Patent Application
20210254466
The present invention relates to a scroll type expander included in, for example, a power generation apparatus using a Rankine cycle.
Examples of a scroll type expander included in a power generation apparatus using a Rankine cycle include a scroll type expander described in PTL 1.
In the scroll type expander described in PTL 1, an expander body includes a cylindrical first housing one end of which in the axial direction is opened and a second housing that closes the opening portion of the first housing. An inlet for a working fluid (refrigerant) is formed on the other end surface of the first housing, and an outlet for the refrigerant is formed on the side surface of the first housing.
PTL 1: JP 2006-57568 A
In the scroll type expander described in PTL 1, the inlet for the refrigerant is formed on the other end surface of the first housing, and the outlet for the refrigerant is formed on the side surface of the first housing. Further, inside the second housing, a sealing member that surrounds the outer peripheral surface of an output shaft is arranged at a position further apart from the first housing than the outlet for the refrigerant. Thus, a large portion of the refrigerant, which is introduced from the inlet and discharged from the outlet, does not move to the position further apart from the first housing than the outlet, and the amount of refrigerant flowing around the sealing member is small. There is a problem in that, because of this phenomenon, when temperature of the expander body increases and the sealing member is heated, it is difficult to cool the sealing member by use of the refrigerant and sealing performance of the sealing member deteriorates. This problem is particularly prominent when ethanol is used as a refrigerant.
The present invention has been made in view of the problem as described above, and an object of the present invention is to provide a scroll type expander that is capable of preventing sealing performance of a sealing member from deteriorating.
In order to solve the above-described problem, one aspect of the present invention is a scroll type expander that includes a housing, a drive shaft, a fixed scroll, an orbiting scroll, a bearing, and a sealing member and is used in a Rankine cycle in which a working fluid circulates. The drive shaft has a base end housed in the housing and a tip end projecting out of the housing. The fixed scroll is fixed to the side closer to the base end of the drive shaft rather than to the tip end of the drive shaft inside the housing. The fixed scroll has a fixed-side scroll portion formed in a spiral shape when viewed from the axial direction of the drive shaft. The orbiting scroll has an orbiting-side scroll portion that is formed in a spiral shape when viewed from the axial direction of the drive shaft and meshes with the fixed-side scroll portion. The orbiting scroll is arranged on the side of the fixed scroll closer to the tip end of the drive shaft in a rotatable structure inside the housing. The bearing is arranged on the side of the orbiting scroll closer to the tip end of the drive shaft inside the housing and configured to support the drive shaft in a rotatable structure with respect to the housing via a plurality of rolling elements. The sealing member is arranged on the side of the bearing closer to the tip end of the drive shaft inside the housing and configured to surround the outer peripheral surface of the drive shaft. The housing includes a suction port, a discharge port, a low-pressure chamber, and a tip end-side low-pressure space. The suction port is formed at a position on the opposite side to the drive shaft with the fixed scroll interposed therebetween and configured to introduce high-pressure working fluid from an external circuit. The discharge port is formed on the side of the bearing closer to the tip end of the drive shaft and configured to discharge low-pressure working fluid to an external circuit. The low-pressure chamber is a chamber that is formed on the outer side of the orbiting-side scroll portion when viewed from the axial direction of the drive shaft. The tip end-side low-pressure space is a space in which the sealing member is arranged. A partition wall that partitions the tip end-side low-pressure space and the low pressure chamber from each other is disposed at a position that is located between the tip end-side low-pressure space and the low pressure chamber when viewed from a radial direction of the drive shaft and located closer to the discharge port than the drive shaft when viewed from the axial direction of the drive shaft. Further, a communication space that communicates the tip end-side low-pressure space and the low pressure chamber with each other is disposed at a position that is located between the tip end-side low-pressure space and the low pressure chamber when viewed from a radial direction of the drive shaft and opposed to the discharge port with the center of the drive shaft interposed therebetween when viewed from the axial direction of the drive shaft.
According to the one aspect of the present invention, high-pressure working fluid that is introduced from the suction port expands in the expansion chamber, which is formed between the fixed-side scroll portion and the orbiting-side scroll portion, becomes low-pressure working fluid the temperature of which has decreased, and moves to the low-pressure chamber. The low-pressure working fluid that has been prevented from moving from the low-pressure chamber to the tip end-side low-pressure space by the partition wall, passing the communication space and interspaces between adjacent rolling elements, moves from the low-pressure chamber to the tip end-side low-pressure space.
