed near the periphery of the valve port 18′P of the valve seat 18′V. The synergistic action of the urging force based on the flow velocity difference at the two positions of the valve port 18′P of the valve seat 18′V and the enlarged portion 18′EN is obtained.

  In addition, the cross-sectional shape along the X coordinate axis shown in FIG. 6A in the communication hole 18′C is not limited to a substantially circular shape, and may be another shape such as an ellipse, for example. In such a case, the tapered portion 20P1 of the needle member 20 has a cross-sectional area between the first inner peripheral surface through which the refrigerant passes and the outer peripheral surface of the tapered portion 20P1 of the needle member 20 through which the refrigerant passes. You may arrange | position so that the magnitude | size of the cross-sectional area between the 2nd inner peripheral surface and the outer peripheral surface of the taper 20P1 of the needle member 20 may differ. Further, the central axis CO of the communication hole 18′C is not limited to such an example, and may be set to be deviated to the right by a predetermined amount ΔD with respect to the central axis CS of the needle member 20, for example.

  FIGS. 7A and 7B show still another example of the needle subassembly used in the throttling device shown in FIG. 7A and 7B, the same components as those in the example shown in FIG. 3 are denoted by the same reference numerals, and redundant description thereof is omitted.

  The needle subassembly includes a guide tube 28 fixed to the inner peripheral portion 10a of the tube body 10, a valve seat 28V that is integrally formed with the guide tube 28 and that constitutes a refrigerant flow rate adjusting unit that adjusts the flow rate of the refrigerant, and a needle. A member 20; a coil spring 16 that urges the needle member 20 toward the valve seat 28V; a spring receiving member 22 that supports one end of the coil spring 16; and a cylinder that receives one end of the needle member 20. And a stopper member 12 having a shape.

  The guide tube 28 is made by machining with any material of, for example, copper, brass, aluminum, or stainless steel. The guide tube 28 includes a fixed portion 28A that is fixed to the inner peripheral portion 10a of the tube body 10 and a guide portion 28B that guides the guide shaft portion 20P2 of the needle member 20 in a slidable manner.

  The guide tube 28 is fixed by a projection formed by the depression 10CA1 of the tube main body 10 by caulking, biting into the groove 28CA1 on the outer peripheral portion of the fixing portion 28A. The guide tube 28 has a metal stopper member 12 on the outer peripheral portion of the end portion of the guide portion 28B closest to the one end 10E1 of the tube main body 10.

  A guide portion 28B is formed in the guide tube 28 at a portion upstream of a later-described communication hole 28C. The guide shaft portion 20P2 of the needle member 20 is slidably fitted in the hole portion 28b of the guide portion 28B.

  The valve seat 28 </ b> V in the guide tube 28 has a valve port 28 </ b> P into which the tapered portion 20 </ b> P <b> 1 in the needle member 20 is inserted in the center of the inside. The valve port 28P has a circular opening penetrating along the central axis of the valve seat 28V with a predetermined uniform diameter. The valve port 28P is not limited to such an example. For example, the valve port 28P may penetrate in a divergent shape toward the one end 10E1 along the central axis of the valve seat 28V.

  The valve port 28P and the hole 28b of the valve seat 28V of the fixed portion 28A in the guide tube 28 are formed on a common central axis. At this time, since the guide portion 28B and the fixed portion 28A of the guide tube 28 are integrally formed, the valve port 28P and the hole portion 28b of the valve seat 28V have a common central axis so that their centers coincide with each other. It becomes easy to process on the line with high accuracy.

  A substantially circular communication hole 28C is formed immediately below the valve seat 28V between the valve seat 28V and the guide portion 28B in the fixed portion 28A. As shown in FIG. 7A, the communication hole 28C functioning as the refrigerant introduction hole passes through the guide tube 28 along the Y coordinate axis. The communication hole 28C allows the valve port 28P to communicate between the outer peripheral portion of the guide tube 28 and the stopper member 12 and the inner peripheral portion 10a of the tube main body 10.

