Patent Application
20230228280
The present disclosure relates to a scroll casing that accommodates a fan, a centrifugal fan provided with this scroll casing, an air-conditioning apparatus and a refrigeration cycle apparatus each including this scroll casing.
Some related-art air conditioning apparatuses have, between an air inlet and an air outlet, a heat exchanger and a centrifugal fan provided with a scroll casing. In such an air-conditioning apparatus, a fan accommodated in the scroll casing rotates to cause air drawn in from the air inlet of the air-conditioning apparatus to flow into the fan along the bell mouth that forms a suction port of the scroll casing. The airflow discharged from the fan is subjected to pressure rising in the scroll casing, discharged from a discharge port of the scroll casing, passes through the heat exchanger, and then blown out from the air outlet of the air-conditioning apparatus into a space to be air-conditioned (see Patent Literature 1, for example).
Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2005-69177
The scroll casing installed in an air-conditioning apparatus with such a configuration suffers from insufficient rising in pressure of airflow since it is impossible to sufficiently enlarge the discharge port due to structural restrictions inside the apparatus. In addition, such inability to sufficiently enlarge the discharge port limits a range of passage of the airflow discharged from the discharge port when it passes through the heat exchanger. Therefore, if the scroll casing tilts or the like for some reasons and, as a result, the direction of the discharge port of the airflow changes, the airflow cannot pass through some areas of the heat exchanger, whereby a drift flow occurs. Such a drift flow may result in inefficient heat exchange.
For an air-conditioning apparatus, there is a need to improve the workability in assembling a centrifugal fan into a housing of the air-conditioning apparatus, and under such circumstances, a scroll casing having a configuration that can achieve this improvement in workability has been required.
The present disclosure has been made to solve the above-mentioned problems and an object thereof is to obtain a scroll casing capable of attaining a pressure rising effect and a drift flow suppression effect, and also can improve workability in assembly, as well as to obtain a centrifugal fan, an air-conditioning apparatus and a refrigeration cycle apparatus provided with the scroll casing.
The scroll casing for a centrifugal fan according to the present disclosure includes a fan configured to generate airflow, the scroll casing comprising: a scroll portion configured to accommodate the fan and guide an airflow generated by the fan in a spiral shape; a discharge portion provided at a winding end portion of the scroll portion and having a discharge port configured to cause airflow to be discharged; and a tongue portion provided at a part connecting a winding start portion of the scroll portion and the discharge portion, wherein the discharge portion forms a flow passage of which an area of a cross section crossing orthogonally to a flow direction of the airflow gradually enlarges toward the discharge port, an extended plate formed so as to extend from the winding end portion in the discharge portion is, in a cross section obtained by cutting the extended plate in a thickness direction thereof, inclined relative to an inner wall surface of a housing configured to accommodate the centrifugal fan, and the extended plate has a change point at which an enlargement ratio of the area of the cross section on a downstream side is increased so as to be larger than that on an upstream side due to a change in degree of inclination, and wherein, when a portion on the upstream side than the change point is named as a first portion and a portion on the downstream side than the change point is named as a second portion, an angle θ1 and an angle θ2 satisfy a relationship of either 0≤θ2<θ1 or 0<θ2≤θ1, where θ1 is defined by the first portion and a virtual line that is parallel to the inner wall surface of the housing and passes the change point, and the angle θ2 is defined by the second portion and the virtual line, and a distance L1 and a distance L2 satisfy a relationship of L2<L1, where L1 is a distance in a direction parallel to the virtual line between an end portion on the upstream side of the tongue portion and the change point and the distance L2 is a distance in a direction parallel to the virtual line between the change point and an end portion on the downstream side of the second portion.
According to the present disclosure, since the angle θ1 and the angle θ2 satisfy a relationship of either 0≤θ2<θ1 or 0<θ2≤θ1, the pressure rising effect and the drift flow suppression effect can be obtained. Further, since the distance L1 and the distance L2 satisfy a relationship of L2<L1, workability in assembly is improved.