Because of this capability, it becomes possible to increase the flow rate of the low-pressure working fluid, the temperature of which has decreased from a state when the working fluid was introduced into the housing, that passes the vicinity of the drive shaft and the sealing member and to thereby actively cool the sealing member. Thus, it becomes possible to provide the scroll type expander that is capable of suppressing heating of the sealing member and preventing sealing performance of the sealing member from deteriorating.
A first embodiment of the present invention will now be described with reference to the drawings. In the illustration of the drawings referred to in the following description, the same or similar signs are assigned to the same or similar constituent components. However, it should be noted that the drawings are schematic, where a relation between thickness and planar dimensions, thickness ratios between respective layers, and the like are different from actual ones. Therefore, specific thickness and dimensions should be determined in consideration of the following description. It should also be noted that portions having differences in dimensional relationships and ratios among the drawings are included.
Further, the following first embodiment indicates a configuration to embody the technical idea of the present invention by way of example, and the technical idea of the present invention does not limit the materials, shapes, structures, arrangements, and the like of the constituent components to those described below. The technical idea of the present invention can be subjected to a variety of alterations within the technical scope prescribed by the claims described in CLAIMS. In addition, the directions of “right and left” and “up and down” in the following description are merely definitions for convenience of description, and do not limit the technical idea of the present invention. Thus, it is needless to say that, for example, when the plane of paper is rotated 90 degrees, the “right and left” and the “up and down” are interpreted in an interchanging manner, and, when the plane of paper is rotated 180 degrees, the “left” becomes the “right” and the “right” becomes the “left”.
Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
Using
As illustrated in
The scroll type expander 1 is used in a Rankine cycle in which a working fluid (refrigerant) circulates.
In the first embodiment, a case where ethanol is used as the refrigerant will be described as an example. Note that, as the refrigerant, a substance other than ethanol can be used.
The Rankine cycle will be described below.
The Rankine cycle recovers exhaust heat generated by an engine, which serves as an external heat source, (for example, heat of engine cooling water), converts the heat to power, and outputs the power. In a circulation path for a working fluid that the Rankine cycle has, for example, a heater, the scroll type expander 1, a condenser, and a pump are arranged.
The heater is a heat exchanger that causes heat exchange to be performed between engine cooling water having absorbed heat from the engine and the working fluid circulating in the Rankine cycle and thereby heats the working fluid into superheated steam.
The scroll type expander 1 expands and converts the working fluid, which has been heated in the heater into superheated steam, to rotational energy and thereby generates power (driving force).
The condenser is a heat exchanger that causes heat exchange to be performed between the working fluid having gone through the scroll type expander 1 and the outside air and thereby cools and condenses (liquefies) the working fluid.
The front housing 2 and the rear housing 4 forma housing of the scroll type expander 1 by being fastened to each other by through bolts B with the center plate 3 interposed therebetween.
Oil for lubrication (not illustrated) is enclosed inside the housing, and, when the working fluid moves inside the scroll type expander 1, the oil moves in conjunction with the working fluid and the inside of the scroll type expander 1 is lubricated.
The drive shaft 5 includes a large-diameter portion 5a, a small-diameter portion 5b, and an intermediate portion 5c.
The large-diameter portion 5a constitutes a base end of the drive shaft 5 and is housed in the front housing 2 (housing).
Between the large-diameter portion 5a and the front housing 2, a drive-side bearing 20 (bearing) is arranged. Details of the drive-side bearing 20 will be described later.
The small-diameter portion 5b constitutes a tip end of the drive shaft 5 and has a smaller outer diameter than the large-diameter portion 5a.
The tip end side of the small-diameter portion 5b projects to the outside of the front housing 2.
The intermediate portion 5c is formed between the large-diameter portion 5a and the small-diameter portion 5b and has an outer diameter smaller than the large-diameter portion 5a. The outer diameter is larger than the small-diameter portion 5b.
With the above-described configuration, the drive shaft 5 is arranged inside the front housing 2 (housing) and has both ends supported by the front housing 2 in a rotatable structure.
At a position on the side of the drive-side bearing 20 closer to the tip end of the drive shaft 5 within the side surface of the front housing 2, a discharge port Pout is formed.
The discharge port Pout is an opening portion for discharging low-pressure working fluid from the front housing 2 (housing) to an external circuit.
