JP2016180556A - Throttle device and refrigeration cycle apparatus using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a throttle device including a throttle mechanism as well as a strainer function collecting foreign matters, enabling one part to play a role of two parts, capable of reducing the number of parts, capable of realizing space saving and the saving of manufacturing processes, and contributing to improving manufacturing reliability.SOLUTION: A throttle device 1 according to an embodiment for use in a refrigeration cycle apparatus or the like comprises a strainer 3 provided within a cylindrical throttle device body 2 and collecting foreign matters. The throttle device 1 further comprises a throttle mechanism having a helical channel 5.SELECTED DRAWING: Figure 1

Description

  Embodiments described herein relate generally to a throttle device and a refrigeration cycle device such as an air conditioner or a refrigeration device using the same.

  Conventionally, in a refrigeration cycle used for an air conditioner or the like, a throttling device has been used to adjust the flow rate of refrigerant or refrigeration oil or reduce the pressure. When the amount of restriction is fixed, a capillary tube (capillary tube) is generally used. Usually, the capillary tube is wound in a circular coil shape because the tube diameter is thin and the tube length is long. The capillary tube having such a shape is fixed by a covering made of a rubber tube or the like and a restraining tool such as a binding band in order to suppress friction and noise caused by vibration. In addition, since the tube diameter is small as described above, dust and the like are easily clogged, and a strainer is often provided upstream of the capillary tube. As a result, the reliability is improved, but there are problems such as a reduction in arrangement space due to an increase in the number of parts, a deterioration in manufacturability due to an increase in the number of brazing points, and an increase in cost.

JP 2007-127320 A JP-A-10-332228

  The problems to be solved by the present invention include a strainer function in addition to a strainer function to collect foreign matter, and can play two roles with one part, reduce the number of parts, save space and reduce manufacturing. It is possible to reduce the number of processes and to provide a diaphragm device that contributes to the improvement of manufacturing reliability.

  In order to achieve the above object, the expansion device of the embodiment used in the refrigeration cycle apparatus or the like includes a strainer that collects foreign matter inside the cylindrical expansion device body. Moreover, the throttle mechanism which has a spiral flow path is provided.

It is a figure which shows the aperture_diaphragm | restriction apparatus by 1st Embodiment. It is a figure which decomposes | disassembles and shows a part of aperture device by the same embodiment. It is a figure which shows the aperture_diaphragm | restriction apparatus by 2nd Embodiment. It is a figure which shows the aperture_diaphragm | restriction apparatus by 3rd Embodiment. It is a figure which shows the aperture_diaphragm | restriction apparatus by 4th Embodiment. It is a figure which shows the aperture_diaphragm | restriction apparatus by 5th Embodiment. It is a refrigerating cycle block diagram which shows the refrigerating cycle apparatus using the expansion apparatus in one Embodiment.

DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment for carrying out the invention will be described with reference to FIGS.
(First embodiment)

FIG. 7 is a refrigeration cycle configuration diagram showing a basic configuration of an air-conditioning apparatus 100 (an example of a refrigeration cycle apparatus) using the throttle device according to the first embodiment.
In the air conditioner 100, for example, one outdoor unit 101 and a plurality of (in this case, four) indoor units 102a to 102d are connected by a transition pipe (liquid pipe Pl, gas pipe Pg).
The outdoor unit 101 includes three compressors 103a to 103c. Check valves are provided on the discharge sides of the compressors 103a to 103c, respectively, and an oil separator 105, a four-way valve 106, an outdoor heat exchanger 107, an outdoor expansion valve 108, a liquid tank 109, a liquid, The pipe connection unit 110 is sequentially connected. One end of a liquid pipe Pl that is a connecting pipe connecting the outdoor unit 101 and the indoor units 102a to 102d is connected to the liquid pipe connecting unit 110. The other end of the liquid pipe Pl is branched into a plurality of parts and connected to the liquid pipe connecting parts 121a to 121d of the indoor units 102a to 102d. In each indoor unit 102, a liquid pipe connection part 121, an indoor expansion valve 122, an indoor heat exchanger 123, and a gas pipe connection part 124 are sequentially connected. One end of a gas pipe Pg, which is a connecting pipe connecting the outdoor unit 101 and the indoor units 102a to 102d, is connected to the gas pipe connecting portions 124a to 124d, and the other end side of the gas pipe Pg is gathered into one and is connected to the outdoor It is connected to the gas pipe connection part 111 of the machine 101.
In the outdoor unit 101, the gas pipe connection portion 111 is connected to the suction port of the four-way valve 106, the accumulator 112, and the compressor 103 via the refrigerant pipe 104.
As described above, the main circuit of the refrigeration cycle of the air conditioner 100 is configured.