Hereinbelow, an air-conditioning apparatus in which a centrifugal fan with a scroll casing according to embodiments of the present disclosure is incorporated will be described with reference to the drawings, and other materials. In the following drawings, including
A centrifugal fan 1 is a multi-blade centrifugal fan, such as a sirocco fan or a turbo fan. The centrifugal fan 1 has a fan 2 that generates airflow and a scroll casing 4 that accommodates the fan 2. The centrifugal fan 1 is arranged inside a cuboid-shaped housing 11 of an air-conditioning apparatus 10, as illustrated in
Hereinbelow, the structure of the centrifugal fan 1 will be explained. (Fan 2)
A fan 2 is driven to rotate by a motor or other devices (not illustrated) to forcibly send air outward in the radial direction by centrifugal force generated by the rotation. As illustrated in
As illustrated in
The fan 2 is driven to rotate by a motor (not illustrated), and rotates around the rotational axis RS. As the fan 2 rotates, a gas outside the centrifugal fan 1 flows along a bell mouth 3 (described later), passes through the suction port 2e in the scroll casing 4 and a suction port 2e in the fan 2, and then is sucked into the fan 2. The air sucked into the fan 2 passes between a blade 2d and an adjacent blade 2d and is then sent outward in the radial direction.
The scroll casing 4 accommodates the fan 2 in its inside, as illustrated in
The scroll portion 41 forms a flow passage that converts a dynamic pressure of the airflow generated by the fan 2 into a static pressure. The scroll portion 41 includes two side walls 4a arranged so as to face each other in the rotational axis RS direction of the shaft 2b and cover the fan 2 from both sides in the rotational axis RS direction, and a circumferential wall 4c that encloses the fan 2 in a radial direction of the rotational axis RS. The radial direction of the rotational axis RS is a direction perpendicular to the rotational axis RS. An interior space of the scroll portion 41, which is formed by the side wall 4a and the circumferential wall 4c, is a space that allows air blown out from the fan 2 to flow along the circumferential wall 4c.
As illustrated in
One of the side walls 4a is provided with the bell mouth 3. The bell mouth 3 serves to rectify the gas to be sucked into the fan 2 and sends the gas into the suction port 2e of the fan 2. The bell mouth 3 is formed such that a diameter of its opening gradually decreases from the outside to the inside of the scroll casing 4. Of the opening of the bell mouth 3, a portion with the smallest diameter serves as the suction port 5. Air in the vicinity of the suction port 5 flows smoothly along the bell mouth 3 and also flows efficiently from the suction port 5 into the fan 2. The bell mouth 3 is either integrally molded with the side wall 4a or attached to the side wall 4a as a separate component. The configuration and the form of the bell mouth 3 are not particularly restricted.
The circumferential wall 4c is a wall provided between side walls 4a facing each other. The circumferential wall 4c causes the airflow generated by the fan 2 to flow along its curved wall surface and guides the airflow to the discharge port 43 via the scroll portion 41. The circumferential wall 4c is, for example, positioned parallel to the axial direction of the rotational axis RS of the fan 2 and covers the fan 2. The circumferential wall 4c covers the fan 2 from the radial direction relative to the rotational axis RS and forms an inner circumferential surface that faces the plurality of blades 2d.
The circumferential wall 4c is formed in a spiral shape in the direction of rotation R (see
The spiral shape of the circumferential wall 4c is, for example, a logarithmic spiral, an Archimedes spiral, or a spiral shape based on an involute curve, etc. An inner surface of the circumferential wall 4c forms a smoothly curved surface along the circumferential direction to the fan 2 from the winding start portion 41a, which is the beginning of the spirally-shaped winding, to the winding end portion 41b, which is the end of the spirally-shaped winding. Due to such a configuration, the air delivered from the fan 2 smoothly flows through the flow passage formed between the fan 2 and the circumferential wall 4c in the direction to the discharge portion 42. Therefore, the static pressure of the air in the scroll casing 4 increases efficiently from the tongue portion 44 to the discharge portion 42.
The discharge portion 42 has the discharge port 43 through which the airflow passing through the scroll portion 41 is discharged by the rotation of the fan 2. The discharge port 43 is an opening on the downstream side of the discharge portion 42. The discharge portion 42 is a hollow tube with a rectangular cross section crossing orthogonally to the direction of air flowing along the circumferential wall 4c. The discharge portion 42 forms a flow passage 45 configured to guide air that is sent from the fan 2 and flows in a gap between the circumferential wall 4c and the fan 2 to be discharged to the outside of the scroll casing 4, The cross-sectional area of this flow passage 45 increases from upstream to downstream.
