CN107208819B - Throttling device and refrigeration cycle system - Google Patents

Abstract

The present invention provides the throttling set and refrigerating circulation system that can inhibit the generation of abnormal sound.Throttling set (10) has the valve base part (2) with valve port (21), the needle-valve (4) for keeping the aperture of valve port (21) variable, and the guiding parts (3) of the tubular of guidance needle-valve (4) advance and retreat, it is respectively formed with via defined gap and opposed and be capable of the sliding contact surface (34 of sliding contact each other in needle-valve (4) and guiding parts (3), 46), gap becomes the intermediate flow passage (45) for making fluid circulate from valve port (21) towards secondary side, sliding contact surface (46) in needle-valve (4) forms the concave groove (47) as flow path expansion section to expand the width dimensions of intermediate flow passage (45) in direction of the sliding contact surface (34) of oriented separate guiding parts (3).

Description

Throttling device and refrigeration cycle system

technical field

The invention relates to a throttling device and a refrigeration cycle system.

Background technique

Nowadays, as one of throttling devices, a decompression device (sometimes also called a decompression valve, expansion valve) (for example, refer to Patent Document 1). In the decompression device described in Patent Document 1, the valve opening is changed according to the pressure difference between the refrigerant pressure on the condenser (radiator) side (primary side) and the refrigerant pressure on the evaporator side (secondary side). Differential pressure expansion valve.

The decompression device includes: a casing having an inlet and an outlet; a valve body movably supported in the casing to adjust the opening degree of the valve port on the inlet side; A coil spring that biases the spool on the inlet side. The valve body has a cylindrical guide skirt that is guided in sliding contact with the inner peripheral surface of the housing, and a hole through which the refrigerant flows is formed in the guide skirt. In such a decompression device, the refrigerant that has flowed into the housing from the valve port is introduced into the guide skirt through the hole, flows through the guide skirt to the secondary side, and then flows out from the outlet.

prior art literature

patent documents

Patent Document 1: Japanese Patent No. 3528433

Contents of the invention

The problem to be solved by the invention

In the conventional decompression device, the refrigerant flowing through the hole of the valve element is introduced into the guide skirt and flows toward the secondary side. , so there is a possibility that the refrigerant also flows into the gap. In such a decompression device, if the refrigerant flows through the gap between the valve port and the valve core, or the gap between the guide skirt and the housing, there may be cases in the refrigerant at the position immediately after the refrigerant flows through the narrow gap. Cavitation occurs. If cavitation occurs in the refrigerant, the valve element vibrates slightly and comes into contact with the casing, which may cause abnormal noise.

An object of the present invention is to provide an expansion device and a refrigeration cycle system capable of suppressing generation of abnormal noise.

Solution to the problem

The throttling device of the present invention is a throttling device that decompresses high-pressure fluid from the primary side and sends it to the secondary side, and is characterized in that it includes: a valve seat member that has a valve port and is arranged to separate The space on the primary side and the space on the secondary side; the valve core, which faces the above-mentioned valve port from the secondary side of the above-mentioned valve seat member, and makes the opening of the valve port variable; the cylindrical guide member, which provides the above-mentioned The valve element is inserted, and the valve element is guided to advance and retreat relative to the valve seat member. The valve element and the guide member are respectively formed with sliding contact surfaces that are opposed to each other through a predetermined gap and can slide in contact with each other. The gap becomes In the flow path through which the fluid flows from the valve port toward the secondary side, the sliding contact surface of at least one of the valve element and the guide member is formed with a recess that expands the flow path in a direction away from the other sliding contact surface. The flow path expansion part of the width dimension.

According to such the present invention, by forming the flow path expansion portion on the sliding contact surface of the valve element and the guide member, the fluid flowing into the flow path expansion portion is formed into a turbulent flow. The center side (the side away from the guide member) (in the direction of advance and retreat) exerts a centripetal action on the spool. Therefore, micro-vibration of the valve element can be suppressed, making it difficult to contact the guide member, and generation of abnormal noise can be suppressed.

In this case, the flow path expansion part is preferably constituted by a continuous groove in the circumferential direction of the valve body and the guide member, or formed by a plurality of recesses formed at equal intervals in the circumferential direction of the valve body and the guide member. constitute.

According to this configuration, by forming the grooves continuously in the circumferential direction or forming a plurality of recesses at equal intervals in the circumferential direction to form the flow path expansion portion, it is possible to reduce the force acting on each position of the valve body in the circumferential direction. The pressure of the turbulent flow is equalized, so that the gap between the valve core and the guide member can be uniformed in the circumferential direction.