  7A and 7B, the Y coordinate axis is set so as to intersect the central axis CS of the needle member 20, and the Z coordinate axis is set parallel to the central axis CS of the needle member 20. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis. The central axis CO of the communication hole 28C is set so as to be deviated to the left by a predetermined amount ΔD with respect to the central axis CS of the needle member 20 in FIG. 7A as well as the example shown in FIG. ing. The predetermined amount ΔD (offset amount) is set in a range of 0.1 mm to 0.6 mm, for example. Thereby, between one inner peripheral surface (henceforth 1st inner peripheral surface 28ISa) along the Y coordinate axis which forms the communicating hole 28C, and the outer peripheral surface which the needle member 20 faces in the taper 20P1 The distance is the distance between the other inner peripheral surface (hereinafter also referred to as the second inner peripheral surface 28ISb) along the Y coordinate axis that forms the communication hole 28C and the opposing outer peripheral surface of the tapered portion 20P1 of the needle member 20. Smaller than that. Accordingly, the cross-sectional area between the first inner peripheral surface 28ISa through which the refrigerant passes and the outer peripheral surface of the tapered portion 20P1 of the needle member 20 is such that the second inner peripheral surface 28ISb through which the refrigerant passes and the needle member 20 tapered. It is smaller than the cross-sectional area between the outer peripheral surface of 20P1. Therefore, when the flow of the refrigerant flowing from both ends of the communication hole 28C is a steady flow, the flow rate of the refrigerant passing between the first inner peripheral surface 28ISa and the outer peripheral surface of the tapered portion 20P1 of the needle member 20 is This is faster than the flow rate of the refrigerant passing between the second inner peripheral surface 28ISb and the outer peripheral surface of the tapered portion 20P1 of the needle member 20. Thereby, the flow rate of the refrigerant flowing out to the divergent portion 28d of the fixed portion 28A through the peripheral edge of the valve port 28P of the valve seat 28V corresponding to the first inner peripheral surface 28ISa is the valve seat corresponding to the second inner peripheral surface 28ISb. It becomes faster than the flow rate of the refrigerant flowing out to the divergent portion 28d of the fixed portion 28A through the peripheral edge of the 28V valve port 28P. The pressure of the refrigerant flowing out to the divergent portion 28d of the fixed portion 28A through the peripheral edge of the valve port 28P of the valve seat 28V corresponding to the first inner peripheral surface 28ISa is determined based on the continuous inner equation and Bernoulli's theorem. It becomes smaller than the pressure of the refrigerant flowing out to the divergent portion 28d of the fixed portion 28A through the periphery of the valve port 28P of the valve seat 28V corresponding to the surface 28ISb. As a result, in FIG. 5, the urging force caused by the flow velocity difference (pressure difference) of the refrigerant formed in the vicinity of the peripheral edge of the valve port 28P of the valve seat 28V is applied to the action point AP of the tapered portion 20P1 in the direction indicated by the arrow. That is, by acting almost in the X-coordinate axis direction in FIG. 2, a predetermined moment acts around the rotation center RP of the guide shaft portion 20P2 of the needle member 20 in the clockwise direction, so that the outer peripheral portion of the guide shaft portion 20P2 and the guide A sliding resistance is generated as a reaction between the inner periphery of the hole 28b of the portion 28B. At that time, since the distance L between the action point AP of the tapered portion 20P1 and the rotation center RP of the guide shaft portion 20P2 of the needle member 20 can be set relatively long, the above-described urging force is further increased.

  Furthermore, a divergent portion 28d whose inner diameter gradually increases toward the downstream side than the diameter of the valve port 28P is formed on the inner side of the fixed portion 28A at the downstream side of the valve seat 28V in the guide tube 28. . The divergent portion 28d is continuous with the inner peripheral portion 28e of the cylindrical fixing portion 28A. Between the inner peripheral portion 28e of the cylindrical portion of the fixed portion 28A and the outer peripheral portion of the tapered portion 20P1 of the needle member 20, as shown in FIG. 7B, an annular flow path 28R through which the refrigerant passes is formed. It is formed. As shown in FIG. 7A, the cylindrical portion forming the inner peripheral portion 28e extends toward the outermost protruding portion 20F of the tapered portion 20P1 of the needle member 20, and the substantially circular through hole 28AH is formed. Have. As shown in FIG. 7B, the through hole 28AH flows out into the divergent portion 28d through the peripheral edge of the valve port 28P of the valve seat 28V corresponding to the second inner peripheral surface 28ISb of the communication hole 28C described above. In order to reduce the flow velocity of the refrigerant in the flow path 28R, the cylindrical portion is penetrated along the direction along the X coordinate axis, that is, along the radial direction of the cylindrical fixing portion 28A.

  Thereby, the flow rate of the refrigerant in the flow path 28R formed by a part of the cylindrical portion provided with the through hole 28AH is slower than the flow rate of the refrigerant passing through the flow path 28R facing each other with the tapered portion 20P1 interposed therebetween. . Accordingly, the direction of the urging force acting on the action point AP of the tapered portion 20P1 in the needle member 20 based on the refrigerant flow rate difference is the refrigerant flow rate difference (pressure difference) formed in the vicinity of the periphery of the valve port 28P of the valve seat 28V. Therefore, the synergistic action of the urging force based on the flow velocity difference between the valve port 28P of the valve seat 28V and the through hole 28AH is obtained.

  In addition, the cross-sectional shape along the X coordinate axis shown in FIG. 7A in the communication hole 28C described above is not limited to a substantially circular shape, and may be another shape such as an ellipse, for example. In such a case, the tapered portion 20P1 of the needle member 20 has a cross-sectional area between the first inner peripheral surface through which the refrigerant passes and the outer peripheral surface of the tapered portion 20P1 of the needle member 20 through which the refrigerant passes. You may arrange | position so that the magnitude | size of the cross-sectional area between the 2nd inner peripheral surface and the outer peripheral surface of the taper 20P1 of the needle member 20 may differ. Further, the central axis CO of the communication hole 28C is not limited to such an example, and may be set to be shifted to the right by a predetermined amount ΔD with respect to the central axis CS of the needle member 20, for example.