The discharge portion 42 has an extended plate 42a, a diffuser plate 42b, a first side wall 42c, and a second side wall 42d. The extended plate 42a is formed so as to extend from the winding end portion 41b of the circumferential wall 4c, and is a plate-like portion formed as an integral part of the circumferential wall 4c. The diffuser plate 42b is formed integrally with the tongue portion 44 of the scroll casing 4 and is a plate-like portion provided so as to face the extended plate 42a. The diffuser plate 42b is formed such that it is angled relative to the extended plate 42a in such a manner that the cross-sectional area of the flow passage gradually increases along the direction of flow of air in the discharge portion 42.
The extended plate 42a and the diffuser plate 42b are formed between the first sidewall 42c and the second side wall 42d. Thus, due to the extended plate 42a, the diffuser plate 42b, the first side wall 42c, and the second side wall 42d, the discharge port 42 is formed as the flow passage 45 with a rectangular cross-sectional shape.
The tongue portion 44 is formed of a curved surface having a set radius of curvature, and smoothly connects the winding start portion 41a of the circumferential wall 4c with the discharge portion 42, The tongue portion 44 is a throttling portion necessary to blow out air sucked from the suction port 5 in a centrifugal direction and rises the pressure thereof. The tongue portion 44 inhibits the inflow of air from the end of winding to the start of winding of the spirally-shaped flow passage formed in the scroll casing 4.
When the fan 2 accommodated in the scroll casing 4 rotates, air is sucked into the housing from the air inlet 11a of the housing 11. The air sucked into the housing 11 flows into the fan 2 along the bell mouth 3 which forms the suction port 2e of scroll casing 4. The air flowing into the fan 2 is blown out outwardly in the radial direction of the fan 2. The air blown out from the fan 2 rises in pressure by passing through discharge portion 42 of which the cross-sectional area of the flow passage expands from the upstream side to the downstream side. After being discharged from the discharge port 43, the air of which the pressure has risen is supplied to the heat exchanger 12. The air that has supplied to the heat exchanger 12 exchanges heat with a heat exchange medium such as refrigerant flowing inside the heat exchanger 12 when passing through the heat exchanger 12, and the temperature and humidity thereof are adjusted. The air that has passed through the heat exchanger 12 is blown out from the air outlet 11b of the housing 11 to a space to be air-conditioned.
The scroll casing 4 of Embodiment 1 has a configuration that is capable of obtaining a pressure rising effect and a drift flow suppression effect. The specific configuration that realizes these effects will be described below with reference to
First, the configuration of the scroll casing 4, which provides a pressure rising effect and a drift flow suppression effect, is explained.
As illustrated in
A virtual line parallel to the inner wall 11c of housing 11 (see
Specifically, the angle θ1 and the angle θ2 satisfy a relationship of either 0≤θ2<θ1 or 0<θ2≤θ1.
With the above-mentioned relationship of θ1 and θ2, the flow passage 45 in the discharge portion 42 enlarges in two stages. As a result, separation of the airflow flowing along the inner wall surface of the second portion 42ab of the discharge portion 42 can be suppressed, whereby a pressure rising effect can be obtained. In addition, because the airflow sticks to the inner wall surface of the second portion 42ab, a cross-sectional area of a passage through which airflow passes is expanded, whereby drift flow of air passing through the heat exchanger 12 can be suppressed. As a result, heat exchange in the heat exchanger 12 can be performed efficiently.
The scroll casing 4 according to Embodiment 1 has a configuration that allows workability in assembly to be improved. Hereinbelow, a specific configuration that enables improvement in workability in assembly will be explained with reference to
As illustrated in
Improvement in workability in assembly due to the relationship L2<L1 will be explained. Explanation will be made using a scroll casing having a relationship L2>L1 as a comparative example.
In the comparative example, as illustrated in
To avoid such interference, it suffices that the opening 13a of the partition plate 13 be enlarged. However, if the opening 13a of the partition plate 13 is enlarged, in a state where the scroll casing 41A is installed in the housing 11, a gap is generated between the periphery of the opening 13a of the partition plate 13 and the outer circumference of the discharge portion 42A, and this gap is required to be closed with a separate component.