  In the outdoor unit 101, in addition to the main circuit, a circuit for returning the refrigeration oil separated by the oil separator 105 to the compressors 103a to 103c and a circuit for balancing the refrigeration oil between the compressors 103a to 103c (hereinafter, summarized) A so-called oil leveling circuit). Hereinafter, the oil leveling circuit will be described.

One ends of oil discharge pipes 130a to 130c are respectively connected to predetermined height positions on the case side surfaces of the compressors 103a to 103c, and the other ends of the oil discharge pipes 130a to 130c are connected to the oil collecting pipe 131. The oil discharge pipes 130a to 130c are provided with check valves 132a to 132c and throttle devices 1a to 1c.
A bypass pipe 133 that branches from the high-pressure side refrigerant pipe 104 is connected to one end of the oil collecting pipe 131, and a throttling device 1 d is provided in the bypass pipe 133.
An oil guide pipe 140 is connected to the other end of the oil collecting pipe 131. The oil guide pipe 140 is connected to an inlet of a distributor 141 described later.
A first oil return pipe 151 is connected to the bottom of the oil separator 105, and a second oil return pipe 152 is connected to the side of the oil separator 105.
The first oil return pipe 151 is provided with a throttle device 1e and an electromagnetic on-off valve 153, and is connected between the oil guide pipe 140 and the distributor 141. The second oil return pipe 152 is provided with a throttling device 1 f and connected to the oil collecting pipe 131.
The distributor 141 is provided with three flow paths branched therein, and communicates with the three outlets.
One ends of oil return pipes 155a to 155c are connected to the three outlets of the distributor 141, respectively. The other ends of the oil return pipes 155a to 155c are connected to the suction pipes of the compressors 103a to 103c, respectively.

  As described above, the oil equalizing circuit is provided with a plurality of throttle devices 1a to 1f, and in order to prevent damage to the compressor due to lack of refrigerating machine oil while minimizing the pressure loss due to the oil equalizing circuit, The flow rates of the refrigerant and the refrigerating machine oil flowing in the oil equalizing circuit are adjusted by the expansion devices 1a to 1f.

In addition, an outdoor fan 125 is disposed opposite the outdoor heat exchanger 107 provided in the outdoor unit 101, and the operation is controlled by an outdoor control unit that is electrically connected to a remote controller (not shown) together with the compressor 103 and the like. .
The outdoor unit 101 is provided with an inverter, rectifies the voltage of the commercial AC power supply, converts the rectified voltage into an AC voltage having a frequency according to a command from the outdoor control unit, and outputs the AC voltage. The compressor 103 is a variable capacity type, and is driven by the output of the inverter.
Indoor fans 126a to 126d are arranged facing the indoor heat exchangers 123a to 123d provided in the indoor units 102a to 102d. The indoor fans 126a to 126d are driven and controlled by a driving operation on the remote controller.