In addition, it is preferable to further include a spring member arranged in the above-mentioned guide member, which urges the above-mentioned valve element toward the above-mentioned valve port side, and utilizes the pressure difference between the high-pressure fluid on the primary side and the low-pressure fluid on the secondary side. The opening degree of the valve port is changed by deforming the spring member and moving the valve body.

According to this configuration, in the differential pressure type throttle device (differential pressure type expansion valve) including the spring member that biases the valve element toward the valve port side, the generation of abnormal noise can be suppressed as described above. Here, the differential pressure throttling device does not have a drive mechanism to drive the spool forward and backward, and the spool moves forward and backward passively through the balance of the pressure of the fluid and the force of the spring component, so the spool easily causes micro Vibration tendency. Also in such a differential pressure throttle device, as described above, the centripetal action can be obtained by using the pressure of the turbulent flow formed by the enlarged flow path, so that the microvibration of the valve element can be effectively suppressed.

In addition, it is preferable to further include a main body housing in which the valve seat member and the guide member are inserted, and which constitutes a primary chamber on the primary side of the valve seat member and a secondary chamber on the secondary side of the valve seat member. In the chamber, a body-side flow path through which fluid flows from the valve port toward the secondary chamber is formed between the body housing and the guide member. According to this structure, by providing the main body case into which the valve seat member and the guide member are inserted, and forming the main body side flow path between the main body case and the guide member, the fluid can be smoothly directed toward the secondary chamber through the main body side flow path. (secondary side) circulation. Therefore, the flow rate desired to be controlled by the main body side flow channel can be ensured without being affected by the turbulent flow generated by the flow channel expansion part. In addition, by being inserted into the main body casing and being protected, even if stress from piping or the like acts upon assembly into the system, deformation of the seat member and guide member can be prevented, so that the forward and backward movement of the valve element and guide can be further suppressed. Abnormal noise caused by contact of parts.

In this case, it is preferable that the guide member is integrally formed continuously with the secondary side of the valve seat member, and that the guide member is formed at a position adjacent to the valve seat member to connect the valve port and the main body side flow path. Connected holes. According to this configuration, since the guide member is integrally formed with the valve seat member, the installation state of the guide member inside the main body casing can be stabilized, and the valve element inside can be guided to advance and retreat stably. In addition, since the communication hole is formed in the guide member, the fluid can smoothly flow from the valve port to the main body side flow path.

In addition, it is preferable that the end portion of the guide member near the secondary side is closed by a cover member, and at a position adjacent to the cover member of the guide member, a channel communicating with the inside of the guide member and the main body side flow path is formed. the second connecting hole. According to this configuration, since the end portion of the guide member near the secondary side is closed by the cover member, and the second communication hole is formed at the adjacent position, it is possible to appropriately adjust the flow rate of the guide member according to the opening area of the second communication hole. The flow rate of fluid that circulates within a component. Therefore, the centripetal action described above can be effectively realized by appropriately adjusting the flow rate of the fluid that flows through the flow path between the guide member and the valve core, that is, the fluid that flows into the flow path expansion portion to form a turbulent flow. . At this time, since the main flow path of the fluid is the main body side flow path outside the guide member, even if the flow rate of the fluid inside the guide member is adjusted, the flow of the fluid flowing through the throttling device will not be hindered, and the fluid can be smoothly flowed. flow towards the secondary side.

The refrigerating cycle system of the present invention is characterized in that it includes: a compressor for compressing refrigerant as a fluid; a condenser for condensing the compressed refrigerant; the above-mentioned throttling device for expanding the condensed refrigerant to depressurize it; and An evaporator that evaporates a decompressed refrigerant.

According to such a refrigerating cycle system of the present invention, it is possible to suppress the occurrence of abnormal noise in the throttle device as described above.

The effects of the invention are as follows.

According to the throttling device and the refrigerating cycle system of the present invention, by providing the flow path expansion part on the sliding contact surface of the valve core and the guide member, the centripetal force of the valve core can be obtained by utilizing the pressure of the turbulent flow formed by the flow path expansion part. Therefore, it is possible to suppress the abnormal sound caused by the contact between the spool and the guide member, thereby promoting quietness.

Description of drawings

FIG. 1 is a cross-sectional view showing a throttle device according to a first embodiment of the present invention.

Fig. 2 is a schematic configuration diagram of a refrigeration cycle including the expansion device.

Fig. 3 is an enlarged cross-sectional view showing a main part of the throttle device.

Fig. 4 is a cross-sectional view showing a modified example of the throttle device.

Fig. 5 is a cross-sectional view showing another modified example of the above throttle device.