On the other hand, in the scroll casing 4 according to Embodiment 1, as shown in
The explanation on the assembly of the air-conditioning apparatus 10 is continued. Next, as illustrated in
As described above, the scroll casing 4 of the centrifugal fan 1 according to Embodiment 1 accommodates the fan 2 that generates airflow, the scroll portion 41, which guides the airflow generated by the fan 2 in a spiral shape, the discharge portion 42, and the tongue portion 44. The discharge portion 42 is formed at the winding end portion 41b of the scroll portion 41 and has the discharge port 43 for discharging airflow. The tongue portion 44 is a portion formed at a position where the winding start portion 41a of the scroll portion 41 and the discharge portion 42 are connected. The discharge portion 42 forms a flow passage of which an area of a cross section crossing orthogonally to the flow direction of the airflow gradually enlarges toward the discharge port 43. The extended plate 42a formed so as to extend from the winding end portion 41b in the discharge portion 42 is, in a cross section obtained by cutting the extended plate 42a in a thickness direction thereof, inclined relative to the inner wall surface 11c of the housing 11 that accommodates the centrifugal fan 1. The extended plate 42a has the change point A at which an enlargement ratio of the area of the cross section on the downstream side becomes larger than that on the upstream side due to a change in the degree of inclination of the extended plate 42a. In the extended plate 42a, when a part on a side upstream than the change point A is named as the first portion 42aa and a part on a side downstream than the change point A is named as the second portion 42ab, the following relationship is satisfied. The angle θ1 and the angle θ2 satisfy a relationship of 0<θ2<θ1, where θ1 is defined by the first portion 42aa and a virtual line that is parallel to the inner wall surface 11c of the housing 11 and passes the change point A, and the angle θ2 is defined by the second portion 42ab and the virtual line. The distance L1 and the distance L2 satisfy a relationship of L2<L1, where L1 is a distance in a direction parallel to the virtual line between an end portion on the upstream side of the tongue portion 44 and the change point A and the distance L2 is a distance in a direction parallel to the virtual line between the change point A and an end portion on the downstream side of the second portion 42ab. The centrifugal fan according to Embodiment 1 includes the scroll casing 4 and the fan 2 housed in the scroll casing 4.
Due to the relationship of 0<θ2<θ1, a pressure rising effect and a drift flow suppression effect can be obtained. Further, due to the relationship of L2<L1, workability in assembly is improved.
The air-conditioning apparatus according to Embodiment 1 includes the centrifugal fan 1 mentioned above, the housing 11 that accommodates the centrifugal fan 1 and the heat exchanger 12 arranged on the discharge side of the centrifugal fan 1.
Due to the provision of the centrifugal fan 1 mentioned above, it is possible to obtain an air-conditioning apparatus capable of attaining both a pressure rising effect and a drift flow suppression effect, and also capable of improving workability in assembly.
An air-conditioning apparatus 10A of Embodiment 2 is the same as the air-conditioning apparatus 10 of Embodiment 1, except that the air-conditioning apparatus 10A further has an air-guiding component 6. The air-guiding component 6 is a rod-shaped component and has a guide surface 6a that connects smoothly the end portion 43a on the downstream side of the second portion 42ab in the discharge portion 42 and a wall surface 11ca. The wall surface 11ca is, among the inner wall surface 11c of the housing 11, located on a portion an extended from the second portion 42ab. With this air-guiding component 6, the airflow discharged from the discharge port 43 is smoothly guided to the wall surface 11ca along the guide surface 6a of the air-guiding component 6 and then flows into the heat exchanger 12.
Thus, the airflow discharged from the discharge port 43 of the scroll casing 4 is smoothly guided to the heat exchanger 12. Hence, backflow of air that is generated, when the air-guiding component 6 is not provided, at a step formed between the end portion 43a on downstream side and the wall surface 11ca of the housing 11 can be suppressed. As a result, pressure rising and heat exchange by the heat exchanger 12 can be performed more efficiently.
The air-conditioning apparatus of Embodiment 2 has the same effect as that attained in Embodiment 1. In addition, due to the additional provision of the air-guiding component 6 in the air-conditioning apparatus according to Embodiment 1, the following advantageous effect can be obtained. Specifically, the airflow discharged from the discharge port 43 can be smoothly guided to the heat exchanger 12 along the guide surface 6a of the air-guiding component 6 through the wall surface 11ca, resulting in more efficient pressure rising and heat exchange in the heat exchanger 12.