Next, the flow of the refrigerant during the cooling operation in the refrigeration cycle of the air conditioner 100 will be described.
When the compressors 103a to 103c are driven, the refrigerant is compressed, becomes a high-temperature and high-pressure gas refrigerant, and is discharged from the compressors 103a to 103c. The gas refrigerant discharged from the compressors 103a to 103c is guided to the oil separator 105 through the refrigerant pipe 104, where the refrigeration oil contained in the gas refrigerant is separated.
The gas refrigerant exiting the oil separator 105 is guided to the outdoor heat exchanger 107 through the four-way valve 106 to exchange heat with the outdoor air. Here, the gas refrigerant is condensed and liquefied, and is led to the liquid pipe connection parts 121a to 121d of the indoor units 102a to 102d through the outdoor expansion valve 108, the liquid tank 109, the liquid pipe connection part 110, and the liquid pipe Pl in order.
In the indoor units 102a to 102d, they are adiabatically expanded by the expansion valves 122a to 122d and flow to the indoor heat exchangers 123a to 123d. The indoor heat exchangers 123a to 123d exchange heat with room air to evaporate and gasify. At this time, latent heat of evaporation is taken from the room air, and the room air is changed to cold air. The cool air is blown into the room by the action of the indoor fans 126a to 126d, and the air is cooled.
The refrigerant that has exited the indoor heat exchangers 123a to 123d exits the indoor units 102a to 102d through the gas pipe connecting parts 124a to 124d, and enters the outdoor unit 101 from the gas pipe Pg and the gas pipe connecting unit 111 of the outdoor unit 101. Led to. The refrigerant guided into the outdoor unit 101 is guided to the four-way valve 106 and the accumulator 112 through the refrigerant pipe 104 in the outdoor unit 101 and separated into gas and liquid in the accumulator 112 and then sucked into the compressors 103a to 103c. . The refrigerant sucked into the compressors 103a to 103d is compressed again, becomes a high-temperature and high-pressure gas refrigerant, and circulates in the above-described system path.
During the heating operation, the refrigerant is guided in the opposite direction to that during the cooling operation by switching the four-way valve 106. The refrigerant is condensed in the indoor heat exchangers 123a to 123d of the indoor units 102a to 102d, and the heat of condensation is released to the indoor air. The indoor air is warmed and blown into the room, thereby heating the room.

Next, the flow of refrigerant and refrigerating machine oil in the oil equalizing circuit will be described.
Refrigerator oil is stored in each sealed case of the compressor 103, and the oil level may be higher than the connection position of the oil discharge pipe 130 connected to each side.
Refrigerating machine oil in excess of the connection position of the oil discharge pipe 130 is led to the oil discharge pipe 130 as a surplus in the compressor 103. The refrigerator is guided to the oil collecting pipe 131 through the expansion devices 1a to 1c.
A small amount of gas refrigerant flows into the oil collecting pipe 131 via the expansion device 1d after being diverted from the high-pressure side refrigerant pipe 104 by the bypass pipe 133. The refrigerating machine oil that has flowed into the oil collecting pipe 131 is guided to the oil equalizing guide pipe 140 by the pressure applied from the bypass pipe 133 and guided to the distributor 141. In the distributor 141, it is led to the flow path branched in three directions from the inflow port, and flows out from each outflow port.
The refrigerating machine oil that has flowed out of the distributor 141 is equally divided into the oil return pipes 155a to 155c, and led to the suction pipes of the compressors 103a to 103c via the oil return pipes 155a to 115c.

On the other hand, refrigeration oil is mixed in the gas refrigerant discharged from the compressors 103a to 103c. The gas refrigerant discharged from the compressors 103a to 103c is separated into refrigerating machine oil and gas refrigerant in the oil separator 105.
The first oil return pipe 151 connected to the bottom of the oil separator 105 is provided with an electromagnetic on-off valve 153. The electromagnetic on-off valve 153 is normally closed. Therefore, the refrigerating machine oil separated here is temporarily stored in the oil separator 105, and only the gas refrigerant is guided to the four-way valve 106.
The refrigerating machine oil stored in the oil separator 105 increases, and finally rises to the connection position of the second oil return pipe 152 connected to the side portion. Refrigerating machine oil in excess of the connection position of the oil return pipe 152 flows into the oil equalizing guide pipe 140 from the second oil return pipe 152 and is compressed as described above through the distributor 141 and the oil return pipes 155a to 155c. Returned to machines 103a-103c.
For some reason, the oil level in the sealed cases of all the compressors 103a to 103c may decrease at the same time. At this time, an open signal is output to the electromagnetic on-off valve 153 provided in the first oil return pipe 151 at the bottom of the oil separator 105.
The refrigerating machine oil stored in the oil separator 105 is guided from the first oil return pipe 151 to the oil equalizing guide pipe 140, and evenly distributed to the compressors 103a to 103c via the distributor 141 and the oil return pipes 155a to 155c. Distributed.