  FIGS. 8A and 8B schematically show a second embodiment of the diaphragm device according to the present invention.

  In the example shown in FIG. 3, the center axis CO of the communication hole 18 </ b> C of the guide tube 18 is set to be deviated to the left by a predetermined amount ΔD with respect to the center axis CS of the needle member 20. 8A, the central axis CO of the communication hole 30C of the guide tube 30 intersects with the central axis CS of the needle member 20. In the example shown in FIG. 8A and 8B, the same components as those in the example shown in FIG. 3 are denoted by the same reference numerals, and redundant description thereof is omitted.

  For example, as shown in FIG. 4, the expansion device is disposed between the outlet of the condenser 6 and the inlet of the evaporator 2 in the piping of the refrigeration cycle system. The throttle device is integrally formed with the tube main body 10 joined to the piping of the above-described refrigeration cycle system, the guide tube 30 fixed to the inner peripheral portion 10a of the tube main body 10, and the flow rate of the refrigerant formed integrally with the guide tube 30. Supporting the valve seat 30V and the needle member 20, the coil spring 16 for urging the needle member 20 in the direction approaching the valve seat 30V, and one end of the coil spring 16 And a cylindrical stopper member 12 that receives one end of the needle member 20 as main elements.

  An outer peripheral portion of the fixing portion 30A of the guide tube 30 having an outer diameter smaller than the inner diameter of the tube main body 10 is fixed to an intermediate portion spaced from the one end 10E2 of the inner peripheral portion 10a of the tube main body 10 by a predetermined distance. .

  The guide tube 30 is made of a material such as copper, brass, aluminum, or stainless steel by machining. The guide tube 30 includes a fixed portion 30A that is fixed to the inner peripheral portion 10a of the tube body 10 and a guide portion 30B that guides the guide shaft portion 20P2 of the needle member 20 in a slidable manner.

  The guide tube 30 is fixed by the protrusions formed by the depressions 10CA1 and 10CA2 of the tube main body 10 by caulking process biting into the grooves 30CA1 and 30CA2 on the outer peripheral portion of the fixing portion 30A. The guide tube 30 has a metal stopper member 12 on the outer peripheral portion of the end portion of the guide portion 30B closest to the one end 10E1 of the tube main body 10.

  A guide portion 30B is formed on the guide tube 30 at a portion upstream of a communication hole 30C described later. A guide shaft portion 20P2 of the needle member 20 is slidably fitted in the hole portion 30b of the guide portion 30B.

  The valve port 30P and the hole 30b of the valve seat 30V of the fixed portion 30A in the guide tube 30 are formed on a common central axis. At this time, since the guide portion 30B and the fixed portion 30A in the guide tube 30 are integrally formed, the valve port 30P and the hole portion 30b of the valve seat 30V have a common central axis so that their centers coincide with each other. It becomes easy to process on the line with high accuracy.

  A substantially circular communication hole 30C is formed directly below the valve seat 30V between the valve seat 30V and the guide portion 30B in the fixed portion 30A. As shown in FIG. 8A, one end of the communication hole 30C functioning as the refrigerant introduction hole extends along the Y coordinate axis and opens directly below the valve seat 30V, and the other end of the communication hole 30C is the fixed portion 30A. And a guide wall 30B. The connecting wall has pores 30H having a diameter smaller than the opening diameter at one end of the communication hole 30C. Thereby, the communication hole 30 </ b> C allows the valve port 30 </ b> P to communicate between the outer peripheral portion of the guide tube 30 and the stopper member 12 and the inner peripheral portion 10 a of the tube main body 10.

  8A and 8B, the Y coordinate axis is set so as to intersect the central axis CS of the needle member 20, and the Z coordinate axis is set parallel to the central axis CS of the needle member 20. Yes. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis. The central axis CO of the communication hole 30C is set so as to be substantially orthogonal to the central axis CS of the needle member 20 in FIG.

  In such a configuration, when the flow of refrigerant flowing from both ends of the communication hole 30C toward the valve port 30P is a steady flow, the pore 30H has a diameter smaller than the opening diameter of one end of the communication hole 30C. Therefore, the flow rate of one refrigerant flowing through the pores 30H is faster than the flow rate of the other refrigerant flowing from one end of the communication hole 30C. As a result, the flow rate at which the one refrigerant described above flows out to the divergent portion 30d of the fixed portion 30A through a part of the periphery of the valve port 30P of the valve seat 30V is the same as the peripheral velocity of the valve port 30P of the valve seat 30V. It becomes large compared with the flow velocity which flows out into the divergent part 30d of the fixing | fixed part 30A through other parts. As a result, in FIG. 8A, the urging force acts on the action point AP of the tapered portion 20P1 in the direction indicated by the arrow, that is, in the direction of the Y coordinate axis in FIG. Since a predetermined moment acts around the rotation center RP of the guide shaft portion 20P2 in the clockwise direction, a sliding resistance occurs as a reaction between the outer peripheral portion of the guide shaft portion 20P2 and the inner peripheral edge of the hole 30b of the guide portion 30B. It will be. Thereby, the hunting of the needle member 20 and the fine vibration of the tapered portion 20P1 of the needle member 20 are more reliably avoided.