The refrigeration cycle apparatus 50 according to Embodiment 3 performs air conditioning by heating or cooling an indoor space by transferring heat between outdoor air and indoor air via refrigerant. The refrigeration cycle apparatus 50 according to Embodiment 3 includes an outdoor unit 100 and an indoor unit 200. In the refrigeration cycle apparatus 50, the outdoor unit 100 and the indoor unit 200 are connected by a refrigerant pipe 300 and a refrigerant pipe 400 to form a refrigerant circuit through which refrigerant circulates. The refrigerant pipe 300 is a gas pipe through which gas-phase refrigerant flows, and the refrigerant pipe 400 is a liquid pipe through which liquid-phase refrigerant flows. Meanwhile, two-phase gas-liquid refrigerant is allowed to flow in the refrigerant pipe 400. In the refrigerant circuit of the refrigeration cycle apparatus 50, a compressor 101, a flow passage switching device 102, an outdoor heat exchanger 123, an expansion valve 105, and an indoor heat exchanger 201 are connected sequentially via the refrigerant pipes.
The outdoor unit 100 includes the compressor 101, the flow passage switching device 102, the outdoor heat exchanger 123, and the expansion valve 105. The compressor 101 compresses sucked refrigerant and discharges the compressed refrigerant. The flow passage switching device 102 is a four-way valve, for example, by which the direction of the refrigerant flow passage is switched. The refrigeration cycle apparatus 50 switches the flow of refrigerant by using the flow passage switching device 102 in accordance with instructions from a controller 110, whereby heating operation or cooling operation can be realized.
The outdoor heat exchanger 123 causes heat exchange to be performed between refrigerant and outdoor air. The outdoor heat exchanger 123 functions as an evaporator during heating operation, and causes heat exchange to be performed between low-pressure refrigerant that flows in from the refrigerant pipe 400 and outdoor air, to thereby evaporate and vaporize refrigerant. The outdoor heat exchanger 123 functions as a condenser during cooling operation, and causes heat exchange to be performed between refrigerant that has been already compressed in the compressor 101 and has flowed in from the pipes near the flow passage switching device 102 and outdoor air, to thereby condense and liquefy refrigerant. The outdoor heat exchanger 123 is provided with an outdoor fan 104 to increase the efficiency of heat exchange between refrigerant and outdoor air. The outdoor fan 104 may be provided with an inverter device to vary an operating frequency of a fan motor, whereby the fan rotation speed may be changed. The expansion valve 105 is a throttle device. By adjusting the flow rate of refrigerant flowing through the expansion valve 105, the expansion valve 105 functions as an expansion valve, and by varying the degree of opening, the pressure of refrigerant is adjusted. For example, if the expansion valve 105 is an electronic expansion valve or the like, the degree of opening is adjusted in accordance with the instructions from the controller 110.
The indoor unit 200 has the indoor heat exchanger 201 that causes heat exchange to be performed between refrigerant and indoor air, and the indoor fan 202 that adjusts the flow of air with which the indoor heat exchanger 201 performs heat exchange. The indoor heat exchanger 201 functions as a condenser during heating operation, and causes heat exchange to be performed between refrigerant flowing in from the refrigerant pipe 300 and indoor air, to thereby condense and liquefy the refrigerant, and the refrigerant flows out toward the refrigerant pipe 400. The indoor heat exchanger 201 functions as an evaporator during cooling operation, and causes heat exchange to be performed between refrigerant brought into a low-pressure state by the expansion valve 105 and indoor air. The indoor heat exchanger 201 causes refrigerant to remove heat from the air to evaporate and gasify, and then to flow out toward the refrigerant pipe 300. The indoor fan 202 is located so as to face the indoor heat exchanger 201. For the indoor fan 202, one or more of the centrifugal fan 1 of Embodiment 1 and the centrifugal fan 1 of Embodiment 2 is applied. The operating speed of the indoor fan 202 is determined by user settings. The indoor fan 202 may be provided with an inverter device to vary the operating frequency of the fan motor (not illustrated) to change the rotation speed of the fan 2.