The drive-side bearing 20 includes a drive-side inner ring 21, a drive-side outer ring 22, and a plurality of drive-side rolling elements 23.
The drive-side inner ring 21 is formed in an annular shape. The inner peripheral surface of the drive-side inner ring 21 is fixed on the outer peripheral surface of the large-diameter portion 5a.
The drive-side outer ring 22 is formed in an annular shape. The outer peripheral surface of the drive-side outer ring 22 is fixed on the inner peripheral surface of the front housing 2.
The drive-side rolling elements 23 are arranged between a recessed portion formed on the outer peripheral surface of the drive-side inner ring 21 and a recessed portion formed on the inner peripheral surface of the drive-side outer ring 22. In the first embodiment, a case where the drive-side rolling elements 23 are formed using cylindrical rollers will be described.
The plurality of drive-side rolling elements 23 are arranged with a gap interposed between each pair of adjacent rolling elements when viewed from the axial direction of the drive shaft 5.
The fixed scroll 6 is housed in the rear housing 4.
The fixed scroll 6 includes a fixed-side base portion 6a, a fixed-side scroll portion 6b, and an inlet 6c.
The fixed-side base portion 6a is formed in a circular plate shape, and one surface thereof is fixed on a surface of the rear housing 4 facing the front housing 2.
The fixed-side scroll portion 6b is formed projecting from the other surface of the fixed-side base portion 6a in a spiral shape when viewed from the axial direction of the drive shaft 5.
The inlet 6c is a through-hole that is formed near the center of the fixed-side base portion 6a and penetrates the fixed-side base portion 6a.
The inlet 6c is in communication with a suction port Pin that penetrates the surface of the rear housing 4 facing the front housing 2.
The suction port Pin is an opening portion that is formed at a position on the rear housing 4 further apart from the drive shaft 5 than the fixed scroll 6 for introducing high-pressure working fluid from an external circuit into the rear housing 4 (housing).
With the above-described configuration, the fixed scroll 6 is fixed to the side closer to the base end of the drive shaft 5 rather than to the tip end of the drive shaft 5 inside the housing.
The orbiting scroll 7 includes an orbiting-side base portion 7a, an orbiting-side scroll portion 7b, and a hollow boss portion 7c.
The orbiting-side base portion 7a is formed in a circular plate shape and arranged between the drive-side bearing 20 and the fixed scroll 6.
One surface of the orbiting-side base portion 7a faces the fixed scroll 6.
The orbiting-side scroll portion 7b is formed projecting from the one surface of the orbiting-side base portion 7a in a spiral shape when viewed from the axial direction of the drive shaft 5.
The orbiting scroll 7 is arranged in such a way that the orbiting-side scroll portion 7b meshes with the fixed-side scroll portion 6b, and, between the fixed-side scroll portion 6b and the orbiting-side scroll portion 7b, an expansion chamber 30 in which introduced working fluid is expanded is formed.
Therefore, the drive-side bearing 20 is arranged on the side of the orbiting scroll 7 closer to the tip end of the drive shaft 5 inside the housing.
In addition, a low-pressure chamber 40 into which the working fluid having been expanded in the expansion chamber 30 and having become low-pressure working fluid flows is formed on the outer side of the orbiting-side scroll portion 7b when viewed from the axial direction of the drive shaft 5 inside the housing.
The hollow boss portion 7c is formed on the other surface of the orbiting-side base portion 7a in a cylindrical shape when viewed from the axial direction of the drive shaft 5.
The driven crank mechanism 8 couples the large-diameter portion 5a and the orbiting scroll 7 and includes an eccentric bush 8a and a crank pin 8b.
The eccentric bush 8a is arranged inside the hollow boss portion 7c via an orbiting-side bearing 50.
The orbiting-side bearing 50 includes an orbiting-side inner ring 51, an orbiting-side outer ring 52, and a plurality of orbiting-side rolling elements 53.
The orbiting-side inner ring 51 is formed in an annular shape. The inner peripheral surface of the orbiting-side inner ring 51 is fixed on the outer peripheral surface of the eccentric bush 8a.
The orbiting-side outer ring 52 is formed in an annular shape. The outer peripheral surface of the orbiting-side outer ring 52 is fixed on the inner peripheral surface of the hollow boss portion 7c.