  The connecting wall forming the communication hole 30C of the guide tube 30 in the example shown in FIG. 8A has a pore 30H having a diameter smaller than the opening diameter of one end of the communication hole 30C. However, the present invention is not limited to such an example. For example, as shown in FIG. 9, the connection wall forming the communication hole 30 ′ C of the guide tube 30 ′ may not have a pore. In such a case, a substantially circular communication hole 30'C is formed immediately below the valve seat between the valve seat in the fixed portion of the guide tube 30 'and the guide portion 30'B. As shown in FIG. 9, one end of the communication hole 30 ′ C functioning as the refrigerant introduction hole extends along the Y coordinate axis and opens directly below the valve seat, and the other end of the communication hole 30 ′ C is connected to the guide tube 30. It is formed by the connection wall which connects the fixed part of 'and the guide part 30'B. The Y coordinate axis is set so as to intersect the central axis CS of the needle member 20, and the Z coordinate axis is set parallel to the central axis CS of the needle member 20. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis.

  Even in such a configuration, when the flow of the refrigerant flowing from one end of the communication hole 30′C toward the valve port along the direction indicated by the arrow is a steady flow, the other end of the communication hole 30C is blocked. Therefore, the flow rate of one refrigerant between the inner wall surface of the connecting wall and the outer peripheral surface of the tapered portion 20P1 is higher than the flow rate of the other refrigerant flowing from one end of the communication hole 30′C. As a result, the flow rate at which the above-mentioned one refrigerant flows out to the divergent part of the fixed part through a part of the periphery of the valve port of the valve seat is fixed through the other part of the periphery of the valve port of the valve seat. It becomes large compared with the flow velocity which flows out into the divergent part of the part. As a result, in FIG. 9, the urging force acts on the point of action of the taper 20P1 in the direction indicated by the arrow F, that is, in the direction of the Y coordinate axis in FIG. 9, so that the guide shaft portion 20P2 of the needle member 20 Since a predetermined moment acts around the rotation center in the clockwise direction, a sliding resistance is generated as a reaction between the outer peripheral portion of the guide shaft portion 20P2 and the inner peripheral edge of the hole of the guide portion 30′B. Thereby, the hunting of the needle member 20 and the fine vibration of the tapered portion 20P1 of the needle member 20 are more reliably avoided.

  Further, as a modification of the guide tube used in the example shown in FIG. 8A, for example, as shown in FIG. 10, the central axis CO of the communication hole 32C of the guide tube 32 is the needle member 20. The communication hole 32C may be a through hole, and the fine hole 32H may be configured to communicate with the communication hole 32C.

  In such a case, the guide tube 32 is made by machining with a material similar to the material of the guide tube 30, for example. The guide tube 32 includes a fixed portion that is fixed to the inner peripheral portion 10a of the tube body 10 and a guide portion that guides the guide shaft portion 20P2 of the needle member 20 in a slidable manner. A guide portion is formed in a portion of the guide tube 32 upstream of the communication hole 32C. A guide shaft portion 20P2 of the needle member 20 is slidably fitted in the hole portion of the guide portion.

  Between the valve seat and the guide portion in the fixed portion, a substantially circular communication hole 32C is formed immediately below the valve seat. As shown in FIG. 10, both ends of the communication hole 32C functioning as the refrigerant introduction hole extend along the Y coordinate axis and open right under the valve seat. Further, a pore 32H is opened on one inner peripheral surface forming the communication hole 32C. As shown in FIG. 10, the pore 32H extends along the X coordinate axis, intersects with the communication hole 32C, and communicates with the inside of the communication hole 32C. Accordingly, the communication hole 32 </ b> C allows the valve port to communicate between the outer peripheral portion (not shown) of the guide tube 32 and the stopper member 12 and the inner peripheral portion 10 a of the tube main body 10.

  In FIG. 10, the Y coordinate axis is set so as to intersect the central axis CS of the needle member 20, and the Z coordinate axis is set parallel to the central axis CS of the needle member 20. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis. The center axis CO of the communication hole 32C is set so as to be substantially orthogonal to the center axis CS of the needle member 20 in FIG.

  Even in such a configuration, when the flow of the refrigerant flowing from both ends of the communication hole 32C toward the valve port along the direction indicated by the arrow is a steady flow, one outer peripheral portion of the tapered portion 20P1 of the needle member 20 And the flow rate of one refrigerant passing between the opening end inside the pore 32H passes between the other outer peripheral portion of the tapered portion 20P1 of the facing needle member 20 and the inner peripheral surface forming the communication hole 32C. This is slower than the flow rate of the other refrigerant. As a result, the flow rate at which the above-mentioned one refrigerant flows out to the divergent part of the fixed part through a part of the periphery of the valve port of the valve seat is fixed through the other part of the periphery of the valve port of the valve seat. It becomes large compared with the flow velocity which flows out into the divergent part of the part. As a result, in FIG. 10, the biasing force acts on the point of action of the tapered portion 20 </ b> P <b> 1 in the direction indicated by the arrow F, that is, substantially in the X coordinate axis direction in FIG. 10. Since a predetermined moment acts around the center of rotation, sliding resistance occurs as a reaction between the outer peripheral portion of the guide shaft portion 20P2 and the inner peripheral edge of the hole of the guide portion. Thereby, the hunting of the needle member 20 and the fine vibration of the tapered portion 20P1 of the needle member 20 are more reliably avoided.