FIG. 1 is a cross-sectional view showing the diaphragm device 1 (1a to 1f) described above. As shown in FIG. 1, the expansion device 1 includes a cylindrical expansion device body 2, a strainer 3, and an expansion mechanism 4.
The diaphragm body 2 is a cylindrical tube having upper and lower ends opened. The upper and lower ends are the entrances and exits for fluid (refrigerator oil and refrigerant). Here, the lower side is referred to as an inlet portion 2a, and the upper side is referred to as an outlet portion 2b. In FIG. 7, the direction indicated by the arrows of each of the expansion devices 1 a to 1 f is the fluid flow direction.
The expansion device body 2 is provided with a large-diameter pipe portion 2c between the inlet portion 2a and the outlet portion 2b, and the strainer 3 and the inner member 4 are accommodated in the large-diameter pipe portion 2c.

FIG. 2 is an enlarged cross-sectional view showing a part (part A) of FIG. As shown in FIG. 2, the aperture mechanism 4 includes a cylindrical inner member 41, and a spiral groove 5 is provided on the outer peripheral portion of the inner member 41. The spiral groove 5 is provided by, for example, threading. Accordingly, both end portions of the inner member 41 are formed with so-called incomplete screw portions, and these portions serve as communication ports 51 described later. In the present embodiment, the groove shape of the spiral groove 5 is a groove having a semicircular cross section, unlike a normal screw. Since the outer periphery of the inner member 41 is in close contact with the inner wall of the expansion device body 2, a spiral flow path 5 a is formed between the spiral groove 5 and the inner wall of the expansion device body 2. That is, the inner member 41 and the diaphragm main body 2 constitute the diaphragm mechanism 4. The channel area of the spiral channel 5a is sufficiently smaller than the channel area (tube diameter) of the expansion device body 2.
Two annular recesses 2d and 2e are provided on the outer peripheral portion of the large-diameter pipe portion 2c with a predetermined interval in the vertical direction. The annular recesses 2d and 2e are formed by drawing, for example, and become annular projections 2di and 2ei projecting radially inward inside the large-diameter pipe portion 2c. The inner member 41 is fixed to the large-diameter pipe portion 2c by being sandwiched between the two annular convex portions 2di and 2ei.

The strainer 3 is a bowl-shaped mesh (wire net) provided so as to protrude in the flow direction, and has a convex shape on the throttle mechanism side. The strainer 3 collects foreign matter on the upstream side of the throttle mechanism 4 so that the foreign matter does not enter the spiral flow path 5 a of the throttle mechanism 4.
After the strainer 3 and the inner member 41 are fixed to the large-diameter pipe portion 2c, the inlet portion 2a and the outlet portion 2b are contracted to form the expansion device 1 shown in FIG.

  In the expansion device 1 configured as described above, the fluid that has flowed into the expansion device 1 from the inlet 2a first passes through the strainer 3 to remove foreign matter. Then, it flows from the communication port 51 of the throttle mechanism 4 into the spiral flow path 5 a formed by the spiral groove 5. The fluid flows along the spiral flow path 5a to the opposite side of the throttle mechanism 4, exits the throttle mechanism 4 from the communication port 51 on the outlet side, and flows out of the throttle device 1 from the outlet portion 2b.

  The fluid is throttled when it flows through the spiral flow path 5a of the throttle mechanism 4.

  In the first embodiment, the strainer that collects foreign matter and the throttle mechanism can be made into one component, so the number of components can be reduced.