Next, cooling operation is described as an example of the operation of the refrigeration cycle apparatus 50. High-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 flows into the outdoor heat exchanger 123 via the flow passage switching device 102. The gas refrigerant that flows into the outdoor heat exchanger 123 is condensed by heat exchange with outdoor air blown by the outdoor fan 104 to turn into low-temperature refrigerant, and flows out of the outdoor heat exchanger 123. Refrigerant that flows out of the outdoor heat exchanger 123 is expanded and depressurized by the expansion valve 105 to turn into low-temperature and low-pressure two-phase gas-liquid refrigerant. This two-phase gas-liquid refrigerant flows into the indoor heat exchanger 201 of the indoor unit 200, evaporates by heat exchange with indoor air blown by the indoor fan 202, and flows out of the indoor heat exchanger 201 as low-temperature and low-pressure gas refrigerant. At this time, the indoor air cooled by the heat absorbed by refrigerant is turned to be air for air conditioning, and is blown out from the discharge port of the indoor unit 200 into a space to be air-conditioned. The gas refrigerant that flows out of the indoor heat exchanger 201 is sucked into the compressor 101 via the flow passage switching device 102 and is compressed again. The above operation is repeated.
Next, heating operation is described as an example of the operation of the refrigeration cycle apparatus 50. High-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 flows into the indoor heat exchanger 201 of the indoor unit 200 via the flow passage switching device 102. The gas refrigerant that flows into the indoor heat exchanger 201 is condensed by heat exchange with indoor air blown by the indoor fan 202 to turn into low-temperature refrigerant, and flows out of the indoor heat exchanger 201. At this time, the indoor air heated by the heat received from the gas refrigerant is turned to be air for air conditioning, and is blown out from the discharge port of the indoor unit 200 into a space to be air-conditioned. Refrigerant that flow out of the indoor heat exchanger 201 is expanded and depressurized by the expansion valve 105 to turn into low-temperature and low-pressure two-phase gas-liquid refrigerant. This two-phase gas-liquid refrigerant flows into the outdoor heat exchanger 123 of the outdoor unit 100, evaporates by heat exchange with outdoor air blown by the outdoor fan 104, and flows out of the outdoor heat exchanger 123 as low-temperature and low-pressure gas refrigerant. The gas refrigerant that flows out of the outdoor heat exchanger 123 is sucked into the compressor 101 via the flow passage switching device 102 and is compressed again. The above operation is repeated.
The refrigeration cycle apparatus 50 according to Embodiment 3 is provided with the centrifugal fan 1, etc. according to Embodiment 1, and hence the pressure of the airflow can be risen efficiently in the scroll portion 41 and heat exchange can be performed efficiently in the indoor heat exchanger 201.
The configurations described in the embodiments mentioned above are merely examples, and can be combined with other known technologies, and a part of the configurations can be omitted or changed to the extent that such omission or change do not to depart from the gist of the present disclosure.
1: centrifugal fan, 2: fan, 2a: main plate, 2b: shaft, 2d: blade, 2e: suction port, 3: bell mouth, 4: scroll casing, 4a: side wall, 4c: circumferential wall, 5: suction port, 6: air-guiding component, 6a: guide surface, 10: air-conditioning apparatus, 10A: air-conditioning apparatus, 11: housing, 11a: air-inlet, 11b: air-outlet, 11c: inner wall surface, lice: wall surface, 12: heat exchanger, 13: partition plate, 13a: opening, 41: scroll portion, 41A: scroll casing, 41a: winding start portion, 41b: winding end portion, 42: discharge portion, 42A: discharge portion, 42a: extended plate, 42aa: first portion, 42ab: second portion, 42b: diffuser plate, 42c: first side wall, 42d: second side wall, 43: discharge port, 43Aa: end portion on the downstream side, 43a: end portion on the downstream side, 44: tongue portion, 45: flow passage, 50: refrigeration cycle apparatus, 100: outdoor unit, 101: compressor, 102: flow passage switching device, 104: outdoor fan, 105: expansion valve, 110: controller, 123: outdoor heat exchanger, 200: indoor unit, 201: indoor heat exchanger, 202: indoor fan, 300: refrigerant pipe, 400: refrigerant pipe, 410: first case portion, 410A: first case portion, 411: second case portion
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2020/029089 | 7/29/2020 | WO |