  FIGS. 11A and 11B schematically show a third embodiment of the diaphragm device according to the present invention.

  In the example shown in FIG. 3, the center axis CO of the communication hole 18 </ b> C of the guide tube 18 is set to be deviated to the left by a predetermined amount ΔD with respect to the center axis CS of the needle member 20. In the example shown in FIG. 11A, the central axis CO of the communication hole 34 </ b> C of the guide tube 34 is substantially perpendicular to the central axis CS of the needle member 20. 11A and 11B, the same components as those in the example shown in FIG. 3 are denoted by the same reference numerals, and redundant description thereof is omitted.

  For example, as shown in FIG. 4, the expansion device is disposed between the outlet of the condenser 6 and the inlet of the evaporator 2 in the piping of the refrigeration cycle system. The throttle device is integrally formed with the tube main body 10 joined to the piping of the above-described refrigeration cycle system, the guide tube 34 fixed to the inner peripheral portion 10a of the tube main body 10, and adjusts the flow rate of the refrigerant. The valve seat 34V, the needle member 20, the coil spring 16 that urges the needle member 20 toward the valve seat 34V, and one end of the coil spring 16 are supported. And a cylindrical stopper member 12 that receives one end of the needle member 20 as main elements.

  The outer peripheral portion of the fixing portion 34A of the guide tube 34 having an outer diameter smaller than the inner diameter of the tube main body 10 is fixed to an intermediate portion spaced from the one end 10E2 of the inner peripheral portion 10a of the tube main body 10 by a predetermined distance. .

  The guide tube 34 is made by machining with a material similar to the material of the guide tube 30 shown in FIGS. 8A and 8B, for example. The guide tube 34 includes a fixed portion 34A that is fixed to the inner peripheral portion 10a of the tube body 10 and a guide portion 34B that guides the guide shaft portion 20P2 of the needle member 20 so as to be slidable.

  The guide tube 34 is fixed by the protrusions formed by the depressions 10CA1 and 10CA2 of the tube main body 10 by caulking process biting into the grooves 34CA1 and 34CA2 on the outer peripheral portion of the fixing portion 34A. The guide tube 34 has a metal stopper member 12 on the outer peripheral portion of the end portion of the guide portion 34B closest to the one end 10E1 of the tube main body 10.

  A guide portion 34B is formed in the guide tube 34 at a portion upstream of a communication hole 34C described later. The guide shaft portion 20P2 of the needle member 20 is slidably fitted in the hole portion 34b of the guide portion 34B.

  The valve port 34P and the hole 34b of the valve seat 34V of the fixed portion 34A in the guide tube 34 are formed on a common central axis. At this time, since the guide portion 34B and the fixed portion 34A of the guide tube 34 are integrally formed, the valve port 34P and the hole portion 34b of the valve seat 34V have a common central axis so that their centers coincide with each other. It becomes easy to process on the line with high accuracy.

  A substantially circular communication hole 34C is formed immediately below the valve seat 34V between the valve seat 34V and the guide portion 34B in the fixed portion 34A. As shown in FIG. 11A, both ends of the communication hole 34C functioning as the refrigerant introduction hole extend along the Y coordinate axis and open directly below the valve seat 30V. A C-shaped flow rate adjusting piece 36 is provided at a position adjacent to one open end of the communication hole 34C. The flow rate adjusting piece 36 restricts the flow rate of the refrigerant flowing into the communication hole 34C from one opening end to be smaller than the flow rate of the refrigerant flowing into the communication hole 34C from the other opening end. The The flow rate adjusting piece 36 is fixed to the outer peripheral portion of the guide tube 34 by a holding force based on its own elastic force. Accordingly, the communication hole 34C allows the valve port 34P to communicate between the outer peripheral portion of the guide tube 34 and the stopper member 12 and the inner peripheral portion 10a of the tube main body 10.

  11A and 11B, the Y coordinate axis is set so as to intersect the central axis CS of the needle member 20, and the Z coordinate axis is set parallel to the central axis CS of the needle member 20. Yes. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis.