  By reducing the number of parts, the number of welding and brazing can be reduced and the number of processes can be reduced. Moreover, the reduction of the number of welding and brazing can contribute to the improvement of manufacturing reliability.

Further, since the number of parts is reduced, restrictions in the structural design of the refrigeration cycle are relaxed (arrangement space is increased), so that the degree of freedom in design is increased.
In particular, in the air conditioning apparatus 100 including the plurality of expansion devices 1a to 1f as shown in FIG. In addition, the larger the operating capacity of the large-scale air conditioner, the more effective because the number of parts to be used, and thus the number of throttle devices increases.

  Moreover, an arbitrary throttle mechanism can be obtained by changing the tube diameter of the throttle device main body 2, the depth of the spiral groove 5, and the number of turns (number of strips).

(Second Embodiment)
FIG. 3 is a diagram illustrating a diaphragm device according to the second embodiment. FIG. 3A is a view showing the inside of the diaphragm device 1, and FIG. 3B is an enlarged cross-sectional view of a part of the diaphragm mechanism 4. About each part of this 2nd Embodiment, the same part as 1st Embodiment of FIG.1 and FIG.2 is shown with the same code | symbol.

  The second embodiment is different from the first embodiment in that fixed portions 6 provided above and below the diaphragm mechanism 4 are provided as shown in FIG.

As shown in FIG. 3A, in the diaphragm device 1, the fixing portions 6 are provided integrally with the inner member 41 at both ends of the inner member 41 of the diaphragm mechanism 4. The fixed portion 6 is provided with a small diameter portion 7 that connects the inner member 41 and the fixed portion 6. The fixed portion 6 is provided with substantially the same diameter as the inner member 41, and the small diameter portion 7 is provided with a smaller diameter than the fixed portion 6.
As shown in FIG. 3B, the fixed portion 6 is provided with an axial flow passage 61 provided through the fixed portion 6 in the flow direction (axial direction), and has a diameter communicating with the axial passage 61. A direction passage 62 is provided through the small diameter portion 7 in the radial direction. That is, the axial flow passage 61 and the radial flow passage 62 are orthogonal to each other in the small diameter portion 7. A flow path formed by the axial flow path 61 and the radial flow path 62 is referred to as a guide flow path 8. The guide channel 8 communicates with the communication port 51 of the throttle mechanism 4 in a space 9 formed between the small diameter portion 7 and the throttle device body 2.

  As shown in FIGS. 1 and 2, when the throttle mechanism 4 does not have the fixing portion 6 (when the throttle mechanism 4 is directly fixed to the large-diameter pipe portion 2 c), the communication port 51 that guides the fluid to the spiral groove 5 is provided. There was a possibility that the ring-shaped protrusions 2di and 2ei interfere with or be blocked. Although it is possible to prevent the communication port 51 from being blocked at the time of manufacture, it is more preferable that interference can be easily avoided because it takes time for positioning.

  Therefore, in the present embodiment, columnar fixing portions 6 are provided at both ends of the inner member 41 of the aperture mechanism 4, and the fixing portions 6 are fixed by the annular convex portions 2 di and 2 ei of the aperture device main body 2, thereby providing a communication port. 51 will not be blocked.

  Furthermore, by providing the guide channel 8 inside the fixed portion 6, the fluid can smoothly flow without the communication port 51 of the throttle mechanism 4 being blocked by the annular convex portions 2di and 2ei.

When the fluid first flows from the inlet portion 2a to the inside of the expansion device (upstream side), it passes through the strainer 3 and removes foreign matters. Then, it passes through the guide flow path 8 (the axial flow path 61 and the radial flow path 62) provided in the fixed portion 6 of the inner member 41. Then, the fluid flows into the space 9 between the small diameter portion 7 and the expansion device main body 2 and flows into the spiral flow path 5a from the communication port 51. The fluid flows along the spiral flow path 5a and flows out from the outlet side communication port 51 to the outlet side space 9. The fluid that flows out to the space 9 on the outlet side passes through the guide channel 8 on the outlet side, and flows out of the expansion device 1 from the outlet 2b.