Fig. 6 is a cross-sectional view showing a throttle device according to a second embodiment of the present invention.

Detailed ways

Next, embodiments of the present invention will be described with reference to the drawings. 1 is a cross-sectional view showing a throttle device according to a first embodiment, in which (A) is a longitudinal cross-sectional view, and (B) is a cross-sectional view taken along line AA of (A). Fig. 3 is an enlarged sectional view showing a main part of the throttle device, and (B) in the figure is an enlarged view of part A of (A).

The expansion device 10 of this embodiment is used in the refrigeration cycle shown in FIG. 2 . This refrigeration cycle has a compressor 100, a condenser 110, an expansion device 10, and an evaporator 120, and refrigerant circulates in directions indicated by arrows in the figure. For example, when the refrigeration cycle is configured as an air conditioner, the refrigerant compressed by the compressor 100 is supplied to the condenser 110 , and the refrigerant condensed by the condenser 110 is sent to the expansion device 10 . The expansion device 10 expands and decompresses the refrigerant to send it to the evaporator 120 as described below. Furthermore, the cooling function is obtained by cooling the room through heat exchange between the refrigerant evaporated by the evaporator 120 and the air in the room. The refrigerant evaporated by the evaporator 120 is compressed by the compressor 100 again, and the above cycle is repeated.

As shown in FIG. 1(A), the throttle device 10 includes a main body casing 1 made of a metal pipe, a metal valve seat member 2, a guide member 3, a needle valve 4 as a spool, a resistance member 5, and a spring. The coil spring 6 of the parts, the cover part 7, and the limiting part 8. In addition, the valve seat member 2 and the guide member 3 are integrally formed by cutting a metal material or the like.

The main body casing 1 has a cylindrical shape centered on the axis L, and constitutes a primary chamber 11 connected to the condenser 110 and a secondary chamber 12 connected to the evaporator 120 .

The valve seat member 2 has a substantially cylindrical shape that matches the inner surface of the main body housing 1 . A riveting groove 2a is formed on the entire circumference of the outer peripheral surface of the valve seat member 2 (the entire circumference around the axis L). ) is fixed in the main body shell 1. Thus, the valve seat member 2 is disposed between the primary chamber 11 and the secondary chamber 12 . In addition, a valve port 21 that is a cylindrical hole centered on the axis L is formed on the valve seat member 2, and a valve port 21 that opens from the valve port 21 to the primary chamber 11 side coaxially with the valve seat member 2 is formed on the primary chamber 11 side. The cylinder part 22.

The guide member 3 has a cylindrical shape and is erected in the secondary chamber 12 from the valve seat member 2 , and a gap between the guide member 3 and the main body casing 1 forms a main body side flow path 13 . The guide member 3 has a cylindrical guide hole 31 centered on the axis L, and a plurality of communication channels for communicating the inside of the guide hole 31 with the outside (main body side flow path 13 ) are formed at positions adjacent to the valve seat member 2 . Hole 32. In addition, a plurality of second communication holes 33 that communicate the inside of the guide hole 31 with the outside (the main body side flow path 13 ) are formed near the end of the guide member 3 on the side of the secondary chamber 12 . The total opening area is formed to be smaller than the communicating hole 32 .

The needle valve 4 has a conical needle portion 41 formed by making the end surface of the front end portion 41 a substantially flat, an insertion portion 42 inserted into the guide hole 31 of the guide member 3 , and two holes formed in the insertion portion 42 . The raised portion 43 of the secondary end. The insertion portion 42 has a substantially cylindrical shape, and by inserting the insertion portion 42 into the guide hole 31 , the needle valve 4 is guided so as to move forward and backward along the axis L. As shown in FIG. Furthermore, the space behind the needle valve 4 of the guide hole 31 becomes an intermediate pressure chamber 44 . The needle portion 41 is inserted through the valve port 21 , and the gap between the needle valve 4 and the valve port 21 is changed as the needle valve 4 moves forward and backward, whereby the valve opening degree is variably controlled.

As shown in FIG. 3 , the outer peripheral surface of the insertion portion 42 and the inner peripheral surface of the guide hole 31 face each other through a predetermined gap, and the gap becomes an intermediate flow path through which the refrigerant flows from the valve port 21 to the intermediate pressure chamber 44 . (fluid path) 45. Further, a sliding contact surface 46 is formed on the outer peripheral surface of the insertion portion 42 and a sliding contact surface 34 is formed on the inner peripheral surface of the guide hole 31 , and these sliding contact surfaces 34 , 46 are in sliding contact with each other. The gap dimension L1 between the sliding contact surfaces 34 and 46 is set, for example, to about 0.1 mm or less so that the needle valve 4 is guided forward and backward by the guide member 3 without play.