  In such a configuration, when the flow of refrigerant flowing from both ends of the communication hole 34C toward the valve port 34P is a steady flow, the flow rate adjusting piece 36 is provided at a position adjacent to one open end of the communication hole 34C. Therefore, the flow rate of one refrigerant flowing through one open end is faster than the flow rate of the other refrigerant flowing from the other end of the communication hole 34C. As a result, the flow rate at which the one refrigerant described above flows out to the divergent portion 34d of the fixed portion 34A through a part of the periphery of the valve port 34P of the valve seat 34V is such that the other refrigerant is the periphery of the valve port 34P of the valve seat 34V. It becomes large compared with the flow velocity which flows out into the divergent part 34d of 34 A of fixed parts through the other part. As a result, in FIG. 11A, the urging force acts on the action point AP of the taper 20P1 in the direction indicated by the arrow F, that is, in the direction of the Y coordinate axis in FIG. Since a predetermined moment acts clockwise around the rotation center RP of the 20 guide shaft portions 20P2, sliding resistance acts as a reaction between the outer peripheral portion of the guide shaft portion 20P2 and the inner peripheral edge of the hole 34b of the guide portion 34B. Will occur. Thereby, the hunting of the needle member 20 and the fine vibration of the tapered portion 20P1 of the needle member 20 are more reliably avoided.

  12 (A) and 12 (B) schematically show a fourth embodiment of the diaphragm device according to the present invention.

  In the example shown in FIG. 3, the center axis CO of the communication hole 18 </ b> C of the guide tube 18 is set to be deviated to the left by a predetermined amount ΔD with respect to the center axis CS of the needle member 20. In the example shown in FIG. 12A, the central axis CO of the communication hole 34 </ b> C of the guide tube 34 is substantially orthogonal to the central axis CS of the needle member 20. 12A and 12B, the same components as those in the example shown in FIGS. 3 and 11A are denoted by the same reference numerals, and redundant description thereof is omitted. 12A and 12B, the Y coordinate axis is set so as to intersect the central axis CS of the needle member 20, and the Z coordinate axis is set parallel to the central axis CS of the needle member 20. Yes. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis.

  For example, as shown in FIG. 4, the expansion device is disposed between the outlet of the condenser 6 and the inlet of the evaporator 2 in the piping of the refrigeration cycle system. The throttle device is integrally formed with the tube main body 10 joined to the piping of the above-described refrigeration cycle system, the guide tube 34 fixed to the inner peripheral portion 10a of the tube main body 10, and adjusts the flow rate of the refrigerant. The valve seat 34V, the needle member 20, the coil spring 16 that urges the needle member 20 toward the valve seat 34V, and one end of the coil spring 16 are supported. And a cylindrical stopper member 42 for receiving one end of the needle member 20 as main elements.

  The outer peripheral portion of the fixing portion 34A of the guide tube 34 having an outer diameter smaller than the inner diameter of the tube main body 10 is fixed to an intermediate portion spaced from the one end 10E2 of the inner peripheral portion 10a of the tube main body 10 by a predetermined distance. .

  The guide tube 34 has a metal stopper member 42 on the outer peripheral portion of the end portion of the guide portion 34B closest to the one end 10E1 of the tube main body 10.

  The cylindrical stopper member 42 is formed of, for example, a copper alloy thin plate material with a uniform thickness by pressing. Since the stopper member 42 is formed by press molding, it is manufactured at a relatively low cost.

  One end of the stopper member 42 is fixed to the guide portion 34B by the protrusion formed by the depression 42CA1 of the stopper member 42 by caulking process biting into the groove 34CB1 at the end portion of the guide portion 34B. The caulking recess 42CA1 is formed at a plurality of locations, for example, 3 locations with a predetermined interval along the circumferential direction of the stopper member 42. The cylindrical stopper member 42 has a closed end at the other end, and has a structure that covers the coil spring 16 and the spring receiving member 22.

  A flow rate adjusting projection 42D is integrally formed at a position adjacent to the recess 42CA1 in the outer peripheral portion of the stopper member 42. The flow rate adjusting projection 42D restricts the flow rate of the refrigerant flowing into the communication hole 34C from one opening end to be smaller than the flow rate of the refrigerant flowing into the communication hole 34C from the other opening end. It is said. The flow rate adjusting projection 42D is a predetermined circle that forms a dominant arc along the circumferential direction of the stopper member 42 so as to close a gap between the outer peripheral portion of the stopper member 42 and the inner peripheral portion 10a of the tube body 10. It extends with a circumferential angle.

  The other end of the stopper member 42 extends from the guide portion 34B toward the one end 10E1 side of the tube body 10. In addition, the closed end portion has a flat inner surface. The inner surface of the closed end portion receives an end surface 20P5 of an adjusting screw 20P4 described later. The adjustment screw 20P4 is formed integrally with one end of the guide shaft portion 20P2 of the needle member 20, and is screwed into the female screw 22A at one end of the spring receiving member 22. Inside the stopper member 42, a hollow portion 44 into which a liquid refrigerant enters is formed.