The each orbiting-side rolling elements 53 are arranged between a recessed portion formed on the outer peripheral surface of the orbiting-side inner ring 51 and a recessed portion formed on the inner peripheral surface of the orbiting-side outer ring 52. In the first embodiment, a case where the orbiting-side rolling elements 53 are formed using cylindrical rollers will be described.
The plurality of orbiting-side rolling elements 53 are arranged with a gap interposed between each pair of adjacent rolling elements when viewed from the axial direction of the drive shaft 5.
The crank pin 8b is arranged in parallel with the drive shaft 5.
The central axis of the crank pin 8b is offset from the rotation center of the drive shaft 5.
The crank pin 8b is inserted into an insertion hole (not illustrated) formed in the eccentric bush 8a. The insertion hole is formed at a position offset from the center of the eccentric bush 8a.
The eccentric bush 8a is configured to be swingable about the axis of the crank pin 8b. Because of this configuration, in the driven crank mechanism 8, an orbiting motion of the crank pin 8b directly serves as an orbiting motion of the eccentric bush 8a, and, on the contrary, an orbiting motion of the eccentric bush 8a directly serves as an orbiting motion of the crank pin 8b.
Therefore, the driven crank mechanism 8 causes a rotational motion of the drive shaft 5 to be converted to an orbiting motion of the orbiting scroll 7 or an orbiting motion of the orbiting scroll 7 to be converted to a rotational motion of the drive shaft 5.
Note that, in order to prevent vibration or the like from occurring by balancing the eccentric bush 8a and the orbiting scroll 7, a counter weight 8c (balance weight) is fixed to the eccentric bush 8a.
The sealing member 9 is formed including a mechanical seal 9a, an O-ring 9b, and a seal holder 9c and prevents oil present between the drive shaft 5 and the front housing 2 from leaking to the outside.
The mechanical seal 9a is formed in an annular shape surrounding a portion of the outer peripheral surface of the drive shaft 5, using, for example, a metallic material. The mechanical seal 9a is located apart from the outer peripheral surface of the drive shaft 5 and, in conjunction therewith, is in contact with the inner surface of the front housing 2.
The O-ring 9b is formed in an annular shape that comes into contact with and surrounds a portion of the outer peripheral surface of the drive shaft 5, using, for example, a resin material. The O-ring 9b is arranged at a position located closer to the drive-side bearing 20 than the mechanical seal 9a.
The seal holder 9c is formed in a cylindrical shape and holds the mechanical seal 9a and the O-ring 9b on the inner peripheral surface thereof.
With the above-described configuration, the sealing member 9 is arranged on the side of the drive-side bearing 20 closer to the tip end of the drive shaft 5 inside the front housing 2 (housing) and surrounds a portion of the outer peripheral surface of the drive shaft 5.
Inside the front housing 2 (housing), a space in which the sealing member 9 is arranged forms a tip end-side low-pressure space 60 into which low-pressure working fluid flows from the low-pressure chamber 40.
In the tip end-side low-pressure space 60, a portion of the mechanical seal 9a is exposed.
Therefore, gaps formed between adjacent drive-side rolling elements 23 communicate the tip end-side low-pressure space 60 with the low-pressure chamber 40.
Note that the tip end-side low-pressure space 60 includes a passage portion connecting to the discharge port Pout.
The rotation preventing mechanism 10 is arranged between the other surface of the orbiting-side base portion 7a and the center plate 3 and prevents the orbiting scroll 7 from rotating.
The rotation preventing mechanism 10 includes a ball coupling having a plurality of balls 10a. Note that, in
The plurality of balls 10a are arranged in a radial structure with a gap interposed between each pair of adjacent balls 10a when viewed from the axial direction of the drive shaft 5.
Therefore, gaps formed between adjacent balls 10a communicate the tip end-side low-pressure space 60 with the low-pressure chamber 40.
The partition wall W is disposed at a position that is located between the tip end-side low-pressure space 60 and the low pressure chamber 40 when viewed from a radial direction of the drive shaft 5 and, in conjunction therewith, located closer to the discharge port Pout than the drive shaft 5 when viewed from the axial direction of the drive shaft 5 and partitions the tip end-side low-pressure space 60 and the low pressure chamber 40 from each other.
The partition wall W is arranged on the outer side of the drive-side bearing 20 in radial directions of the drive shaft 5.
As illustrated in
The opening portion Wo formed in the partition wall W forms a communication space 70 that communicate the tip end-side low-pressure space 60 with the low-pressure chamber 40.