The resistance member 5 is attached to the boss portion 43 of the needle valve 4 and extends from the insertion portion 42 toward the secondary side. The resistance member 5 is formed of a leaf spring or the like, and has a plurality of vane portions 51 for slidingly contacting the inner peripheral surface of the guide hole 31 . The resistance member 5 provides sliding resistance to the forward and backward movement of the needle valve 4 by bringing the vane portion 51 into sliding contact with the inner peripheral surface of the guide hole 31 . That is, if the pressure of the refrigerant fluctuates with the opening and closing of the valve port 21, there is a possibility that the needle valve 4 may fluctuate slightly and repeatedly open and close. beat.

The coil spring 6 is arranged in a compressed state between the needle valve 4 and the cover member 7 via the resistance member 5 in the guide hole 31 . The cover member 7 is fixed to the guide member 3 by caulking the guide member 3 at the positions of the caulking grooves on its outer periphery. The coil spring 6 exerts force on the needle valve 4 toward the primary chamber 11 side, and the needle valve 4 moves to the closed position side where the needle-like portion 41 blocks the valve port 21 by using the force, and the gap between the primary chamber 11 and the secondary chamber 12 When the pressing force due to the differential pressure exceeds the urging force of the coil spring 6 , the needle valve 4 moves to the open position side (secondary side) where the needle portion 41 opens the valve port 21 .

The stopper 8 has a substantially cylindrical shape, has a caulking groove 8a formed on its outer periphery, and is fixed to the valve seat member 2 by caulking the cylindrical portion 22 of the valve seat member 2 at the position of the caulking groove 8a. And, as shown in FIG. 1(B), the stopper member 8 is formed with cutouts 81 having a D-shaped cross-section formed by cutting off two parts of its outer peripheral surface, and the refrigerant can pass through these cutouts. 81 to flow from the primary chamber 11 toward the valve port 21. The front end portion 41 a of the needle portion 41 of the needle valve 4 abuts against the stopper 8 , thereby forming a gap between the needle portion 41 and the valve port 21 . That is, the tip end portion 41 a of the needle valve 4 is positioned by the stopper member 8 , and the needle valve 4 is supported in a state where it is not seated on the valve seat member 2 .

According to the above structure, when the high-pressure refrigerant from the condenser 110 flows into the primary chamber 11, the refrigerant in the primary chamber 11 passes through the valve from the notch 81 of the stopper 8 as shown by the arrows in FIGS. 1 and 3 . The gap between the mouth 21 and the needle-like portion 41 allows the flow to flow into the pilot hole 31 . The refrigerant flowing out of the guide hole 31 is split, and the refrigerant flowing on one side flows from the communication hole 32 of the guide member 3 to the main body side flow path 13 , and the refrigerant flowing on the other side passes through the intermediate flow path 45 to the middle. The pressure chamber 44 flows in. The refrigerant in the body-side flow path 13 flows into the secondary chamber 12 as it is, but the refrigerant in the intermediate pressure chamber 44 flows out into the secondary chamber 12 through the second communication hole 33 of the guide member 3 . The refrigerant thus expanded, decompressed, and flowed into the secondary chamber 12 is sent to the evaporator 120 .

In the throttle device 10 described above, the sliding contact surface 46 of the sliding contact surface 46 of the insertion portion 42 of the needle valve 4 and the sliding contact surface 34 of the inner peripheral surface of the guide member 3 is formed as shown in FIG. 3 . A circumferentially continuous groove 47 centered on the axis L. The groove 47 is recessed in a direction away from the sliding contact surface 34 of the guide member 3 (direction toward the axis L), and the dimension L2 between the bottom of the groove 47 and the sliding contact surface 34 is formed to be larger than that of the sliding contact surface 34. , 46 and 46 have a larger gap size L1. That is, the groove 47 is used to form a channel expansion portion that expands the width dimension of the intermediate channel 45 .

Here, as shown in FIG. 3(B), the gap dimension L1 between the sliding contact surfaces 34 and 46 is about 0.1 mm or less. On the other hand, the depth dimension of the groove 47 (from the sliding contact surface 46 to the groove 47 The dimension to the bottom) L3 is preferably about 0.4 mm to 1.5 mm. Also, the width dimension L4 of the groove 47 along the axis L is preferably equal to or greater than its depth dimension L3. In addition, the angle of the inclined surface continuing from the sliding contact surface 46 of the groove 47 is approximately 45°, and the bottom part thereof is a V-shaped groove having an arcuate curved surface shape.