  A predetermined gap is formed between the inner peripheral surface of the stopper member 42 other than the recess 42CA1 and the outer peripheral surface of the end portion of the guide portion 34B other than the groove 34CB1. Therefore, the refrigerant supplied from the one end 10E1 side of the tube main body 10 flows into the hollow portion 44 of the stopper member 42 through the clearance or the clearance between the hole 34b of the guide portion 34B and the outer peripheral portion of the guide shaft portion 20P2. The

  In such a configuration, when the flow of the refrigerant flowing from both ends of the communication hole 34C toward the valve port 34P is a steady flow, the flow rate adjustment protrusion 42D flows into the communication hole 34C from one opening end. Since the flow rate of the refrigerant to be reduced is limited to be smaller than the flow rate of the refrigerant flowing into the communication hole 34C from the other opening end, the flow rate of the one refrigerant flowing through the one opening end is It becomes faster than the flow rate of the other refrigerant flowing from the other end. As a result, the flow rate at which the one refrigerant described above flows out to the divergent portion 34d of the fixed portion 34A through a part of the periphery of the valve port 34P of the valve seat 34V is such that the other refrigerant is the periphery of the valve port 34P of the valve seat 34V. It becomes large compared with the flow velocity which flows out into the divergent part 34d of 34 A of fixed parts through the other part. As a result, in FIG. 12A, the urging force acts on the action point AP of the taper 20P1 in the direction indicated by the arrow F, that is, the direction of the Y coordinate axis in FIG. Since a predetermined moment acts clockwise around the rotation center RP of the 20 guide shaft portions 20P2, sliding resistance acts as a reaction between the outer peripheral portion of the guide shaft portion 20P2 and the inner peripheral edge of the hole 34b of the guide portion 34B. Will occur. Thereby, the hunting of the needle member 20 and the fine vibration of the tapered portion 20P1 of the needle member 20 are more reliably avoided.

  13 (A) and 13 (B) schematically show a fifth embodiment of the diaphragm device according to the present invention.

  In the example shown in FIG. 3, the center axis CO of the communication hole 18 </ b> C of the guide tube 18 is set to be deviated to the left by a predetermined amount ΔD with respect to the center axis CS of the needle member 20. In the example shown in FIG. 13A, the central axis CO of the communication hole 34 </ b> C of the guide tube 34 is substantially orthogonal to the central axis CS of the needle member 20. 13A and 13B, the same components as those in the example shown in FIGS. 3 and 11A are denoted by the same reference numerals, and redundant description thereof is omitted. 13A and 13B, the Y coordinate axis is set so as to intersect the central axis CS of the needle member 40, and the Z coordinate axis is set parallel to the central axis CS of the needle member 40. The X coordinate axis is orthogonal to the Y coordinate axis and the Z coordinate axis.

  For example, as shown in FIG. 4, the expansion device is disposed between the outlet of the condenser 6 and the inlet of the evaporator 2 in the piping of the refrigeration cycle system. The throttle device is integrally formed with the tube main body 10 joined to the piping of the above-described refrigeration cycle system, the guide tube 34 fixed to the inner peripheral portion 10a of the tube main body 10, and adjusts the flow rate of the refrigerant. The valve seat 34V, the needle member 40, the coil spring 16 that urges the needle member 40 in the direction approaching the valve seat 34V, and one end of the coil spring 16 are supported. And a cylindrical stopper member 12 for receiving one end of the needle member 40 as main elements.

  The needle member 40 is made of a material similar to the material of the needle member 20 described above by machining, for example, and can slide in a tapered portion 40P1 formed facing the valve seat 34V and a hole portion 34b in the guide portion 34B. The guide shaft portion 40P2 fitted to the guide shaft, the spring receiving member connecting portion 40P3 formed at the tip of the guide shaft portion 40P2, and the adjustment screw 40P4 are configured as main elements.

  The minimum diameter portion of the truncated conical tapered portion 40P1 having a predetermined taper angle is set to be slightly smaller than the diameter of the guide shaft portion 40P2. The tapered portion 40P1 is a base portion having a diameter larger than the diameter of the valve port 34P when the end surface 40P5 of the adjusting screw 40P4 of the needle member 40 is brought into contact with the inner surface of the closed end of the stopper member 12, that is, the most detailed later. A connecting portion with the end overhanging portion 40F is provided at a position separated from the valve port 34P by a predetermined distance in the direction of the divergent portion 34d.

  The tapered portion 40P1 has a flat surface 40PE at a position separated from the central axis CS by a predetermined distance. The flat surface 40PE is formed along the central axis CS of the tapered portion 40P1 by a predetermined length from the vicinity of the lower portion of the tapered portion 40P1 to the connecting portion of the guide shaft portion 40P2. As a result, the operating pressure of the refrigerant between the peripheral edge of the valve port 34P and the flat surface 40PE acts in the radial direction of the tapered portion 40P1 in FIG. The outer peripheral surface of the facing detail 40P1 is pressed toward the peripheral edge of the valve port 34P. Thereby, during the movement of the needle member 40, sliding resistance is generated between the outer peripheral portion of the guide shaft portion 40P2 and the hole 34b of the guide tube 34. Thereby, the hunting of the needle member 40 and the slight vibration of the tapered portion 40P1 of the needle member 40 are more reliably avoided.

  The spring receiving member 22 is fixed to the spring receiving member connecting portion 40P3 of the needle member 40 by caulking. The spring receiving member connecting portion 40P3 is formed by, for example, an annular groove. The spring receiving member 22 is fixed by the protrusion formed by the depression 22CA1 of the spring receiving member 22 by caulking process biting into the groove of the spring receiving member connecting portion 40P3.