The communication space 70 is arranged on the outer side of the drive-side bearing 20 in radial directions of the drive shaft 5.
Using
When the scroll type expander 1 is used, high-temperature (for example, 250° C.) and high-pressure working fluid that has been introduced into the expansion chamber 30 by way of the suction port Pin and the inlet 6c expands inside the expansion chamber 30. This operation causes the orbiting scroll 7 to perform an orbiting motion with respect to the fixed scroll 6.
When the orbiting scroll 7 performs an orbiting motion with respect to the fixed scroll 6, the expansion chamber 30 moves from a central portion to a peripheral portion while increasing capacity thereof, associated with the orbiting motion of the orbiting scroll 7, as a result of which the working fluid expands and the pressure of the working fluid becomes low and, in conjunction therewith, the temperature of the working fluid decreases to a low level (for example, 150° C.)
The working fluid after expansion is discharged to the low-pressure chamber 40 and, further, passing gaps formed between adjacent balls 10a, moves to a space formed between the orbiting scroll 7, the drive-side bearing 20, and the partition wall W.
In the configuration of the first embodiment, the partition wall W, which is disposed at a position located closer to the discharge port Pout than the drive shaft 5 when viewed from the axial direction of the drive shaft 5, partitions the tip end-side low-pressure space 60 and the low-pressure chamber 40 from each other. In addition to the above, the communication space 70, which is disposed at a position, within the partition wall W, that is opposed to the discharge port Pout with the center of the drive shaft 5 interposed therebetween when viewed from the axial direction of the drive shaft 5, communicates the tip end-side low-pressure space 60 with the low pressure chamber 40. Further, the gaps formed between adjacent drive-side rolling elements 23 communicate the tip end-side low-pressure space 60 with the low-pressure chamber 40.
Because of this configuration, the low-pressure working fluid that has moved to the space formed between the orbiting scroll 7, the drive-side bearing 20, and the partition wall W is prevented from moving from the low-pressure chamber 40 to the tip end-side low-pressure space 60 by the partition wall W.
Thus, the low-pressure working fluid in the space formed between the orbiting scroll 7, the drive-side bearing 20, and the partition wall W passes the gaps formed between adjacent drive-side rolling elements 23 and the communication space 70, as illustrated by a dashed-line arrow F1 in
The low-pressure working fluid that has moved to the tip end-side low-pressure space 60 actively passes the vicinity of the drive shaft 5 and the sealing member 9 and moves to the discharge port Pout, as illustrated by a dashed-line arrow F2 in
It should be noted that the foregoing first embodiment is one example of the present invention, the present invention is not limited to the foregoing first embodiment, and, even when the present invention may be carried out in modes other than the embodiment, depending on designs, various changes may be made to the present invention within a scope not departing from the technical idea of the present invention.
The scroll type expander 1 of the first embodiment enables advantageous effects that will be described below to be attained.
(1) The scroll type expander 1 includes the drive-side bearing 20 that supports the drive shaft 5 in a rotatable structure with respect to the housing via the plurality of drive-side rolling elements 23. In addition to the above, the housing includes the suction port Pin that is formed at a position further apart from the drive shaft 5 than the fixed scroll 6 and the discharge port Pout that is formed on the side of the drive-side bearing 20 closer to the tip end of the drive shaft 5. Further, the housing includes the low-pressure chamber 40 that is formed on the outer side of the orbiting-side scroll portion 7b when viewed from the axial direction of the drive shaft 5 and the tip end-side low-pressure space 60 that is a space in which the sealing member 9 is arranged. The partition wall W that partitions the tip end-side low-pressure space 60 and the low pressure chamber 40 from each other is disposed at a position that is located between the tip end-side low-pressure space 60 and the low pressure chamber 40 when viewed from a radial direction of the drive shaft 5 and located closer to the discharge port Pout than the drive shaft 5 when viewed from the axial direction of the drive shaft 5. Further, the communication space 70 that communicates the tip end-side low-pressure space 60 with the low pressure chamber 40 is disposed at a position that is located between the tip end-side low-pressure space 60 and the low pressure chamber 40 when viewed from a radial direction of the drive shaft 5 and is opposed to the discharge port Pout with the center of the drive shaft 5 interposed therebetween when viewed from the axial direction of the drive shaft 5.