  In the second embodiment, by providing the fixing portion 6 and further providing the guide flow path 8, it is possible to provide a throttling device in which the throttle mechanism 4 can be easily attached and the flow path can be reliably secured.

(Third embodiment)
FIG. 4 is a diagram showing a diaphragm device according to the third embodiment. About each part of this 3rd Embodiment, the same part as the 1st and 2nd embodiment of FIG. 1 thru | or FIG. 3 is shown with the same code | symbol.

  The third embodiment differs from the first embodiment in that the shape of the axial flow passage 61 formed in the fixed portion 6 is as shown in FIG. The shape is large and the center side is small.

  As shown in FIG. 4, the axial flow passage 61 is a conical flow passage having a large hole diameter on the end portion side of the fixed portion 6 and a small hole diameter on the small diameter portion 7 side, and is tapered in cross-sectional shape. Is formed.

  By forming the axial flow passage 61 in a tapered shape, the fluid flowing into the expansion device main body 2 is more smoothly guided to the expansion mechanism 4 and efficiency is improved.

  In the third embodiment, the opening portion of the flow path of the axial flow passage 61 is formed in a tapered shape with a large end portion side, a small central portion side, and a more efficient throttling device that facilitates fluid flow. Can be provided.

(Fourth embodiment)
FIG. 5 is a diagram illustrating a diaphragm device according to the fourth embodiment. Fig.5 (a) is a figure which shows the inside of the aperture_diaphragm | restriction apparatus 1, FIG.5 (b) is a BB cross-section part of Fig.5 (a). About each part of this 4th Embodiment, the same part as the 1st thru | or 3rd embodiment of FIG. 1 thru | or FIG. 4 is shown with the same code | symbol.

  The fourth embodiment differs from the other embodiments in that a plurality of axial flow passages 61 are arranged so as to draw concentric circles, as shown in FIG.

  In particular, as shown in FIG. 5B, a plurality of the axial flow passages 61 of the fixed portion 6 are arranged so as to draw concentric circles so as to surround the small diameter portion 7, so that Fluid can flow without the need to form 62.

  As in other embodiments, when the fluid first flows from the inlet portion 2a into the expansion device 1 (upstream side), it passes through the strainer 3 and removes foreign matter. Then, after passing through the guide flow path 8 provided in the fixed portion 6 of the inner member 41 of the throttle mechanism 4, here, a plurality of axial flow paths 61, the space 9 between the small diameter portion 7 and the throttle device main body 2 is obtained. And fluid flows. Further, the fluid flows from the communication port 51 into the spiral flow path 5 a formed by the spiral groove 5. The fluid that has flowed into the spiral flow path 5a flows out from the communication port 51 on the outlet side into the space 9 on the outlet side along the spiral flow path 5a. The fluid that flows out to the space 9 on the outlet side passes through the guide channel 8 on the outlet side, and flows out of the expansion device 1 from the outlet 2b.

  In the fourth embodiment, an efficient throttle device can be provided by having a plurality of axial flow paths 61 arranged concentrically.

  By arranging a plurality of the axial flow paths 61 so as to draw concentric circles, it is possible to flow a fluid without forming the radial flow path 71. For this reason, the process at the time of manufacture becomes easy.

(Fifth embodiment)
FIG. 6 is a diagram illustrating a diaphragm device according to the fifth embodiment. About each part of this 5th Embodiment, the same part as the 1st thru | or 4th embodiment of FIG. 1 thru | or FIG. 5 is shown with the same code | symbol.

  The fifth embodiment differs from the other embodiments in that the spiral groove 5 has an R shape as shown in FIG.

As shown in FIG. 6, by performing R processing on the peak portion 5 b forming the spiral groove 5, convenience at the time of manufacture is improved. The valley portion 5c forming the spiral groove 5 has a semicircular cross-sectional shape as described in the first embodiment.
For example, when the brass inner member 41 is press-fitted into the copper diaphragm main body 2, the sharp spiral groove 5 damages the inner surface of the diaphragm main body 2, damages it, or creates burrs and clogs the spiral groove 5. There is a possibility. However, by forming the crest portion 5b forming the spiral groove 5 into an R shape, it is possible to prevent the inner surface of the expansion device body from being damaged and burrs from appearing.