  The male screw of the adjustment screw 40P4 formed integrally with the spring receiving member connecting portion 40P3 of the needle member 40 is screwed into the hole of the female screw 22A on the inner peripheral portion of the spring receiving member 22. The hole of the female screw 22A extends in a direction away from the recess 22CA1 with respect to the guide portion 34B. The adjustment screw 40P4 adjusts the urging force of the coil spring 16.

  In each of the embodiments described above, the guide shaft portion of the needle member is formed at a position spaced upstream from the valve port. However, the present invention is not limited to such an example. The end portion of the guide shaft portion may be formed at a position close to the valve port, or the end portion of the guide shaft portion may be configured to be inserted into the valve port.

10 Tube body 12, 42 Stopper member 14, 44 Hollow part 16 Coil spring 18, 28, 30, 30 ', 32, 34 Guide tube 18B, 28B, 30B, 34B Guide part 18C, 18'C, 28C, 30C, 30 'C, 32C, 34C Communication passage 18P, 28P, 30P, 34P Valve port 18V, 28V, 30V, 34V Valve seat 20, 40 Needle member 20P1, 40P1 Tip 20P2, 40P2 Guide shaft 22 Spring receiving member

Claims (10)

A tube main body that is arranged in a pipe for supplying a refrigerant and has open ends at both ends communicating with the pipe;
A valve seat disposed on the inner periphery of the tube body and having a valve port;
A taper having a base at a position spaced from the valve port, arranged to be close to or spaced from the valve port of the valve seat, and controlling an opening area of the valve port; A guide shaft portion extending toward the upstream side of the flow of the refrigerant, and a needle member having
A guide portion disposed on the upstream side of the flow of the refrigerant from the position of the valve seat in the inner peripheral portion of the tube body, and a guide shaft portion of the needle member is slidably disposed;
A biasing member disposed between the guide portion and one open end of the tube main body, and biasing the needle member in a direction approaching the valve port of the valve seat;
The difference between the flow rate of the refrigerant flowing between the tapered portion of the needle member and the inner peripheral edge portion of the valve port through the guide portion and the valve seat, the guide portion and the valve arranged on the primary side. A flow rate control means for controlling to be generated between the seat and the seat;
A diaphragm device comprising:   The expansion device according to claim 1, wherein an enlarged portion communicating with the valve port is formed at a position downstream of the valve seat so as to face a tapered portion of the needle member.   The flow rate control means is formed between the guide portion and the valve seat, and the position of the central axis of the communication hole communicating with the valve port and opening at both ends is set to one with respect to the position of the central axis of the needle member. 2. A diaphragm according to claim 1, comprising a biased configuration.   The enlarged portion is formed at a position that is substantially in the same direction as a direction in which the position of the central axis of the communication hole deviates to one with respect to the position of the central axis of the needle member, and that is downstream of the valve seat. 3. A diaphragm according to claim 2, wherein   The flow rate control means is formed between the guide portion and the valve seat, and includes a configuration in which a central axis of a communication hole communicating with the valve port intersects a central axis of the needle member, and one end of the communication hole is 2. The aperture device according to claim 1, wherein the aperture is open and the other end of the communication hole is closed.   The flow rate control means is formed between the guide portion and the valve seat, and has a configuration in which a central axis of a communication hole communicating with the valve port intersects a central axis of the needle member, and one end of the communication hole is 2. The diaphragm apparatus according to claim 1, further comprising an opening end portion that opens, and the other end of the communication hole has an opening end portion that has an inner diameter smaller than an inner diameter of the opening end portion.   The flow rate control means is formed between the guide portion and the valve seat, and has a configuration in which a central axis of a communication hole that opens at both ends communicating with the valve port intersects with a central axis of the needle member. 2. The aperture device according to claim 1, further comprising a pore having an inner diameter smaller than an inner diameter of the opening end of the hole and facing the needle member through the communication hole.   6. The throttle device according to claim 5, wherein the other end of the communication hole is closed by a flow rate adjusting piece. A stopper member provided at an end of the guide portion so as to surround the guide shaft portion of the needle member and the urging member; and having a hollow portion into which the refrigerant enters, and the flow rate control means includes the guide A center axis of a communication hole formed between a valve portion and the valve seat and open at both ends communicating with the valve port intersects with the center axis of the needle member,
The flow rate control means is a refrigerant formed along the circumferential direction of the stopper member between the outer peripheral portion of the stopper member and the inner peripheral portion of the tube body, and flows into the communication hole from one open end. The throttle device according to claim 1, further comprising a flow rate adjusting projection that restricts the flow rate of the refrigerant to be smaller than a flow rate of the refrigerant flowing into the communication hole from the other opening end. An evaporator, a compressor, and a condenser;
A refrigeration cycle system, wherein the expansion device according to any one of claims 1 to 9 is provided in a pipe disposed between an outlet of the condenser and an inlet of the evaporator.

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