Thus, high-pressure working fluid that is introduced into the housing expands in the expansion chamber 30, becomes low-pressure working fluid the temperature of which has decreased, and moves to the low-pressure chamber 40. Further, the low-pressure working fluid that has been prevented from moving from the low-pressure chamber 40 to the tip end-side low-pressure space 60 by the partition wall W, passing the communication space 70 and interspaces between adjacent drive-side rolling elements 23, moves from the low-pressure chamber 40 to the tip end-side low-pressure space 60.
In addition to the above, it becomes possible to move the low-pressure working fluid, which has been prevented from moving from the low-pressure chamber 40 to the tip end-side low-pressure space 60 by the partition wall W, to a position apart from the discharge port Pout.
Because of this capability, it becomes possible to increase the flow rate of the low-pressure working fluid, the temperature of which has decreased from a state when the working fluid was introduced into the housing, that passes the vicinity of the drive shaft 5 and the sealing member 9 and to thereby actively cool the sealing member 9.
In addition to the above, it becomes possible to increase working fluid that moves from the communication space 70, passes the vicinity of the drive shaft 5 and the sealing member 9, and is discharged from the discharge port Pout and to thereby efficiently increase the flow rate of low-pressure working fluid that passes the vicinity of the drive shaft 5 and the sealing member 9.
As a result, it becomes possible to provide the scroll type expander 1 that is capable of suppressing heating of the sealing member 9 and preventing sealing performance of the sealing member 9 from deteriorating.
Since it becomes possible to suppress heating of the sealing member 9, it becomes possible to produce the scroll type expander 1 without applying an expensive sealing member 9 the sealing performance of which is maintained even in a high-temperature environment. This capability enables the production cost of the scroll type expander 1 to be prevented from increasing.
Further, compared with a configuration in which, for example, the partition wall W is disposed at a position located farther from the discharge port Pout than the drive shaft 5 and the communication space 70 is closer to the discharge port Pout than the drive shaft 5 when viewed from the axial direction of the drive shaft 5, it becomes possible to efficiently increase the flow rate of working fluid that moves from a position further apart from the discharge port Pout than the drive shaft 5 within the tip end-side low-pressure space 60, passes the vicinity of the drive shaft 5 and the sealing member 9, and reaches the discharge port Pout.
(2) The partition wall W is arranged on the outer side of the drive-side bearing 20 in radial directions of the drive shaft 5.
As a result, it becomes possible to increase the flow rate of the low-pressure working fluid that is prevented from moving from the low-pressure chamber 40 to the tip end-side low-pressure space 60 by the partition wall W and to efficiently increase the flow rate of the low-pressure working fluid passing the vicinity of the drive shaft 5 and the sealing member 9.
(3) The communication space 70 is arranged on the outer side of the drive-side bearing 20 in radial directions of the drive shaft 5.
Thus, it becomes possible to efficiently move the low-pressure working fluid, which is prevented from moving from the low-pressure chamber 40 to the tip end-side low-pressure space 60 by the partition wall W, to a position apart from the discharge port Pout.
As a result, it becomes possible to efficiently increase the flow rate of the low-pressure working fluid passing the vicinity of the drive shaft 5 and the sealing member 9.
(4) The rotation preventing mechanism 10 for preventing the orbiting scroll 7 from rotating includes a plurality of balls 10a arranged in a radial structure with a gap interposed between each pair of adjacent balls 10a when viewed from the axial direction of the drive shaft 5, and the gaps formed between adjacent balls 10a communicate the tip end-side low-pressure space 60 with the low pressure chamber 40.
Thus, it becomes possible to make the low-pressure working fluid that has moved to the low-pressure chamber 40 move from the low pressure chamber 40 to the tip end-side low-pressure space 60, passing interspaces between adjacent balls 10a.
As a result, it becomes possible to increase the flow rate of the low-pressure working fluid, the temperature of which has decreased from a state when the working fluid was introduced into the housing, to the tip end-side low-pressure space 60.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2018-110528 | Jun 2018 | JP | national |
This application is a U.S. National Stage patent application under 35 U.S.C. § 371 of International Patent Application No. PCT/JP2019/019751, filed on May 17, 2019, which claims the benefit of Japanese Patent Application No. 2018-110528, filed on Jun. 8, 2018, the disclosures of each of which are incorporated herein by reference in their entirety.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2019/019751 | 5/17/2019 | WO | 00 |