Since such a groove 47 as a flow path expansion portion is formed on the sliding contact surface 46 of the needle valve 4, the refrigerant flowing to the secondary side in the intermediate flow path 45 flows into the groove 47 and is formed in the groove 47. Turbulence like a whirlpool. The pressure when the turbulent flow collides with the inner surface of the groove 47 obtains a centripetal action that biases the needle valve 4 toward the center side of the axis L, thereby maintaining the sliding contact surface 34 of the needle valve 4 and the guide hole 31 . 46 gap size L1 between each other. Furthermore, since the groove 47 is formed, the sliding contact surface 46 of the insertion portion 42 is divided into two equal parts, the primary side and the secondary side along the axis L, and the respective sliding contact surfaces 46 are configured to be in sliding contact with the guide member 3 . Surface 34 is in sliding contact.

In addition, the groove 47 as the flow path expansion part is not limited to the forms shown in FIGS. 1 to 3 , and may be as shown in FIGS. form. In the throttle device 10 shown in FIG. 4(A), a total of two grooves 47 are provided on the insertion portion 42 of the needle valve 4 and arranged on the primary side and the secondary side along the axis L. As shown in FIG. In other words, the sliding contact surface 46 of the insertion portion 42 is divided into three equal parts along the axis L, the primary side, the middle part, and the secondary side, and the respective sliding contact surfaces 46 are configured to be in sliding contact with the sliding contact surface 34 of the guide member 3 . Therefore, by using the two grooves 47 to generate centripetal action due to the turbulent flow at two places on the primary side and the secondary side of the insertion portion 42 , it is possible to prevent inclination of the needle valve 4 .

In the throttle device 10 shown in FIG. 4(B), the insertion portion 42 of the needle valve 4 is provided with a groove 47 formed long along the axis L. As shown in FIG. The width dimension L4 of the groove 47 is set to about five times (5L3) the depth dimension L3. Therefore, the sliding contact surfaces 46 are provided at the ends of the insertion portion 42 separated toward the primary side and the secondary side along the axis L, and the respective sliding contact surfaces 46 are configured to be in sliding contact with the sliding contact surfaces 34 of the guide member 3 . The groove 47 shown in FIG. 4(B) is a square groove recessed approximately at right angles from the sliding contact surface 46. Since the refrigerant passing through the gap between the sliding contact surfaces 34 and 46 causes a sharp change in flow velocity, Turbulent flow tends to be generated at the edges of the sliding contact surface 46 and the groove 47 .

In the throttling device 10 shown in FIG. 5(A), a plurality of recesses 48 formed at equal intervals in the circumferential direction are formed in the insertion portion 42 of the needle valve 4, and the expansion of the flow path is constituted by these plurality of recesses 48. department. The plurality of recesses 48 includes, for example, six recesses provided at intervals of 60° around the axis L, and each recess 48 is formed by hemispherically recessing the sliding contact surface 46 of the insertion portion 42 by cutting or the like. The depth dimension L3 of each concave portion 48 is the same as that of the groove 47, and is preferably about 0.4 mm to 1.5 mm. In addition, the size L4 of each concave portion 48 is preferably equal to or greater than the depth L3 thereof.

In the throttling device 10 shown in FIG. 5(B), the insertion portion 42 of the needle valve 4 is formed in a cylindrical shape, and substantially the entire outer peripheral surface thereof serves as a sliding contact surface 46. On the other hand, inside the guide member 3, The sliding contact surface 3 of the peripheral surface is formed with a groove 35 continuous in the circumferential direction. The groove 35 is formed by denting the sliding contact surface 34 of the guide member 3 by cutting or the like, and the groove 35 constitutes the enlarged flow path. The depth L3 of the groove 35 is the same as that of the groove 47, and is preferably about 0.4 mm to 1.5 mm. Also, the width dimension L4 of the groove 35 along the axis L is preferably equal to or greater than the depth dimension L3 thereof. The groove 35 is a square groove recessed substantially perpendicularly from the sliding contact surface 34 , and turbulent flow is likely to occur at the edge of the sliding contact surface 34 and the groove 35 .

According to the above-mentioned present embodiment, when the refrigerant flows through the intermediate flow path 45 formed between the guide hole 31 of the guide member 3 and the needle valve 4, the refrigerant flows into the groove 47 (or the concave portion 48, the groove 35). The turbulent flow is formed, and the turbulent flow urges the needle valve 4 toward the center side of the axis L, thereby suppressing the microvibration of the needle valve 4 and making it difficult to contact the guide member 3, thereby suppressing the occurrence of abnormal noise.