  In the fifth embodiment, by forming the crest portion 5b forming the spiral groove 5 into an R shape, it is possible to provide an aperture device that is highly convenient during manufacturing.

  According to the diaphragm device of at least one embodiment described above, in addition to the strainer function of collecting foreign matter, the diaphragm mechanism is provided, so that the diaphragm device 1 which is one part can play two roles, It is possible to provide an aperture device that can reduce the number of parts, save space and reduce manufacturing processes, and contribute to improvement in manufacturing reliability.

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. This embodiment and its modifications are included in the invention described in the claims and their equivalents, as well as included in the scope and gist of the invention.

DESCRIPTION OF SYMBOLS 1 ... Throttling apparatus, 100 ... Air conditioning apparatus (refrigeration cycle apparatus), 101 ... Outdoor unit, 102 ... Indoor unit, Pl ... Refrigerant pipe (liquid tank), Pg ... Refrigerant pipe (gas tank), 103 ... Compressor, 104 DESCRIPTION OF SYMBOLS ... Refrigerant tank, 105 ... Oil separator, 106 ... Four-way valve, 107 ... Outdoor heat exchanger, 108 ... Outdoor expansion valve, 109 ... Liquid tank, 110 ... Liquid tank connection part, 111 ... Gas pipe connection part, 112 ... Accumulator, 121 ... Liquid tank connection part, 122 ... Indoor expansion valve, 123 ... Indoor heat exchanger, 124 ... Gas pipe connection part, 125 ... Outdoor fan, 126 ... Indoor fan, 130 ... Oil discharge tank, 131 ... Oil collecting pipe, 132 ... Check valve, 133 ... Bypass rod, 140 ... Oil guide rod, 141 ... Distributor, 151 ... First oil return rod, 152 ... Second oil return rod, 153 ... Electromagnetic switching valve, 155 ... Oil return rod 2 ... Aperture device book (Cylinder-shaped throttling device main body) 2a ... inlet part, 2b ... outlet part, 2c ... large diameter pipe part, 2d ... annular concave part, 2e ... annular concave part, 2di ... annular convex part, 2ei ... annular convex part, 3 ... Strainer, 4 ... Restriction mechanism, 41 ... Inner member, 5 ... Spiral groove, 5a ... Spiral flow path, 51 ... Communication port, 6 ... Fixed part, 61 ... Axial flow path, 62 ... Radial flow path, 7 ... Small diameter Part, 8 ... guide channel, 9 ... space

Claims (8)

A throttling device used in a refrigeration cycle device,
A strainer that collects foreign matter inside the cylindrical throttle body,
A throttle mechanism having a spiral flow path;
Squeezing device with The diaphragm mechanism has an inner member in which a spiral groove is formed on the outer peripheral surface;
The aperture device according to claim 1, wherein the spiral channel is formed between the spiral groove and an inner wall of the aperture device main body. The diaphragm mechanism has fixing portions that fix the diaphragm mechanism to the diaphragm device main body at both ends of the inner member,
The aperture device according to claim 2, wherein the fixed portion includes a guide channel that guides fluid to the spiral channel. The guide channel is
An axial flow path for guiding the fluid in the axial direction;
4. A throttling device according to claim 3, comprising a radial flow path orthogonal to the axial flow path. The aperture device according to claim 4, wherein the axial flow path is formed such that an opening of the flow path is formed larger on the end side and smaller on the center side. The guide channel is
4. A throttle device according to claim 3, comprising a plurality of axial flow paths arranged concentrically. The crest portion that forms the spiral groove of the aperture mechanism has an R shape.
The aperture device according to claim 1.   A refrigeration cycle apparatus comprising the expansion device according to any one of claims 1 to 7.

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