And, since the grooves 47 (or the grooves 35) are continuously formed along the circumferential direction of the needle valve 4 (or the guide member 3), or the recesses 48 are formed at equal intervals along the circumferential direction of the needle valve 4, it is possible to cause The pressure of the turbulent flow is equalized at each position of the valve 4 along the circumferential direction, so that the gap size L1 between the needle valve 4 and the guide member 3 can be made uniform in the circumferential direction.

Furthermore, the throttling device 10 includes a main body housing 1 into which the valve seat member 2 and the guide member 3 are inserted, and since the main body side flow path 13 is formed between the main body housing 1 and the guide member 3, the refrigerant can be smoothly flowed. It flows toward the secondary chamber 12 through the main body side channel 13 . Moreover, since it is inserted into the main body housing 1 and protected, and the guide member 3 is integrally formed with the valve seat member 2, deformation of the valve seat member 2 and the guide member 3 can be prevented, thereby further suppressing the forward and backward movement of the needle valve 4 and the valve seat member 2. Abnormal noise caused by the contact of the guide member 3. In addition, since the communication hole 32 is formed in the guide member 3 , the refrigerant can smoothly flow from the valve port 21 to the main body side flow path 13 .

And, since the end portion close to the secondary side of the guide member 3 is closed by the cover member 7, and the second communication hole 33 is formed at an adjacent position, it can be appropriately adjusted according to the opening area of the second communication hole 33 . The flow rate of the refrigerant flowing through the guide member 3 . Therefore, by appropriately adjusting the flow rate of the refrigerant flowing into the groove 47 (or the concave portion 48, the groove 35) in the intermediate flow path 45 inside the guide member 3 to form a turbulent flow, the effect on the Centripetal action of needle valve 4. At this time, since the main flow path of the refrigerant is the main body side flow path 13, even if the flow rate of the refrigerant in the intermediate flow path 45 is adjusted, the flow of the refrigerant flowing through the expansion device 10 will not be hindered, and the cooling can be achieved. The agent flows smoothly toward the secondary side.

Next, a throttle device according to a second embodiment of the present invention will be described based on FIG. 6 . The expansion device 10A of the present embodiment is significantly different from the expansion device 10 described above in that the main body casing 1 and the guide member 3 are omitted, and the pipe P for circulating the refrigerant in the refrigeration cycle is used as the guide member. Hereinafter, points of difference from the first embodiment will be described in detail, and the same or similar configurations as those of the first embodiment will be given the same reference numerals and descriptions thereof will be omitted in some cases.

The throttle device 10A is provided inside the pipe P, and includes a valve seat member 2A, a needle valve 4A, a resistance member 5A, a coil spring 6A, a stopper member 8A, and an adjustment member 9 .

The valve seat member 2A is a substantially cylindrical shape that matches the inner surface of the pipe P, and has a riveting groove 2a formed on the entire circumference of its outer peripheral surface. By riveting the pipe P at the position of the riveting groove 2a, the valve seat member 2A is Fixed in the pipe P. Thus, the valve seat member 2A partitions the inside of the pipe P into a primary side (condenser 110 ) and a secondary side (evaporator 120 ). Furthermore, a valve port 21 that is a cylindrical hole centered on the axis L is formed in the valve seat member 2A, and a female thread portion 23 that opens from the valve port 21 to the primary side is formed on the primary side.

The needle valve 4A is guided to move forward and backward along the axis L by the insertion portion 42 thereof slidingly contacting the inner surface of the pipe P to be guided. The outer peripheral surface of the insertion portion 42 and the inner peripheral surface of the pipe P face each other through a predetermined gap, and the gap becomes a flow path 45A through which the refrigerant flows from the valve port 21 toward the secondary side. Further, a sliding contact surface 46 is formed on the outer peripheral surface of the insertion portion 42 and a sliding contact surface P1 is formed on the inner peripheral surface of the pipe P, and these sliding contact surfaces 46 and P1 are in sliding contact with each other. Two continuous grooves 47 are formed in the sliding contact surface 46 of the insertion portion 42 along the circumferential direction centering on the axis L. As shown in FIG. These grooves 47 are formed to be recessed in a direction away from the sliding contact surface P1 of the pipe P, and the grooves 47 constitute a flow path expansion portion that expands the width of the flow path 45A.

The resistance member 5A has a plurality of vane portions 51 that are in sliding contact with the inner surface of the pipe P, and provides sliding resistance to the forward and backward movement of the needle valve 4A, thereby preventing bouncing of the needle valve 4A. The coil spring 6A is arranged between the needle valve 4A and the adjustment member 9 in a compressed state through the resistance member 5A in the pipe P. As shown in FIG. The adjustment member 9 has an adjustment member main body 91 integrally formed in the shape of an external thread, and a fixing member 92 that is riveted and fixed to the pipe P and screwed to the adjustment member main body 91 . The via hole 93 for the communication on the side (the evaporator 120). The adjustment member main body 91 has a slit for fitting a flat head screwdriver at its secondary side end, and the coil spring 6A can be adjusted by changing the amount of screwing of the fixing member 92 into the adjustment member main body 91 . Force against the needle valve 4A.

The stopper member 8A is integrally formed in an external thread shape, and is attached to the internal thread portion 23 of the valve seat member 2A by screwing. A conduction hole (not shown) through which the refrigerant flows from the primary side (condenser 110 ) toward the valve port 21 is formed through the stopper member 8A.

The stopper member 8 positions the needle-like portion 41 of the needle valve 4A by contacting the front end thereof, and adjusts the needle valve 4A by changing the amount of screwing into the internal thread portion 23 of the valve seat member 2A. The gap between the needle-shaped portion 41 and the valve port 21 can adjust the flow rate (release flow rate) of the refrigerant flowing through the gap. After the position adjustment of the stopper member 8A is performed in this way, the stopper member 8A is fixed to the valve seat member 2A by bonding, brazing, caulking, or the like, for example.

According to the expansion device 10A of this embodiment, when the refrigerant flows through the flow path 45A formed between the sliding contact surface 46 of the needle valve 4A and the sliding contact surface P1 of the pipe P, the refrigerant flows into the groove 47 to form a The turbulent flow biases the needle valve 4A toward the center of the axis L, thereby suppressing microvibration of the needle valve 4A, making it difficult to contact the pipe P, and suppressing the occurrence of abnormal noise. In addition, by omitting the main body case 1 and the guide member 3 in the first embodiment and using the pipe P as the guide member, the number of parts can be reduced and the structure of the throttle device 10A can be simplified.

In addition, this invention is not limited to the above-mentioned embodiment, Other structure etc. which can achieve the object of this invention are included, The present invention also includes the deformation|transformation etc. which are shown below. For example, in the above-mentioned embodiment, the differential pressure type throttling device (differential pressure type expansion device) in which the valve element is moved by using the differential pressure of the refrigerant on the primary side and the secondary side to adjust the opening degree of the valve port is shown. valve), but the throttling device of the present invention is not limited to a differential pressure throttling device, and may also have a drive mechanism for driving a spool (for example, an electric valve, a solenoid valve, etc.). In addition, in the above-mentioned embodiment, an example in which the valve element is a needle valve has been described, but it is not limited to this, and may be a ball valve having an insertion portion inserted into the guide member, or a conical shape with a large apex angle. valve etc. In addition, the expansion device of the present invention is not limited to use in an expansion valve of a refrigeration cycle, and can be used in various piping systems for passing various fluids such as gas and liquid.

In addition, in the above-mentioned first embodiment, the valve seat member 2 is riveted and fixed to the main body casing 1, the cover member 7 is riveted and fixed to the guide member 3, and the stopper member 8 is riveted and fixed to the cylinder portion 22 of the valve seat member 2, but each of these The components are not limited to being fixed by riveting, and may be fixed by appropriate fixing methods such as welding, bonding, and brazing. Similarly, in the above-mentioned second embodiment, the valve seat member 2A is caulked and fixed to the pipe P, and the fixing member 92 of the adjustment member 9 is caulked and fixed to the pipe P. Soldering and other appropriate fixing methods to fix.

In addition, in the above-mentioned embodiment, the groove 47 that is continuous along the circumferential direction on the outer peripheral surface of the valve element, or a plurality of recesses 48 formed at equal intervals along the circumferential direction of the valve element, or the inner peripheral surface of the guide member along the The grooves 35 continuous in the circumferential direction form the enlarged flow path, but the enlarged flow path in the present invention is not limited to the grooves 35, 47, and recesses 48 described above. That is, the flow path expansion part is formed on at least one of the valve core and the guide member, and is concaved in a direction away from the other to enlarge the width dimension of the flow path, or it may be along the circumferential direction and formed obliquely in the axial direction. It is not limited to either one of the spool and the guide member, but may be formed on both.

Furthermore, in the above embodiment, the recess 48 is composed of six recesses provided in the insertion portion 42 of the needle valve 4 at intervals of 60° around the axis L, but the number of recesses is not particularly limited. However, the recesses are preferably provided at equal intervals in the circumferential direction. In addition, in the above-mentioned embodiment, each recess 48 is formed by hemispherically recessing the sliding contact surface 46 of the insertion portion 42, but the shape of the recess is not limited to the hemispherical shape, and may be a square, a rectangle, other polygonal shapes, etc. Furthermore, an ellipse shape or an oval shape may be sufficient as it. At this time, when the concave portion has a rectangular shape, an elliptical shape, or an oblong shape, it is preferable that the longitudinal direction thereof is provided along the axial direction of the valve body.

In addition, in the above-mentioned embodiment, as the dimensions of the grooves 35, 47, and the concave portion 48, the width dimension L4 is equal to or greater than the depth dimension L3, or the width dimension L4 is about 5 times the depth dimension L3. (That is, the example of L3≤L4≤5L3), however, as the width dimension L4 of the groove and the concave part, it is preferably equal to the depth dimension L3 or more than the depth dimension L3 and less than twice the depth dimension (that is, L3≤L4≤2L3 ). By setting the width dimension L4 of the groove or the concave portion in this way, turbulent flow can be easily generated, and the area of the sliding contact surface can be secured to maintain durability. In addition, as the cross-sectional shape of the groove, it may be a V-shaped groove with a curved bottom portion as in the above-mentioned embodiment, but it may also be a V-shaped groove with an acute angle without a curved surface at the bottom portion. The larger the slope and the sliding contact surface The angle formed is more prone to turbulence. In addition, as the cross-sectional shape of the groove and the recessed portion, a square groove having a larger angle with the sliding contact surface is more preferable than a V-shaped groove, so that a sharp flow velocity of the refrigerant is generated at the edge of the sliding contact surface. Changes are prone to turbulence.

The embodiments of the present invention have been described above in detail with reference to the drawings, but the specific configurations are not limited to these embodiments, and the present invention includes design changes and the like within a range not departing from the gist of the present invention.

Explanation of symbols

1—Main shell, 2, 2A—Seat parts, 3—Guiding parts, 4, 4A—Needle valve (spool), 6—Coil spring (spring parts), 7—Cover parts, 10, 10A—Throttling device , 11—primary chamber, 12—secondary chamber, 13—main side flow path, 21—valve port, 32—communication hole, 33—second communication hole, 34—sliding contact surface, 35—groove, 45—middle Flow path (flow path), 46—sliding contact surface, 47—groove (flow path expansion portion), 48—recess (flow path expansion portion), 100—compressor, 110—condenser, 120—evaporator, P - Piping (guide part), P1 - sliding contact surface.

Claims (4)

1. a kind of throttling set carries out decompression to the fluid of the high pressure from primary side and sends out to secondary side, feature exists In having:

Valve base part with valve port, and is arranged to separate the space of primary side and the space of secondary side；

Spool faces above-mentioned valve port by secondary side from than above-mentioned valve base part, and keeps the aperture of the valve port variable；And

The guiding parts of tubular supplies above-mentioned spool interpolation, and the spool is guided to retreat relative to above-mentioned valve base part,

In above-mentioned spool and above-mentioned guiding parts, it is respectively formed with via defined gap and opposed and can slide connect each other The sliding contact surface of touching, above-mentioned gap become the flow path for making fluid circulate from above-mentioned valve port towards secondary side,

In above-mentioned spool and the above-mentioned sliding contact surface for being only limitted to either one of above-mentioned guiding parts, formed oriented far from another The concave flow path expansion section to expand the width dimensions of above-mentioned flow path in direction of the sliding contact surface of side, connects in the sliding of another party Contacting surface does not form above-mentioned flow path expansion section.

2. throttling set according to claim 1, which is characterized in that

Above-mentioned flow path expansion section is by only either one the groove continuously in a circumferential of above-mentioned spool and above-mentioned guiding parts come structure At, or by above-mentioned spool and above-mentioned guiding parts only either one circumferentially with multiple recess portions for being formed at equal intervals come structure At.

3. throttling set according to claim 1 or 2, which is characterized in that

Spring members are also equipped with, which configures in above-mentioned guiding parts, and Xiang Shangshu valve port side carries out above-mentioned spool Force,

Deform above-mentioned spring members using the pressure difference of the fluid of the low pressure of the fluid and secondary side of the high pressure of primary side, and And keep above-mentioned spool mobile, to be changed to the aperture of above-mentioned valve port.

4. a kind of refrigerating circulation system, which is characterized in that have:

The compressor that refrigerant as fluid is compressed；Make the condenser of the refrigerant condensation of compression；Make the system of condensation Throttling set described in any one of claims 1 to 3 that cryogen expands to depressurize；And make the steaming of the refrigerant evaporation of decompression Send out device.